CN110374991B - Double-wave-line ball speed reducing bearing with high rotation precision - Google Patents
Double-wave-line ball speed reducing bearing with high rotation precision Download PDFInfo
- Publication number
- CN110374991B CN110374991B CN201910759700.1A CN201910759700A CN110374991B CN 110374991 B CN110374991 B CN 110374991B CN 201910759700 A CN201910759700 A CN 201910759700A CN 110374991 B CN110374991 B CN 110374991B
- Authority
- CN
- China
- Prior art keywords
- groove
- shell
- annular
- ball
- grooves
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 230000001603 reducing effect Effects 0.000 title claims abstract description 11
- 230000007246 mechanism Effects 0.000 claims abstract description 26
- 230000009467 reduction Effects 0.000 claims abstract description 21
- 238000009434 installation Methods 0.000 claims abstract description 15
- 230000005540 biological transmission Effects 0.000 abstract description 22
- 238000005299 abrasion Methods 0.000 abstract description 5
- 238000000465 moulding Methods 0.000 abstract 1
- 230000033001 locomotion Effects 0.000 description 12
- 238000005096 rolling process Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 238000007493 shaping process Methods 0.000 description 3
- 239000003638 chemical reducing agent Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
- F16H2001/323—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear comprising eccentric crankshafts driving or driven by a gearing
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
- Friction Gearing (AREA)
- Retarders (AREA)
Abstract
The invention discloses a double-wave-line ball speed reduction bearing with high rotation precision, which comprises an input shaft, wherein the input shaft comprises a first installation part, an eccentric part and a second installation part which are sequentially connected along the axial direction; a first shell is movably sleeved on the periphery of the first mounting part; the first shell is provided with an annular abdication groove in a molding way, a driving disc is movably sleeved on the periphery of the eccentric part, and the driving disc is positioned in the abdication groove; a ball mechanism is arranged between the inner end surface of the driving disc and the abdication groove; the outer periphery of the second installation part is movably sleeved with a second shell, an inner cycloid groove is formed in the second shell, an outer cycloid groove is formed in the driving disc, the wave number of the inner cycloid groove is larger than that of the outer cycloid groove, and a plurality of first balls are distributed between the inner cycloid groove and the outer cycloid groove; the invention aims to provide the double-wave-line ball speed reducing bearing which can improve the speed reducing ratio, reduce abrasion loss, has small error and transmission ratio error and has multiple output modes and high rotation precision.
Description
Technical Field
The invention relates to the field of speed reduction bearings, in particular to a double-wave-line ball speed reduction bearing with high rotation precision.
Background
In the production process of mechanical equipment, the rotation speed ratio of two stages is required to be adjusted through a speed reducer, and the high-speed rotation of the upper-stage equipment is reduced, so that larger torque is obtained. The existing speed reducing bearing generally adopts a gear meshing mode for transmission, and the speed reducing effect is realized through tooth difference generated between gears. Along with the improvement of degree of automation, in same production line, often need use a plurality of antifriction bearings, and adopt gear engagement's antifriction bearing, in the transmission in-process, sliding friction between gear and the gear can cause very big mechanical loss, when the antifriction bearing of a certain link breaks down, influences the production efficiency of whole production line easily.
Disclosure of Invention
The invention aims to provide the double-wave-line ball speed reduction bearing which can improve the speed reduction ratio, reduce abrasion loss, has small error and transmission ratio error, and has multiple output modes and high rotation precision.
To achieve the purpose, the invention adopts the following technical scheme: the dual-line ball speed reduction bearing with high rotation precision comprises an input shaft, wherein the input shaft comprises a first installation part, an eccentric part and a second installation part which are sequentially connected along the axial direction; the periphery of the first installation part is movably sleeved with a first shell, and one end, close to the eccentric part, of the first shell extends to the periphery of the eccentric part; an annular abdication groove is formed in the middle of one end, close to the eccentric part, of the first shell, a driving disc is movably sleeved on the periphery of the eccentric part, the driving disc is positioned in the abdication groove, and the eccentric part drives the driving disc to eccentrically move in the abdication groove; a ball mechanism is arranged between one end of the driving disc, which is close to the first shell, and the inner end surface of the abdication groove; the outer periphery of the second installation part is movably sleeved with a second shell, one end of the second shell, which is opposite to the driving disc, is provided with an inner cycloid groove, one end of the driving disc, which is opposite to the second shell, is provided with an outer cycloid groove, the wave number of the inner cycloid groove is larger than that of the outer cycloid groove, and a plurality of first balls are distributed between the inner cycloid groove and the outer cycloid groove; the first shell is connected with a first annular shell and a second annular shell in sequence along the axial direction, the first annular shell and the second annular shell are movably sleeved on the periphery of the second shell, an annular accommodating groove is formed between the first annular shell, the second annular shell and the second shell, and a crossed roller mechanism is arranged in the accommodating groove.
Preferably, the inner cycloid groove comprises a plurality of first arc grooves which are bent towards the inner side of the second shell, the first arc grooves are connected end to end along the Zhou Xiangyi sequence to form a ring shape, and the inner bottom surface of the first arc grooves is of an arc groove structure; the epicycloidal groove comprises a plurality of second arc grooves which are bent towards the outer side of the driving disc, the plurality of second arc grooves are connected end to end along the Zhou Xiangyi sequence to form a ring shape, and the inner bottom surface of the second arc grooves is of an arc groove structure; the number of the first arc-shaped grooves is larger than that of the second arc-shaped grooves.
Preferably, the number of the first arc grooves is n+2, the number of the second arc grooves is N, the number of the first balls is n+1, and N is an integer greater than zero.
Preferably, a plurality of first ball grooves are distributed at one end of the driving disc, which is close to the first shell, a plurality of second ball grooves which are in one-to-one correspondence with the first ball grooves are distributed at the inner end surface of the yielding groove, and the ball mechanism comprises a plurality of second balls which are correspondingly arranged between the first ball grooves and the second ball grooves; the first ball groove is of a first spherical crown type structure, and the diameter of a circle where the first spherical crown type structure is located is larger than that of the second ball; the second ball groove is of a second spherical crown type structure, and the diameter of a circle where the second spherical crown type structure is located is larger than the diameter of the second ball; the sum of the height of the first spherical cap structure and the height of the second spherical cap structure is smaller than the diameter of the second ball.
Preferably, an annular first mounting groove is formed in the outer wall of the second shell along the circumferential direction, the radial section of the first mounting groove is of an L-shaped structure, and one right-angle end of the L-shaped structure faces the middle of the second shell; the inner end surface of the first annular shell is provided with a first annular gap along the circumferential direction, and the first annular gap faces the second annular shell; the inner end surface of the second annular shell is provided with a second annular gap along the circumferential direction, and the second annular gap faces the first annular shell; the radial section of the first annular gap is perpendicular to the radial section of the second annular gap; the holding groove is formed by matching a first mounting groove, a first annular notch and a second annular notch, and the radial section of the holding groove is of a rectangular structure.
Preferably, the crossed roller mechanism comprises a first roller, a second roller, a limiting ring and limiting holes, wherein the limiting holes are formed in a plurality of side walls of the limiting ring and are uniformly distributed in the circumferential direction; the limiting ring is sleeved on the periphery of the first mounting groove, and the limiting hole is positioned in the middle of the accommodating groove; the first rollers are arranged in a plurality, the second rollers are arranged in a plurality, the first rollers and the second rollers are arranged in a plurality of limiting holes in a staggered mode, the central axes of the first rollers are perpendicular to the central axes of the second rollers, two ends of the first rollers are respectively parallel to two opposite inner walls of the accommodating groove, and two ends of the second rollers are respectively parallel to the other two opposite inner walls of the accommodating groove.
Preferably, a collar is formed between the first mounting portion and the eccentric portion.
Preferably, a first bearing is disposed between the first mounting portion and the first housing.
Preferably, a second bearing is provided between the eccentric portion and the driving disk.
Preferably, a third bearing is disposed between the second mounting portion and the second housing.
According to the invention, by adopting the structure, through the cooperation of the eccentric part, the driving disc, the first swing wire groove, the second swing wire groove, the first ball and the second shell, the speed reduction transmission is realized, and the speed reduction ratio of the bearing is improved; the driving disc, the ball mechanism and the first shell cooperate to release the eccentric action of the eccentric part, so that the bearing has a stable transmission structure and small rolling friction loss; the rolling transmission mode of the first ball and the second ball is adopted, so that the friction loss is small, the transmission efficiency is high, the transmission ratio error is small, and the rolling transmission device is applicable to the condition of higher rotating speed; the first annular shell, the second shell and the crossed roller mechanism are matched, so that the bearing has higher rotation precision.
The adaptability of the speed reducing bearing is improved through two output modes, namely, the input shaft is used as a power input end through fixing the first shell, the first annular shell and the second annular shell, the second shell is used as a power output end, and the first cycloid groove, the first ball and the second cycloid groove are matched to achieve a good speed reducing effect; 2. by fixing the second housing, the input shaft is made to function as a power input end, and the first housing, the first annular housing, and the second annular housing are made to function as a power output end to output in the opposite direction.
Drawings
The present invention is further illustrated by the accompanying drawings, which are not to be construed as limiting the invention in any way.
FIG. 1 is a schematic perspective view of the present invention;
FIG. 2 is a schematic side elevational view of the present invention;
FIG. 3 is a schematic cross-sectional view of the structure of FIG. 2 taken along line A-A;
FIG. 4 is an enlarged partial schematic view at B in FIG. 3;
FIG. 5 is a schematic illustration of the construction of the present invention with the first and second annular shells removed;
FIG. 6 is a schematic top view of the first housing of the present invention;
FIG. 7 is a schematic perspective view of the first annular housing, the second annular housing and the second housing of the present invention;
FIG. 8 is a schematic perspective view of the first housing, drive disk and input shaft of the present invention;
fig. 9 is a schematic perspective view of a driving disk and an input shaft in the present invention.
Wherein: the input shaft 1, the first mounting portion 1a, the eccentric portion 1b, the second mounting portion 1c, the collar 1d, the first housing 2, the relief groove 2a, the second ball groove 2b, the driving disk 3, the first ball groove 3a, the ball mechanism 4, the second ball 4a, the second housing 5, the first mounting groove 5a, the inner cycloid groove 6, the first arcuate groove 6a, the outer cycloid groove 7, the second arcuate groove 7a, the first ball 8, the first annular housing 9, the first annular gap 9a, the second annular housing 10, the second annular gap 10a, the cross roller mechanism 11, the first roller 11a, the second roller 11b, the stop ring 11c, the stop hole 11d, the first bearing 12, the second bearing 13, and the third bearing 14.
Detailed Description
The technical scheme of the invention is further described below by the specific embodiments with reference to the accompanying drawings.
Referring to fig. 1 to 9, a dual-line ball reduction bearing with high rotation accuracy of the present embodiment includes an input shaft 1, the input shaft 1 including a first mounting portion 1a, an eccentric portion 1b, and a second mounting portion 1c connected in order in an axial direction.
The periphery of the first installation part 1a is movably sleeved with a first shell 2, and one end, close to the eccentric part 1b, of the first shell 2 extends to the periphery of the eccentric part 1 b.
The middle part shaping that is close to of the one end of eccentric part 1b of first casing 2 has annular groove 2a of stepping down, the peripheral movable sleeve of eccentric part 1b is equipped with driving disk 3, driving disk 3 is located step down in groove 2a, eccentric part 1b drives driving disk 3 is in step down in groove 2a and do eccentric motion.
A ball mechanism 4 is arranged between one end of the driving disc 3, which is close to the first housing 2, and the inner end surface of the yielding groove 2 a.
The periphery movable sleeve of second installation department 1c is equipped with second casing 5, second casing 5 with the shaping of the relative one end of driving disk 3 has interior pendulum wire casing 6, the shaping of the relative one end of driving disk 3 with second casing 5 has outer pendulum wire casing 7, the wave number of interior pendulum wire casing 6 is greater than the wave number of outer pendulum wire casing 7, interior pendulum wire casing 6 with a plurality of first balls 8 are distributed between the outer pendulum wire casing 7.
The first shell 2 is connected with a first annular shell 9 and a second annular shell 10 in sequence along the axial direction, the first annular shell 9 and the second annular shell 10 are movably sleeved on the periphery of the second shell 5, an annular accommodating groove is formed between the first annular shell 9, the second annular shell 10 and the second shell 5, and a crossed roller mechanism 11 is arranged in the accommodating groove.
With this structure, the input shaft 1 is connected with an external driving device, and when the first housing 2, the first annular housing 9 and the second annular housing 10 are fixedly connected with an external frame, the input shaft 1 is used as a power input end, and the second housing 5 is used as a power output end and connected with an external connecting device. The input shaft 1 drives the eccentric part 1b to rotate, the eccentric part 1b drives the driving disc 3 to make eccentric motion in the yielding groove 2a, and the ball mechanism 4 is used for releasing the eccentric motion of the driving disc 3, so that sliding friction and loss are reduced. The inner cycloid groove 6, the first ball 8 and the outer cycloid groove 7 are matched to realize rolling transmission movement, and the inner cycloid groove 6 and the outer cycloid groove 7 are utilized to generate differential tooth movement, so that the rotating speed of the second shell 5 is reduced, the speed reduction effect of the bearing is realized, the transmission efficiency is improved, the reduction ratio is improved, the abrasion loss is reduced, the error is small, and the transmission ratio error is small.
The second shell 5 is fixedly connected with the external frame, and when the input shaft 1 is connected with an external driving device, the input shaft 1 is used as a power input end, and the first annular shell 9, the second annular shell 10 and the first shell 2 are used as power output ends. The input shaft 1 drives the eccentric part 1b to rotate, and as the second shell 5 is fixed, the first ball 8, the driving disc 3 and the ball mechanism 4 cooperate to enable the first shell 2, the first annular shell 9 and the second annular shell 10 to generate rotation motion opposite to the rotation direction of the input shaft 1, and the output in the opposite direction can be realized by connecting the second annular shell 10 or the first shell 2 with an external connecting device.
The traditional cross disc structure is removed, so that the structure of the speed reducing bearing is more simplified, and the speed reducing bearing with smaller size can be manufactured.
The crossed roller mechanism 11 is arranged among the first annular shell 9, the second annular shell 10 and the second shell 5, so that the bearing has excellent rotation precision, can bear larger axial and radial loads, saves installation space, and reduces shaft length and processing cost.
Referring to fig. 3, 7 and 8, the inner cycloid groove 6 includes a plurality of first arc grooves 6a curved toward the inner side of the second housing 5, the plurality of first arc grooves 6a are connected end to end along the sequence Zhou Xiangyi to form a ring shape, and the inner bottom surface of the first arc grooves 6a is an arc groove structure; the outer cycloid groove 7 comprises a plurality of second arc grooves 7a which are bent towards the outer side of the driving disc 3, the second arc grooves 7a are connected end to end along the Zhou Xiangyi sequence to form a ring shape, and the inner bottom surface of the second arc grooves 7a is of an arc groove structure; the number of the first arc-shaped grooves 6a is larger than the number of the second arc-shaped grooves 7 a.
By adopting the structure, the inner cycloid groove 6 is formed by connecting the first arc-shaped grooves 6a into the ring shape, the outer cycloid groove 7 is formed by connecting the second arc-shaped grooves 7a into the ring shape, the inner cycloid groove 6 and the outer cycloid groove 7 are matched to clamp the first balls 8, so that the first balls 8 can conveniently roll and drive in the inner cycloid groove 6 and the outer cycloid groove 7, sliding friction is converted into rolling friction, friction loss between the driving disc 3 and the second shell 5 is reduced, and meanwhile, good transmission effect can be achieved.
The eccentric distance between the eccentric part 1b and the input shaft 1 is set as a, the diameter of the pitch circle is set as b, the outline of the inner cycloid groove 6 is an annular line with the amplitude of a and inscribed in the circle with the pitch circle diameter of b, and the outline of the outer cycloid groove 7 is an annular line with the amplitude of a and circumscribed in the circle with the pitch circle diameter of b.
Preferably, the number of the first arc grooves 6a is n+2, the number of the second arc grooves 7a is N, the number of the first balls 8 is n+1, and N is an integer greater than zero.
By adopting the structure, the arrangement mode of the N+2 first arc grooves 6a, the N+1 first balls 8 and the N second arc grooves 7a is adopted, so that the first arc grooves 6a, the first balls 8 and the second arc grooves 7a are matched to generate differential tooth motion, the purpose of speed reduction transmission is achieved, meanwhile, the N+1 balls can ensure that a good transmission effect is kept between the driving disc 3 and the second shell 5, and the phenomenon of dead clamping or inflexible rotation is avoided due to the generation of transmission gaps.
Referring to fig. 3 and 9, a plurality of first ball grooves 3a are distributed at one end of the driving disc 3 near the first housing 2, a plurality of second ball grooves 2b corresponding to the first ball grooves 3a one by one are distributed at an inner end surface of the yielding groove 2a, and the ball mechanism 4 includes a plurality of second balls 4a corresponding to the first ball grooves 3a and the second ball grooves 2 b.
The first ball groove 3a is a first spherical cap structure, and the diameter of a circle where the first spherical cap structure is located is larger than the diameter of the second ball 4 a; the second ball groove 2b is of a second spherical cap type structure, and the diameter of a circle where the second spherical cap type structure is positioned is larger than the diameter of the second ball 4 a; the sum of the height of the first spherical cap structure and the height of the second spherical cap structure is smaller than the diameter of the second ball 4a.
With this structure, the first ball grooves 3a and the second ball grooves 2b fit to sandwich the second balls 4a, and the drive disc 3 and the first housing 2 are rollingly driven by the second balls 4a, and the eccentric action of the drive disc 3 is released during the rolling drive of the second balls 4a.
The first ball groove 3a and the second ball groove 2b provide sufficient eccentric space for the second ball 4a so that the second ball 4a can release the eccentric action of the eccentric portion 1 b; the sum of the height of the first spherical crown type structure and the height of the second spherical crown type structure is smaller than the diameter of the second ball 4a, so that sliding friction generated by contact between the driving disc 3 and the first shell 2 can be avoided, and friction loss is reduced.
The second ball 4a, the first ball groove 3a and the second ball groove 2b are matched, so that the transmission efficiency is high, the friction force in the transmission process can be effectively reduced, and the mechanical power is improved.
Referring to fig. 3 and 4, the outer wall of the second housing 5 is provided with a first annular mounting groove 5a along the circumferential direction, the radial section of the first mounting groove 5a is in an L-shaped structure, and one right-angle end of the L-shaped structure faces the middle of the second housing 5.
The inner end surface of the first annular housing 9 is provided with a first annular gap 9a along the circumferential direction, and the first annular gap 9a faces the second annular housing 10; the inner end surface of the second annular housing 10 is provided with a second annular gap 10a along the circumferential direction, and the second annular gap 10a faces the first annular housing 9; the radial section of the first annular gap 9a is perpendicular to the radial section of the second annular gap 10 a.
The accommodating groove is formed by matching a first mounting groove 5a, a first annular notch 9a and a second annular notch 10a, and the radial section of the accommodating groove is of a rectangular structure.
With this structure, the first mounting groove 5a, the first annular gap 9a and the second annular gap 10a cooperate to form a receiving groove, so that the installation of the crossed roller mechanism 11 is facilitated, one end face of the first mounting groove 5a is parallel to the first annular gap 9a, part of rollers of the crossed roller mechanism 11 are clamped between one end face of the first mounting groove 5a and the first annular gap 9a, the other end face of the first mounting groove 5a is parallel to the second annular gap 10a, and the other part of rollers of the crossed roller mechanism 11 are clamped between the other end face of the first mounting groove 5a and the second annular gap 10a, so that the bearing can bear larger axial and radial loads.
Referring to fig. 5, the crossed roller mechanism 11 includes a first roller 11a, a second roller 11b, a limiting ring 11c, and a limiting hole 11d, where the limiting hole 11d is provided with a plurality of side walls uniformly distributed on the limiting ring 11c along the circumferential direction; the limiting ring 11c is sleeved on the periphery of the first mounting groove 5a, and the limiting hole 11d is located in the middle of the accommodating groove.
The first rollers 11a are provided with a plurality of first rollers 11b, the second rollers 11b are provided with a plurality of second rollers 11b, the first rollers 11a and the second rollers 11b are arranged in the limiting holes 11d in a staggered mode, the central axes of the first rollers 11a are perpendicular to the central axes of the second rollers 11b, two ends of the first rollers 11a are parallel to two opposite inner walls of the accommodating groove respectively, and two ends of the second rollers 11b are parallel to two other opposite inner walls of the accommodating groove respectively.
By adopting the structure, the first roller 11a and the second roller 11b are separated through the cooperation of the limiting ring 11c and the accommodating groove, the first roller 11a and the second roller 11b are prevented from contacting each other to accelerate abrasion, the output stability of the second shell 5 is improved, the good rotation precision is realized, and the first annular shell 9, the second annular shell 10, the crossed roller mechanism 11 and the second shell 5 cooperate to enable the bearing to bear larger axial and radial loads.
Referring to fig. 3, a collar 1d is preferably formed between the first mounting portion 1a and the eccentric portion 1 b.
With this structure, the provision of the collar 1d can facilitate positioning of the input shaft 1.
Preferably, a first bearing 12 is provided between the first mounting portion 1a and the first housing 2.
With this structure, the provision of the first bearing 12 enables the movable connection between the first mounting portion 1a and the first housing 2 to be maintained.
Preferably, a second bearing 13 is provided between the eccentric portion 1b and the drive disk 3.
With this structure, the provision of the second bearing 13 enables the movable connection between the eccentric portion 1b and the drive disk 3 to be maintained.
Preferably, a third bearing 14 is provided between the second mounting portion 1c and the second housing 5.
With this structure, provision of the third bearing 14 enables the second mounting portion 1c and the second housing 5 to be kept movably connected.
During operation, the input shaft 1 is connected with an external driving device, the first shell 2, the first annular shell 9 and the second annular shell 10 are fixedly connected with an external frame, the input shaft 1 is used as a power input end, and the second shell 5 is used as a power output end and is connected with an external connecting device. The input shaft 1 drives the eccentric part 1b to rotate, the eccentric part 1b drives the driving disc 3 to make eccentric motion in the yielding groove 2a, and the ball mechanism 4 is used for releasing the eccentric motion of the driving disc 3, so that sliding friction and loss are reduced. The inner cycloid groove 6, the first ball 8 and the outer cycloid groove 7 are matched to realize rolling transmission movement, and the inner cycloid groove 6 and the outer cycloid groove 7 are utilized to generate differential tooth movement, so that the rotating speed of the second shell 5 is reduced, the speed reduction effect of the bearing is realized, the transmission efficiency is improved, the reduction ratio is improved, the abrasion loss is reduced, the error is small, and the transmission ratio error is small.
The second shell 5 is fixedly connected with an external frame, the input shaft 1 is connected with an external driving device, the input shaft 1 is used as a power input end, and the first annular shell 9, the second annular shell 10 and the first shell 2 are used as power output ends. The input shaft 1 drives the eccentric part 1b to rotate, and as the second shell 5 is fixed, the first ball 8, the driving disc 3 and the ball mechanism 4 cooperate to enable the first shell 2, the first annular shell 9 and the second annular shell 10 to generate rotation motion opposite to the rotation direction of the input shaft 1, and the output in the opposite direction can be realized by connecting the second annular shell 10 or the first shell 2 with an external connecting device.
The technical principle of the present invention is described above in connection with the specific embodiments. The description is made for the purpose of illustrating the general principles of the invention and should not be taken in any way as limiting the scope of the invention. Other embodiments of the invention will be apparent to those skilled in the art from consideration of this specification without undue burden.
Claims (8)
1. The double-wave-line ball speed reducing bearing with high rotation precision comprises an input shaft, and is characterized in that the input shaft comprises a first installation part, an eccentric part and a second installation part which are sequentially connected along the axial direction;
the periphery of the first installation part is movably sleeved with a first shell, and one end, close to the eccentric part, of the first shell extends to the periphery of the eccentric part;
an annular abdication groove is formed in the middle of one end, close to the eccentric part, of the first shell, a driving disc is movably sleeved on the periphery of the eccentric part, the driving disc is positioned in the abdication groove, and the eccentric part drives the driving disc to eccentrically move in the abdication groove;
a ball mechanism is arranged between one end of the driving disc, which is close to the first shell, and the inner end surface of the abdication groove;
the outer periphery of the second installation part is movably sleeved with a second shell, one end of the second shell, which is opposite to the driving disc, is provided with an inner cycloid groove, one end of the driving disc, which is opposite to the second shell, is provided with an outer cycloid groove, the wave number of the inner cycloid groove is larger than that of the outer cycloid groove, and a plurality of first balls are distributed between the inner cycloid groove and the outer cycloid groove;
the first shell is connected with a first annular shell and a second annular shell in sequence along the axial direction, the first annular shell and the second annular shell are movably sleeved on the periphery of the second shell, annular accommodating grooves are formed among the first annular shell, the second annular shell and the second shell, and crossed roller mechanisms are arranged in the accommodating grooves;
the inner cycloid groove comprises a plurality of first arc grooves which are bent towards the inner side of the second shell, the first arc grooves are connected end to end along the Zhou Xiangyi sequence to form a ring shape, and the inner bottom surface of the first arc grooves is of an arc groove structure; the epicycloidal groove comprises a plurality of second arc grooves which are bent towards the outer side of the driving disc, the plurality of second arc grooves are connected end to end along the Zhou Xiangyi sequence to form a ring shape, and the inner bottom surface of the second arc grooves is of an arc groove structure; the number of the first arc-shaped grooves is larger than that of the second arc-shaped grooves;
a plurality of first ball grooves are distributed at one end of the driving disc, which is close to the first shell, a plurality of second ball grooves which are in one-to-one correspondence with the first ball grooves are distributed at the inner end surface of the yielding groove, and the ball mechanism comprises a plurality of second balls which are correspondingly arranged between the first ball grooves and the second ball grooves;
the first ball groove is of a first spherical crown type structure, and the diameter of a circle where the first spherical crown type structure is located is larger than that of the second ball; the second ball groove is of a second spherical crown type structure, and the diameter of a circle where the second spherical crown type structure is located is larger than the diameter of the second ball; the sum of the height of the first spherical cap structure and the height of the second spherical cap structure is smaller than the diameter of the second ball.
2. The dual-wave ball reduction bearing of claim 1, wherein the number of first arcuate grooves is n+2, the number of second arcuate grooves is N, the number of first balls is n+1, and N is an integer greater than zero.
3. The dual-line ball reduction bearing with high rotation precision according to claim 1, wherein an annular first mounting groove is formed in the outer wall of the second housing along the circumferential direction, the radial section of the first mounting groove is of an L-shaped structure, and one right-angle end of the L-shaped structure faces the middle of the second housing;
the inner end surface of the first annular shell is provided with a first annular gap along the circumferential direction, and the first annular gap faces the second annular shell; the inner end surface of the second annular shell is provided with a second annular gap along the circumferential direction, and the second annular gap faces the first annular shell; the radial section of the first annular gap is perpendicular to the radial section of the second annular gap;
the holding groove is formed by matching a first mounting groove, a first annular notch and a second annular notch, and the radial section of the holding groove is of a rectangular structure.
4. The dual-line ball reduction bearing with high rotation precision according to claim 3, wherein the crossed roller mechanism comprises a first roller, a second roller, a limiting ring and limiting holes, wherein the limiting holes are formed in a plurality of side walls of the limiting ring and are uniformly distributed in the circumferential direction; the limiting ring is sleeved on the periphery of the first mounting groove, and the limiting hole is positioned in the middle of the accommodating groove;
the first rollers are arranged in a plurality, the second rollers are arranged in a plurality, the first rollers and the second rollers are arranged in a plurality of limiting holes in a staggered mode, the central axes of the first rollers are perpendicular to the central axes of the second rollers, two ends of the first rollers are respectively parallel to two opposite inner walls of the accommodating groove, and two ends of the second rollers are respectively parallel to the other two opposite inner walls of the accommodating groove.
5. The dual-line ball reduction bearing of claim 1, in which a collar is formed between the first mounting portion and the eccentric portion.
6. The dual-line ball reduction bearing of claim 1, wherein a first bearing is provided between the first mounting portion and the first housing.
7. The dual-line ball reduction bearing of claim 1, wherein a second bearing is provided between the eccentric portion and the drive disk.
8. The dual-line ball reduction bearing of claim 1, wherein a third bearing is provided between the second mounting portion and the second housing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910759700.1A CN110374991B (en) | 2019-08-16 | 2019-08-16 | Double-wave-line ball speed reducing bearing with high rotation precision |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910759700.1A CN110374991B (en) | 2019-08-16 | 2019-08-16 | Double-wave-line ball speed reducing bearing with high rotation precision |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110374991A CN110374991A (en) | 2019-10-25 |
| CN110374991B true CN110374991B (en) | 2024-03-26 |
Family
ID=68259703
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910759700.1A Active CN110374991B (en) | 2019-08-16 | 2019-08-16 | Double-wave-line ball speed reducing bearing with high rotation precision |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN110374991B (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111173895B (en) * | 2020-01-06 | 2021-05-04 | 河南烛龙高科技术有限公司 | Two-stage closed type undercut cycloid oscillating tooth transmission unit |
| CN111120586B (en) * | 2020-01-06 | 2021-03-16 | 河南烛龙高科技术有限公司 | Closed undercut cycloid oscillating tooth reduction gear of doublestage |
| CN111075889A (en) * | 2020-01-22 | 2020-04-28 | 佛山市力普鑫精密技术有限公司 | Combined speed reducer |
| CN111173898A (en) * | 2020-01-22 | 2020-05-19 | 佛山市力普鑫精密技术有限公司 | But decelerator of pre-compaction regulation |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002206546A (en) * | 2000-11-10 | 2002-07-26 | Nsk Ltd | Needle bearing |
| KR20050112682A (en) * | 2004-05-27 | 2005-12-01 | 주식회사 해성산전 | A high degree of efficiency and hardness inscribed toothed wheel using cycloid tooth type |
| JP2015132359A (en) * | 2014-01-15 | 2015-07-23 | 有限会社ファインメック | Speed reducer |
| WO2016204220A1 (en) * | 2015-06-18 | 2016-12-22 | Ntn株式会社 | Tapered roller bearing and planet bearing device |
| KR20170024874A (en) * | 2015-08-26 | 2017-03-08 | 경일대학교산학협력단 | Apparatus for opening/closing floodgate |
| CN109538706A (en) * | 2018-12-29 | 2019-03-29 | 王小三 | A kind of helical teeth planetary gear ball Combined speed reducer |
| CN210461387U (en) * | 2019-08-16 | 2020-05-05 | 佛山市力普鑫精密技术有限公司 | Double-wave-line ball reduction bearing with high rotation precision |
-
2019
- 2019-08-16 CN CN201910759700.1A patent/CN110374991B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002206546A (en) * | 2000-11-10 | 2002-07-26 | Nsk Ltd | Needle bearing |
| KR20050112682A (en) * | 2004-05-27 | 2005-12-01 | 주식회사 해성산전 | A high degree of efficiency and hardness inscribed toothed wheel using cycloid tooth type |
| JP2015132359A (en) * | 2014-01-15 | 2015-07-23 | 有限会社ファインメック | Speed reducer |
| WO2016204220A1 (en) * | 2015-06-18 | 2016-12-22 | Ntn株式会社 | Tapered roller bearing and planet bearing device |
| KR20170024874A (en) * | 2015-08-26 | 2017-03-08 | 경일대학교산학협력단 | Apparatus for opening/closing floodgate |
| CN109538706A (en) * | 2018-12-29 | 2019-03-29 | 王小三 | A kind of helical teeth planetary gear ball Combined speed reducer |
| CN210461387U (en) * | 2019-08-16 | 2020-05-05 | 佛山市力普鑫精密技术有限公司 | Double-wave-line ball reduction bearing with high rotation precision |
Also Published As
| Publication number | Publication date |
|---|---|
| CN110374991A (en) | 2019-10-25 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN110374991B (en) | Double-wave-line ball speed reducing bearing with high rotation precision | |
| US4576057A (en) | Anti-friction nut/screw drive | |
| CN108662089B (en) | Servo reducer and robot deceleration joint using same | |
| CN108953541B (en) | RV speed reducer with ultralow reduction ratio | |
| CN113309842B (en) | Cycloidal pin gear harmonic speed reducer | |
| CN110121610B (en) | Transmission speed reducer | |
| KR101724659B1 (en) | Reverse cycloid reducer | |
| CN110374990B (en) | Single-wave-line speed reducing bearing with high durability | |
| CN110374988B (en) | Simple cycloid speed reducing bearing with strong load capacity | |
| CN210461387U (en) | Double-wave-line ball reduction bearing with high rotation precision | |
| CN210265711U (en) | Cycloidal gear speed reducer | |
| CN210769832U (en) | Double-wave-line speed reduction bearing with high bearing capacity | |
| CN115163757B (en) | Cycloidal pin gear planetary reducer | |
| CN211648782U (en) | Single wave line speed reduction bearing of high incorruptibility | |
| CN211343712U (en) | Single cycloid speed reduction bearing with strong load capacity | |
| CN110805660A (en) | Differential cycloidal gear speed change device | |
| CN111895058B (en) | Forming design method of speed reducer | |
| KR20210018816A (en) | Fixed ratio ground or friction drive | |
| EP4119813A1 (en) | Combined tooth surface cycloidal movable tooth transmission mechanism | |
| EP2837849A1 (en) | Wave gear mechanism | |
| CN211009753U (en) | Differential cycloidal gear speed change device | |
| CN112178134B (en) | Large-scale high-rigidity impact-resistant precise speed reducer | |
| CN208749929U (en) | A kind of precision speed reduction device for robot | |
| CN210770053U (en) | Cycloidal pin gear speed reducing mechanism | |
| CN212928684U (en) | Speed reducer and power output equipment with same |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20240709 Address after: Room 1302, Building 6, Zhangcheng Huating, No. 5 Xicheng Road, Zhangmutou Town, Dongguan City, Guangdong Province 523000 Patentee after: Wang Xiaosan Country or region after: China Address before: 528137 No. 4, Lehua South Road, Leping Town, Sanshui District, Foshan City, Guangdong Province Patentee before: Foshan Lipuxin Precision Technology Co.,Ltd. Country or region before: China |