CN110374988B - Simple cycloid speed reducing bearing with strong load capacity - Google Patents
Simple cycloid speed reducing bearing with strong load capacity Download PDFInfo
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- CN110374988B CN110374988B CN201910759690.1A CN201910759690A CN110374988B CN 110374988 B CN110374988 B CN 110374988B CN 201910759690 A CN201910759690 A CN 201910759690A CN 110374988 B CN110374988 B CN 110374988B
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- 230000001603 reducing effect Effects 0.000 title claims abstract description 17
- 230000007246 mechanism Effects 0.000 claims abstract description 25
- 238000009434 installation Methods 0.000 claims abstract description 15
- 230000005540 biological transmission Effects 0.000 abstract description 19
- 230000033001 locomotion Effects 0.000 description 12
- 230000000694 effects Effects 0.000 description 5
- 238000005096 rolling process Methods 0.000 description 5
- 238000005299 abrasion Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 3
- 241001391944 Commicarpus scandens Species 0.000 description 1
- 239000003638 chemical reducing agent Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000007493 shaping process Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
Classifications
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- 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
- F16C19/49—Bearings with both balls and rollers
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- 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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/583—Details of specific parts of races
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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Abstract
The invention discloses a single-cycloid speed reducing bearing with strong load capacity, which comprises an input shaft, wherein the input shaft comprises a first installation part, an eccentric part and a second installation part; a first shell is movably sleeved on the periphery of the first mounting part; the first shell is provided with a yielding groove in a forming mode, a driving disc is movably sleeved on the periphery of the eccentric part, and the driving disc is positioned in the yielding groove; a roller mechanism is arranged between the driving disc and the abdication groove; the driving disc is provided with a plurality of first roller grooves, the abdication grooves are provided with a plurality of second roller grooves, and the roller mechanism comprises a plurality of rollers correspondingly arranged between the first roller grooves and the second roller grooves; the periphery of the second installation part is movably sleeved with a second shell, and a plurality of ball positioning grooves are formed in the second shell; the invention aims to provide the single-cycloid speed reducing bearing with strong radial bearing capacity, high wear resistance, high transmission efficiency and low noise and strong load capacity, which can bear heavy load and impact load.
Description
Technical Field
The invention relates to the field of speed reduction bearings, in particular to a single-cycloid speed reduction bearing with high load capacity.
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.
In the transmission process, gears are meshed with each other, frictional resistance is large, radial bearing capacity is poor, shock resistance is poor, and tooth roots are easy to break. The existing speed reducing bearing is generally driven by a cross disc, so that the size of the bearing is large, and the speed reducing bearing cannot be applied to some precise equipment.
Disclosure of Invention
The invention aims to provide a single-cycloid speed reducing bearing with strong radial bearing capacity, high transmission efficiency and low noise, which can bear heavy load and impact load and has wear resistance.
To achieve the purpose, the invention adopts the following technical scheme: the simple cycloid speed reducing bearing with high load capacity 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 roller 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; a plurality of first roller grooves are distributed at one end of the driving disc, which is close to the first shell, a plurality of second roller grooves which are in one-to-one correspondence with the first roller grooves are distributed at the inner end surface of the yielding groove, and the roller mechanism comprises a plurality of rollers which are correspondingly arranged between the first roller grooves and the second roller grooves; the 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 a plurality of ball positioning grooves in a circumferential direction, one end of the driving disc, which is opposite to the second shell, is provided with an outer swinging wire groove, and the number of the ball positioning grooves is larger than the number of the outer swinging wire grooves; the ball positioning groove is internally provided with a ball, one end of the ball is positioned in the corresponding ball positioning groove, and the other end of the ball is positioned in the outer swinging wire 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 end surface of the ball positioning groove is of a spherical crown structure; the epicycloidal groove comprises a plurality of arc grooves which are bent towards the outer side of the driving disc, the arc grooves are connected end to end along the Zhou Xiangyi sequence to form a ring shape, and the inner bottom surface of the arc grooves is of an arc groove structure; one end of the ball is positioned in the spherical crown type, and the other end of the ball is positioned in the arc-shaped groove.
Preferably, the number of the ball positioning grooves is N, the number of the arc grooves is N-1, the number of the balls is N, and N is an integer greater than zero.
Preferably, the first roller groove is a first circular counter bore, and the diameter of the first circular counter bore is larger than that of the roller; the second roller groove is a second circular counter bore, and the diameter of the second circular counter bore is larger than that of the roller; the sum of the depth of the first circular counterbore and the depth of the second circular counterbore is less than the height of the roller.
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, the ball positioning groove, the balls and the epicycloidal groove are matched, and the gear difference is generated between the ball positioning groove and the epicycloidal groove, so that the speed reduction effect is realized, and the speed reduction ratio of the bearing is improved; the first roller groove, the second roller groove and the roller are matched, in the transmission process, the eccentric function of releasing the driving disc is achieved, the roller is in linear contact with the first roller groove and the second roller groove, the radial bearing capacity is high, heavy load or impact load can be borne, the friction coefficient is small, the roller is suitable for working conditions of higher rotating speed, the processing technology of the roller is simple, and the roller is convenient to install; adopt ball constant head tank and ball complex mode, the ball is in the rolling drive of ball constant head tank, is difficult to take place wearing and tearing, and the transmission is more efficient, and the noise is littleer, more durable, and bearing life is longer.
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 roller groove 2b, the driving disk 3, the first roller groove 3a, the roller mechanism 4, the roller 4a, the second housing 5, the first mounting groove 5a, the ball positioning groove 6, the outer swing groove 7, the arc groove 7a, the balls 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 retainer ring 11c, the retainer 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 single-cycloid reduction bearing with high load capacity of the present embodiment includes an input shaft 1, wherein the input shaft 1 includes a first mounting portion 1a, an eccentric portion 1b, and a second mounting portion 1c connected in sequence 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 roller mechanism 4 is arranged between one end of the driving disc 3, which is close to the first shell 2, and the inner end surface of the yielding groove 2 a; the driving disc 3 is provided with a plurality of first roller grooves 3a distributed at one end close to the first shell 2, a plurality of second roller grooves 2b corresponding to the first roller grooves 3a one by one are distributed at the inner end surface of the yielding groove 2a, and the roller mechanism 4 comprises a plurality of rollers 4a correspondingly arranged between the first roller grooves 3a and the second roller grooves 2 b.
The periphery of the second installation part 1c is movably sleeved with a second shell 5, one end of the second shell 5 opposite to the driving disc 3 is provided with a plurality of ball positioning grooves 6 in a circumferential direction, one end of the driving disc 3 opposite to the second shell 5 is provided with an outer swinging wire groove 7 in a molding mode, and the number of the ball positioning grooves 6 is larger than the number of the outer swinging wire grooves 7; the ball positioning groove 6 is internally provided with a ball 8, one end of the ball 8 is positioned in the corresponding ball positioning groove 6, and the other end of the ball 8 is positioned in the epicycloidal groove 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 roller mechanism 4 is used for releasing the eccentric motion of the driving disc 3, so that sliding friction and loss are reduced. The ball positioning groove 6, the ball 8 and the outer cycloid groove 7 cooperate to realize rolling transmission movement, and the ball positioning 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 balls 8, the driving disc 3 and the roller mechanism 4 cooperate to enable the first shell 2, the first annular shell 9 and the second annular shell 10 to generate rotary motion opposite to the rotary direction of the input shaft 1, and the second annular shell 10 or the first shell 2 is connected with an external connecting device, so that the output in the opposite direction can be realized.
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.
The first roller groove 3a and the second roller groove 2b are matched to clamp the roller 4a, the driving disc 3 and the first shell 2 are driven by the roller 4a, and the eccentric action of the driving disc 3 is released in the process of driving the roller 4a. In the transmission process of the driving disc 3 and the first shell 2, linear contact is generated between the roller 4a and the first roller groove 3a and the second roller groove 2b, the radial bearing capacity is higher, the device is suitable for bearing heavy load or impact load, the friction coefficient is small, the device is suitable for working conditions of high rotating speed, the roller 4a is simpler to process, the process requirement is lower, and the device is convenient to install.
The ball positioning groove 6 has stronger wear resistance, the ball 8 is in rolling transmission between the outer cycloid groove 7 and the ball positioning groove 6, abrasion is not easy to occur, the transmission is more efficient, the noise is small, the ball positioning groove is more durable, and the service life is longer.
Referring to fig. 3, 7 and 8, the inner end surface of the ball positioning groove 6 has a spherical crown structure; the outer cycloid groove 7 comprises a plurality of arc-shaped grooves 7a which are bent towards the outer side of the driving disc 3, the arc-shaped grooves 7a are connected end to end along the Zhou Xiangyi sequence to form a ring shape, and the inner bottom surface of each arc-shaped groove 7a is of an arc-shaped groove structure; one end of the ball 8 is positioned in the spherical crown, and the other end of the ball 8 is positioned in the arc-shaped groove 7 a.
By adopting the structure, the ball positioning groove 6 and the epicycloidal groove 7 are matched to clamp the ball 8, so that the ball 8 can conveniently roll and drive in the ball positioning groove 6 and the epicycloidal groove 7, the sliding friction is converted into rolling friction, the friction loss between the driving disc 3 and the second shell 5 is reduced, and meanwhile, a good transmission effect can be realized.
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, and the outline of the outer cycloid groove 7 is an annular line with the amplitude of a and externally connected with the circle with the pitch circle diameter of b.
Preferably, the number of the ball positioning grooves 6 is N, the number of the arc grooves 7a is N-1, and the number of the balls 8 is N, where N is an integer greater than zero.
By adopting the structure, the arrangement mode of the N ball positioning grooves 6, the N balls 8 and the N-1 arc grooves 7a is adopted, so that differential tooth motion is generated among the ball positioning grooves 6, the balls 8 and the arc grooves 7a, the purpose of speed reduction transmission is achieved, meanwhile, the N balls can ensure that a good transmission effect is kept between the driving disc 3 and the second shell 5, the phenomenon that a transmission gap is generated and the locking or rotation is inflexible is avoided.
Preferably, the first roller groove 3a is a first circular counter bore, and the diameter of the first circular counter bore is larger than that of the roller 4 a; the second roller groove 2b is a second circular counter bore, and the diameter of the second circular counter bore is larger than that of the roller 4 a; the sum of the depth of the first circular counterbore and the depth of the second circular counterbore is less than the height of the roller 4a.
With this structure, the first circular counterbore has a diameter larger than that of the roller 4a, and the second circular counterbore has a diameter larger than that of the roller 4a, and the first and second roller grooves 3a and 2b provide sufficient eccentric space for the roller 4a so that the roller 4a can release the eccentric action of the eccentric portion 1 b; the sum of the depth of the first circular counter bore and the depth of the second circular counter bore is smaller than the height of the roller 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.
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 roller mechanism 4 is used for releasing the eccentric motion of the driving disc 3, so that sliding friction and loss are reduced. The ball positioning groove 6, the ball 8 and the outer cycloid groove 7 cooperate to realize rolling transmission movement, and the ball positioning 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 balls 8, the driving disc 3 and the roller mechanism 4 cooperate to enable the first shell 2, the first annular shell 9 and the second annular shell 10 to generate rotary motion opposite to the rotary direction of the input shaft 1, and the second annular shell 10 or the first shell 2 is connected with an external connecting device, so that the output in the opposite direction can be realized.
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 simple cycloid speed reducing bearing with high load capacity 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 roller 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; a plurality of first roller grooves are distributed at one end of the driving disc, which is close to the first shell, a plurality of second roller grooves which are in one-to-one correspondence with the first roller grooves are distributed at the inner end surface of the yielding groove, and the roller mechanism comprises a plurality of rollers which are correspondingly arranged between the first roller grooves and the second roller grooves;
the 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 a plurality of ball positioning grooves in a circumferential direction, one end of the driving disc, which is opposite to the second shell, is provided with an outer swinging wire groove, and the number of the ball positioning grooves is larger than the number of the outer swinging wire grooves; the ball positioning groove is internally provided with a ball, one end of the ball is positioned in the corresponding ball positioning groove, and the other end of the ball is positioned in the outer swinging wire 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 end surface of the ball positioning groove is of a spherical crown structure; the epicycloidal groove comprises a plurality of arc grooves which are bent towards the outer side of the driving disc, the arc grooves are connected end to end along the Zhou Xiangyi sequence to form a ring shape, and the inner bottom surface of the arc grooves is of an arc groove structure; one end of the ball is positioned in the spherical crown type, and the other end of the ball is positioned in the arc-shaped groove;
the first roller groove is a first circular counter bore, and the diameter of the first circular counter bore is larger than that of the roller; the second roller groove is a second circular counter bore, and the diameter of the second circular counter bore is larger than that of the roller; the sum of the depth of the first circular counterbore and the depth of the second circular counterbore is less than the height of the roller.
2. The single-cycloid reduction bearing with high load capacity according to claim 1, wherein the number of the ball positioning grooves is N, the number of the arc grooves is N-1, the number of the balls is N, and N is an integer greater than zero.
3. The single-cycloid speed reducing bearing with strong load capacity according to claim 1, wherein the outer wall of the second housing is provided with a first annular mounting groove 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 part 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. A single-cycloid speed reducing bearing with high load capacity 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 arranged in a plurality and uniformly distributed on the side wall of the limiting ring along 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. A single-cycloidal reduction bearing according to claim 1 wherein a collar is formed between the first mounting portion and the eccentric portion.
6. A single-cycloidal speed reducing bearing with high load capacity according to claim 1, wherein a first bearing is provided between the first mounting portion and the first housing.
7. A single-cycloid reduction bearing with high load capacity according to claim 1, characterized in that a second bearing is provided between the eccentric and the drive disc.
8. A single-cycloidal speed reducing bearing with high load capacity according to 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 |
|---|---|---|---|
| CN201910759690.1A CN110374988B (en) | 2019-08-16 | 2019-08-16 | Simple cycloid speed reducing bearing with strong load capacity |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910759690.1A CN110374988B (en) | 2019-08-16 | 2019-08-16 | Simple cycloid speed reducing bearing with strong load capacity |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110374988A CN110374988A (en) | 2019-10-25 |
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| CN201910759690.1A Active CN110374988B (en) | 2019-08-16 | 2019-08-16 | Simple cycloid speed reducing bearing with strong load capacity |
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| 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 |
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|---|---|---|---|---|
| JP2003074672A (en) * | 2001-05-24 | 2003-03-12 | Koyo Seiko Co Ltd | Pulley unit |
| JP2003139154A (en) * | 2001-11-06 | 2003-05-14 | Nsk Ltd | Bearing unit |
| CN104819253A (en) * | 2015-02-25 | 2015-08-05 | 佛山市诺尔贝机器人技术有限公司 | Multi-crankshaft cycloid speed reducer |
| CN208057914U (en) * | 2018-04-04 | 2018-11-06 | 海尚集团有限公司 | Vector cycloid speed reducer |
| CN109578540A (en) * | 2018-12-29 | 2019-04-05 | 王小三 | A kind of straight-tooth planetary gear ball Combined speed reducer |
| CN211343712U (en) * | 2019-08-16 | 2020-08-25 | 佛山市力普鑫精密技术有限公司 | Single cycloid speed reduction bearing with strong load capacity |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5833405B2 (en) * | 2011-10-11 | 2015-12-16 | Ntn株式会社 | Magnetic load sensor and linear actuator for linear actuator |
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Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003074672A (en) * | 2001-05-24 | 2003-03-12 | Koyo Seiko Co Ltd | Pulley unit |
| JP2003139154A (en) * | 2001-11-06 | 2003-05-14 | Nsk Ltd | Bearing unit |
| CN104819253A (en) * | 2015-02-25 | 2015-08-05 | 佛山市诺尔贝机器人技术有限公司 | Multi-crankshaft cycloid speed reducer |
| CN208057914U (en) * | 2018-04-04 | 2018-11-06 | 海尚集团有限公司 | Vector cycloid speed reducer |
| CN109578540A (en) * | 2018-12-29 | 2019-04-05 | 王小三 | A kind of straight-tooth planetary gear ball Combined speed reducer |
| CN211343712U (en) * | 2019-08-16 | 2020-08-25 | 佛山市力普鑫精密技术有限公司 | Single cycloid speed reduction bearing with strong load capacity |
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