CN201062640Y - Stitching type tooth-embedding overrun clutch - Google Patents

Abstract

The utility model provides a drive-on claw overrunning clutch, which has a plurality of implementing proposals such as unidirectional and bi-directional overrunning clutches, and unidirectional and bi-directional controllable sliders, etc., and has the advantages of huge driving torque, high speed, no collision, small volume, resistance to heavy impact, simplicity, reliability and long service life, etc. The utility model is characterized in that an embedding controlling mechanism which can prevent the embedding of a force transmission embedding mechanism and a separation embedding mechanism in the overrunning separation state is installed, the embedding controlling mechanism is axially positioned in the two embedding mechanisms, and radially positioned in, between or outside the two embedding mechanisms; the lift angle forming the blocking work surfaces of the two mechanisms is enough to ensure the frictional self lock of the both mechanisms as well as the steadiness of the blocking operating mode during the propping of the both mechanisms , so that the mechanisms have the capacity of being adaptive to the axial distance change and automatically compensating the wear, so as to maintain the zero collision in a long term in the overrunning state of the two embedding mechanisms, and guarantee the absolute reliability of the separation blocking process and the embedding resetting process of the embedding mechanisms. In addition, the direction and state controlling mechanism is simple and reliable, the clutch is relatively easy to be manufactured and assembled, and the new and old parts are highly interchangeable.

Description

Press-fit type jaw overrunning clutch

Technical Field

The utility model relates to a clutch in the mechanical transmission field, in particular to but not only relate to a tooth inlays formula clutch that has the function of surmounting in rotation.

Technical Field

The existing overrunning clutches are developed by a pawl-ratchet mechanism and have an embedded type and a friction type. In three application fields of indexing, overrunning and non-return of the overrunning clutch, the friction type is most suitable for the indexing field due to accurate positioning, and the embedded type is most suitable for two fields of overrunning and non-return which have relatively low requirements on slip angles and have relatively high requirements on torque transmission capacity. However, the clutch is hardly used in practice due to the fact that the clutch is engaged, particularly, the dog clutch is engaged during overrunning, and the torque is transmitted to the clutch due to the collision and the noise of the collision. Chinese patent application nos. 99248119.8 and 99239680.8 disclose two types of dog-type overrunning clutches, but both patents still do not solve the problem of collision or large torque because the collision or torque still does not correspond to most or all of the pressure on the force-transmitting tooth surface and the half-tooth collision phenomenon is necessary.

SUMMERY OF THE UTILITY MODEL

An object of the utility model is to provide a can transmit big torque, surmount the pressfitting formula tooth that does not have collision and sound behind the separation and inlay freewheel clutch to and direction and state all controllable type pressfitting formula tooth that can control inlay freewheel clutch.

Before describing the technical scheme, the related nouns or concepts are explained as follows:

belongs to a main ring: a rotating member rigidly attached by an attached stop ring or an attached stop ring.

Blocking the reference ring: a rotating member as a reference object for which the stopper ring is relatively stationary in the fitting operation state; the end face thereof which directly faces the blocker ring in the axial direction is referred to as a reference end face, and the cylindrical face thereof which directly faces the blocker ring in the radial direction is referred to as a reference cylindrical face.

Separating the reference ring: a rotating member as a reference object for which a release ring is relatively stationary and circumferentially fixed in the overrunning clutch; the end face thereof which directly faces the separating ring in the axial direction is referred to as a reference end face.

Blocking the working surface: after the axial separation of the block fitting mechanism, the tip surface portion of the tooth for abutting contact between the radial teeth of both the ring gears constituting the mechanism is denoted by λ.

Blocking working conditions: the blocking teeth of the blocking embedding mechanisms are in opposite contact with each other, so that the working condition of embedding of other axial embedding mechanisms positioned outside the blocking embedding mechanisms in the axial direction is prevented.

δ angle and ρ angle: in the blocking working condition, on one hand, the sliding end surface or the cylindrical surface of the blocking ring is in contact with the reference end surface or the reference cylindrical surface of the blocking reference ring to form a sliding friction pair, on the other hand, the blocking working surface of the blocking tooth of the blocking ring is in axial contact with the blocking working surface of the auxiliary blocking tooth to form a static friction pair, when the circumferential position of the blocking ring relative to the auxiliary blocking ring is limited only by the static friction pair, the static friction pair needs to be self-locked, wherein the minimum lift angle of the blocking working surface which can ensure the self-locking of the static friction pair is defined as delta, and the maximum lift angle is defined as rho.

Limiting the working surface: a limiting surface is given to the circumferential relative position of the blocking ring. For the control embedding mechanism, when lambda is less than delta, the self-locking can not be realized due to the opposite vertex contact between the two blocking teeth, so that only the side surface of the blocking tooth and the side surface of the limiting bulge in the middle of the tooth top of the blocking tooth are limiting working surfaces; when delta is more than or equal to lambda is less than or equal to rho, all the side faces and the blocking working faces of the blocking teeth are limiting working faces because the abutting contact between the blocking teeth of the two sides can be reliably self-locked.

Full-tooth embedding depth: when the axial fitting mechanism is completely fitted, the axial distance from the highest tooth top point of one fitting tooth to the highest tooth top point of the other fitting tooth is obtained.

Minimum barrier height: the blocking engagement means must be separated by a minimum axial distance necessary to achieve the abutting contact between its blocking working surfaces.

Maximum limit embedding depth: the circumferential constraint action of the limiting embedding mechanism is guaranteed to exist, and the maximum distance which can be separated in the axial direction of the embedding mechanism is blocked. For the control embedding mechanism, the depth is the axial distance between the highest points in the upper boundaries of the limit working faces of the two embedding parties in the complete embedding state.

Separation angle: the axial engagement mechanism is transited from the engagement state to the critical state between the engagement state and the separation opposite vertex state, and the minimum circumferential angle of relative rotation is required between the two gear rings.

Initial separation height: under the action of the elastic embedding force, the axial embedding mechanism is formed by the initial minimum axial separation distance which is required by the two components for realizing the relative rotation. The distance must be zero, whereas the distance may be non-zero, turning in the opposite direction allowed by the design.

Entrance margin K of the blocking fitting mechanism: when the influence of other embedding mechanisms and the circumferential freedom of the blocking ring are not considered, the maximum circumferential angle of the gear rings forming the blocking embedding mechanism can be continuously staggered from the minimum blocking height on the premise of not influencing the axial embedding of the mechanism.

In the present invention, when the two sides of the assembly of one engaging mechanism respectively use the two sides of the assembly of the other engaging mechanism as the axial supporting base, the former engaging mechanism is called to be axially located within the latter engaging mechanism, otherwise, it is out. In addition, the utility model discloses the short for of independent barrier ring is "barrier ring".

The utility model discloses a pressfitting formula jaw freewheel clutch, by first engaging element, second engaging element, stop ring, affiliated spacing ring, spring and spring holder based on same axial lead constitution, second engaging element can axial displacement, but its part non-gomphosis surface is formed with the characteristic curved surface that can transmit the torque, the spring mounting is between second engaging element and spring holder; the first and the second jointing elements are axially and oppositely embedded to form a working embedding mechanism which is a force-transmission embedding mechanism and a separation embedding mechanism, the embedding end surfaces of the two jointing elements are uniformly distributed with the same number of teeth, and in the embedding mechanism, the rotation of one jointing element relative to the other jointing element results in that the torque is transmitted in one direction and is axially separated in the other direction; the method is characterized in that: 1) the blocking embedded mechanism is arranged for preventing the embedding of the working embedded mechanism in the overrunning separation state, is axially positioned in the working embedded mechanism, is radially positioned in or out of the working embedded mechanism, and is formed by axially embedding a blocking ring and an auxiliary blocking ring, and the peripheral surfaces of the embedded end surfaces of the two rings are all provided with the same number of radial blocking teeth with axial blocking effect; the minimum blocking height of the blocking embedding mechanism is greater than the initial separating height of the separating embedding mechanism in two rotating directions and less than the full-tooth embedding depth of the working embedding mechanism, the auxiliary blocking ring is rigidly integrated with the auxiliary ring, the auxiliary ring is a second joint element or a first joint element, the blocking ring is supported in one direction by the blocking reference end face of the blocking reference ring, and the sliding end face of the blocking reference ring and the blocking reference end face form a circumferential free sliding friction pair; the blocking reference ring is a first or second engagement element opposite the primary ring of the secondary blocking ring; 2) the limiting embedding mechanism is arranged for limiting the circumferential relative position of a blocking ring in the blocking embedding mechanism and consists of the blocking ring and an auxiliary limiting ring; the auxiliary limiting ring and the auxiliary blocking ring are rigidly integrated into a same ring, the limiting embedding mechanism and the blocking embedding mechanism are overlapped to form a control embedding mechanism, in the control embedding mechanism, the blocking teeth are also limiting teeth, the auxiliary blocking teeth are also auxiliary limiting teeth, the blocking working surfaces of the tooth tops of the two are spiral surfaces with the rising angle not larger than rho, and a limiting bulge is formed in the middle of at least one tooth top surface; meanwhile, the maximum limit embedding depth of the limit embedding mechanism is larger than the full-tooth embedding depth of the working embedding mechanism.

More simply, the side surface of the limiting bulge which is at the same side with the blocking working surface is preferably made into a spiral surface with the lead angle of beta, and beta is more than or equal to | delta | and less than 180 degrees.

The utility model discloses a controllable pressfitting formula jaw freewheel clutch, by first engaging element, second engaging element, separating ring, attached separating ring, stop ring, attached spacing ring, spring and spring holder based on same axial lead constitution, second engaging element can axial displacement, but its part non-gomphosis surface is formed with the characteristic curved surface that can transmit the torque, the spring mounting is between second engaging element and spring holder; the first joint element and the second joint element are axially and oppositely embedded to form a force transmission embedding mechanism capable of transmitting torque in two directions, and the embedding end faces of the two joint elements are uniformly distributed with the same number of radial teeth; the method is characterized in that: 1) the device is provided with a separation embedding mechanism which can lead the two parts to separate when the two parts rotate relatively, the separation embedding mechanism is axially positioned in the force transmission embedding mechanism, the separation embedding mechanism is radially positioned in or out of the force transmission embedding mechanism, the separation embedding mechanism is formed by axially embedding a separation ring and an auxiliary separation ring, the embedding end surfaces of the two rings are uniformly distributed with the same number of radial separation teeth, and the number of the radial separation teeth is the same as the number of the force transmission teeth; said accessory breakaway ring being rigidly integral with an owner ring that is the second engagement element or the first engagement element; the release ring is supported unidirectionally by a release reference end face of the release reference ring, which is a first engaging element or a second engaging element opposite to the owner ring of the accessory release ring; 2) the blocking embedded mechanism is composed of a blocking ring and an auxiliary blocking ring in the axial direction and used for preventing the separation embedded mechanism from being embedded in the transcendental separation state, the blocking embedded mechanism is axially positioned in the separation embedded mechanism or in the force transmission embedded mechanism, the blocking embedded mechanism is radially positioned in, between or outside the force transmission embedded mechanism and the separation embedded mechanism, and radial blocking teeth with the axial blocking effect are arranged on the embedded end faces of the two rings; the minimum blocking height of the blocking embedding mechanism is larger than the full-tooth embedding depth of the force transmission embedding mechanismThe separation and embedding mechanism is larger than the initial separation height of the separation and embedding mechanism in two opposite rotating directions and smaller than the full-tooth embedding depth of the separation and embedding mechanism; said secondary blocker ring being rigidly integral with an owner ring which is the second engagement element, the release ring or the first engagement element; the blocking ring is supported in a one-way mode by a blocking reference end face of the blocking reference ring, and a sliding end face of the blocking ring and the blocking reference end face form a circumferential free sliding friction pair; the blocking reference ring is a separate ring, a first engagement element or a second engagement element opposite the primary ring of the secondary blocking ring; 3) the limiting embedding mechanism is arranged for limiting the circumferential relative position of a blocking ring in the blocking embedding mechanism and consists of the blocking ring and an auxiliary limiting ring; the auxiliary limiting ring and the auxiliary blocking ring are rigidly integrated into a same ring, the limiting embedding mechanism and the blocking embedding mechanism are overlapped to form a control embedding mechanism, in the control embedding mechanism, the blocking teeth are also limiting teeth, the auxiliary blocking teeth are also auxiliary limiting teeth, the blocking working surfaces of the tooth tops of the two are spiral surfaces with the rising angle not larger than rho, and a limiting bulge is formed in the middle of at least one tooth top surface; meanwhile, the maximum limit embedding depth of the limit embedding mechanism is greater than the full-tooth embedding depth of the separation embedding mechanism; 4) circumferential degree of freedom theta of force transmission embedding mechanism_tThe force-transferring embedding mechanism is determined in such a way that when the separating embedding mechanism transcends separation in two working rotation directions, no contact or collision occurs between the two components of the force-transferring embedding mechanism; 5) the separating ring positioning and locking mechanism capable of fixing the separating ring on a specific circumferential position relative to the separating reference ring is arranged, and the overrunning clutch has separating and overrunning functions only after the separating ring is locked in the circumferential direction.

To obtain a bidirectional overrunning clutch, the first engagement element may be axially fixed; a second joint element is used as a common main ring of the auxiliary stop ring and the auxiliary limiting ring, the stop ring is arranged in an inner hole of the separating ring, and the separating ring is arranged in an inner hole of the first joint element; blocking working surfaces are correspondingly manufactured on two sides of the top surfaces of the radial teeth of the two sides for controlling the embedding of the embedding mechanism, and the side surface of the limiting bulge on the same side with the blocking working surfaces is made into a screw with a lead angle betaRotating the surface, wherein [ delta ] is more than or equal to beta and less than 180 degrees, and the initial separation height of the separation embedding mechanism in two rotation directions is designed to be zero; correspondingly, the entrance margin K of the blocking and fitting mechanism conforms to the inequality: k > theta_c+θ_f+ γ + η; meanwhile, the separating ring positioning and locking mechanism is made into an axial pin hole type positioning mechanism which can respectively fix the separating ring at two different specific circumferential positions relative to the first engaging element, when the separating ring is fixed at the first relative position, the overrunning clutch can only transmit torque and separating overrunning in the first direction, when the separating ring is fixed at the second relative position, the overrunning clutch can only transmit torque and separating overrunning in the second direction, and in addition, a positioning control mechanism for controlling the mechanism is also arranged; in the above inequality, γ ═ max (γ)₁，γ₂) The relevant parameters are defined as follows:

θ_c: the separation ring separates the circumferential included angle corresponding to the tooth top surface,

θ_f: the auxiliary separating ring separates the circumferential included angle corresponding to the tooth top surface,

γ₁: a separation angle of the separation and engagement mechanism in the first direction,

γ₂: a separation angle of the separation and engagement mechanism in the second direction,

eta: the technological correction is the correction brought by the fact that a guide angle, a force transmission tooth root are contracted, a circumferential gap of the separation embedding mechanism and the full-tooth embedding depth of the force transmission mechanism and the separation embedding mechanism are not equal.

Furthermore, in order to obtain a compulsory bidirectional overrunning clutch or a bidirectional sliding device, an embedded limiting mechanism which can forcibly limit the blocking ring at a specific circumferential position relative to the separating ring, namely a blocking ring rotation stopping mechanism is arranged, the blocking ring can lose axial blocking capability only when limited at the specific position, and the overrunning clutch can be axially embedded and reset; accordingly, the circumferential limit position of the release ring relative to the first engagement element is limited by a release ring stop mechanism, which is arranged between the release ring and the first engagement element, and whose circumferential degree of freedom, which is not less than the circumferential angle between the first relative position and the second relative position and not so great as to enable the release ring to start having the ability to completely prevent the clutch from axially engaging, is sufficient for the release ring positioning and locking mechanism to perform its function in the rotation interval corresponding to this circumferential degree of freedom; and, the lift angle β must satisfy the inequality: beta is more than or equal to | delta | and less than 90 degrees to phi, wherein phi is a friction angle of a friction pair formed between the side surface of the limiting bulge and the blocking tooth or the auxiliary blocking tooth; in addition, the separating ring positioning and locking mechanism is specifically an axial pin hole type positioning mechanism, and the axial positions of two groups of locking pins and the stop ring rotation stopping mechanism are controlled by the positioning control mechanism.

In addition, the first jointing element can be axially fixed to obtain the controllable bidirectional force-transmission one-way overrunning slider; a second joint element is used as a common main ring of the auxiliary stop ring and the auxiliary limiting ring, the stop ring is arranged in an inner hole of the separating ring, and the separating ring is arranged in an inner hole of the first joint element; the initial separation height of the separation embedding mechanism in at least one rotation direction is zero; the side surface of the limiting bulge in the control embedding mechanism, which is on the same side with the blocking working surface, is a spiral surface with an elevation angle beta, wherein beta is more than or equal to | delta | and less than 90-phi; in addition, the overrunning clutch state control mechanism is specially arranged, the overrunning clutch state control mechanism is formed by combining a separating ring positioning and locking mechanism, a separating ring limiting mechanism and a stop ring rotation stopping mechanism, and the circumferential positions among the separating ring, the stop ring and the first joint element can be limited; here, the separating ring positioning locking mechanism is a pin-hole type circumferential positioning mechanism consisting of corresponding axial pin holes and pins distributed on the separating ring and the first joint element; a release ring limiting mechanism for limiting the circumferential limit position of the release ring relative to the first engaging element, arranged between the release ring and the first engaging element, the circumferential degree of freedom of which is not so small as to influence the force-transmitting engaging mechanism to realize the circumferential degree of freedom theta thereof_tTo an extent not so great as to cause separation of the ringsThe degree of completely preventing the axial embedding of the clutch is achieved, and the separating ring positioning and locking mechanism can fully realize the function in the rotating interval corresponding to the circumferential freedom degree; the stop ring rotation stopping mechanism can limit the stop ring on a specific circumferential position relative to the separating ring in a forced mode, at the moment, the stop ring loses axial stopping capacity, and the overrunning clutch can be embedded and reset in the axial direction.

For further options, the condition control mechanism may further comprise a positioning control mechanism for operating the separating ring positioning locking mechanism and the stop ring rotation stopping mechanism.

All the stop ring rotation stopping mechanisms are pin-slot type axial embedding mechanisms consisting of axial grooves or section gaps on the sliding end surfaces of the stop rings, axial through holes on the stop reference end surfaces of the separating rings and rotation stopping pins; all the separating ring limiting mechanisms are pin-hole type limiting mechanisms consisting of axial pin holes in toothless end faces of the separating rings, axial through holes in separating reference end faces of the first joint elements and limiting pins embedded into the two holes; all the positioning control mechanisms achieve the aim of giving and controlling the axial positions of a locking pin of the separating ring positioning locking mechanism and a rotation stopping pin of the stop ring rotation stopping mechanism in a purely mechanical mode.

For perfect and reliable operation of the blocking engagement mechanism, it is preferable to impose a constraint on the blocking ring to force it to rest relatively on the reference end face or reference cylindrical face of the blocking reference ring in the engaged state.

In addition, in order to ensure the matching precision and facilitate lubrication, the overrunning clutch can be uniformly packaged into a shell, the shell consists of a shaft sleeve, a bowl-shaped shell and an end cover, and the torque transmission or overrunning between the rotating shaft or the shaft sleeve and the shell is realized by a mode that the shaft sleeve is circumferentially fixed or directly made into a rigid whole with the inner hole surface of the first joint element and a circumferential fixing mode formed by combining the outer cylindrical surface of the shell and the outer cylindrical surface of the second joint element in a spline connection mode, wherein the shell also has the function of a spring seat.

The utility model discloses in, there is not any unmatched place in the torque transmission link, and power transmission gomphosis mechanism more can be the zigzag of the big torque of transmission or rectangular cross section's terminal surface tooth, in addition, the interpolation has blockking the gomphosis mechanism within the gomphosis mechanism in the axial, outside, still adds separation ring location locking mechanism, separation ring stop gear, stop ring spline mechanism or location operating mechanism, consequently, the utility model provides a purpose has all obtained fine realization. Namely, the circumferential relative position in the blocking embedding mechanism under the blocking working condition is well maintained by utilizing the limiting bulge in the blocking embedding mechanism when the rising angle lambda of the blocking working surface is less than delta or utilizing the self friction self-locking characteristic of the blocking working surface when the rising angle lambda of the blocking working surface meets the relation that delta is less than or equal to lambda and less than or equal to rho, so that the purposes of maintaining the blocking relation, preventing the embedding reset of the separation embedding mechanism in an overrunning state and eliminating the impact or collision are achieved; the control mechanism of state type is used for controlling the respective circumferential relative positions of the separating ring and the blocking ring, so that the purposes of controlling the existence and nonexistence of the overrunning capacity and the blocking capacity and the directions of torque transmission and separating overrunning are well achieved.

Compared with the existing jaw overrunning clutch, the utility model has higher rotating speed, larger transmitted torque, no noise in the overrunning state and simple control on the working direction and state; compared with a friction type overrunning clutch, the friction type overrunning clutch has incomparable torque transmission capacity particularly in the one-way field, has higher working rotating speed, smaller residual torque, higher reliability and efficiency and longer service life because an asymmetric rotating component is not arranged and the friction torque is irrelevant to the rotating speed and can automatically compensate a blocking ring with axial abrasion. In the field of non-classified application, the potential is huge.

Drawings

FIG. 1 is an axial cross-sectional view of a simplest embodiment of a one-way overrunning clutch.

Fig. 2 is a schematic view of the second engaging element of fig. 1, (a) is an axial sectional view of a right side view of (b), (b) is a front view, and (c) is an enlarged expanded schematic view of a partial tooth profile radial projection in the T direction in (b).

Fig. 3 is a schematic view of the blocker ring of fig. 1, (a) is a front view, (b) is an axial half-sectional view of a left side view, and (c) is an enlarged expanded schematic view of a partial radial projection in the T-direction of (a).

Fig. 4 is a partial development view of radial projections of the tooth profiles of the respective interlocking mechanisms in fig. 1 on the same outer cylindrical surface under different working conditions, (a) is a tooth profile relationship diagram of the working interlocking mechanism in an interlocking state, (b) is a tooth profile relationship diagram of the control interlocking mechanism corresponding to (a), (c) is a tooth profile relationship diagram of the working interlocking mechanism in a blocking working condition, (d) is a tooth profile relationship diagram of the control interlocking mechanism corresponding to (c), and (e) is a partial enlargement diagram of (a), and an arrow represents a relative overrunning rotation direction.

FIG. 5 is a schematic view of all possible abutting contact relationships of the blocking and embedding mechanism with various tooth shapes in the blocking working condition, which are shown in the form of a radial projection expansion diagram, wherein the left side contour lines in all the figures belong to the blocking ring, and the right side contour lines in all the figures belong to the auxiliary blocking ring; (a) the various cases of controlling the fitting mechanism are shown by (a) to (c) which show three special tooth profiles, (d) to (i) which show all tooth profiles when | δ | < λ ≦ ρ, and (e) to (i) which show special tooth profiles in which β ═ λ and are coplanar; (j) the tooth profile suitable for the radial type position-restricting fitting mechanism is shown.

Fig. 6 is an axial cross-sectional view of an embodiment of the present invention having an axial fitting locking function.

Fig. 7 is an axial half-sectional view of the retaining ring gear of fig. 6, which serves as an axial stop.

Fig. 8 is an axial half-sectional view of the second coupling member of fig. 6.

Figure 9 is an axial cross-section of an embodiment of the invention in which the blocking ring is in the form of an axial displacement.

Fig. 10 is an axial cross-sectional view of a first package of the present invention.

Fig. 11 is an axial sectional view of a second package of the present invention.

Fig. 12 is an axial cross-sectional view of an example of an application of the present invention to a two-axis assembly.

Fig. 13 is an axial cross-sectional view of an application of the present invention for use in a power machine electric start-up clutch.

FIG. 14 is an axial cross-sectional view of a first embodiment of a controllable overrunning clutch.

Fig. 15(a) is an axial sectional view of a right side view of the first engaging element in fig. 14, and (b) is a front view.

Fig. 16(a) is an axial sectional view of a right side view of the separating ring in fig. 14, and (b) is a front view.

Fig. 17(a) is an axial sectional view in right side view of the second coupling element of fig. 14, (b) is a front view, and (c) is an enlarged expanded schematic view of a partial tooth profile radial projection in the T-direction in (b).

Fig. 18(a) is a front view of the blocker ring of fig. 14, (b) is an axial cross-sectional view of a left side view, and (c) is an enlarged expanded view of a partial radial projection in the T-direction of (a).

Fig. 19(a) is a right side view of the positioning pin spring in fig. 14, and (b) is a front view.

Fig. 20(a) is a front view of the positioning operation ring in fig. 14, and (b) is a left side view.

FIG. 21 is a partially developed schematic view of radial projections of the tooth profiles of the respective interlocking mechanisms of FIG. 14 on the same outer cylindrical surface under different working conditions; (a) the (b) and (c) are the tooth form relation schematic diagram when the torque is transmitted in the first direction, wherein (a) belongs to the separation embedding mechanism, (b) belongs to the force transmission embedding mechanism, and (c) belongs to the control embedding mechanism; (d) the (e) and (f) are the tooth-shaped relation schematic diagrams when the separation and the overrunning are carried out in the first direction, wherein (d) belongs to a separation embedding mechanism, (e) belongs to a force transmission embedding mechanism, and (f) belongs to a control embedding mechanism; (g) the (h) and (i) are schematic diagrams of the tooth form relationship when the separation exceeds the second direction, wherein (g) belongs to a separation embedding mechanism, (h) belongs to a force transmission embedding mechanism, and (i) belongs to a control embedding mechanism, and an arrow represents a relative exceeding rotation direction.

FIG. 22(a) is an axial cross-sectional view of a second embodiment of the controllable overrunning clutch, and (b) is an expanded, partially enlarged circumferential cross-sectional view of a cylindrical surface on which the axis of the release ring pin is located in (a).

Fig. 23(a) is an axial sectional view showing a simplified structure of the embodiment of the controllable overrunning clutch, (b) is an H-direction view of the first engagement element in (a), (c) is an H-direction view of the release ring in (a), (d) is a front view of the rotation stop control ring in (a), and (e) is an axial sectional view of a left side view of (d).

Fig. 24(a) is an axial sectional view showing a simplified structure of a fourth embodiment of the controllable overrunning clutch, (b) is an H-direction view of a first engagement element in (a), (c) is a front view of a link ring in (a), and (d) is an enlarged view of an axial sectional view of a left side view of (c).

Detailed Description

The essential explanation is as follows: in the text of the present description and in all the figures, identical or similar components and features thereof are provided with the same reference signs, so that the present description is given in detail only when they appear for the first time and will not be given repeated detailed description when it appears again thereafter.

The simplest embodiment of the one-way overrunning clutch of the present invention is shown in fig. 1 to 4, and is in the form of a wheel-shaft transmission. The first engaging element 50 is rigidly integrated with the first sleeve 187, and the second engaging element 60 is fitted around the first sleeve 187 with its fitting end faces facing each other, and constitutes a working fitting mechanism with the first engaging element 50. Gear teeth 206 are integrally formed on an outer cylindrical surface of second coupling member 60. The compression spring 182 is mounted between the non-engagement end face of the second engaging element 60 and a spring seat 184 in the form of a snap ring, the spring seat 184 being axially fixed in a snap ring groove of the first sleeve 187. The blocking ring 70 is a split elastic ring which is fitted in an annular conical recess on the inner ring side of the face tooth of the first engaging element 50 and, with the latter as its reference ring, has its sliding end face abutting against the blocking reference end face 128 and its engaging end facing towards the second engaging element 60.

The structure of the second engaging element 60 is shown in fig. 2. The outer ring surface of the embedding end is evenly distributed with second force transmission teeth 62, the inner ring surface is evenly distributed with auxiliary blocking teeth 102, and the two are radially connected into a whole. The auxiliary blocking tooth flank surfaces 108, 66 and the tooth root surface 110 are completely coplanar with the second force transmission tooth flank surfaces 136, 66 and the tooth root surface 138 respectively, the blocking working surface 104 is a spiral surface with a lead angle lambda, and lambda is greater than delta and less than or equal to rho. The second force-transmitting tooth 62 is a combination of a force-transmitting tooth and an auxiliary disengaging tooth, and the angle of inclination of the disengaging flank 136 is significantly larger than the friction angle, so as to ensure that the two engaging elements can generate a large enough axial disengaging force when rotating relatively, and overcome the constraint of the pressing spring 182 to realize axial disengagement; the angle of inclination of the force-transmitting flank 66 is small, zero or negative (root retraction), preferably negative, to suit the requirements of a helical engagement. Correspondingly, the first engaging element 50 and the second engaging element 60 have a completely identical force transmission toothing and layout.

The stop ring 70 is constructed as shown in FIG. 3 as an open elastomeric ring having a cross-section 74. The blocking teeth 72 are rigidly and integrally distributed on the outer ring side of the annular base body 71, and each tooth surface is a spiral face type blocking working surface 76 with a lead angle lambda, a tooth flank surface 78c and 78d, a top surface 84 of a tooth top middle limiting bulge 82 and a spiral face type limiting flank surface 86 with a lead angle beta, wherein | delta | is more than or equal to beta and less than 180 degrees. The blocker tooth slot width is sufficient to accommodate the secondary blocker tooth 102. The bottom end face of the barrier ring is its circumferential sliding end face 90, and the top end face is its fitting end face. The outer circular surface of the blocking ring 70 and the mating inner hole surface of the first engaging element 50 are both conical surfaces with a small outside and a large inside.

As shown in fig. 4(a), (b) and (e), the first engaging element 50 and the second engaging element 60 axially constitute a one-way working engaging mechanism which is both a force-transmitting engaging mechanism and a separating engaging mechanism, and the blocking ring 70 and the auxiliary blocking ring constitute a control engaging mechanism which is both a blocking engaging mechanism and a limit engaging mechanism, and the circumferential degrees of freedom of the two engaging mechanisms may be zero. In the chimeric state, IT < AG < D_c< BE, wherein IT represents the initial separation height of the separation/engagement mechanism in the non-designed separation override direction (the horizontal line symbol represents the axial distance, the same applies hereinafter), which is constant at zero in the designed separation override direction, D_cRepresenting the full-tooth embedding depth of the working embedding mechanism or the separating embedding mechanism, AG representing the minimum blocking height of the blocking embedding mechanism, and BE representing the maximum limit embedding depth of the limit embedding mechanism. The mutual relationship of the fitting mechanism in the overrun condition is shown in fig. 4(c) and (d).

It will be understood that the arrangement of three uniformly distributed, diametrically identical radial teeth on each of the blocking ring 70 and the secondary blocking ring 102, and exactly the radial extension of the second force-transmission tooth 62 in the circumferential direction, is not essential, purely for the sake of simplicity of construction and process, etc. In the case where the secondary stopper ring cannot be formed integrally with the primary ring, the secondary stopper ring can be handled by a method of manufacturing the secondary stopper ring separately in advance and then rigidly combining the secondary stopper ring with the primary ring by welding or interference fit.

This embodiment is further described below with reference to fig. 1 and 4 in conjunction with the working process.

In the engaged condition, torque from the first shaft is transmitted through the first bushing 187 to the first coupling member 50, through the working engagement mechanism to the second coupling member 60 and out through its upper gear teeth 206, or in reverse. Because the asymmetric rotating component is not provided, and the circumferential pressure on the force transmission tooth surface can be 100% used for torque transmission, or the effective utilization rate of the mechanical potential energy of the material can be 100% in both the surface pressure stress and the bending strength, which is far higher than the level of about 10% in the prior art (about 90% is consumed on the normal pressure stress which is not directly related to the torque), therefore, the asymmetric rotating component has the advantages of relatively higher working rotating speed, larger transmission capacity and impact resistance, smaller volume and the like. For example, the maximum torque would be much greater than the highest parameter 949,200 nm of Formsprag, USA, and the diameter would also be significantly less than its corresponding 965 mm, and the rotational speed would be significantly higher than 75 rpm.

Referring to fig. 1 and 4, when the relative rotation speed of the two engagement elements in the designed direction of mutual separation is greater than zero, the overrunning clutch starts to separate and overrun, and the two separation flanks 136 and 126 in the disengaging and engaging mechanism slide and climb each other against the elastic force of the compression spring 182 until the axial separation distance of the second engagement element 60 from the first engagement element 50 reaches D_c. Due to the parameter AG < D_cThus, the lowest point a of the secondary blocker tooth abutment face 104 of the control engagement mechanism already axially passes the lowest point G of the blocker tooth abutment face 76. Since the stop ring 70 is still on the first engagement element 50 due to the self-restraint action of its radial elasticity, the process of overriding the disengagement is sufficient to ensure that D is reached in the first synchronization of the axial disengagement distance of the control engagement, as long as the inlet margin K of the blocking engagement is not far from its lower limit value_cAt this point, the secondary blocker tooth blocking face 104 has already reliably jumped the upper blocker tooth blocking face 76, and the interference with each other and the establishment of a stable self-locking stiction relationship, in turn, drives the blocking ring 70 to circumferentially slide on the reference end face 128 of the first engagement element 50, thereby stopping the axial separation process between the two engagement elements at the maximum separation distance. Therefore, the axial distance between the second engaging element 60 and the first engaging element 50 is constantly zero, and the two are in a zero-contact overrunning sliding friction condition without any impact and collision, which can remarkably reduce the wear speed of the two, eliminate noise and prolong the service life. In addition, the top surfaces of the first force transmission teeth or the second force transmission teeth can be made into a step shape with a high inner end, so that the average sliding friction radius and the residual torque under the overrunning working condition are obviously reduced. The same ratio friction type overrunning clutch hasSmaller friction radius, sliding linear velocity, residual torque and wear consumption.

It should be emphasized that in the controlled engagement mechanism of the present embodiment, the helicoidal surface of the blocking face is characterized by the precondition of ensuring zero collision of the transmission teeth in the blocking condition, i.e. λ > 0 is required. And the lambda which is more than or equal to the lambda is the necessary condition for blocking the friction self-locking between working surfaces in the working condition, and the necessary condition for blocking the embedding mechanism to have the capability of self-adapting to the axial separation distance and the capability of automatically compensating various axial abrasion in a certain range, thereby greatly improving the overall performance, the reliability and the service life of the overrunning clutch, and the compensation amount can be given according to the requirement during the manufacturing. Particularly, when delta is more than 0 and lambda is more than 0 and less than delta, the auxiliary blocking tooth 102 can slide and climb relatively because the two blocking working surfaces which are contacted with each other in a butting way cannot be self-locked, and the axial separation distance of the blocking embedding mechanism is larger than D_cUntil the stop lug 82 is encountered. That is, with proper design, an overrunning rotational condition is achieved that allows no contact between the two engagement elements. In addition, the self-locking relationship between the blocking working faces only exists in the corresponding overrun rotation, that is, in the relative rotation in which the lift angle of the blocking working face in the opposite contact is made positive, but never exists in the relative rotation in which the lift angle is made negative, because the lift angle λ ' — λ < - δ |, λ ' in the latter rotation falls completely outside the lower limit of the self-locking requirement λ ' ≧ δ. Thus, by changing the relative rotational direction of the two engagement members in the blocking condition, the original self-locking relationship between the blocking faces will be immediately lost, and the blocking ring 70 will no longer rotate integrally with the secondary blocking tooth 102, but will rest on the reference ring reference end face 128.

Therefore, the embedded reset of the overrunning clutch of the utility model is very simple and natural, and the overrunning clutch can be used for reverse overrunning. That is, the overrunning clutch is immediately engaged and reset as long as the relative rotational speed of the two engagement elements in the designed direction of mutual disengagement is less than zero. Or, in any extreme case, at most one tooth in the above-mentioned relative rotational direction, namely, the second coupling element 60 is engaged with respect to the first coupling element 50The secondary blocking tooth 102 is able to slide off the blocking tooth blocking face 76 and engage and reset with the second force transmitting tooth 62 in synchronism with the rotation of the arrow in the opposite direction and by one tooth. See fig. 4(c) and 4 (d). Only in the case that the second force transmission tooth 62 circumferentially misses the tooth notch of the first force transmission tooth before the point a of the lowest point of the auxiliary blocking tooth blocking working surface 104 has not slipped off the point G of the lowest point of the blocking tooth blocking working surface 76, the fitting reset process needs to be rotated by one tooth, but the phenomenon of seizure or tooth breakage never occurs. Because IT < AG < D_cBE, the limit of the initial separation height, point I is axially separated from point T, therefore, the relative rotation of the two force transmission teeth can not cause the conditions of the axial overlap and extrusion of the tooth flank, but only can BE the result of reverse overrunning separation; and point E and point H are axially equal in height enough to ensure that the blocking tooth notch rotates synchronously with the depending blocking tooth 102. Therefore, the overrunning clutch of the utility model has the advantages of simple mechanism and reliable process in two processes of separation blocking and embedding resetting.

It should be noted that the constraint imposed on the blocker ring 70 in this embodiment is only to ensure the desired reliability and performance and is therefore not necessary. The constraint mode is a self-constraint mode of the elastic open ring and also has another constraint mode of the complete ring. The blocking ring 70, the restraining method, the blocking fitting mechanism, the limit fitting mechanism, their relationships with other members, and the descriptions regarding δ and ρ are more thoroughly and carefully described in the "basic type jaw self-locking differential" of the utility model filed by the applicant of this patent, which is incorporated by reference in its entirety and will not be described in detail herein.

Fig. 5 shows all possible abutting contact conditions of the blocking engagement with various tooth profiles in the blocking operating mode. In FIGS. 5(d) - (i), | δ | < λ ≦ ρ, all tooth profiles of the fitting control mechanism are shown that can achieve zero contact friction at the tooth tip of the separation tooth and have a wear compensation function. Fig. 5(d) shows a case where β ≠ λ; fig. 5(e) - (i) all show the special case where β ═ λ and the flank 118 of the stop tooth crest mid-stop lobe is coplanar with the stop running surface 108, which is advantageous for manufacturing. Fig. 5(a), 5(b) and 5(j) correspond to various tooth relationships with impact wear after overload separation.

It should be noted that, since the operation principle, relationship and process of the block fitting mechanism and the like are completely the same, the following embodiments will not be repeated, and only the specific structure will be explained as necessary.

Fig. 6 to 8 show a configuration having an axial fitting locking function. A second sleeve 189 in the form of a splined hub is the centre of rotation of the overall clutch and is in circumferentially fixed relationship with internally splined teeth on the internal bore face of second coupling element 60, all constrained to second sleeve 189 by two snap rings 190. A wave-shaped restraining spring 92 is interposed between the stop ring 70 and the external spline of the second sleeve 189, and therefore the stop ring 70 is always in close contact with the stop reference end surface 128. The bearings 192 serve to reduce residual torque during overrunning.

The limit gear ring 196 is a key feature of this embodiment, and as shown in fig. 7, there are "L" shaped limit teeth 200 that completely correspond to the first transmission teeth uniformly distributed at one end of the ring base, and there are circumferential teeth protrusions 198 on the upper half of the teeth. The ring is circumferentially fixed (by screws or by making the inner shoulder into a fitting tooth shape) to the outer circumferential surface of the first engaging element 50, the inner shoulder 274 can bear unidirectional tensile force, the top surface 202 of the "L" shaped limit tooth is not higher than the starting point of the reverse separation curve of the first power transmission tooth 52 in the axial direction, i.e., the point T in fig. 4(c), and only the circumferential tooth projection 198 projects from the power transmission side surface of the first power transmission tooth. Correspondingly, as shown in fig. 8, the outer end face of the second force transfer tooth 62 is formed with a circumferential groove 69 having a width and depth to accommodate the circumferential tooth projection 198. Thus, the fitting relationship can lock the axial relationship after the clutch is fitted. Of course, this sacrifices a little torque transfer capability, since the thickness of the force transmitting teeth must be reduced by the presence of the circumferential teeth 198.

It will be appreciated that the present embodiment can be easily modified to an overrunning coupler, and the specific structure and description thereof can be referred to the detailed description of the utility model 'zero-collision jaw universal safety clutch' filed by the applicant of the present patent, which is incorporated by reference in its entirety and will not be described in detail herein.

Fig. 9 shows an embodiment with the first coupling element 50 as secondary blocking ring and the second coupling element 60 as blocking reference ring. The blocking ring 70 is arranged in an end face annular groove on the inner side of the second force transmission tooth 62, and is restrained on a blocking reference end face 128 by a restrained spring 92 and a clamping ring 94, and the restrained clamping ring 94 is fixed in a clamping ring groove on the outer cylindrical surface of the notch of the annular groove; a stop shoulder is formed on one end of the second bushing 189 to be spaced apart from the first engagement member 50 by a washer 204.

Fig. 10 shows a first package of the present invention. The key point of fig. 10, in comparison with fig. 6, is that the entire encapsulation of the overrunning clutch is achieved by fixing the bowl-shaped housing 214 on the outer circumferential surface of the first engagement element 50, and the sealing ring 210 only plays an auxiliary role. The ring gear 212 may also be fixed to the first engaging element 50 not by the bolt 208, but in the form of a flat key, or formed directly thereon.

The second packaging form of the present invention is shown in fig. 11. Is a direct encapsulation to the embodiment of fig. 1. In contrast to fig. 10, the bowl-shaped casing 214 of the present package has a function of transmitting torque by engagement of the spline teeth 220 on its inner circumferential surface with the external spline teeth on the outer circumferential surface of the second engagement element 60, and the key grooves on its outer circumferential surface or the threaded holes 216 on the end surface are used for force transmission. An annular end cap 222 is secured to the open end face of the bowl-shaped housing 214 by screws 224. The other end of the support ring 98 of the restraining spring 92 presses against the outer ring of the bearing 192 to provide simultaneous support of the blocker ring 70. Obviously, if the blocking ring 70 is in the form of a self-restraining resilient split ring, then the restraining spring 92 and support ring 98 would not be required.

It will be readily appreciated that the bearings 192 in both the first and second packs have a good radial orientation of the pack housing and reduce residual torque during overrunning. And both may be sleeveless in the form of a sleeve-less sleeve 189 or 187, mounted directly on the shaft.

Fig. 12 shows an application example of the one-way overrunning clutch in the two-shaft assembly of the loader, and the application example has the structural form of the embodiment shown in fig. 6. But the second collar 189 is replaced with the second rotating shaft 188 and the spring seat 184 is replaced with the pinion 232. Pinion 232 and second coupling member 60 are both circumferentially fixed to second shaft 188 in a splined manner. The large gear 234 is formed directly on the first engaging member 50. Bearings 228 and 236 are mounted between the first coupling member 50 and the second shaft 188 and the pinion 232, respectively. The entire assembly is axially retained by retaining ring 226 and end base bearings 192.

Fig. 13 shows an example of the application of the one-way overrunning clutch in the electric starting clutch of the engine. Can be seen as a variation of the embodiment of fig. 12 with the pinion 232 removed. The first engagement element 50 is axially restrained by a gearbox bearing seat 238 (between which rolling bearings may also be mounted). A captive snap ring 94 is mounted on a second shaft 188 having an outer diameter identical to the outer diameter of the splines. The compression spring 182 presses against a shoulder on the outer cylindrical surface of the second engaging member 60, and the spring seat 184 is fixed to the end surface of the second rotating shaft 188 by the screw 240.

Fig. 14 shows a first embodiment of the controllable overrunning clutch, which is a bidirectional overrunning clutch with a first packaging form. Compared to fig. 10, a release ring 120 between the first engaging element 50 and the stopper ring 70 in the radial and axial directions is added, and a release ring positioning lock mechanism, which is mounted on the non-fitting end surface of the first engaging element 50 and is composed of positioning pins 150a and 150b, a plate-like positioning pin spring 156, a positioning operation ring 140, and a snap ring 190. Wherein the positioning pins 150a and 150b are fitted in axial positioning through holes 154a and 154b, respectively, on the non-fitting end faces of the first engagement elements. The cylindrical surfaces of the outer ends of the positioning pins 150 are all provided with grooves perpendicular to the axis, and the outer diameter ends of the sheet-shaped positioning pin springs 156 are embedded in the grooves. The radially central portion of the spring 156 is pressed by the positioning and actuating ring 140 against the non-engaging end face of the first engaging element 50 and is fixed circumferentially with its radially positioning lug 156c engaging in the end-face recess 59 of the first engaging element 50. The snap ring 190 axially restrains the positioning manipulation ring 140 from the outer end to the first engagement element 50. See fig. 15 and 19. In this and subsequent embodiments, the blocking reference ring is acted upon by the separating ring 120, which is acted upon by the first engaging element 50. And force transmission teeth and separating teeth are not distributed, the number of the force transmission teeth and the number of the separating teeth of all the components are all the same, and the force transmission teeth and the separating teeth are strictly and uniformly distributed in the circumferential direction.

For the sake of convenience of distinction and consistency of description, in the present specification, all numbers of the first set of locking members in the split ring positioning locking mechanism are assigned with the end sign a, and all numbers of the second set of locking members are assigned with the end sign b, and accordingly, the split ring is circumferentially fixed by the first set of locking members at a first relative position corresponding to the first direction with respect to the split reference ring, and the split ring is circumferentially fixed by the second set of locking members at a second relative position corresponding to the second direction with respect to the split reference ring. The circumferential angle between the two opposite positions is denoted as epsilon. When the separating ring is locked, the overrunning clutch can only transmit torque or separate overrunning in the working direction corresponding to the locking position. When only one direction of operation or general direction is indicated, no tail numbers a or b are attached.

As shown in fig. 15, on the outer ring side of the engaging end face of the first engaging element 50, a circle of force-transmitting teeth 52 are uniformly distributed, and the inclination angle of the tooth surfaces on both sides of the teeth is small, zero or negative (i.e. the tooth root is retracted), and the teeth can only be used for transmitting torque; in the region of the non-fitting end surface corresponding to the separation reference end surface 58, three sets of axial positioning through holes 154a and 154b are arranged with an inner interval of the circumferential angle E. In addition, a threaded bore 248 for fastening the force-transmitting toothed ring and a recess 59 in the end face are arranged on this end face.

As shown in fig. 16, the engaging end face of the separating ring 120 is formed with a ring of separating teeth 122, both side tooth surfaces of which have a circumferential separating function, like the above-described subsidiary separating tooth flank 136, and the cross section of which is trapezoidal or crowned-waist trapezoidal. The inner bore shoulder end surface of the separating ring 120 is the stop datum end surface 128. On the non-fitting end face of the ring, three sets of axial positioning pin holes 152a and 152b having an inner interval circumferential angle of E-epsilon are arranged correspondingly on a circle of revolution having the same diameter as the center of the positioning through hole 154. E is a free amount that can be arbitrarily chosen, but overlap of the registration pin holes 152a and 152b should be avoided.

The structure of the second engaging element 60 is shown in fig. 17. The second force transmission tooth 62, the auxiliary separating tooth 132 and the auxiliary blocking tooth 102 are sequentially formed in three annular areas on the embedded end face from outside to inside. The tooth profiles of the second force transmission teeth 62 and the satellite disengagement teeth 132 are identical to the first force transmission teeth 52 and the disengagement teeth 122, respectively. The subsidiary blocker tooth 102 is symmetrically formed with a blocker working surface 104 at both sides of the tooth crest. For the convenience of machining, the three face teeth are integrally connected in the radial direction, with the effect that after the partial entities of the auxiliary separating tooth 132 and the auxiliary blocking tooth 102 are cut off by using the radially extending surface of the second force transmission tooth sheave profile surface as a boundary, the circumferential clearance of the separating and fitting mechanism is kept unchanged, and the blocking working surface 104 of the auxiliary blocking tooth is completely retained. Therefore, the corresponding tooth body portion of the middle tooth crest 106 of the auxiliary blocking tooth 102 and the root portion of the auxiliary separating tooth flank 136 are cut off, the auxiliary blocking tooth flank 86 is coplanar with the second force-transmitting tooth flank 66, and the tooth root surfaces 110, 138 and 68 of the auxiliary blocking tooth 102, the auxiliary separating tooth 132 and the second force-transmitting tooth 62 are coplanar.

As shown in fig. 18, the blocking tooth 72 is integrally formed on the same end face of the annular base body 71, i.e., the blocking tooth root face 80. Two sides of the crest face of the blocking tooth are symmetrically provided with two identical spiral face type blocking working faces 76, the lift angle is lambda, and lambda is greater than delta and less than or equal to rho. The middle part of the tooth top is provided with a limit bulge 82, both side surfaces 86 of the limit bulge are helical surfaces with the lead angles of beta, and beta is more than or equal to | delta | and less than 180 degrees.

Fig. 19 shows the structure of the leaf shaped detent stud spring 156. The radial spring strips 156a and 156b of the same set have a circumferential angle E, and for ease of installation and control, the three sets are all formed on the same annular base, with the detent lugs 156c on the base engaging the notches 59 of the first engagement element to ensure that the spring strips 156a and 156b are aligned with the detent through holes 154a and 154b, respectively, on the first engagement element. In addition, the radially outer end portions of the spring pieces 156 each have a tilted shape as shown in fig. 19 (a).

Fig. 20 shows a structure of the positioning operation ring 140. The ring end face 141 has an annular projection 276 formed on an inner ring region and three sets of cylindrical cam projections 142 and 144 formed on an outer ring region. Where 142 is the anti-rotation limit projection of the operating ring, it is disposed in the groove between the cam projections 144a and 144b, thus forming two grooves 145a and 145 b. The circumferential angle between any point in the two grooves is smaller than E, so that one of the spring strips 156a and 156b must circumferentially overlap the projection 144a or 144 b. In addition, to facilitate circumferential pressing of the protrusion 144 against the spring plate 156, the corresponding sides thereof are each machined with a ramp surface 143.

Fig. 21 shows the relationship between the tooth profiles of the individual interlocking mechanisms of fig. 14. The first engaging element 50 and the second engaging element 60 form a force-transmitting engagement mechanism having a circumferential degree of freedom θ_tThe mechanism can be separated smoothly without any contact or collision when the separating and embedding mechanism surpasses and separates in two directions; the separating ring 120 and the auxiliary separating ring form a separating and embedding mechanism with zero two-way initial separation height; the stop ring 70 and the auxiliary stop ring form a control embedding mechanism, and the inlet margin K of the mechanism is

(the correlation symbol represents the circumferential angle between the corresponding points), where K > θ_c+θ_f+ γ + η; in the clutch-engaged state, D_t＜AG＜D_c< BE, here, D_tRepresenting the full-tooth embedding depth of the force-transferring embedding mechanism, and other parameters are described as before. All possible abutting contact conditions of the blocking engagement with various tooth profiles in the blocking mode can be seen in fig. 5.

The present embodiment will be further described with reference to fig. 14 to 21 in conjunction with the working process. Since the processes of force transmission, overrunning, separation blocking and embedding resetting are completely the same as or similar to the one-way overrunning clutch, the description is not repeated here, and only the reversing mechanism and the embedding resetting process are mainly described.

Fig. 14 and 21(a) to (f) each correspond to the first direction, and the release ring is circumferentially fixed at a first relative position by the first set of locking members. That is, the positioning pin 150a is stably fitted into both the positioning through hole 154a of the first engaging element 50 and the positioning pin hole 152a of the release ring 120 by elastic pressing of the outer diameter end of the spring piece 156a against the groove at the trailing end thereof; the pressing force of the spring plate 156a comes from the pressing of the cam protrusion 144a of the positioning operation ring 140 to the radial middle portion thereof. At this time, the spring plate 156b is just located in the cam groove 145b of the positioning operation ring 140 to keep its original tilting state, and drives the positioning pin 150 to be fitted into only one hole of the positioning through hole 154b of the first engaging element 50. Fig. 21(a) - (c) show the force transfer conditions in the first direction, and fig. 21(d) - (f) show the overrun conditions in the first direction.

In the embedding reset process, although the blocking tooth notch in the one-way overrunning clutch can not rotate synchronously with the auxiliary blocking tooth 102, the K is more than theta_c+θ_fThe parameter + γ + η ensures that, as well as the preceding description, it is also possible to ensure that the synchronous engagement reset of the entire clutch is achieved after at most one force transmission tooth has been rotated, without the reverse blocking situation occurring, as long as K is not far from its lower limit.

The reversing operation for changing the operating direction of the overrunning clutch from the first direction to the second direction is very simple. As compared with fig. 14, the positioning operation ring 140 is rotated in the second direction until the limit projection 142 contacts the spring piece 156 a. The clockwise direction in the left side view of fig. 14 is the second direction. After the rotation, the spring piece 156a just falls into the groove 145a of the positioning operation ring, and immediately restores the original tilted shape and drives the positioning pin 150a to move out of the positioning pin hole 152a of the separation ring, so that the locking of the separation ring 120 is released, and the first group of locking members of the a-series temporarily stands by. At the same time, the spring plate 156b is axially bent by the projection 144b and its radially outer end is continuously elastically pressed against the positioning pin 150b, so that as long as the clutch is rotated in the second direction, the first coupling member 50 must be rotated through the circumferential angle e relative to the release ring 120, and the pin head of the positioning pin 150b is naturally inserted into the positioning pin hole 152b, thereby finally completing the entire reversing operation. That is, the separating ring 120 is fixed in the second relative position by the second set of locking members of the b-series (fig. 21 (g)). In this relative position, the overrunning clutch has full functionality similar to that in the first direction. Fig. 21(g) to (i) show the overrun condition in the second direction. The reverse operation of the above operation is performed to change the working direction of the overrunning clutch from the second direction to the first direction. That is, the reversing operation is simply a swinging motion of the positioning operation ring 140 back and forth between two circumferential positions. It is understood that the reversing operation is to switch the working states of the two sets of axial control components in the mutually opposite states by means of the reciprocating motion in the circumferential direction or the axial direction of the positioning operation ring 140 and the like. The indirect result is that the separating ring 120 oscillates back and forth between the first and second relative positions.

The essential explanation is: the commutation can only be performed in a jogged state, regardless of whether the rotor is rotating; the direction of rotation of the positioning operating ring 140 when reversing, with respect to the desired torque transmission direction, can be the same or opposite, all depending only on whether the recesses 145 or the protrusions 144 are placed between two sets of positioning through holes.

As shown in fig. 22, the second embodiment is a bidirectional overrunning clutch with a second packaging form. This embodiment is essentially a variation of the embodiment of fig. 14: a positioning pin 150 of the separating ring positioning locking mechanism is divided into two parts, namely a positioning pin 150 and a reversing back pin 146; the positioning pin spring 156 is deformed from a sheet shape in the operating slot 55 into a cylindrical shape in the split ring positioning pin hole 152, still acting on the tail end of the positioning pin 150; the manner in which the locating stud 150 exits the locking station is changed from elastic to rigid. As shown in fig. 22(b), the length of the reverse retreat pin 146 is equal to the depth of the positioning through hole 154. The positioning and manipulation ring 140 still takes the form of a cylindrical cam similar to that of fig. 15 and also takes the form of a positive control with the groove 145 interposed between the two sets of positioning through holes. The overrunning clutch in fig. 22 operates in a first direction. At this time, the operation of switching the working direction from the first direction to the second direction can be completed by rotating the positioning operation ring 140 in the second direction, that is, in the downward direction in fig. 22(b) (the rotation stop point is not shown). Because the rotation forces the reversing and backing pin 146a to push the positioning pin 150a back into the separating ring positioning pin hole 152a and aligns the groove 145b of the positioning operation ring 140 with the reversing and backing pin 146b, the positioning pin 150b can be inserted into the positioning through hole 154b to lock the separating ring 120 at the second relative position when the positioning pin spring 156b is axially pressed, thereby ending the whole reversing action. The process is completely as before and is not repeated.

In contrast to the release ring positioning locking mechanisms in the embodiments shown in fig. 14 and 22, it is apparent that they are structurally related only to the first engagement element 50 as the release reference ring, the release ring 120 as the blocking reference ring, and the blocker ring 70, and are not related to the clutch structure, the packing form, and other components. The substantial differences and variations between the two embodiments are only shown in the working mechanism of the separating ring positioning locking mechanism and the specific components thereof, namely, the part for controlling the working state and the working direction. Therefore, in order not to repeat the explanation and highlight the essential features of the embodiments, all the embodiments are illustrated and described in the form of a precise diagram of the second packaging form from the lower implementation side, and only the control part is involved, and the explanation about the torque transmission, the separation override, the blocking limit, the packaging form and the like is not related.

Fig. 23 shows a third embodiment of a controllable overrunning clutch, which is a bidirectional overrunning clutch that can perform a reversing action at any time and at any time, and can also be used as a controllable bidirectional glider for a motor vehicle. This embodiment only provides the function of a positive locking stop ring 70 over the embodiment shown in figure 22. In contrast to fig. 22, the length of the reversing setback pin 146, which is still equal to the depth of the detent through hole 154, is comprised of incomplete inner and outer cylindrical surfaces, with a crescent shaped cross section, whose outer cylindrical surface is in sliding engagement with the cylindrical bore portion of the detent through hole 154 and the inner cylindrical surface of the detent pin hole 152, and whose inner cylindrical surface is in sliding engagement axially and circumferentially with the outer cylindrical surface of the setback lobe 149. The retreating teeth 149 define the retreating pin 146 from the inner diameter direction, and are axial annular teeth fitted into an annular portion of the positioning through hole 154, and the outer annular surface thereof is a portion of a rotating cylindrical surface on which the axial center of the positioning pin hole 152 is located, as shown in fig. 23(a) to 23 (e). The rotation stop pin 160 is inserted through the annular limit through hole 174 on the first engaging element 50 into the rotation stop through hole 172 of the separating ring. To facilitate integral control, the backstop teeth 149 and the anti-rotation stud 160 are integrally formed on a link ring 170 that is axially confined in the operating slot 55 by a snap ring 190. The link ring return spring 250 is installed between the link ring 170 and the positioning operation ring 140, and axially presses the positioning operation ring 140 against the sidewall of the operation groove 55, and presses the link ring 170 against the standby position of the snap ring 190. In the standby station, the top surface of the retreating convex tooth 149 is not higher than the top surface of any group of retreating pins 146, and the pin top surface of the rotation stopping pin 160 is positioned in the rotation stopping through hole 172; and when the link ring 170 compresses the spring 250 to the extreme, the top of the set-back tooth 149 may fit into the corresponding annular groove 167 of the separator ring and the top of the rotation stop pin 160 may pass over the blocker ring reference end face 128 on the separator ring 120.

As shown in fig. 2(a) -23 (E), the circumferential angles between the positioning through holes 154a and 154b of the same set and between the receding convex teeth 149a and 149b of the same set are both E, and the circumferential angle between the positioning pin holes 152a and 152b of the same set is E-epsilon. The locating through holes 154, locating pin holes 152, and rotation stop pins 160 do not require uniform spacing. Since the rotation stop pins 160 are always fitted into the rotation stop through holes 172 of the separating ring, the link ring 170 is circumferentially fixed to the separating ring 120 by the rotation stop pins 160. Thus, the separating ring 120 constitutes a separating ring stopper mechanism by the rotation stop pin 160 and the annular stopper through hole 174 on the first engaging element 50. The circumferential freedom degree of the limiting mechanism is theta_d，θ_dE, but at most not so great that the separator ring separator teeth begin to have the ability to completely prevent axial engagement of the clutch. That is, the separating ring separating teeth 122 must not penetrate too much into the first power transmission tooth space in the circumferential direction. Optimum value theta_dε. Further, the degree of freedom in the circumferential direction between the unseated teeth 149 and the annular portion of the positioning through-hole 154 must not be less than θ_d. The circumferential positions of the annular stopper through-hole 174 and the annular portion of the positioning through-hole 154 are determined such that when the rotation stop pin 160 is positioned at the center in the circumferential direction of the annular stopper through-hole 174, the unseating tooth 149 is also positioned at the center in the circumferential direction of the annular portion of the positioning through-hole 154 and at the extreme end in the circumferential directionThe set retraction lobe 149 must also radially confine the retraction pin 146; the circumferential position of the detent recesses 91 or the two open sections 74 on the sliding end face 90 of the blocking ring is determined in such a way that, when the detent pins 160 engage in them, the blocking ring 70 remains in a position which ensures that the freewheel can be axially engaged and reset, preferably in a position which results in the auxiliary blocking teeth being centered in the tooth spaces after engagement.

The operating condition shown in fig. 23 corresponds to a first orientation, with the separating ring being held in a first relative position by a first set of locking members. The reversing process is completely the same as that of the embodiment shown in fig. 22, and the operating state of the two control assemblies of the a-series and the b-series can be switched by rotating the positioning operation ring 140. In the process, if the overrunning clutch is in the embedded state, the locking process of the separating ring 120 is completely the same as the previous process, the reversing operation is ended, and the process is not repeated; if the overrunning clutch is in a separation overrunning state, the overrunning clutch cannot be embedded and transmit torque due to the fact that the separation ring is located at the overrunning position in the first direction after the separation ring is successfully located at the second relative position in the work rotation after reversing, in this case, the second step of operation is needed, namely the energy storage spring 252 is pressed by external force in the rotation state in the second direction until the energy storage spring is released immediately after the clutch is embedded and reset, and the operation can be completed in an instant. Here, the elastic force of the charge spring 252 is greater than the sum of the elastic forces of the return spring 250 and the positioning pin spring 156 and is less than the elastic force of the compression spring 182. The process is as follows, exerting enough axial external force to the energy storage spring 252, forcing the retreating teeth 149 integrated with the link ring 170 to push the positioning pin 150 back into the positioning pin hole 152, releasing all direction locking, and simultaneously embedding the retreating teeth 149 into the annular groove 167 on the separating ring, the rotation stopping stud pin 160 is also synchronously pressed against the stop ring sliding end face 90 and is embedded between the rotation stopping groove 91 or the two opening sections 74 on the end face during relative rotation, thereby stopping the stop ring 70 on the separating ring 120 in the circumferential direction. Then, the separating ring 120 is rotated integrally with the auxiliary blocking tooth 102 in the circumferential direction by the blocking ring 70 until being blocked by the separating ring stopper mechanism. Thereafter, the auxiliary blocking tooth 102 slides and climbs relative to the blocking tooth 72, turns over the middle protrusion 82 and then is embedded into the next tooth groove of the blocking ring, and other embedding mechanisms are synchronously embedded and reset, so that the force transmission embedding mechanism is positioned at the correct force transmission station. At this time, the external force acting on the energy storage spring 252 is removed, the return spring 250 forces the link ring 170 to synchronously return to the standby station, and the positioning pin 150b is then inserted into the positioning through hole 154b again, thereby finally completing the reversing action. It will be appreciated that this function can also be used to force engagement to transmit torque regardless of whether the clutch is in an overrunning condition.

The above is a rotation-stopping embedding resetting method, and the precondition for use is that the lift angle beta of the two side surfaces 86 of the limit bulge at the middle part of the tooth crest of the blocking tooth must satisfy the inequality: beta is more than or equal to | delta | and less than 90-phi, and the side surface 86 and the barrier working surface 76 are optimally coplanar, namely, beta is equal to lambda.

To prevent the backing pin 146 from being mistakenly inserted into the positioning pin hole 152, a limiting shoulder or radial protrusion may be disposed at the rear end thereof, and a corresponding groove may be disposed outside the positioning through hole 154.

In addition to being used in a bi-directional overrunning clutch, the present embodiment may also be used as a bi-directional controllable glider for a motor vehicle. During the overrunning sliding in the forward or reverse direction, the sliding working condition can be forcibly ended only by forcibly inching the external force or pressing the energy storage spring 252 for a long time, and the transmission connection between the engine and the wheels is recovered. The controlled nature here is that the function of the decoupling ring and the blocking ring can be eliminated artificially simultaneously, so that the clutch is immediately equivalent to a jaw coupling. And the overrunning clutch will immediately resume all the functions of the controllable runner in the direction determined by the circumferential position of the positioning operating ring 140 after the above-mentioned forced external force is removed.

Fig. 24 shows a fourth embodiment of the controllable overrunning clutch, namely a one-way clutch for a motor vehicle. Functionally, it is a simplification of the embodiment shown in fig. 23, i.e. its overtaking function in the second direction only, i.e. the second set of locking members, is eliminated. It can transmit torque in both directions but can only be controllably overridden in the first direction. In this embodiment, the rotation stop pins 160 and the positioning pins 150 are served by different portions of the same axial cylinder formed on the end face of the link ring 170. As shown in fig. 24(c) and (d), in the space with the height h on the end face of the link ring 170, the rotation cylindrical surface corresponding to the axis of the cylinder is used as a boundary, and after a part of the cylinder located outside is cut off, the part corresponding to the incomplete cylindrical surface is the main body of the rotation stop pin 160, and the part corresponding to the complete cylindrical surface is the positioning pin 150. Where h is greater than the depth of positioning through-hole 154. A circumferential groove 171 is formed on an outer cylindrical surface of the link ring 170. The operating slot cover 246 has an "L" shaped cross section, and a radial through hole for installing the energy storage spring 252 is formed on an axial ring body of the operating slot cover, and the energy storage spring 252 may be a spring steel wire or a spring steel plate, etc. During assembly, the energy-accumulating spring 252 is first inserted from the outside to the inside into the radial through hole of the operating slot cover 246 (the insertion should be tight) and reaches the circumferential groove 171 of the link ring 170, and the two rings are elastically connected in the axial direction. Then the two rings, the return spring 250 and the snap ring 190 are put in place in sequence to complete the installation of the whole control operation mechanism. Wherein the return spring 250 is axially between the operating slot cover 246 and the first engagement element 50.

After installation, the positioning pins 150 and the rotation stopping pins 160 are naturally located in the positioning through holes 154 and the positioning pin holes 152 at the same time, and the separating ring 120 is circumferentially locked; at the instant the positioning stud 150 moves out of the positioning through hole 154 and completely sinks into the positioning stud hole 152, the pin top face of the positioning stud 150 or the rotation-stopping stud 160 should not pass over the blocking reference end face 128 on the separating ring 120, and the link ring 170 should not axially interfere with the first engaging element 50 when it starts to pass over this end face. In the circumferential direction, the rotation stop pin 160 and the annular portion of the positioning through hole 154 constitute a separation ring stopper mechanism having a degree of freedom θ in the circumferential direction_dThe circumferential degree of freedom theta of the force transmission embedding mechanism is realized without being influenced by small amount_tTo the extent that the throw-off ring starts to have the ability to completely prevent the clutch from being axially engaged, and the free space is completely located on the side of the lock-up position in the overrunning throw-off direction, see fig. 24 (b).

As previously mentioned, to ensure that the secondary blocker tooth 102 rides over the blocker tooth's central projection 82, the angle of elevation β of the projection on the same side as the blocking face 76 should satisfy the inequality: beta is more than or equal to | delta | and less than 90 degrees to phi, the side face is preferably coplanar with the barrier working face 76, and all barrier teeth are preferably uniformly distributed in the circumferential direction. In addition, since the reverse override function is eliminated, the separate fitting mechanism and the block fitting mechanism may be of a bidirectional type in the embodiment of fig. 14 or of a unidirectional type in the embodiment of fig. 1.

The mechanism of the working process of this embodiment is substantially the same as that of the embodiment shown in fig. 23. Only the reversing process is omitted. The glider shown in figure 24(a) is in the normal torque transfer position and can now enter the normal overrunning disengagement condition. After the vehicle enters the sliding state, the sliding device can be immediately embedded and reset to start transmitting torque due to reverse overrunning as long as the vehicle accelerates. If the overrunning state needs to be ended manually and forcibly, the one-way slider can immediately enter the working condition of the jaw coupling only by a simple operation of axially pressing the operating slot cover 246 to the limit and then loosening the operating slot cover. The process description is as before and is not repeated. If the motor vehicle recovers power driving at the moment, the second force transmission gear ring which rotates to a normal station returns the synchronous belt of the separating ring 120 to a normal one-way force transmission and separation station through the separating and embedding mechanism, so that the locking and positioning action of the separating ring is naturally completed, and the next working cycle starts from this.

It is readily understood that both unidirectional and bidirectional controllable runners are applicable to all vehicles. If the two gliders are arranged on a transmission shaft system with changeable torque direction, the forcing mechanism of the one-way glider and the reversing mechanism of the two-way glider are linked with the torque direction changing mechanism. If the two kinds of gliders are used for a transmission shafting with fixed torque direction, only the forced control mechanisms of the two kinds of gliders are linked with the brake operating mechanism of the motor vehicle, and then an independent operating mechanism is connected in parallel, so that the gliders can be controlled independently and are extremely simple to use. Obviously, the one-way controllable glider is superior to the two-way glider, the overtaking function can be cancelled by the linkage of the reversing operation mechanism when reversing, and the one-way controllable glider is simpler to be used in front of motorcycles, electric mopeds and gearboxes. The performance, the service life, the reliability, the structure, the process, the use and the maintenance of the sliding device are obviously superior to those of the prior sliding devices.

After understanding the above control mechanism, more control mechanism schemes should be devised without difficulty. More publications and descriptions are disclosed in patents on the same subject matter as the patentees.

The foregoing description and drawings are given as illustrative of the present invention only with respect to a limited number of embodiments thereof, and it is to be understood that the embodiments are presented by way of illustration and that various changes, equivalents, permutations and alterations in structure or arrangement of parts may be made without departing from the spirit and scope of the inventive concept.

Claims (10)

1. A press-fit type jaw overrunning clutch comprises a first joint element, a second joint element, a stop ring, an auxiliary limiting ring, a spring and a spring seat, wherein the first joint element, the second joint element, the stop ring, the auxiliary limiting ring, the spring and the spring seat are based on the same axial lead; the first joint element and the second joint element are axially oppositely embedded to form a working embedding mechanism which is a force transmission embedding mechanism and a separation embedding mechanism, the embedding end surfaces of the two joint elements are circumferentially and uniformly distributed with the same number of radial teeth, one side surface of each radial tooth is used for transmitting torque, and the other side surface of each radial tooth is used for axially separating; in the working engagement mechanism, as a result of rotation of one engagement element relative to the other, torque is transmitted in one direction and axially separated in the other direction; the method is characterized in that:

(a) the blocking embedded mechanism is arranged for preventing the embedding of the working embedded mechanism in the overrunning separation state, is axially positioned in the working embedded mechanism, is radially positioned in or out of the working embedded mechanism, and is formed by axially embedding a blocking ring and an auxiliary blocking ring, and the peripheral surfaces of the embedded end surfaces of the two rings are all provided with the same number of radial blocking teeth with the axial blocking function; the minimum blocking height of the blocking embedding mechanism is larger than the initial separation height of the working embedding mechanism in two rotation directions and smaller than the full-tooth embedding depth of the working embedding mechanism; said secondary blocker ring being rigidly integral with an owner ring, which is the second or first coupling element; the blocking ring is supported in a one-way mode by a blocking reference end face of the blocking reference ring, and a sliding end face of the blocking ring and the blocking reference end face form a circumferential free sliding friction pair; the blocking reference ring is a first or second engagement element opposite the primary ring of the secondary blocking ring;

(b) the limiting embedding mechanism is arranged for limiting the circumferential relative position of a blocking ring in the blocking embedding mechanism and consists of the blocking ring and an auxiliary limiting ring; the auxiliary limiting ring and the auxiliary blocking ring are rigidly integrated into a same ring, the limiting embedding mechanism and the blocking embedding mechanism are superposed to form a control embedding mechanism, in the control embedding mechanism, the blocking teeth are also limiting teeth, and the auxiliary blocking teeth are also auxiliary limiting teeth;

(c) in the control embedding mechanism, the blocking working faces of the tooth crests of the blocking tooth and the auxiliary blocking tooth are helical faces with the lead angles not larger than rho, and a limiting bulge is formed in the middle of at least one tooth crest face, wherein rho is the maximum lead angle of the blocking working face, which can enable a static friction pair formed by axial contact of the blocking working faces of the two blocking working faces to be successfully self-locked in the blocking working condition; and

(d) the maximum limit embedding depth of the limit embedding mechanism is larger than the full-tooth embedding depth of the working embedding mechanism.

2. The overrunning clutch according to claim 1, wherein: the side face of the limiting bulge in the control embedding mechanism, which is on the same side with the blocking working face, is a spiral face with a lead angle beta, beta is not less than | delta | and is less than 180 degrees, wherein | delta | is the absolute value of the minimum lead angle delta of the blocking working face, which can enable a static friction pair formed by the axial contact of the blocking working face of the blocking tooth and the blocking working face of the auxiliary blocking tooth to successfully self-lock in the blocking working condition.

3. A controllable press-fit type jaw overrunning clutch is composed of a first joint element, a second joint element, a separating ring, an auxiliary separating ring, a blocking ring, an auxiliary limiting ring, a spring and a spring seat, wherein the first joint element, the second joint element, the separating ring, the auxiliary separating ring, the blocking ring, the auxiliary limiting ring, the spring and the spring seat are based on the same axial lead; the first joint element and the second joint element are axially and oppositely embedded to form a force transmission embedding mechanism capable of transmitting torque in two directions, the embedding end faces of the two joint elements are uniformly distributed with the same number of force transmission teeth in the circumferential direction, and the force transmission teeth are radial teeth with two tooth side faces capable of transmitting torque; the method is characterized in that:

(a) the separation embedding mechanism is arranged, can cause self separation when the two parts rotate relatively, is positioned in the force transmission embedding mechanism in the axial direction and is positioned in or out of the force transmission embedding mechanism in the radial direction, and is formed by axially embedding a separation ring and an auxiliary separation ring, the embedding end surfaces of the two rings are uniformly distributed with the same number of separation teeth in the circumferential direction, the separation teeth are radial teeth with axial separation capacity, and the number of the separation teeth is equal to the number of the force transmission teeth; said accessory breakaway ring being rigidly integral with an owner ring that is the second engagement element or the first engagement element; the release ring is supported unidirectionally by a release reference end face of the release reference ring, which is a first engaging element or a second engaging element opposite to the owner ring of the accessory release ring;

(b) the device is provided with a blocking embedded mechanism for preventing the embedding of the separation embedded mechanism in an overrunning separation state, the blocking embedded mechanism is axially positioned in the separation embedded mechanism or in the force transmission embedded mechanism, the blocking embedded mechanism is radially positioned in, between or outside the force transmission embedded mechanism and the separation embedded mechanism, and is formed by axially embedding a blocking ring and an auxiliary blocking ring, and the same number of radial blocking teeth with axial blocking function are arranged on the periphery of the embedded end surfaces of the two rings; the minimum blocking height of the blocking embedding mechanism is larger than the full-tooth embedding depth of the force transmission embedding mechanism, larger than the initial separation height of the separation embedding mechanism in two relative rotation directions and smaller than the full-tooth embedding depth of the separation embedding mechanism; said secondary blocker ring being rigidly integral with an owner ring which is the second engagement element, the release ring or the first engagement element; the blocking ring is supported in a one-way mode by a blocking reference end face of the blocking reference ring, and a sliding end face of the blocking ring and the blocking reference end face form a circumferential free sliding friction pair; the blocking reference ring is a separate ring, a first engagement element or a second engagement element opposite the primary ring of the secondary blocking ring;

(c) the limiting embedding mechanism is arranged for limiting the circumferential relative position of a blocking ring in the blocking embedding mechanism and consists of the blocking ring and an auxiliary limiting ring; the auxiliary limiting ring and the auxiliary blocking ring are rigidly integrated into a same ring, the limiting embedding mechanism and the blocking embedding mechanism are superposed to form a control embedding mechanism, in the control embedding mechanism, the blocking teeth are also limiting teeth, and the auxiliary blocking teeth are also auxiliary limiting teeth;

(d) in the control embedding mechanism, the blocking working surfaces of the tooth tops of the blocking tooth and the auxiliary blocking tooth are helical surfaces with the lead angle not more than rho, and a limiting bulge is formed in the middle of at least one tooth top;

(e) the maximum limit embedding depth of the limit embedding mechanism is greater than the full-tooth embedding depth of the separation embedding mechanism;

(f) force-transferring embedding machineCircumferential degree of freedom theta of structure_tThe force-transferring embedding mechanism is determined in such a way that when the separating embedding mechanism exceeds and separates in two working rotation directions, no contact or collision occurs between the two components of the force-transferring embedding mechanism;

(g) the circumferential position of the separating ring relative to the separating reference ring is controlled by a separating ring positioning and locking mechanism, the separating ring can be fixed at a specific circumferential position relative to the separating reference ring by the mechanism, when the mechanism is locked, the overrunning clutch can only transmit torque and separating overrunning in one direction, and when the mechanism is unlocked, the overrunning clutch can not transmit overrunning in two directions but can transmit torque.

4. The overrunning clutch according to claim 3, wherein:

(a) the first engagement element is axially fixed;

(b) the auxiliary stop ring and the auxiliary limit ring both use the second joint element as the auxiliary main ring, the stop reference ring is a separation ring, and the separation reference ring is a first joint element;

(c) the two stopping working surfaces of the tooth tops of the stopping tooth and the auxiliary stopping tooth are respectively and correspondingly formed on two sides of each tooth top surface;

(d) two side surfaces of the limiting bulge in the control embedding mechanism are spiral surfaces with lead angles of beta, beta is more than or equal to | delta | < 180 degrees, and related parameters are defined as above;

(e) the initial separation height of the separation embedding mechanism in two opposite rotation directions is zero, and the rotation of the mechanism in the two opposite rotation directions can cause the mechanism to axially separate;

(f) the entrance margin K of the blocking embedding mechanism conforms to the inequality: k > theta_c+θ_f+ γ + η, where γ ═ max (γ)₁，γ₂) The relevant parameters are defined as follows:

θ_c: the separation ring separates the circumferential included angle corresponding to the tooth top surface,

θ_f: the auxiliary separating ring separates the circumferential included angle corresponding to the tooth top surface,

γ₁: a separation angle of the separation and engagement mechanism in the first direction,

γ₂: a separation angle of the separation and engagement mechanism in the second direction,

eta: the correction caused by the fact that the lead angle, the shrinkage of the tooth root of the force transmission tooth, the circumferential clearance of the separation embedding mechanism and the axial separation distance of the force transmission embedding mechanism are larger than the full-tooth embedding depth of the force transmission embedding mechanism;

(g) the separating ring positioning and locking mechanism is an axial pin hole type positioning mechanism which can respectively fix the separating ring at two different specific circumferential positions relative to the first engaging element, when the separating ring positioning and locking mechanism is fixed at the first relative position, the overrunning clutch can only transmit torque and separating overrunning in a first direction, and when the separating ring positioning and locking mechanism is fixed at the second relative position, the overrunning clutch can only transmit torque and separating overrunning in a second direction, and the second direction is opposite to the first direction; the mechanism consists of two sets of axial pin holes on the toothless end surface of the separating ring, two sets of axial through holes on the separating reference end surface of the first joint element, and two sets of locking pins, and the positions of all the axial holes are determined with the effect that when the first set of locking pins are simultaneously embedded in the first set of axial pin holes on the separating ring and the first joint element, the separating ring is circumferentially fixed on a first relative position of the first joint element, and when the second set of locking pins are simultaneously embedded in the second set of axial pin holes on the separating ring and the first joint element, the separating ring is circumferentially fixed on a second relative position of the first joint element;

(h) and the separating ring positioning and locking mechanism is controlled by the positioning control mechanism.

5. The overrunning clutch according to claim 4, wherein:

(a) the blocking ring rotation stopping mechanism is an embedded limiting mechanism which can forcibly limit the blocking ring at a specific circumferential position relative to the separating ring, when the mechanism is embedded, the blocking ring loses axial blocking capability, the overrunning clutch can be axially embedded and reset, and when the mechanism is not embedded, the blocking ring has axial blocking capability;

(b) the circumferential limit position of the separating ring relative to the first joint element is limited by a separating ring limiting mechanism, the limiting mechanism is arranged between the separating ring and the first joint element, the circumferential freedom degree of the limiting mechanism is not less than the circumferential included angle between the first relative position and the second relative position and is not so large as to enable the separating ring to start to have the capability of completely preventing the clutch from axially embedding, and the separating ring positioning and locking mechanism can fully realize the function in the rotating range corresponding to the circumferential freedom degree;

(c) the positioning control mechanism is a mechanism for controlling the axial positions of two groups of locking pins of the separating ring positioning locking mechanism, and simultaneously has the function of controlling the stop mechanism of the stop ring;

(d) the lead angles beta of two side surfaces of the limiting bulge in the control embedding mechanism meet the inequality: beta is more than or equal to | delta | and less than 90 degrees to phi, wherein phi is the friction angle of a friction pair formed between the side surface of the limiting bulge and the blocking tooth or the auxiliary blocking tooth, and | delta | is defined as above.

6. The overrunning clutch according to claim 3, wherein:

(a) the first engagement element is axially fixed;

(b) the auxiliary stop ring and the auxiliary limit ring both use the second joint element as the auxiliary main ring, the stop reference ring is a separation ring, and the separation reference ring is a first joint element;

(c) the initial separation height of the separation embedding mechanism in at least one relative rotation direction is zero;

(d) the side surface of the limiting bulge in the control embedding mechanism, which is on the same side with the blocking working surface, is a spiral surface with a lead angle beta, beta is more than or equal to | delta | and less than 90-phi, and the parameters are defined as above;

(e) the state control mechanism is formed by combining the separating ring positioning and locking mechanism, the separating ring limiting mechanism and the stop ring rotation stopping mechanism; wherein,

the separating ring positioning and locking mechanism is a pin-hole type positioning mechanism consisting of an axial pin hole on a toothless end surface of the separating ring, an axial through hole on a separating reference end surface of the first joint element and a locking pin, and the positions of the two corresponding axial holes are determined by the effect that when the locking pin is simultaneously embedded into the two axial holes to fix the separating ring at a specific circumferential position relative to the first joint element, the overrunning clutch can only transmit torque and separate overrunning in one direction;

the separating ring limiting mechanism is a mechanism which can limit the circumferential relative position between the separating ring and the first joint element, is arranged between the separating ring and the first joint element, and has the circumferential freedom degree which is not small enough to influence the force transmission embedding mechanism to realize the circumferential freedom degree theta thereof_tThe degree of the clutch engagement is not so large that the release ring starts to have the capability of completely preventing the clutch from being axially engaged, and the release ring positioning and locking mechanism can fully realize the function in the rotating interval corresponding to the circumferential freedom degree;

the stop ring rotation stopping mechanism is an embedded limiting mechanism which can forcibly limit the stop ring at a specific circumferential position relative to the separating ring, when the stop ring rotation stopping mechanism is embedded, the stop ring loses axial stopping capacity, the overrunning clutch can be embedded and reset axially, and when the stop ring rotation stopping mechanism is not embedded, the stop ring has axial stopping capacity.

7. The overrunning clutch according to claim 6, wherein: the state control mechanism further comprises a positioning control mechanism for operating the separating ring positioning locking mechanism and the stop ring rotation stopping mechanism.

8. The overrunning clutch according to claim 5 or 7, wherein:

(a) the stop ring rotation stopping mechanism is a pin-slot type axial embedding mechanism consisting of an axial groove or a section notch on the sliding end surface of the stop ring, an axial through hole on the stop reference end surface of the separation ring and a rotation stopping pin;

(b) the separating ring limiting mechanism is a pin-slot type limiting mechanism consisting of an axial pin hole in a toothless end face of the separating ring, an axial through hole in a separating reference end face of the first joint element and limiting pins embedded into the two holes;

(c) the operation objects of the positioning control mechanism are a locking pin of the separating ring positioning locking mechanism and a rotation stopping pin of the stop ring rotation stopping mechanism, namely, the purpose of controlling the axial positions of the two pins is achieved by means of two types of mechanical motions of axial displacement or circumferential rotation.

9. The overrunning clutch according to any one of claims 1 to 7, wherein: the stop ring in the fitting state can be relatively static on the reference end surface or the reference cylindrical surface of the stop reference ring through constraint.

10. The overrunning clutch according to any one of claims 1 to 7, wherein: the overrunning clutch is integrally packaged in a shell, the shell consists of a shaft sleeve, a shell and an annular end cover, a characteristic curved surface capable of transmitting torque is formed on an inner hole surface of the shaft sleeve, an outer cylindrical surface and an inner hole surface of a first joint element are circumferentially fixed or directly and rigidly manufactured into a whole, the shell is an annular sleeve with an annular disc end socket, the characteristic curved surface capable of transmitting torque is formed on the outer surface of the shell, the inner hole surface and the outer cylindrical surface of a second joint element are circumferentially fixed in a spline connection mode, the outer end of the shell is sleeved on the shaft sleeve or the first joint element through the outer end of the first joint element, the annular end cover is sleeved on the shaft sleeve through the outer end of a spring, and the annular end cover has the function of a spring seat and is fixedly connected on.

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