CN211343712U - Single cycloid speed reduction bearing with strong load capacity - Google Patents
Single cycloid speed reduction bearing with strong load capacity Download PDFInfo
- Publication number
- CN211343712U CN211343712U CN201921341983.XU CN201921341983U CN211343712U CN 211343712 U CN211343712 U CN 211343712U CN 201921341983 U CN201921341983 U CN 201921341983U CN 211343712 U CN211343712 U CN 211343712U
- Authority
- CN
- China
- Prior art keywords
- roller
- shell
- grooves
- annular
- groove
- 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
Images
Landscapes
- Friction Gearing (AREA)
- Transmission Devices (AREA)
Abstract
The utility model discloses a simple cycloid reduction bearing with strong load capacity, which comprises an input shaft, wherein the input shaft comprises a first mounting part, an eccentric part and a second mounting part; a first shell is movably sleeved on the periphery of the first mounting part; the first shell is formed with an abdicating groove, the periphery of the eccentric part is movably sleeved with a driving disc, and the driving disc is positioned in the abdicating groove; a roller mechanism is arranged between the driving disc and the abdicating groove; the driving disc is distributed with a plurality of first roller grooves, the abdicating groove is distributed 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; a second shell is movably sleeved on the periphery of the second mounting part, and a plurality of ball positioning grooves are formed in the second shell; the utility model aims at providing a radial bearing capacity is strong, can bear heavy load and impact load, and is stand wear and tear, and transmission efficiency is high, the strong simple cycloid reduction bearing of load capacity that the noise is little.
Description
Technical Field
The utility model relates to a speed reduction bearing field especially relates to a simple cycloid speed reduction bearing that load capacity is strong.
Background
In the production process of mechanical equipment, the rotation speed ratio of two stages needs to be adjusted through a speed reducer, and the high-speed rotation of superior equipment is decelerated, so that a larger torque is obtained. The existing speed reduction bearing generally adopts a gear meshing mode for transmission, and the speed reduction effect is realized through the tooth difference generated between gears.
In the transmission process, the gears are meshed with each other, the friction resistance is large, the radial bearing capacity is poor, the anti-seismic performance is poor, and the tooth root is easy to break. The existing speed reduction bearing is generally driven by a cross disk, so that the size of the bearing is large, and the bearing cannot be applied to some precision equipment.
SUMMERY OF THE UTILITY MODEL
An object of the utility model is to provide a radial bearing capacity is strong, can bear heavy load and impact load, and is stand wear and tear, and transmission efficiency is high, the strong simple cycloid speed reduction bearing of load capacity of noise is little.
To achieve the purpose, the utility model adopts the following technical proposal: a simple cycloid speed reduction bearing with strong load capacity comprises an input shaft, wherein the input shaft comprises a first mounting part, an eccentric part and a second mounting part which are sequentially connected along the axial direction; a first shell is movably sleeved on the periphery of the first mounting part, and one end of the first shell, which is close to the eccentric part, extends to the periphery of the eccentric part; an annular abdicating 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 and located in the abdicating groove, and the eccentric part drives the driving disc to do eccentric motion in the abdicating groove; a roller mechanism is arranged between one end of the driving disc close to the first shell and the inner end face of the abdicating groove; a plurality of first roller grooves are distributed at one end, close to the first shell, of the driving disc, a plurality of second roller grooves which are in one-to-one correspondence with the first roller grooves are distributed at the inner end face of the abdicating groove, and the roller mechanism comprises a plurality of rollers which are correspondingly arranged between the first roller grooves and the second roller grooves; a second shell is movably sleeved on the periphery of the second mounting part, a plurality of ball positioning grooves are formed in one end, opposite to the driving disc, of the second shell along the circumferential direction, outer swinging grooves are formed in one end, opposite to the second shell, of the driving disc, and the number of the ball positioning grooves is larger than the wave number of the outer swinging grooves; balls are arranged in the ball positioning grooves, one ends of the balls are positioned in the corresponding ball positioning grooves, and the other ends of the balls are positioned in the epicycloidal grooves; the first shell is sequentially connected with a first annular shell and a second annular shell 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 cross roller mechanisms are arranged in the accommodating grooves.
Preferably, the inner end surface of the ball positioning groove is of a spherical crown structure; the epicycloidal groove comprises a plurality of arc-shaped grooves which are bent towards the outer side of the driving disc, the arc-shaped grooves are sequentially connected end to end along the circumferential direction to form a ring shape, and the inner bottom surface of each arc-shaped groove is of an arc-shaped groove structure; one end of the ball is positioned in the spherical crown, 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-shaped 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 counter bore and the depth of the second circular counter bore 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-angled end of the L-shaped structure faces the middle of the second shell; a first annular gap is formed in the inner end face of the first annular shell along the circumferential direction, and the first annular gap faces the second annular shell; a second annular gap is formed in the inner end face of the second annular shell along the circumferential direction, and the second annular gap faces the first annular shell; the radial section of the first annular gap is vertical to the radial section of the second annular gap; the holding tank is formed by the cooperation of first mounting groove, first annular breach and second annular breach, the radial section of holding tank is the rectangle structure.
Preferably, the crossed roller mechanism comprises a first roller, a second roller, a limiting ring and a plurality of limiting holes, and the plurality of limiting holes are 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 roller is provided with a plurality of, the second roller is provided with a plurality of, and is a plurality of first roller and a plurality of the second roller is crisscross to be set up in a plurality of spacing downtheholely, the axis of first roller with the axis mutually perpendicular of second roller, the both ends of first roller respectively with wherein two relative inner walls of holding tank parallel, the both ends of second roller respectively with the other two relative inner walls of holding tank parallel.
Preferably, a collar is formed between the first mounting portion and the eccentric portion.
Preferably, a first bearing is arranged between the first mounting part and the first housing.
Preferably, a second bearing is provided between the eccentric portion and the drive disc.
Preferably, a third bearing is arranged between the second mounting part and the second housing.
The utility model adopts the above structure, the ball positioning groove, the ball 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 to play a role in releasing the eccentricity of the driving disc in the transmission process, the roller is in linear contact with the first roller groove and the second roller groove, the radial bearing capacity is high, the heavy load or impact load can be borne, the friction coefficient is small, the high-speed roller is suitable for the working condition of high rotating speed, the processing technology of the roller is simple, and the installation is convenient; adopt ball constant head tank and ball complex mode, the ball is at the roll drive of ball constant head tank, is difficult to take place wearing and tearing, and the transmission is more high-efficient, and the noise is littleer, and is more durable, and bearing life is longer.
Drawings
The accompanying drawings are provided to further illustrate the present invention, but the content in the accompanying drawings does not constitute any limitation to the present invention.
Fig. 1 is a schematic perspective view of the present invention;
fig. 2 is a schematic side view of the present invention;
FIG. 3 is a schematic cross-sectional view taken along A-A of FIG. 2;
FIG. 4 is an enlarged partial schematic view at B of FIG. 3;
fig. 5 is a schematic structural view of the present invention with the first annular housing and the second annular housing 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, the driving plate and the input shaft of the present invention;
fig. 9 is a schematic perspective view of the driving disk and the input shaft of the present invention.
Wherein: the device comprises an input shaft 1, a first mounting part 1a, an eccentric part 1b, a second mounting part 1c, a shaft collar 1d, a first shell 2, a yielding groove 2a, a second roller groove 2b, a driving disk 3, a first roller groove 3a, a roller mechanism 4, a roller 4a, a second shell 5, a first mounting groove 5a, a ball positioning groove 6, an epicycloidal groove 7, an arc-shaped groove 7a, a ball 8, a first annular shell 9, a first annular notch 9a, a second annular shell 10, a second annular notch 10a, a crossed roller mechanism 11, a first roller 11a, a second roller 11b, a limiting ring 11c, a limiting hole 11d, a first bearing 12, a second bearing 13 and a third bearing 14.
Detailed Description
The technical solution of the present invention is further explained by the following embodiments with reference to the accompanying drawings.
Referring to fig. 1 to 9, the simple cycloid deceleration bearing with high load capacity of the present embodiment includes an input shaft 1, and is characterized in that the input shaft 1 includes a first mounting portion 1a, an eccentric portion 1b, and a second mounting portion 1c, which are sequentially connected along an axial direction.
The peripheral activity cover of first installation department 1a is equipped with first casing 2, being close to of first casing 2 the one end of eccentric portion 1b extends to the periphery of eccentric portion 1 b.
The utility model discloses a first casing 2, including eccentric portion 1b, the middle part shaping of first casing 2 is close to the one end of eccentric portion 1b has annular groove 2a of stepping down, the peripheral movable sleeve of eccentric portion 1b is equipped with driving-disc 3, driving-disc 3 is located in the groove 2a of stepping down, eccentric portion 1b drives driving-disc 3 is in it is eccentric motion to step down in the groove 2 a.
A roller mechanism 4 is arranged between one end of the driving disc 3 close to the first shell 2 and the inner end face of the abdicating groove 2 a; a plurality of first roller grooves 3a are distributed at one end, close to the first shell 2, of the driving disc 3, a plurality of second roller grooves 2b which correspond to the first roller grooves 3a in a one-to-one mode are distributed at the inner end face of the abdicating groove 2a, and the roller mechanism 4 comprises a plurality of rollers 4a which are correspondingly arranged between the first roller grooves 3a and the second roller grooves 2 b.
A second shell 5 is movably sleeved on the periphery of the second mounting part 1c, a plurality of ball positioning grooves 6 are formed in one end, opposite to the driving disk 3, of the second shell 5 along the circumferential direction, outer swinging wire grooves 7 are formed in one end, opposite to the second shell 5, of the driving disk 3, and the number of the ball positioning grooves 6 is larger than the wave number of the outer swinging wire grooves 7; the ball positioning grooves 6 are internally provided with balls 8, one ends of the balls 8 are positioned in the corresponding ball positioning grooves 6, and the other ends of the balls 8 are positioned in the epicycloidal grooves 7.
With the structure, the input shaft 1 is connected with an external driving device, when 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 serves as a power input end, and the second shell 5 serves 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 do eccentric motion in the abdicating groove 2a, and the roller mechanism 4 is used for releasing the eccentric motion of the driving disc 3, so that the sliding friction is reduced, and the loss is reduced. The ball constant head tank 6, ball 8 and the cooperation of epicycloidal groove 7 realize rolling transmission motion, utilize ball constant head tank 6 and epicycloidal groove 7 to produce the motion of poor tooth, make the rotational speed of second casing 5 reduce, realize the deceleration action of bearing, improved transmission efficiency, promoted the speed reduction ratio, reduced the wearing and tearing loss, the error is little, and the drive ratio error is little.
The second shell 5 is fixedly connected with an external frame, when the input shaft 1 is connected with an external driving device, the input shaft 1 serves as a power input end, and the first annular shell 9, the second annular shell 10 and the first shell 2 serve as power output ends. The input shaft 1 drives the eccentric part 1b to rotate, the second shell 5 is fixed, the balls 8, the driving disc 3 and the roller mechanism 4 are matched 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 reverse direction output can be achieved.
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 processed and manufactured.
The cross 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 the installation space, and reduces the shaft length and the processing cost.
The first roller groove 3a and the second roller groove 2b are matched to clamp the roller 4a, the driving disk 3 and the first shell 2 are driven through the roller 4a, and the eccentric action of the driving disk 3 is released in the driving process of the roller 4 a. In the transmission process of the driving disc 3 and the first shell 2, the roller 4a is in linear contact with the first roller groove 3a and the second roller groove 2b, the radial bearing capacity is high, the device is suitable for bearing heavy load or impact load, the friction coefficient is small, the device is suitable for working conditions with high rotating speed, the processing of the roller 4a is simple, the technological requirement is low, and the device is convenient to install.
Ball constant head tank 6 has stronger ability of resistance to wear, and ball 8 rolls the transmission between outer cycloid groove 7 and ball constant head tank 6, is difficult to take place wearing and tearing, and the transmission is more high-efficient, and the noise is little, and is more durable, and life is longer.
Referring to fig. 3, 7 and 8, the inner end surface of the ball positioning groove 6 is of a spherical cap type structure; the epicycloidal 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 sequentially connected end to end along the circumferential direction 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 cap, and the other end of the ball 8 is positioned in the arc-shaped groove 7 a.
Adopt this kind of structure, ball 8 is cliied in the cooperation of ball constant head tank 6 and epicycloid groove 7, makes things convenient for ball 8 to roll transmission in ball constant head tank 6 and epicycloid groove 7, converts sliding friction into rolling friction, reduces the friction loss between driving-disc 3 and the second casing 5, can carry out good transmission simultaneously.
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 a circular line with amplitude of a and circumscribing the circle with the diameter of the pitch circle of b.
Preferably, the number of the ball positioning grooves 6 is N, the number of the arc-shaped grooves 7a is N-1, the number of the balls 8 is N, and N is an integer greater than zero.
Adopt this kind of structure, adopt N ball constant head tank 6, N ball 8, the setting mode of N-1 arc wall 7a, make the difference tooth motion of production between ball constant head tank 6, ball 8 and the arc wall 7a, reach speed reduction drive's purpose, simultaneously, N ball can guarantee to keep good transmission effect between driving-disc 3 and the second casing 5, avoids producing the transmission clearance, causes the card to die or rotates inflexible phenomenon.
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 counter bore and the depth of the second circular counter bore is less than the height of the roller 4 a.
With this structure, the first circular counter bore has a diameter larger than that of the roller 4a, and the second circular counter bore has a diameter larger than that of the roller 4a, and the first roller groove 3a and the second roller groove 2b provide a sufficient biasing space for the roller 4a to enable the roller 4a to 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 of the driving disc 3 and the first shell 2 can be avoided, and friction loss is reduced.
Referring to fig. 3 and 4, an annular first mounting groove 5a is formed in the outer wall of the second housing 5 along the circumferential direction, and a radial section of the first mounting groove 5a has an L-shaped structure, and a right-angled end of the L-shaped structure faces the middle of the second housing 5.
A first annular gap 9a is formed in the inner end face of the first annular shell 9 along the circumferential direction, and the first annular gap 9a faces the second annular shell 10; a second annular gap 10a is formed in the inner end surface of the second annular shell 10 along the circumferential direction, and the second annular gap 10a faces the first annular shell 9; the radial section of the first annular notch 9a is perpendicular to the radial section of the second annular notch 10 a.
The holding tank is formed by the cooperation of a first mounting groove 5a, a first annular notch 9a and a second annular notch 10a, and the radial section of the holding tank is of a rectangular structure.
By adopting the structure, the first mounting groove 5a, the first annular gap 9a and the second annular gap 10a are matched to form a containing groove, so that the installation of the crossed roller mechanism 11 is facilitated, one end surface 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 surface of the first mounting groove 5a and the first annular gap 9a, the other end surface 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 surface 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, and 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 rollers, the second rollers 11b are provided with a plurality of rollers, the first rollers 11a and the second rollers 11b are arranged in the limiting holes 11d in a staggered mode, the central axis of the first rollers 11a is perpendicular to the central axis of the second rollers 11b, two ends of the first rollers 11a are respectively parallel to two opposite inner walls of the accommodating groove, and two ends of the second rollers 11b are respectively parallel to the other two opposite inner walls of the accommodating groove.
By adopting the structure, the first roller 11a and the second roller 11b are separated by matching the limiting ring 11c and the accommodating groove, the first roller 11a and the second roller 11b are prevented from being contacted with each other to accelerate abrasion, the output stability of the second shell 5 is improved, the rotating precision is good, and the bearing can bear larger axial and radial loads by matching the first annular shell 9, the second annular shell 10, the crossed roller mechanism 11 and the second shell 5.
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 the 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 first mounting portion 1a and the first housing 2 to be movably connected.
Preferably, a second bearing 13 is provided between the eccentric portion 1b and the drive disc 3.
With this structure, the provision of the second bearing 13 enables the movable connection between the eccentric portion 1b and the drive plate 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, the third bearing 14 is provided to keep the movable connection between the second mounting portion 1c and the second housing 5.
During operation, input shaft 1 is connected with external drive arrangement, first casing 2, first annular shell 9 and second annular shell 10 all with outside frame fixed connection, input shaft 1 is as power input end, second casing 5 is connected with outside connecting device as power output end. The input shaft 1 drives the eccentric part 1b to rotate, the eccentric part 1b drives the driving disc 3 to do eccentric motion in the abdicating groove 2a, and the roller mechanism 4 is used for releasing the eccentric motion of the driving disc 3, so that the sliding friction is reduced, and the loss is reduced. The ball constant head tank 6, ball 8 and the cooperation of epicycloidal groove 7 realize rolling transmission motion, utilize ball constant head tank 6 and epicycloidal groove 7 to produce the motion of poor tooth, make the rotational speed of second casing 5 reduce, realize the deceleration action of bearing, improved transmission efficiency, promoted the speed reduction ratio, reduced the wearing and tearing loss, the error is little, and the drive ratio error is little.
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 serves as a power input end, and the first annular shell 9, the second annular shell 10 and the first shell 2 serve as power output ends. The input shaft 1 drives the eccentric part 1b to rotate, the second shell 5 is fixed, the balls 8, the driving disc 3 and the roller mechanism 4 are matched 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 reverse direction output can be achieved.
The technical principle of the present invention is described above with reference to specific embodiments. The description is made for the purpose of illustrating the principles of the invention and should not be construed in any way as limiting the scope of the invention. Based on the explanations herein, those skilled in the art will be able to conceive of other embodiments of the present invention without any inventive effort, which would fall within the scope of the present invention.
Claims (10)
1. A simple cycloid speed reduction bearing with strong load capacity comprises an input shaft, and is characterized in that the input shaft comprises a first mounting part, an eccentric part and a second mounting part which are sequentially connected along the axial direction;
a first shell is movably sleeved on the periphery of the first mounting part, and one end of the first shell, which is close to the eccentric part, extends to the periphery of the eccentric part;
an annular abdicating 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 and located in the abdicating groove, and the eccentric part drives the driving disc to do eccentric motion in the abdicating groove;
a roller mechanism is arranged between one end of the driving disc close to the first shell and the inner end face of the abdicating groove; a plurality of first roller grooves are distributed at one end, close to the first shell, of the driving disc, a plurality of second roller grooves which are in one-to-one correspondence with the first roller grooves are distributed at the inner end face of the abdicating groove, and the roller mechanism comprises a plurality of rollers which are correspondingly arranged between the first roller grooves and the second roller grooves;
a second shell is movably sleeved on the periphery of the second mounting part, a plurality of ball positioning grooves are formed in one end, opposite to the driving disc, of the second shell along the circumferential direction, outer swinging grooves are formed in one end, opposite to the second shell, of the driving disc, and the number of the ball positioning grooves is larger than the wave number of the outer swinging grooves; balls are arranged in the ball positioning grooves, one ends of the balls are positioned in the corresponding ball positioning grooves, and the other ends of the balls are positioned in the epicycloidal grooves;
the first shell is sequentially connected with a first annular shell and a second annular shell 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 cross roller mechanisms are arranged in the accommodating grooves.
2. The strong load bearing simple cycloid reduction bearing of claim 1 wherein the inner end surface of the ball locating groove is of a spherical crown type configuration; the epicycloidal groove comprises a plurality of arc-shaped grooves which are bent towards the outer side of the driving disc, the arc-shaped grooves are sequentially connected end to end along the circumferential direction to form a ring shape, and the inner bottom surface of each arc-shaped groove is of an arc-shaped groove structure; one end of the ball is positioned in the spherical crown, and the other end of the ball is positioned in the arc-shaped groove.
3. The strong load bearing simple cycloid reduction bearing of claim 2 wherein the number of ball detent grooves is N, the number of arc grooves is N-1, the number of balls is N, N is an integer greater than zero.
4. A high capacity single cycloid reduction bearing of claim 1 wherein the first roller groove is a first circular counterbore having a diameter greater than the diameter 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 counter bore and the depth of the second circular counter bore is less than the height of the roller.
5. The strong load bearing simple cycloid deceleration bearing of claim 1 wherein the outer wall of the second housing is circumferentially provided with an annular first mounting groove, the radial section of the first mounting groove is L-shaped, and the right-angled end of the L-shaped structure faces the middle of the second housing;
a first annular gap is formed in the inner end face of the first annular shell along the circumferential direction, and the first annular gap faces the second annular shell; a second annular gap is formed in the inner end face of the second annular shell along the circumferential direction, and the second annular gap faces the first annular shell; the radial section of the first annular gap is vertical to the radial section of the second annular gap;
the holding tank is formed by the cooperation of first mounting groove, first annular breach and second annular breach, the radial section of holding tank is the rectangle structure.
6. The strong-load-capacity simple cycloid reduction bearing of claim 5, wherein the crossed roller mechanism comprises a first roller, a second roller, a limiting ring and a limiting hole, and the limiting hole is provided with a plurality of limiting holes which are 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 roller is provided with a plurality of, the second roller is provided with a plurality of, and is a plurality of first roller and a plurality of the second roller is crisscross to be set up in a plurality of spacing downtheholely, the axis of first roller with the axis mutually perpendicular of second roller, the both ends of first roller respectively with wherein two relative inner walls of holding tank parallel, the both ends of second roller respectively with the other two relative inner walls of holding tank parallel.
7. A high load capacity single cycloid reduction bearing as claimed in claim 1 wherein a collar is formed between the first mounting portion and the eccentric portion.
8. A high load capacity single cycloid reduction bearing as claimed in claim 1 wherein a first bearing is provided between the first mounting portion and the first housing.
9. The strong load bearing simple cycloid reduction bearing of claim 1 wherein a second bearing is disposed between the eccentric portion and the drive plate.
10. A high load capacity single cycloid reduction bearing as claimed in 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 |
|---|---|---|---|
| CN201921341983.XU CN211343712U (en) | 2019-08-16 | 2019-08-16 | Single cycloid speed reduction bearing with strong load capacity |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921341983.XU CN211343712U (en) | 2019-08-16 | 2019-08-16 | Single cycloid speed reduction bearing with strong load capacity |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN211343712U true CN211343712U (en) | 2020-08-25 |
Family
ID=72135743
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201921341983.XU Active CN211343712U (en) | 2019-08-16 | 2019-08-16 | Single cycloid speed reduction bearing with strong load capacity |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN211343712U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110374988A (en) * | 2019-08-16 | 2019-10-25 | 佛山市力普鑫精密技术有限公司 | A kind of single pendulum line speed reduction bearing that load-bearing capacity is strong |
-
2019
- 2019-08-16 CN CN201921341983.XU patent/CN211343712U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110374988A (en) * | 2019-08-16 | 2019-10-25 | 佛山市力普鑫精密技术有限公司 | A kind of single pendulum line speed reduction bearing that load-bearing capacity is strong |
| CN110374988B (en) * | 2019-08-16 | 2024-03-26 | 佛山市力普鑫精密技术有限公司 | Simple cycloid speed reducing bearing with strong load capacity |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN108468758B (en) | Speed reducer | |
| KR20130048412A (en) | Decelerator and motor brake with the same | |
| CN207093681U (en) | A kind of Cycloid Steel Ball Planetary Transmission mechanism and its joint of robot deceleration device | |
| CN106352024B (en) | A kind of single eccentric short transmission chain retarder | |
| CN211343712U (en) | Single cycloid speed reduction bearing with strong load capacity | |
| CN113309842A (en) | Cycloidal pin gear harmonic speed reducer | |
| CN109578540B (en) | Straight tooth planet wheel ball combined type speed reducer | |
| CN110374991B (en) | Double-wave-line ball speed reducing bearing with high rotation precision | |
| CN210461387U (en) | Double-wave-line ball reduction bearing with high rotation precision | |
| CN210769832U (en) | Double-wave-line speed reduction bearing with high bearing capacity | |
| CN107017733B (en) | Miniature hub motor | |
| CN110374988B (en) | Simple cycloid speed reducing bearing with strong load capacity | |
| CN211648782U (en) | Single wave line speed reduction bearing of high incorruptibility | |
| CN111442064B (en) | Cycloid speed reducer with dynamic balance | |
| CN210265711U (en) | Cycloidal gear speed reducer | |
| CN210770053U (en) | Cycloidal pin gear speed reducing mechanism | |
| CN110374990B (en) | Single-wave-line speed reducing bearing with high durability | |
| CN213776101U (en) | Roller type rotary drive | |
| CN212717869U (en) | Double-arc herringbone-tooth planetary gear transmission mechanism | |
| WO2021184423A1 (en) | Bispherical cycloidal roller nutation drive device | |
| CN2535610Y (en) | Rolling-contact type swinging adjustable-gear planetary speed-reducer | |
| CN212455371U (en) | But decelerator of pre-compaction regulation | |
| CN220687946U (en) | Cycloidal pin gear speed reducer with large reduction ratio | |
| CN212407473U (en) | Planetary reducer | |
| TWI820817B (en) | Conjugate cam reducer |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |