WO1994008139A1

WO1994008139A1 - Hydraulic pump/motor

Info

Publication number: WO1994008139A1
Application number: PCT/JP1993/001413
Authority: WO
Inventors: Toshio Okamura
Original assignee: Toshio Okamura
Priority date: 1992-09-29
Filing date: 1993-09-29
Publication date: 1994-04-14
Also published as: JPH06108981A

Abstract

A hydraulic pump/motor as a hydraulic pump or hydraulic motor having a rotating type rotor characterized in that a rotor accommodating chamber having a circular cross section is formed in a housing, that a rotor is accommodated in said rotor accommodating chamber, that a fluid operation chamber is formed outside said rotor in said rotor accommodating chamber and a shaft member adapted to rotate integrally with said rotor extends outwardly of said housing. A pressure receiving projection is integrally formed on the rotor, and a sealing portion is formed on this pressure receiving projection, the sealing portion being adapted to be brought into sliding contact with the inner circumferential surface of the rotor accommodating chamber in a surface contacting fashion. A vane mechanism is provided in the housing in which a movable partition member is biassed toward the rotor by means of a spring, and furthermore in the housing a supply port and an exit port are formed in positions on the sides of the vane mechanism. A pair of vane mechanisms may be provided in the housing, a plurality of pressure receiving projections may be provided on the rotor, and the movable partition member of each vane mechanism may be constituted by a plurality of members. Moreover, a plurality of the afore-mentioned hydraulic pumps/motors may be arranged in series to form a unit, and a common shaft member may be provided for the plurality of hydraulic pumps/motors.

Description

Description Fluid pressure pump Z motor Technical field

The present invention relates to a fluid pressure pump or a fluid pressure pump motor as a fluid pressure motor, and in particular, forms a pressure receiving projection that partitions a fluid working chamber on an outer peripheral portion of a rotor housed in a rotor housing chamber of a housing; And a fluid pump z motor provided with a vane mechanism for partitioning a fluid working chamber. Background art

2. Description of the Related Art Conventionally, positive displacement fluid pressure pump motors having various complicated structures have been put to practical use. Displacement type hydraulic pump motor with rotating rotor Although the structure is relatively simple, a vane pump / motor with multiple vanes mounted on the rotor and multiple retractable partition members mounted on the rotor In such a slit pump / motor, the structure of the π-motor and its attached mechanism is complicated.

Here, the rotary rotor type motor / compressor described in Japanese Patent Application Laid-Open No. HEI 4-1496 is a compressor incorporating an electric motor. In this compressor, a rotor housing chamber having a circular cross section is provided in a housing. The stator of the induction motor (smaller than the inner diameter of the rotor), in which a cylindrical rotor having a smaller diameter is mounted in the rotor accommodating chamber and a plurality of induction coils are mounted in the rotor. A part of the inner peripheral surface of the rotor is attracted by the magnetized coil of the stator and contacts the stator, and a part of the outer peripheral surface of the rotor is the inner peripheral surface of the rotor housing chamber. And a fluid working chamber is formed outside the rotor in the rotor housing chamber, and a vane mechanism for partitioning the fluid working chamber is provided in the housing, and on both sides of the vane mechanism of the housing. A supply port and an outlet port are formed. When the power supply to the induction coil is switched to a predetermined rotation direction, the rotor rotates around the stator while maintaining the state of being sucked by the stator, and pressurizes the air sucked from the supply port in the fluid working chamber. Discharge to the exit boat. In the conception process of the present invention, the inventor of the present application came up with a fluid pump motor 200 as shown in FIG.

In this fluid pressure pump motor 200, a rotor housing chamber 202 having a circular cross section is formed in a housing 201, and a cylindrical body eccentric with respect to its axis is formed in the rotor housing chamber 202. The rotor 203 is rotatably housed integrally with the shaft member 204, and a part of the outer peripheral surface of the rotor 203 is slidably contacted with the inner peripheral surface of the rotor housing chamber 202, and A fluid working chamber 205 is formed outside the rotor 203 of the rotor housing chamber 202, and a vane mechanism 206 that partitions the fluid working chamber 205 is formed in the housing 201. The vane mechanism 206 mounts a movable partition member 208 in a mounting hole 207 formed in the housing 201 such that the movable partition member 208 can move forward and backward with respect to the rotor accommodating chamber 202. The partition member 208 is elastically urged toward the rotor accommodating chamber 202 by a spring 209, and the supply port 210 exits on both sides of the vane mechanism 206. Port one DOO 2 1 丄 and are formed.

When the fluid pressure pump / motor 200 is used as a fluid pressure motor, when fluid pressure is supplied from the supply port 210 to the first working chamber 205a, the first working chamber 205a The fluid pressure acts on the rotor 203, the fluid in the second working chamber 205b is discharged from the outlet port 211, and the rotor 203 is driven to rotate clockwise. When the fluid pressure pump motor 200 is used as a fluid pressure pump, the shaft member 204 is driven to rotate clockwise by an electric motor or the like (not shown), and the shaft member 204 is moved from the supply port 210 to the first port. When the fluid is sucked into the working chamber 205a, the rotation of the rotor 203 pressurizes the fluid in the second working chamber 205b and is discharged from the outlet port 211. The conventional displacement-type various fluid pressure pump motors, including those described in the above-mentioned publications, have a problem that the structure is complicated and the production cost is high. In the fluid pressure pump motor shown in FIG. 24 or the rotary compressor described in Japanese Patent Publication No. 1115714, the outer peripheral surface of the rotor and the inner peripheral surface of the rotor chamber are in line contact. Because of this, there are problems such as easy wear and lack of durability, and the inability to increase the supplied fluid pressure and discharge pressure.

Furthermore, since the rotor is eccentric with respect to the center of the rotor chamber, the rotation angle range where the pressure receiving area of the rotor receives the maximum is narrow, and the rotation angle range where the maximum torque and the maximum discharge amount are output is narrow. In other words, there is a problem that the size of the fluid pressure pump Z motor increases.

An object of the present invention is to make it possible to simplify the structure of a fluid pump motor having a rotor, to reduce the wear of a rotary rotor to increase its durability, and to increase the supply fluid pressure and discharge fluid pressure. In other words, it is necessary to increase the rotation angle range for outputting the maximum torque and the maximum discharge amount to increase the capacity, that is, to reduce the size. Disclosure of the invention

A fluid pressure pump / motor according to the present invention includes: a housing; a rotor housing chamber having a circular cross-section formed in the housing; a rotor housed in the rotor housing chamber so as to be rotatable around its shaft; A fluid working chamber formed in a portion outside of the rotor, and a shaft member connected to the rotor and extending out of the housing.

A pressure receiving projection formed on the rotor and projecting to an inner peripheral surface of the rotor accommodating chamber so as to partition the fluid working chamber;

A seal portion formed at an outer peripheral end portion of the pressure receiving protrusion portion and slidably contacting an inner peripheral surface of the rotor receiving hole in a surface contact manner and in a sealable manner;

A mounting hole formed in the housing; and a movable hole which is mounted to the mounting hole so as to be able to move forward and backward with respect to the rotor accommodating chamber, and whose inner end is slidably contacted with the outer peripheral surface of the rotor so as to partition the floating operation chamber. A partition member, and a biasing hand for biasing the movable partition member toward the rotor A vane mechanism having a step and

The housing includes a supply port and an outlet port formed near the leading side and the trailing side of the movable partition member of the vane mechanism in the rotor rotation direction, respectively.

In the fluid pressure pump motor according to the present invention, a fluid working chamber is formed on the outer peripheral side of the rotor in the rotor housing chamber, and the fluid working chamber includes a pressure receiving projection of the rotor and a movable partition member of the vane mechanism. And is divided into a supply-side fluid working chamber portion communicating with the supply port and an outlet-side fluid working chamber portion communicating with the outlet port.

When used as a fluid pressure motor, when fluid pressure is supplied from the supply port to the supply-side fluid working chamber, the fluid pressure of the supply-side fluid working chamber acts on one side of the pressure receiving projection of the rotor. In addition, the discharge pressure (drain pressure in the case of a hydraulic motor, and atmospheric pressure in the case of an air motor) acts on the other side of the pressure receiving projection of the rotor. It is driven to rotate by the pressure difference. When the pressure receiving protrusion of the rotor approaches the vane mechanism, the movable partition member retreats and the rotor passes through the vane mechanism, and the pressure receiving protrusion of the rotor returns to the supply-side fluid working chamber portion of the supply side. Due to the fluid pressure acting, the rotor will continue to rotate.

When used as a fluid pressurizing pump, when the shaft member is rotationally driven by a rotary driving means such as an external electric motor, fluid is sucked from the supply port into the supply-side fluid chamber by the rotating rotor, and the rotor is turned into a vane. Each time the fluid passes through the mechanism, the supply fluid working chamber is switched to the outlet fluid working chamber, and the fluid in the outlet fluid working chamber is pressurized by the rotor and discharged from the outlet port. Become. Thus, the suction of the fluid into the supply-side fluid working chamber and the discharge from the outlet-side fluid working chamber are performed in parallel.

In this simple-structure positive displacement hydraulic pump / motor, the rotor has at least one pressure receiving projection projecting to the inner peripheral surface of the rotor housing chamber so as to partition the fluid working chamber. Can be formed on a relatively narrow range of pressure receiving protrusions on the outer periphery In this case, since the rotor rotation angle range at which the maximum torque or the maximum discharge amount is obtained can be increased, the capacity of the hydraulic pump motor can be increased, that is, the size can be reduced.

Further, since a seal portion is formed at the outer peripheral end of the pressure receiving protrusion so as to be in sliding contact with the inner peripheral surface of the rotor accommodating chamber so as to be able to seal, the wear resistance of the seal portion is enhanced and its durability is improved. The efficiency of the fluid pressure pump motor can be increased by improving the sealing performance of the seal portion at the same time, and the supply fluid pressure and the discharge fluid pressure can be increased. BRIEF DESCRIPTION OF THE FIGURES

FIG. 1 is a cross-sectional view of a hydraulic pump motor according to an embodiment of the present invention. FIG. 2 is a side view of the hydraulic pump motor of FIG.

Fig. 3 is a vertical cross-sectional view (cross-sectional view taken along the line 3-3 in Fig. 1) of the hydraulic pump Z motor in Fig. 1.

FIG. 4 is a hydraulic circuit diagram for the hydraulic motor of the hydraulic pump / motor of FIG. 1, FIG. 5 is a hydraulic circuit diagram of the hydraulic pump of the hydraulic pump motor of FIG. 1, and FIG. It is a cross-sectional view of the fluid pressure pump of the first alternative embodiment,

FIG. 7 is a longitudinal sectional view (sectional view taken along line 7-7 in FIG. 6) of the fluid pressure pump / motor shown in FIG.

FIG. 8 is a cross-sectional view of a fluid pressure pump motor of a first modified example.

FIG. 9 is a sectional view of a main part of the fluid pressure pump motor shown in FIG.

FIG. 10 is a sectional view of a main part of the fluid pressure pump / motor of FIG. 8,

FIG. 11 is a cross-sectional view of a fluid pressure pump Z motor according to a second modification,

FIG. 12 is a hydraulic circuit diagram of the hydraulic pump / motor of the hydraulic pump / motor of FIG. 11; FIG. 13 is a hydraulic circuit diagram of the hydraulic pump / motor of the hydraulic pump / motor of FIG. 11; FIG. 14 is a cross-sectional view of a fluid pressure pump motor of a third modified example,

FIG. 15 is a cross-sectional view of the hydraulic pump Z motor unit of the second alternative embodiment, and FIG. 16 is a vertical cross-sectional view of the unit of FIG. 15 (line 16—16 in FIG. 15). Cross section) FIG. 17 is a hydraulic circuit diagram for the hydraulic motor of the unit of FIG. 15;

FIG. 18 is a hydraulic circuit diagram for the hydraulic motor of the unit of FIG. 15;

FIG. 19 is a partial view of a modification of the unit of FIG. 15 corresponding to FIG.

FIG. 20 is a hydraulic circuit diagram for the hydraulic pump of the unit of FIG. 15;

FIG. 21 is a hydraulic circuit diagram for the hydraulic pump of the unit of FIG. 15;

FIG. 22 is a hydraulic circuit diagram of a hydraulic pump Z motor unit of a third alternative embodiment, and FIG. 23 is a hydraulic circuit diagram of a hydraulic pump pump motor unit of a fourth alternative embodiment. FIG. 24 is a longitudinal sectional view of a fluid pressure pump motor according to the prior art. BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

First, the first embodiment will be described.

As shown in FIGS. 1 to 3, the fluid pressure motor M includes a housing 1, a σ-motor 2, an output shaft 3, a vane mechanism 4, and the like.

The housing 1 includes a housing main body 10 having a cylindrical rotor housing hole 5a therein, a first end plate 11 for closing a right end side of the housing main body 10, and a left end side of the housing main body 10 for closing the left end side. The housing 1 is formed with a second end plate 12 and the like, and a rotor housing chamber 5 is formed in the housing 1 in which both ends of the rotor housing hole 5a are closed by the first and second end plates 11 and 12. . The housing 1 and the rotor 2 are made of a material such as iron, steel, stainless steel, aluminum, aluminum alloy, synthetic resin, FRP (fiber reinforced synthetic resin), or high-strength ceramic. Can also be configured.

The rotor 2 has a cylindrical rotor body 20 and a pressure receiving projection 21 integrally formed on the rotor body 20 so as to protrude outside the outer periphery of the rotor body 20. 1 is formed in parallel with the axis X of the rotor housing 5 and the same length as the rotor main body 20, and the tip of the pressure receiving projection 21 comes into surface contact with the inner peripheral surface of the rotor housing 5. And sea A seal portion 22 is formed so as to be slidably contactable with each other. On both sides of the seal portion 22, a gentle curved surface gradually increasing in diameter from the outer peripheral surface of the rotor body 20 toward the seal portion 22. 23 and 23 are formed symmetrically with respect to the seal portion 22. Since the seal portion 22 is formed to have a predetermined width (for example, a width of about 5 to 20 mm) in the circumferential direction, it has excellent sealing properties. The right end surface 24 of the rotor 2 is in sliding contact with the first end plate 11, and the left end surface 25 of the mouth 2 is in sliding contact with the second end plate 12 with a small gap or little gap. It is formed as follows.

The output shaft 3 is for taking out the rotation of the rotor 2 to the outside of the housing 1. The output shaft 3 is disposed concentrically with the axis X of the rotor housing chamber 5. It extends outside the housing 1 through the shaft hole in the center of the stator 2 and the holes in the first and second end plates 11 and 12, and the output shaft 3 is connected to the rotor 2 via a key. The output shaft 3 supporting the rotor 2 is fixed to the first and second end plates 11 and 12 via bearings 32 and 33 so as to be rotatable at both ends.

Reference numerals 14 and 15 denote bolts for fixing the first and second end plates 11 and 12 to the housing body 0, reference numeral 13 denotes a holding plate (this can be omitted), and reference numeral 16 Is a bolt for fixing the holding plate 13 to the housing body 10.

To explain the vane mechanism 4, a slit-shaped mounting hole 40 parallel to the axis X of the rotor housing chamber 5 is formed in the housing main body 10 at one side of the housing main body 10. A movable partition member 41 is slidably mounted in the mounting hole 40, and the movable partition member 41 is provided with three compression members mounted between the movable partition member 41 and the spring receiving member 42. The coil spring 43 elastically urges toward the rotor accommodating chamber 5, so that the seal portion 41s at the tip of the movable partition member 41 is always in sliding contact with the outer peripheral surface of the rotor 2 so as to be able to seal. is there. The seal part 41 s has a width of at least about 2 to 3 mm in the circumferential direction, and is in sliding contact with the outer peripheral surface of the rotor 2 in a face-to-face manner to prevent passage of the fluid.

The movable partition member 41 is made of a metal material having low friction and excellent wear resistance (for example, Or brass, copper-lead alloy, aluminum alloy, etc.), but may be made of a synthetic resin material with high strength and rigidity, or a material such as FRP (textile reinforced synthetic resin) or ceramic. The movable partition member 41 slides on the inner surface of the mounting hole 40 so as to be substantially sealable with a small gap. However, if necessary, the inner surface of the mounting hole 40 is hardened (nitriding, carburizing, etc.) or a small gap between the inner surface of the mounting hole 40 and the movable partition member 41 is supplied. Providing suitable lubrication means also improves the sealing performance.

The spring receiving member 42 is fixed to the housing main body 10 with a gasket 46 (which can be omitted) by, for example, six bolts 44. Pressurized air of a predetermined pressure is supplied to the spring accommodating chamber 47 between the movable partition member 41 and the spring receiving member 42, and the movable partition member 41 is compressed by the compressed air and three compression coil springs 43. The movable partition member 41 may be configured to be elastically urged, or may be configured to elastically urge the movable partition member 41 only by pressurized air.

The housing main body 10 has a first passage 6 opened on the right end surface thereof formed above the mounting hole 40.The housing main body 10 has a second passage 7 opened on the right end surface thereof. One or a plurality of first ports 6a formed below the hole 40 and branched from the first passage 6 are opened to the rotor housing chamber 5 at a position near the upper side of the movable partition member 41, and the second passage 7 One or a plurality of second boats 7a branched from the opening are opened to the rotor housing chamber 5 near the lower side of the movable partition member 41.

The operation of the fluid pressure motor M will be described.

In the rotor housing chamber 5, a working chamber 50 formed outside the rotor 2 is divided into a first working chamber 51 and a second working chamber 52 by a movable partition member 41, and When the rotor 2 rotates, the movable partition member 41 advances and retreats while sliding the seal portion 41 s at the tip of the movable partition member 41 against the outer peripheral surface of the rotor 2, so that the rotor 2 is rotatable. When a hydraulic or pressurized air is supplied to the first passage 6 and the second passage 7 is released to an oil tank or the atmosphere, the fluid pressure is supplied from the first port 6a to the first working chamber 51, 1 Fluid pressure in the working chamber 51 acts on the pressure receiving projection 21 of the rotor 2. Second working chamber 5 2 Since the pressure of the fluid inside is the drain pressure or the atmospheric pressure, the rotor 2 has a pressure difference between the fluid pressure of the first working chamber 51 and the drain pressure or the atmospheric pressure of the second working chamber 52, and the pressure receiving protrusion 2 The torque equal to the product of the cross-sectional area of the rectangular shape of 1 and the distance from the axis X of the rotor 2 (the center X of the rotor chamber 5) to the pressure receiving center of the pressure receiving protrusion 21 acts on the rotor 2. Rotate in the direction of arrow A. However, when the movable partition member 41 is in contact with the curved surface 23 on the trailing side in the rotor rotation direction of the pressure receiving projection 21, the torque is somewhat reduced because the pressure receiving area is small.

The supply of the fluid pressure causes the first working chamber 51 to expand, and the discharge of the fluid causes the second working chamber 52 to shrink while the rotor 2 rotates, and the seal portion 22 to move the movable partition member 4. When approaching 1 and passing through the second port 7a, the first working chamber 51 communicates with the second port Ίa, but the rotor 2 continues to rotate by inertia and the movable partition member 4 When the seal portion 22 of the rotor 2 passes through the movable partition member 41 and the first port 6a, the fluid pressure of the first working chamber 51 acts on the pressure receiving projection 21 of the rotor 2, and By repeating in the same manner as described above, the rotor 2 rotates continuously and smoothly.

On the other hand, when the fluid pressure is supplied to the second passage 7 and the first passage 6 is released to the oil tank or the atmosphere, the first working chamber 51 has the drain pressure or the atmospheric pressure, 2 Since fluid pressure is supplied to the working chamber 52, the rotor 2 rotates in the direction of arrow B. In other words, the first port 6a or the second port 7a on the leading side in the rotation direction of the rotor 2 with respect to the movable partition member 41 becomes a supply port for supplying fluid pressure, and the rotation of the rotor 2 The second port Ίa or the first port 6a on the directional trailing side is the outlet port for discharging fluid.

Since the seal portion 22 of the pressure receiving projection 21 is in sliding contact with the inner peripheral surface of the rotor housing chamber 5 in a surface-contact manner, the seal portion 22 has excellent sealing properties, and the seal portion 22 is hardly worn and has durability. Is improved.

Since the pressure receiving projection 21 is formed to have a narrow width covering about 1/4 of the outer peripheral portion of the rotor 2, the sealing portion 22 of the rotor 2 passes through the supply ports (6a, 7a). . Since the pressure receiving area is maximized early, the output torque is maximized early.

However, by changing the curvature of the curved surfaces 23 on both sides of the pressure receiving projection 21, the pressure receiving projection 21 is formed as follows. It can be formed in about 1/3 of the outer circumference of the motor 2 or in a range of about 1 / 2.In this case, the rate of increase of the radius from the axis of the curved surface 23 is smaller, and The resistance acting on the rotor 2 from the partition member 41 is reduced, and the forward / backward responsiveness of the movable partition member 41 is improved.

The urging force for elastically urging the movable partition member 41 toward the rotor storage chamber 5 is greater than the force of the movable partition member 41 being pushed outward by the fluid pressure acting on the movable partition member 41. The movable partition member 41 needs to have strength and rigidity so as not to be deformed by a fluid pressure acting on the movable partition member 41.

When the hydraulic motor M is a hydraulic motor, the hydraulic circuit is as shown in FIG. 4, and the hydraulic tank 53, the hydraulic pump 54, and the electromagnetic directional valve 55 supply the hydraulic pressure to the first port 6a. Then, the rotor 2 rotates clockwise. Conversely, when hydraulic pressure is supplied to the second port 7a, the rotor 2 rotates counterclockwise.

Here, when the fluid pressure motor M is used as the fluid pressure pump P, an electric motor or an air motor for rotating the output 轴 3 is connected to the output 轴 3, and the output shaft 3 is driven 轴 (3) When the drive shaft (3) is driven to rotate in the direction of arrow A in FIG. 3, the fluid before pressurization is sucked from the first port 6a through the first passage 6, and The fluid pressure discharged from the 2 port 7a is supplied to the outside from the second passage 7. That is, the fluid sucked into the first working chamber 51 moves to the second working chamber 52 via the rotation of the rotor 2, and the fluid in the second working chamber 52 is added by the rotation of the rotor 2. Pressurized and discharged to the second port 7a.

The hydraulic circuit when the fluid pressurizing pump P is a hydraulic pump is as shown in FIG. 5, in which the electric motor 56 drives the drive shaft (3) to rotate, and the oil in the oil tank 57 is supplied to the first passage. After passing through 6, the fluid is sucked into the first port 6a, and the pressurized fluid is discharged to the second port Ίa and supplied to the outside from the second passage 7. Next, an embodiment in which the above-described embodiment is partially modified will be briefly described with reference to FIGS.

In this fluid pressure motor MA, the housing 1A is welded to the housing main body 60 made of a cylindrical member, the first end plate 61, the second end plate 62, and the side of the housing main body 60. It is composed of a block member 63 and the like fixed at.

In the housing 1A, a port storage chamber 5A similar to the rotor storage chamber 5 is formed, and a rotor 2A is stored in the rotor storage chamber 5A.

The rotor 2A is the same as the rotor 2 and includes a rotor body 64 and a pressure receiving protrusion 65 integrally formed therewith. A sealing portion 66 is provided at the tip of the pressure receiving protrusion 65. Curved surfaces 67, 67 are formed on both sides of the seal portion 66. An annular seal groove 78 is formed on each of the left and right end surfaces of the rotor 2A, and an annular seal member 79 is mounted in these seal grooves 78. Reference numerals 68 and 69 denote bolts and nuts connecting the first end plate 61 and the second end plate 62 with the housing body 60 interposed therebetween, and reference numeral 32A denotes a bearing.

The output shaft 3A is similar to the output shaft 3 and extends outside the housing 1A through the first end plate 61, the rotor 2A, and the second end plate 62, and is opposed to the rotor 2A. It is fixed so that it cannot rotate.

To explain the vane mechanism 4A, a mounting hole 70 is formed in the housing body 60 and the block member 63, and the first movable partition member 72 and the second movable partition member 73 are formed in the mounting hole 70. The movable partition member 7 comprises a spring receiving member 7 4 fixed to the outer surface of the block member 6 3 with a plurality of bolts 75, and a first movable partition member 7. 2 is urged toward the rotor housing chamber 5 A by three compression coil springs 76, and the second movable partition member 73 is moved toward the rotor housing chamber 5 A by three compression coil springs 77. Being energized. Reference numeral 73a denotes a cutout portion formed in the second movable partition member 73 to apply the force of the spring 76 to the first movable partition member 72, and reference numeral 72a denotes Apply the force of the spring 7 7 to the second movable partition member 7 3 The notch formed in the first movable partition member 72 to be added is shown. However, the notches 72a and 73a may be omitted as necessary.

In the block member 63, a first passage 6A and a second passage 7A having an oval cross section are formed in the same manner as in the previous embodiment, and a first port 6b communicating with the first passage 6A, A second port Ίb communicating with the second passage 7A is formed in the housing 1A.

The operation of the fluid pressure monitor MA is the same as that of the fluid pressure motor M, except that the movable partition member Ί1 is composed of a first movable partition member 72 and a second movable partition member 73, The movable seal member 7 2 s at the front end of the movable partition member 72 and the seal portion 73 s at the front end of the second movable partition member 73 are in sliding contact with the outer peripheral surface of the rotor 2 A. The contact portion between the partition member 71 and the rotor 2A is double-sealed, and the sealing performance is improved, making it suitable for a hydraulic motor or the like that supplies a relatively high fluid pressure. Since the annular seal members 67 are mounted on the left and right end surfaces of the rotor 2A, it is suitable for a hydraulic motor such as a hydraulic motor that supplies a relatively high fluid pressure. The fluid pressure motor M A of this embodiment can also be applied as a fluid pressure pump similarly to the fluid pressure motor M.

Here, a description will be given of a modified example in which the configuration of the fluid pressure motor MA of the embodiment is partially changed. However, the same components are denoted by the same reference numerals and description thereof is omitted.

As shown in the fluid pressure motor MA 1 of FIGS. 8 to 10, a seal 80 at the tip of the pressure receiving projection 65A of the rotor 2B is formed in the circumferential direction to have a wide width of, for example, about 10 mm or more. On both sides of the rotor portion 80, curved surfaces 8 1, 81 which gradually increase in diameter from the peripheral surface of the rotor body 64 and reach the seal portion 80 are formed, and the shaft of the rotor 2B is formed on the seal portion 80. A seal groove 82 oriented in the direction of the center is formed, and the seal groove 82 is made of synthetic rubber or synthetic resin (eg, nylon, etc.) or metal (eg, iron, brass, copper lead alloy, aluminum alloy, etc.). The seal member 83 is attached, and the seal member 83 is in surface contact with the inner peripheral surface of the rotor housing chamber 5A.

A communication hole communicating from the curved surfaces 8 1, 8 1 to the bottom of the seal groove 82 is formed. It is also possible to employ a configuration in which the member 83 is urged by fluid pressure.

An annular seal groove 78 is formed on each of the left and right end surfaces of the rotor 2A, and an annular seal member 79 is attached to the seal groove 78. The sealing member 85 is also mounted on the sealing groove 85 extending to the sealing groove 82. The seal members 79 and 86 may be made of synthetic rubber, synthetic resin (for example, nylon, etc.) or metal, or may be a composite seal member including a plurality of parts. With the above configuration, the sealing performance can be improved.

In a fluid pressure motor MA2 shown in FIG. 11, a first vane mechanism 4A and a second vane mechanism 4B are provided in a housing 1A so as to be rotationally symmetric with respect to an axis X of a rotor accommodating chamber 5A. The first boat 6b and the second port 7b are formed on the upper and lower sides of the first vane mechanism 4A, and the second port 7b and the first port are formed on the upper and lower sides of the second vane mechanism 4B. Port 6b is formed. Further, the rotor 2C is formed with two pressure receiving portions 65, 65 every 180 degrees in the circumferential direction in a rotationally symmetric manner with respect to the axis X thereof.

When the fluid pressure is supplied to the two first ports 6b, 6b and the two second ports 7, 7b are released to the oil tank or the atmosphere, the rotor 2C rotates in the direction of arrow A, and When fluid pressure is supplied to the two second boats 7b, 7b and the two first ports 6b, 6b are released to the oil tank or the atmosphere, the rotor 2C moves in the direction opposite to the arrow A. It will rotate.

In the fluid pressure motor MA2, since the fluid pressure acts on the two pressure receiving protrusions 65, the output torque force is about twice as large as that of the fluid pressure motor MA1, so the fluid pressure motor is downsized. it can. However, if the two pressure receiving parts 65, 65 contact the vane mechanism 4A, 4B at the same time, the output torque will decrease a little, so the two pressure receiving parts 65, 65 will be 4A, 4B, the force to provide the vane mechanism 4A, 4B non-rotationally symmetric with respect to the center X, or the two pressure receiving portions 65, 65 with respect to the axis X. It may be formed non-rotationally symmetric.

The hydraulic circuit when using the hydraulic motor MA 2 in Fig. 11 as a hydraulic motor is As shown in Fig.12. Reference numeral 90 denotes an oil tank, 91 denotes a hydraulic pump, and 92 denotes an electromagnetic directional control valve.

The hydraulic circuit when the fluid pressure motor MA2 in FIG. 11 is used as the hydraulic pump MA2P is as shown in FIG. Reference numeral 93 denotes an electric motor that rotationally drives the drive shaft 3A, and reference numeral 94 denotes an oil tank.

In the fluid pressure motor MA3 shown in FIG. 14, instead of the rotor 2C of the fluid pressure motor MA2 shown in FIG. 11, three pressure receiving protrusions are provided on the outer periphery of the rotor 2D every 120 degrees. 65, 65, 65 are formed. The operation of the fluid pressure motor M A3 is the same as that of the fluid pressure motor MA 2. However, since each of the three pressure receiving protrusions 65, 65, 65 comes into contact with the vane mechanism 4A, 4B, the torque fluctuation force is reduced. Then, the efficiency of the fluid pressure motor M A3 increases.

In the case of a relatively large hydraulic motor or hydraulic pump, three or more vane mechanisms and first and second ports corresponding to each vane mechanism are provided, and four or more The pressure receiving projection 65 may be formed.

Next, a fluid pressure motor unit MU in which three fluid pressure motors M 1, 2, and M 3 similar to the fluid pressure motor M are integrally incorporated will be described with reference to FIGS. 15 and 16.

The housing of the first fluid pressure motor Ml includes a first end plate 101, a housing main body 104A, and an intermediate plate 102A, and a cylindrical rotor housing chamber 105 in this housing. A is formed, and the rotor accommodating chamber 105A accommodates a rotor 106A similar to the rotor 2 described above, and a vane mechanism 107A is provided on the side of the housing body 104A. A mounting hole 109 A for mounting the movable partition member 108 A of the vane mechanism 107 A is formed in the housing body 104 A, and the first end plate 101 and the intermediate plate 1 are formed. The movable partition member 108A is slidably mounted in the mounting hole 109A, and the spring 110 is moved toward the rotor accommodating chamber 105A. Being energized. The panel receiving plate 1 1 1 is fixed to the housing main body 104 A with bolts 1 12. The housing of the second fluid pressure motor M2 includes the intermediate plate 102A, a housing body 104B having the same structure as the housing body 104A, and an intermediate plate 102B. Have been.

Other structures are the same as those of the first fluid pressure motor M1, so that the rotor housing chamber 105A, the rotor 106B, the vane mechanism 107B, the mounting hole 109B, the movable partition member 1 Description of 08B is omitted.

The housing of the third fluid pressure motor M3 is composed of the intermediate plate 102B, a housing body 104 having the same structure as the housing body 104A, and a second end plate 103. Has been established. Other structures are the same as those of the first fluid pressure motor Ml, so the rotor storage chamber 105C, rotor 106C, vane mechanism 107C, mounting hole 109C, OK The description of the moving partition member 108C is omitted.

An output shaft 113 common to the three fluid pressure motors M 1, M 2, and M 3 includes a first end plate 101, a rotor 106 A, an intermediate plate 102 A, and a rotor 1. 06 B, the intermediate plate 102 B, the rotor 106 C, and the second end plate 103, and extends to the outside of the second end plate 103. The end plates 101, 103 and the two intermediate plates 102A, 102B are rotatably supported via bearings 114, respectively, and the output shaft 113 is connected to the rotor 106A. , 106 B, and 106 C are connected to each other so that they cannot rotate relative to each other. The first end plate 101, a housing body 104A, an intermediate plate 102A, a housing body 104B, an intermediate plate 102B, a housing body 104C, Four bolt holes 1 15 are penetrated through the second end plate 103 in a communicating manner, and three sets of housings are formed by through bolts 1 16 inserted through these four bolt holes 1 15 respectively. It is fixed integrally. An example of a fluid passage formed in a housing when the three fluid pressure motors M 1, M 2, and M 3 are driven in series will be described.

The housing main body 104A, 104B, 104C has a first passage 12OA, 12OB, 120C located above the vane mechanism and a vane mechanism. Second passages 12 A, 12 B, and 12 C located on the lower side are formed. 1st end plate 1 0 1 shaped The formed vertical hole 122 communicates with the first passageway 12OA, and the vertical hole 123A formed in the intermediate plate 102A communicates with the second passageway 122A and the first passageway 122A. The vertical hole 123B formed in the intermediate plate 102B communicates with the passage 120B, and communicates with the second passage 122B and the first passage 120C. The vertical hole 122 formed in the end plate 103 communicates with the second passage 122C.

In the housing body 104 A, 104 B, 104 C, the first passage 120 A, 120 B, 120 C is provided with a movable partition member 108 A, 108 B, 108 In the vicinity of the upper side of C, the first ports 125 A, 125 B, 125 C communicating with the rotor accommodating chambers 105 A, 105 B, 105 C, and the second passages 12 A, 1 A 2nd B, 121C is connected to the rotor housing chambers 105A, 105B, 105C in the vicinity of the lower side of the movable partition member 108A, 108B, 108C. Ports 126 A, 126 B, and 126 C are formed, respectively, powerfully.

When a hydraulic or pressurized pressure is supplied to the vertical hole 122 and the vertical hole 124 is released to the oil tank or the atmosphere, the fluid pressure is increased to a first passage 120 A, a first port 125 A, Working chamber of 1st fluid pressure motor Ml, 2nd port 126A, 2nd passage 1 2 1A, vertical hole 1 2 3A, 1st passage 1 20B, 1st port 125B, 2nd Working chamber of fluid pressure motor M2, 2nd port 1 26B, 2nd passage 1 2 1B, vertical hole 123B, 1st passage 120C, 1st port 125C, 3rd fluid pressure The working chamber of the motor M3, the second port 1 26C, the second passage 1 2 1C, and the vertical hole 1 24 flow in this order.

Accordingly, the fluid pressure that rotationally drives the rotor 106A of the first fluid pressure motor M1 is supplied to the second fluid pressure motor M2, and after rotating the rotor 106B, the third fluid pressure motor After being supplied to M3 and rotating the rotor 106C, it is discharged from the vertical hole 124. In this case, the rotors 106A, 106B, 106C rotate in the direction of arrow A in FIG. However, when the fluid pressure is supplied from the vertical hole 124 and discharged from the vertical hole 122, the flow direction of the fluid pressure is reversed, and the rotor〗 06 A, 106 B, 106 C , Rotate in the opposite direction to arrow A. As described above, the three fluid pressure motors M1, M2, M3 are straightforward! When driven, the output torque of each fluid pressure motor does not increase so much because the pressure difference between the first working chamber and the second working chamber in each fluid pressure motor does not increase so much. Or, the pressure difference between the fluid pressure supplied to the 124 and the drain pressure discharged from the vertical hole 124 or 122 is increased, and the efficiency of utilizing the fluid pressure is improved.

In the fluid pressure motor unit MU, since the three fluid pressure motors Ml, M2, and M3 have the same axial length, the rotor 106A, 106B, 106C having the same structure, and the housing body 104 having the same structure have the same structure. A, 104 B, 104 C, vane mechanism 107 A, 107 B, 107 C of the same structure can be used, and intermediate between the first end plate 101 and the second end plate 103 The plates 102A, 102B can be formed to have substantially the same structure. By changing the number of hydraulic motors to be united using the above-described common parts, hydraulic motor units of various capacities can be configured.

That is, the number of fluid pressure motors incorporated in the fluid pressure motor unit MU may be two or four or more. Also, the axial lengths of the plurality of fluid pressure motors can be made different. In the fluid pressure motor unit MU, by independently forming the fluid passages in the fluid pressure motors M1, 2, and M3, it is possible to drive the individual fluid pressure motors independently. However, even in this case, the rotors 106A, 106B, and 106C rotate integrally.

When a hydraulic circuit that can independently operate each of the fluid pressure motors Ml, M2, and M3 of the fluid pressure motor unit MU is provided, the output torque can be switched to a plurality of steps, and the output shaft rotation speed can be set to a plurality of steps. Switching becomes possible. For example, in a hydraulic motor unit incorporating six hydraulic motors, the output torque can be switched to six stages (torque T1, T2, ··· T6) if the pressure of the supplied hydraulic pressure is constant. In addition, when the flow rate of the supplied fluid pressure is constant, the rotation speed can be switched to six stages (rotation speeds N1, N2, · · · N6).

T KT 2 <· · <T 6, Ν 1> Ν 2> · Ν Ν 6, the output torque Τ And the rotation speed N are (T l, N l), (T 2, N 2) ₍ · · (T 6, N 6). Therefore, with such a fluid pressure motor unit MU, A speed change mechanism can be configured.

The hydraulic motor unit MU is a hydraulic motor unit, and a hydraulic circuit when the hydraulic motor unit is driven in series is as shown in FIG. 17, for example. The hydraulic circuit is provided with an oil tank 130, a hydraulic pump 131, an electromagnetic directional switching valve 132, and the like.

The hydraulic motor unit MU is a hydraulic motor unit, and a hydraulic circuit for driving the hydraulic motor units in parallel is as shown in FIG. 18, for example. The hydraulic circuit includes an oil tank 133, a hydraulic pump 134, a solenoid directional control valve 135, and solenoid on-off valves 13 provided in the passages of the first ports 125A, 125B, and 125C, respectively. 6A, 1 36B, 1 36C, 2nd boat 126A, 1 26B, 126C Solenoid on-off valves 138A, 138B, 138C Solenoid on-off valves 1 37 provided in the passages connecting the first ports 1 25 A, 125 B, 125 C and the second boats 126 A, 126 B, 126 C, respectively A, 137 B, 137 C, etc. are provided.

For example, when driving the first fluid pressure motor M1, the solenoid on-off valves 1336A and 1338A are opened and the solenoid on-off valve 1337A is closed. On the other hand, when the first fluid pressure motor M1 is not driven, the solenoid on-off valves 136A and 138A are closed and the solenoid on-off valve 137A is opened. As a result, the oil in the first fluid pressure motor M1 circulates through the electromagnetic on-off valve 137A, and the rotor 106A enters an idling state. This is the same for the second and third fluid pressure motors M2 and M3. Instead of providing the solenoid on-off valves 13 7 A, 13 7 B, 13 7 C, as shown in Fig. 19, a panel receiving bar 1 17 for receiving the outer end of the spring 110 is provided, The position may be switchable.

Each spring receiving bar 1 17 has, for example, three When the rods of the hydraulic cylinder 118 are connected to drive the fluid pressure motors M1, 2, M3, the hydraulic pump 118 sends the hydraulic pressure to the hydraulic cylinder 118 via the electromagnetic directional control valve 139. When the fluid pressure motors M1, M2, and M3 are not driven, the solenoid directional control valve 1 39 is switched to discharge the hydraulic pressure of the hydraulic cylinder 1 18 and the spring receiving bar 1 With a reversal of 17 forces, the biasing force of the spring 110 does not act on the movable partition members 108 A, 108 B, and 108 C. As a result, the rotors 106A, 106B, 106C are idle.

The fluid pressure motor unit MU is applicable as a fluid pressure pump unit. In this case, the output shaft 113 is configured as a drive shaft (113) that is rotationally driven by an electric motor or an air motor. Assuming that the rotor 106-8 is driven to rotate in the direction of arrow A in FIG. 16, the first boat 125A, 125B, 125C becomes a suction port for sucking the fluid before pressurization. The second ports 126A, 126B, and 126C serve as discharge ports for discharging the pressurized fluid, and the first to third fluid pressure motors M1, M2, and the third to third fluids. The pressure pumps are MlP, M2P, M3P.

The fluid pressure motor unit MU is configured as a hydraulic pump unit MUP, and a hydraulic circuit in a case where the hydraulic pump unit MUP is driven in series is, for example, as shown in FIG. The drive shaft (113) is rotationally driven by an electric motor (142), and the oil supplied from the oil tank (143) is pressurized by the first fluid pressurizing pump (M1P) by the pressure P. Is pressurized by about Δ 加圧 by the second fluid pressurizing pump M 2 P, then pressurized by about ΔP by the third fluid pressurizing pump M 3 P, and thus the pressurized to about 3 ΔP in total. The pressurized fluid is discharged from the third fluid pressurizing pump M 3 P. The hydraulic circuit when the hydraulic pump units M UP are driven in parallel is as shown in FIG. The drive shaft (113) is driven to rotate by an electric motor 144. In the hydraulic circuit, there are oil tanks 144, electromagnetic on-off valves 146A, 16B, 1460, and 1460, which are provided in the passages of ports 1 25A, 125B, and 125C, respectively. 2 ports 1 26 A, 126 B, 126 B Solenoid on-off valves installed in passages of C respectively 1 4 7 A, 1 4 7 B, 147 C, solenoid on-off valves 148 A provided in the passage connecting the first port 125 A, 125 B, 125 C and the second port 126 A, 126 B, 126 C respectively , 148 B, 148 C and so on.

For example, when driving the first fluid pressurizing pump MIP, the solenoid on-off valves 146A and 147A are opened and the solenoid on-off valve 148A is closed. For example, when the first fluid pressurizing pump MIP is not driven, the solenoid on-off valve 146A> 147A is closed and the solenoid on-off valve 148A is opened. Then, the oil in the first fluid pressurizing pump MILP circulates through the electromagnetic on-off valve 148A, and the rotor 106A idles. The same applies to the second fluid pressurizing pump M2P and the third fluid pressurizing pump M3P. In this hydraulic pump unit MUP, the discharge amount of hydraulic pressure can be switched in three stages (discharge amount Q1, Q2, Q3), and the discharge pressure can be switched in three stages (discharge pressure P1, P2, P3). Can be switched. Then, assuming that Q 1> Q2> Q3 and PKP 2 <P 3, the combination of the discharge amount Q and the discharge pressure P is (Q l, P 1) (Q2, P 2), (Q3, P 3) Becomes

Therefore, this hydraulic pump unit MUP is suitable, for example, as a hydraulic pump for driving a hydraulic actuator with various combinations of low load / high speed drive, medium load / medium speed drive, high load / low speed drive. It will be. Instead of providing the electromagnetic direction switching 148A, 148B, 148C, the configuration shown in FIG. 19 can be employed. Next, another embodiment of the fluid pressure motor unit will be described.

As shown in FIG. 22, the air motor Ma and the hydraulic pump MP h are united like the fluid pressure motor unit MU, and the output shaft of the air motor Ma and the drive shaft of the hydraulic pump MP h are integrated.構成 It is composed of the member 150, and the air motor Ma is driven by the pressurized air supplied from the air pump 151, and the oil supplied from the oil tank 152 is pressurized by the hydraulic pump MPh and discharged. I do.

As shown in FIG. 23, the hydraulic motor Mh and the small air pump MPa having a short length in the 轴 direction are unitized in the same manner as the fluid pressure motor unit MU, and the air pump The drive shaft of the MP a and the output shaft of the hydraulic motor M h are constituted by an integral shaft member 15 3, and the hydraulic motor M h is driven by the hydraulic pressure supplied from the hydraulic pump 15 4. In addition to driving the external rotating equipment with the rotational driving force, the air pump MPa is driven with the rotational driving force of the hydraulic motor M h to generate pressurized air, and the pressurizing fan is used as a vane mechanism. The movable partition member 158 is urged toward the rotor 159 by the spring 157 of the spring storage chamber 156 and the pressurized air.

Claims

The scope of the claims

1. A housing, a rotor accommodating chamber having a circular cross section formed in the housing, a rotor accommodated in the rotor accommodating chamber so as to be rotatable around its axis, and a portion of the rotor accommodating chamber outside the rotor. A fluid pressure pump or a fluid pressure motor having a shaft member connected to a rotor and extending out of the housing.

A mounting hole formed in the housing, and a movable partition which is mounted in the mounting hole so as to be able to move back and forth with respect to the rotor accommodating chamber and has an inner end slidably contacting the outer peripheral surface of the rotor so as to partition the fluid working chamber. A vane mechanism comprising: a member; and a biasing means for biasing the movable partition member toward the rotor;

A supply port and an outlet port formed in the vicinity of the rotor rotating direction leading side and the trailing side of the movable partition member of the vane mechanism in the housing;

A fluid pressure pump motor comprising:

2. In the hydraulic pump motor according to claim 1,

A rotor body having a columnar shape concentric with the axis of the rotor housing chamber and the pressure receiving protrusion integrally formed so as to protrude from an outer peripheral surface of the rotor body; On both sides of the seal portion, curved surfaces that increase in diameter from the outer peripheral surface of the rotor body toward the seal portion are formed symmetrically.

A fluid pressure, wherein the rotation direction of the rotor is switchable by switching the supply port to an outlet boat and the outlet port to a supply port. Pump / "motor.

3. The hydraulic pump Z motor according to claim 1,

The movable partition member of the vane mechanism comprises a plurality of movable partition members stacked on each other.

A fluid pump / motor, wherein seal portions are formed at respective inner ends of the plurality of movable partition members so as to slidably contact the outer peripheral surface of the rotor.

4. The fluid pressure pump / motor according to claim 1,

A fluid pump motor, wherein the housing is provided with two vane mechanisms located opposite to each other with the axis of the rotor chamber interposed therebetween, and the rotor is provided with a plurality of pressure receiving projections.

5. In the fluid pressure pump motor according to claim 1,

A fluid, wherein a seal member is mounted in a seal groove formed in a seal portion of the pressure receiving protrusion, and an annular seal member is mounted in an annular seal groove formed on an end surface orthogonal to the axis of the rotor. Pressure pump motor.

6. The fluid pressure pump Z motor according to claim 1, 2, 3, 4, or 5,

A plurality of fluid pressure pump motors are arranged in series in the axial direction, the housings of the plurality of fluid pressure pump motors are connected in a unit shape, and the members of the plurality of fluid pressure pump motors rotate physically. A fluid pressure pump motor, wherein the fluid pressure pump motor is connected in such a way that

7. The fluid pressure pump motor according to claim 6, wherein

A fluid pump pump motor, wherein a plurality of fluid pump Z motors are composed of a common single member.

8. In the fluid pressure pump / motor according to claim 6,

A fluid pump Z motor, comprising a series drive fluid pressure circuit for connecting a plurality of fluid pressure pump motors in series.

9. Fluid pressure pump according to claim 6. Z motor-. A fluid pressure pump motor having a parallel drive fluid pressure circuit for connecting a plurality of fluid pressure pump motors in parallel.

10. The fluid pressure pump Z motor according to claim 9, wherein:

A fluid characterized in that the parallel drive fluid pressure circuit is provided with a switching valve capable of switching between an open position for communicating a supply port and an outlet port of each fluid pressure pump / motor and a closed position for non-communication. Compression pump motor.