CN217926975U

CN217926975U - Single-stage cycloidal speed reducer

Info

Publication number: CN217926975U
Application number: CN202221776610.7U
Authority: CN
Inventors: 余杰先; 潘阳
Original assignee: Southern University of Science and Technology
Current assignee: Southern University of Science and Technology
Priority date: 2022-07-11
Filing date: 2022-07-11
Publication date: 2022-11-29
Anticipated expiration: 2032-07-11

Abstract

The utility model discloses a single-stage cycloidal reducer, which comprises a pin gear shell, wherein the outer contour of the pin gear shell is cylindrical and forms a shell; the flange component is sleeved in the pin gear shell and rotates relative to the pin gear shell so as to output the decelerated motion; the cycloid wheel assembly is sleeved in the pin gear shell and arranged between the flange assemblies, and the cycloid wheel assembly is meshed with a pin gear pin arranged in the pin gear shell; the input shaft assembly is matched with the cycloid wheel assembly to decelerate the received motion and then output through the flange assembly, and the deceleration transmission can be realized through a simple structure.

Description

Single-stage cycloidal speed reducer

Technical Field

The utility model relates to a transmission connecting device, in particular to single-stage cycloidal reducer.

Background

Generally, a motor has a characteristic of high rotation speed and low torque, so that it is difficult to drive a large load, and if a heavy object needs to be pushed by the motor, the output motion needs to be decelerated by a speed reducer, thereby increasing the torque.

Common reducers include cycloidal reducers and planetary reducers. Compared with a planetary reducer, the cycloidal reducer in the prior art has high production cost and low power density, so that the cycloidal reducer is obviously lower than the planetary reducer in market share. The biggest factor causing the result is that the design and production of the cycloid gear are complex, the reject ratio of products is high, and parts of the cycloid speed reducer, such as an input structure, a pin gear structure, a flange structure and the like, corresponding to the cycloid gear are also complex in structure, so that the cycloid speed reducer is high in production cost, high in structural complexity and low in power density, and cannot compete with a planetary speed reducer for market share easily.

Accordingly, there is a need for improvements and developments in the art.

SUMMERY OF THE UTILITY MODEL

In view of the deficiencies of the prior art, the object of the present invention is to provide a single-stage cycloidal reducer with simple structure and low production cost. The cycloidal reducer aims at solving the problems of complex structure and high production cost of the existing cycloidal reducer.

The technical scheme of the utility model as follows:

a single stage cycloidal reducer comprising:

the outer contour of the pin gear shell is cylindrical and forms a shell of the single-stage cycloidal speed reducer;

the flange assembly is sleeved in the pin gear shell and rotates relative to the pin gear shell so as to output decelerated motion;

the cycloidal wheel assembly is sleeved in the pin gear shell and arranged between the flange assemblies, and the cycloidal wheel assembly is meshed with a pin gear pin arranged in the pin gear shell;

the input shaft assembly is sleeved in the cycloidal gear assembly and matched with the cycloidal gear assembly to decelerate the received motion and then output through the flange assembly.

In one embodiment, the flange assembly comprises:

the first flange is sleeved in one end of the pin gear shell;

the second flange is sleeved in the other end of the pin gear shell;

the first flange and the second flange are fixedly connected through screws to form the flange assembly.

In one embodiment, the single stage cycloidal reducer further comprises:

the first main bearing is sleeved between the pin gear shell and the first flange so as to support the first flange and limit the axial position of the first flange in the pin gear shell;

and the second main bearing is sleeved between the pin gear shell and the second flange so as to support the second flange and limit the axial direction of the second flange in the pin gear shell.

In one embodiment, the pin gear housing comprises:

a first main bearing position arranged at one end of the pin gear shell facing the first flange to accommodate the first main bearing;

a second main bearing position, wherein the second main bearing position is arranged at one end, facing the second flange, of the pin gear shell so as to accommodate the second main bearing;

the pin gear pin positions are arranged between the first main bearing position and the second main bearing position and are uniformly distributed along the inner wall of the pin gear shell so as to contain the pin gear pins, and the pin gear pin positions are matched with the first main bearing and the second main bearing to limit the axial direction of the pin gear pins in the pin gear shell.

In one embodiment, the cycloidal gear assembly comprises:

the first cycloidal gear is arranged between the first flange and the second flange and is sleeved outside the input shaft assembly, the first cycloidal gear comprises a first base circle and first cycloidal gear teeth arranged around the first base circle, and the first cycloidal gear teeth are meshed with the pin gear pins so as to realize that the first cycloidal gear rotates through one tooth in the opposite direction when the input shaft assembly rotates for one circle;

the second cycloidal gear is arranged between the first cycloidal gear and the second flange and is sleeved outside the input shaft assembly, the second cycloidal gear comprises a second base circle and second cycloidal gear teeth arranged around the second base circle, and the second cycloidal gear teeth are meshed with the pin gear pin so as to realize that the second cycloidal gear rotates by one tooth in the opposite direction when the input shaft assembly rotates for one circle;

the first cycloid wheel and the second cycloid wheel are arranged eccentrically.

In one embodiment, the input shaft assembly comprises:

the main input shaft is matched with the first cycloidal gear and the second cycloidal gear to decelerate the received motion and then output through the first flange and the second flange;

the auxiliary input shafts sequentially penetrate through the first flange, the first cycloidal gear, the second cycloidal gear and the second flange and surround the main input shaft to be uniformly arranged so as to cooperate with the first cycloidal gear and the second cycloidal gear to decelerate received motion and then to be output through the first flange and the second flange.

In one embodiment, the main input shaft comprises:

the input interface is positioned at one end of the main input shaft and is connected with a motion device needing to be decelerated;

the first bearing position is close to the input interface and is arranged corresponding to the first flange so as to be provided with a first bearing, the inner ring of the first bearing is sleeved outside the first bearing position, and the outer ring of the first bearing is sleeved in the first flange so as to realize that the first flange is sleeved outside the main input shaft;

the second bearing position is close to the first bearing position and is arranged corresponding to the first cycloidal gear so as to install a second bearing, the inner ring of the second bearing is sleeved outside the second bearing position, and the outer ring of the second bearing is sleeved in the first cycloidal gear so as to realize that the first cycloidal gear is sleeved outside the main input shaft;

a third bearing position which is close to the second bearing position and is arranged corresponding to the second cycloid wheel so as to install a third bearing, wherein the inner ring of the third bearing is sleeved outside the third bearing position, and the outer ring of the third bearing is sleeved inside the second cycloid wheel so as to realize that the second cycloid wheel is sleeved outside the main input shaft;

the fourth bearing is close to the third bearing and corresponds the second flange sets up to install the fourth bearing, the inner circle cover of fourth bearing is established outside the fourth bearing position, the outer lane cover of fourth bearing is established in the second flange, in order to realize the second flange cover is established outside the main input shaft.

In one embodiment, the second bearing position and the third bearing position are symmetrically displaced by 180 ° with respect to the central axis of the main input shaft, forming an eccentric shaft arrangement, and the eccentricity between the second bearing position and the third bearing position is equal to the eccentricity between the first and second cycloidal gears.

In one embodiment, the secondary input shaft comprises:

a fifth bearing position, which is arranged at one end of the auxiliary input shaft and corresponds to the first flange so as to mount a fifth bearing, wherein the inner ring of the fifth bearing is sleeved outside the fifth bearing position, and the outer ring of the fifth bearing is sleeved inside the first flange so as to realize that the first flange is sleeved outside the auxiliary input shaft;

a sixth bearing position which is close to the fifth bearing position and is arranged corresponding to the first cycloidal gear so as to install a sixth bearing, wherein the inner ring of the sixth bearing is sleeved outside the sixth bearing position, and the outer ring of the sixth bearing is sleeved inside the first cycloidal gear so as to realize that the first cycloidal gear is sleeved outside the auxiliary input shaft;

a seventh bearing position, which is close to the sixth bearing position and is arranged corresponding to the second cycloidal gear so as to install a seventh bearing, wherein an inner ring of the seventh bearing is sleeved outside the seventh bearing position, and an outer ring of the seventh bearing is sleeved inside the second cycloidal gear so as to realize that the second cycloidal gear is sleeved outside the auxiliary input shaft;

and the eighth bearing position is close to the seventh bearing position and corresponds to the second flange, so that the eighth bearing is installed, the inner ring of the eighth bearing is sleeved outside the eighth bearing position, the outer ring of the eighth bearing is sleeved in the second flange, and the second flange is sleeved outside the auxiliary input shaft.

In one embodiment, the sixth bearing location and the seventh bearing location are symmetrically displaced by 180 ° with respect to the central axis of the secondary input shaft, forming an eccentric shaft arrangement, and the eccentricity between the sixth bearing location and the seventh bearing location is equal to the eccentricity between the first and second cycloidal gears.

Has the advantages that: the utility model provides a single-stage cycloidal reducer, which comprises a needle gear shell, wherein the outer contour of the needle gear shell is cylindrical and forms a shell of the single-stage cycloidal reducer; the flange assembly is sleeved in the pin gear shell and rotates relative to the pin gear shell to output the decelerated motion; the cycloidal wheel assembly is sleeved in the pin gear shell and arranged between the flange assemblies, and the cycloidal wheel assembly is meshed with a pin gear pin arranged in the pin gear shell; and the input shaft assembly is sleeved in the cycloid wheel assembly and matched with the cycloid wheel assembly to reduce the received motion and then output through the flange assembly, the single-stage cycloid speed reducer takes the shell as a pin gear shell to accommodate the flange assembly, the cycloid wheel assembly and the input shaft assembly, the compact connection among the assemblies is realized, and meanwhile, the mutual matching realization of speed reduction transmission is ensured, the whole device is high in power density and low in structural complexity, the whole volume is reduced, so that the effects of reducing the production cost and improving the market application occupancy rate are achieved, and good social benefits can be generated.

Drawings

Fig. 1 is a cross-sectional view of a single-stage cycloidal reducer of the present invention;

fig. 2 is an exploded view of the single-stage cycloidal reducer of the present invention;

fig. 3 is a schematic view of a pin gear shell of the single-stage cycloidal reducer according to the present invention;

fig. 4 is an exploded view of a flange assembly of the single-stage cycloidal reducer of the present invention;

fig. 5 is a schematic view of a cycloid wheel assembly of the single-stage cycloid speed reducer of the present invention.

Fig. 6 is an exploded view of the main input shaft of the single-stage cycloidal reducer of the present invention.

Fig. 7 is an exploded view of the auxiliary input shaft of the single-stage cycloidal reducer of the present invention.

Fig. 8 is a schematic diagram showing the cooperation between the input assembly and the cycloidal wheel assembly of the single-stage cycloidal reducer of the present invention.

Detailed Description

The utility model provides a single-stage cycloidal reducer, for making the utility model discloses a purpose, technical scheme and effect are clearer, clear and definite, following right the utility model discloses further detailed description. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.

It should be noted that the terms "center", "upper", "lower", "left", "right", "inner", "outer", "vertical", "horizontal", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplification of description, but do not indicate or imply that the structures referred to must have a specific orientation or must be constructed in a specific orientation, and should not be construed as limiting the present invention.

In addition, the articles "a" and "the" may refer broadly to the singular or plural unless the context specifically states otherwise. If there is a description in an embodiment of the present invention referring to "first", "second", etc., the description of "first", "second", etc. is for descriptive purposes only and is not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature.

The utility model provides a single-stage cycloid speed reducer, as shown in fig. 1, single-stage cycloid speed reducer includes the pin gear shell 100, sets up in the pin gear shell 100 and can be relative pin gear shell 100 pivoted flange subassembly 200, the cover is established in the pin gear shell 100 and set up and be in cycloid wheel subassembly 300 and the cover between the flange subassembly 200 establish input shaft subassembly 400 in cycloid wheel subassembly 300, cycloid wheel subassembly 300 with the meshing of pin gear pin 131 in the pin gear shell 100, so input shaft subassembly 400 with cycloid wheel subassembly 300 cooperation is realized working as when input shaft subassembly 400 is rotatory a week cycloid wheel subassembly 300 is at the distance that opposite direction rotated a tooth, thereby will single-stage cycloid speed reducer passes through after the motion speed reduction that external motion equipment received flange subassembly 200 exports. Single-stage cycloid speed reducer structure complexity is low, and is small, and is with low costs to still less part can realize higher power density, more is favorable to cycloid speed reducer's market to be used.

Specifically, as shown in fig. 2 and 3, the outer contour of the pin gear housing 100 is cylindrical and substantially in the shape of a cylindrical housing, and forms a housing of the single-stage cycloidal reducer to accommodate other components, so as to ensure compact connection between the components and ensure that all the components can be matched with each other to realize speed reduction transmission. Further, a first main bearing position 110 is provided in one end of the pin gear housing 100 to accommodate a first main bearing 211, and a second main bearing position 120 is provided in the other end of the pin gear housing 100 to accommodate a second main bearing 221. The pin gear shell 100 is supported by the first main bearing 211 and the second main bearing 221 and accommodates the flange assembly 200, so that the flange assembly 200 is coaxial with the pin gear shell 100, the flange assembly 200 can freely rotate relative to the pin gear shell 100, the decelerated motion is output to corresponding equipment, and a shell of the single-stage cycloidal reducer is used as the pin gear shell to accommodate other components, so that the overall structure is more compact, fewer components are needed for deceleration, the structure is simple, and the market popularization is facilitated.

Further, between the first main bearing position 110 and the second main bearing position 120, a plurality of pin gear pin positions 130 are provided on an inner wall of the pin gear housing 100 to accommodate the pin gear pins 131. The pin gear positions 130 are uniformly arranged along the inner wall of the pin gear housing 100, so that the pin gear pins 131 are parallel to the axial direction of the pin gear housing 100. Further, the uniform diameter of the pin pins 130 is the base circle diameter of the cycloid wheel assembly 300, and the ratio of the number of the pin pins 130 to the number of cycloid gear teeth of the cycloid wheel assembly 300 is (n + 1): n, so as to ensure that the number of the pin pins 131 is 1 more than the number of the cycloid gear teeth of the cycloid wheel in the cycloid wheel assembly 300, therefore, when the input shaft assembly 400 rotates for one circle, the cycloid wheel assembly 300 moves one tooth in the opposite direction, the rotation motion of the input shaft assembly 400 is decelerated to the rotation motion of the cycloid wheel assembly 300, and the deceleration of the input motion is completed.

Further, as shown in fig. 1, the pin gear 130 is engaged with the first main bearing 211 and the second main bearing 221 such that both ends of the pin gear 131 respectively abut against the first main bearing 211 and the second main bearing 221, thereby limiting an axial upper limit of the pin gear 131 in the pin gear housing 100 and preventing the pin gear 131 from falling out of the pin gear 130.

Further, as shown in fig. 3, a flange 140 is further disposed on the pin gear housing 100. The flange 140 is disposed on the outer wall of the pin gear housing 100 in a form of a convex rib and is disposed along the circumferential direction of the pin gear housing 100 to fixedly connect the single-stage cycloidal reducer with a target device, so that the single-stage cycloidal reducer can stably receive a motion to be reduced, and stably output the reduced motion to a specific device, thereby facilitating market popularization of the single-stage cycloidal reducer.

As shown in fig. 4, the flange assembly 200 includes a first flange 210 and a second flange 220, and the first flange 210 and the second flange 220 are fixed by a screw 230 and a screw hole 240 to form the flange assembly 200, and the cycloidal gear assembly 300 is clamped between the first flange 210 and the second flange 220. Further, a through hole is formed in the flange assembly 200 corresponding to the input shaft assembly 400, so that the input shaft assembly 400 can pass through the through hole.

Further, an inner ring of the first main bearing 211 is sleeved on the first flange 210, and an outer ring of the first main bearing 211 is sleeved in the pin gear housing 100. The first flange 210 is supported by the first main bearing 211 and axially limited in the pin gear housing 100 by the first flange 210, so that the first flange 210 is prevented from falling off. And the first main bearing 211 ensures that the first flange 210 is coaxial with the pin gear housing 100, and the first flange 210 can freely rotate relative to the pin gear housing 100, and outputs the decelerated motion to corresponding equipment, so that the structure is simple, and the assembly and disassembly are convenient.

Further, an inner ring of the second main bearing 221 is sleeved on the second flange 220, and an outer ring of the second main bearing 221 is sleeved in the pin gear housing 100. The second flange 220 is supported by the second main bearing 221 and axially limited in the pin gear housing 100 by the second flange 220, so that the second flange 220 is prevented from falling off. And the second main bearing 221 ensures that the second flange 220 is coaxial with the pin gear housing 100, and the second flange 220 can freely rotate relative to the pin gear housing 100, so that the second flange is matched with the first flange 210 to output the decelerated motion to corresponding equipment, and the structure is simple and the assembly and disassembly are convenient.

Further, as shown in fig. 5, the cycloid wheel assembly 300 includes a first cycloid wheel 310 and a second cycloid wheel 320. The first cycloidal gear 310 and the second cycloidal gear 320 have the same structure, but the first cycloidal gear 310 and the second cycloidal gear 320 are eccentrically arranged, as shown in fig. 8, so as to ensure that a phase difference exists between the first cycloidal gear 310 and the second cycloidal gear 320 during the rotation process. Optionally, the phase difference is 180 °.

Further, as shown in fig. 5, the first cycloid wheel 310 includes: a base circle 311; cycloid gear teeth 312 which are arranged on the outer edge of the base circle 311 and are axially arranged along the base circle 311; a main input shaft location 313 and a secondary input shaft location 314 disposed within the base circle 311 and relative to the input shaft assembly 400; and lightening holes 315 arranged in the base circle 311 and uniformly around the central axis. By designing the lightening holes 315, the weight of the first cycloidal gear 310 may be reduced. The second cycloidal gear 320 has the same structure as the first cycloidal gear 310, and includes a second base circle 321, second cycloidal gear teeth 322, a second main input shaft 323, a second auxiliary input shaft 324, and a second lightening hole 325, which are correspondingly disposed, the second cycloidal gear 320 and the first cycloidal gear 310 are only disposed in an eccentric manner during assembly, and other structures are completely the same, so the structure of the second cycloidal gear 320 will not be described again here.

Further, as shown in fig. 1, the first cycloid wheel 310 is disposed between the first flange 210 and the second flange 220, and the second cycloid wheel 320 is disposed between the first cycloid wheel 310 and the second flange 220, so that the cycloid wheel assembly 300 is disposed between the flange assemblies. Further, as shown in fig. 8, the cycloid gear teeth 312 of the first and second cycloid gears 310 and 320 are engaged with the pin gear 131, and the number of the cycloid gear teeth 312 is 1 less than the number of the pin gear pins 131. In this way, due to the characteristics of the tooth profile curves of the first and second cycloidal gears 310 and 320 and the limitation of the pin 131, the movement of the first and second cycloidal gears 310 and 320 becomes a planar movement having both revolution and rotation. When the input shaft assembly 400 rotates for one circle, the first cycloid wheel 310 and the second cycloid wheel 320 rotate by one tooth in the direction opposite to the direction of the input shaft assembly 400, so that the speed is reduced, a lower output speed is obtained after the flange assembly 200 outputs motion, the speed reduction effect is realized by a simple structure, the power density is high, the structure complexity is low, and the market share of the single-stage cycloid speed reducer is more favorably improved.

Further, a spacer may be disposed between the first flange 210 and the first cycloidal gear 310, and a spacer may be disposed between the second flange 220 and the second cycloidal gear 320, so as to limit the first cycloidal gear 310 and the second cycloidal gear 320 in the axial direction of the pin gear housing 100, respectively, and provide a lubricating effect.

Further, as shown in fig. 2, the input shaft assembly 400 includes a main input shaft 410 and a plurality of sub input shafts 420, the main input shaft 410 is coaxial with the needle housing 100, and the plurality of sub input shafts 420 are uniformly arranged around the main input shaft 410. Optionally, input shaft subassembly 400 includes threely vice input shaft 420 just vice input shaft 420 encircles main input shaft 410 sets up at interval 120 each other, through vice input shaft 420 is supplementary main input shaft 410 cooperates cycloid wheel subassembly 300 realizes the speed reduction to rotary motion, and is supplementary simultaneously flange subassembly 400 outputs the rotary motion after slowing down for whole structure is compacter, stable, need not additionally to increase the part and can avoid vibrating and influence output stability.

As shown in fig. 6, an input interface 419 is disposed at one end of the main input shaft 410, the input interface 419 is disposed in a flat manner, and the main input shaft 410 is connected to a motion device to be decelerated through the input interface 419, so as to input a motion to be decelerated to the single-stage cycloidal reducer. Further, the main input shaft 410 is provided with a first bearing position 411, a second bearing position 412, a third bearing position 413 and a fourth bearing position 414 in this order from one end of the input port 419 to the other end. When the main input shaft 410 passes through the through holes of the first flange 210 and the second flange 220 and the main input shaft position 313 of the first cycloidal gear 310 and the second cycloidal gear 320 sequentially passes through the first flange 210, the first cycloidal gear 310, the second cycloidal gear 320 and the second flange 220, the first bearing position 411 corresponds to the first flange 210, the second bearing position 412 corresponds to the first cycloidal gear 310, the third bearing position 413 corresponds to the second cycloidal gear 320, and the fourth bearing position 414 corresponds to the second flange 220.

Further, the second bearing position 412 and the third bearing position 413 are symmetrical and shifted by 180 ° with respect to the central axis of the main input shaft 410, forming an eccentric shaft arrangement, and the eccentricity between the second bearing position 412 and the third bearing position 413 is equal to the eccentricity between the first cycloidal gear 310 and the second cycloidal gear 320. So as to drive the first cycloid wheel 310 and the second cycloid wheel 320 to move when the main input shaft 410 rotates.

Further, as shown in fig. 6, the main input shaft 410 is further provided with a first bearing 415, a second bearing 416, a third bearing 417 and a fourth bearing 418, respectively. Wherein, the inner ring of the first bearing 415 is sleeved on the first bearing position 411, and the outer ring of the first bearing 415 is sleeved in the through hole of the first flange 210, so as to realize that the first flange 210 is sleeved outside the main input shaft 410; the inner ring of the second bearing 416 is sleeved on the second bearing position 412, and the outer ring of the second bearing 416 is sleeved in the main input shaft position 313 of the first cycloidal gear 310, so that the first cycloidal gear 310 is sleeved outside the main input shaft 410; the inner ring of the third bearing 417 is sleeved on the third bearing position 413, and the outer ring of the third bearing 417 is sleeved in the main input shaft position of the second cycloidal gear 320, so that the second cycloidal gear 320 is sleeved outside the main input shaft 410; the inner race of the fourth bearing 418 is arranged on the fourth bearing 414, and the outer race of the fourth bearing 418 is arranged in the through hole of the second flange 220, so that the second flange 220 is arranged outside the main input shaft 410.

Further, since the second bearing 412 and the third bearing 413 are eccentric shafts and have the same eccentricity as the first cycloidal gear 310 and the second cycloidal gear 320, when the main input shaft 410 receives input motion through the input interface 419, the second bearing 416 and the third bearing 417 rotate synchronously, and the phase difference between the two bearings is 180 °, so as to synchronously drive the first cycloidal gear 310 and the second cycloidal gear 320 to move, thereby ensuring that the main input shaft 410 rotates for one circle, the first cycloidal gear 310 and the second cycloidal gear 320 move in reverse direction for one tooth, so as to realize deceleration of the input motion, and then output the motion through the flange assembly 200, thereby obtaining a lower output speed. Single-stage cycloid wheel speed reducer utilizes simple structure can realize the reduction gearing effect, and power density is big, the structure complexity is low, can effectively improve market share to produce good social.

Further, bushings may be disposed between the first bearing 415 and the second bearing 416, between the second bearing 416 and the third bearing 417, and between the third bearing 417 and the fourth bearing 418, so as to limit the positions of the first bearing 415, the second bearing 416, the third bearing 417, and the fourth bearing 418 in the axial direction of the pin gear housing 100, and prevent the components from being displaced relatively during operation, which affects the transmission effect.

As shown in fig. 7, the sub input shaft 420 is provided with a fifth bearing 421, a sixth bearing 422, a seventh bearing 423, and an eighth bearing 424 in this order from one end to the other end. When the auxiliary input shaft 420 passes through the through holes of the first flange 210 and the second flange 220 and the auxiliary input shaft 314 of the first cycloidal gear 310 and the second cycloidal gear 320 sequentially passes through the first flange 210, the first cycloidal gear 310, the second cycloidal gear 320 and the second flange 220, the fifth bearing 421 corresponds to the first flange 210, the sixth bearing 422 corresponds to the first cycloidal gear 310, the seventh bearing 423 corresponds to the second cycloidal gear 320, and the eighth bearing 424 corresponds to the second flange 220.

Further, the sixth bearing position 422 and the seventh bearing position 423 are symmetrical with respect to the central axis of the secondary input shaft 420 and are offset by 180 °, forming an eccentric shaft arrangement, and the eccentricity between the sixth bearing position 422 and the seventh bearing position 423 is equal to the eccentricity between the first cycloidal gear 310 and the second cycloidal gear 320. So as to drive the first and second cycloidal gears 310 and 320 to move when the auxiliary input shaft 420 rotates.

As shown in fig. 7, a fifth bearing 425, a sixth bearing 426, a seventh bearing 427, and an eighth bearing 428 are further provided on the sub input shaft 420, respectively. An inner ring of the fifth bearing 425 is sleeved on the fifth bearing position 421, and an outer ring of the fifth bearing 425 is sleeved in the through hole of the first flange 210, so that the first flange 210 is sleeved outside the auxiliary input shaft 420; an inner ring of the sixth bearing 426 is sleeved on the sixth bearing position 422, and an outer ring of the sixth bearing 426 is sleeved in the auxiliary input shaft 314 of the first cycloidal gear 310, so that the first cycloidal gear 310 is sleeved outside the auxiliary input shaft 420; an inner ring of the seventh bearing 427 is sleeved on the seventh bearing position 423, and an outer ring of the seventh bearing 427 is sleeved in the secondary input shaft position of the second cycloidal gear 320, so that the second cycloidal gear 320 is sleeved outside the secondary input shaft 420; the inner ring of the eighth bearing 428 is sleeved on the eighth bearing location 424, and the outer ring of the eighth bearing 428 is sleeved in the through hole of the second flange 220, so that the second flange 220 is sleeved outside the auxiliary input shaft 420.

Further, since the sixth bearing 422 and the seventh bearing 423 are eccentric shafts and have the same eccentricity as the first cycloidal gear 310 and the second cycloidal gear 320, when the secondary input shaft 420 rotates along with the main input shaft 410, the sixth bearing 426 and the seventh bearing 427 rotate synchronously with a phase difference of 180 ° to drive the first cycloidal gear 310 and the second cycloidal gear 320 to move, so as to ensure that the secondary input shaft 420 rotates one circle, the first cycloidal gear 310 and the second cycloidal gear 320 move in reverse direction by one tooth, thereby realizing the deceleration of the input motion, and outputting the motion through the flange assembly 200 to obtain a lower output speed. Single-stage cycloid wheel speed reducer utilizes simple structure can realize the speed reduction transmission effect, and power density is big, the structure complexity is low, can effectively improve market share to produce good social.

Further, bushings are arranged between the fifth bearing 425 and the sixth bearing 426, between the sixth bearing 426 and the seventh bearing 427, and between the seventh bearing 427 and the eighth bearing 428, so as to limit the position of the fifth bearing 425, the sixth bearing 426, the seventh bearing 427, and the eighth bearing 428 in the axial direction of the pin gear housing 100, and prevent the relative displacement of the components during the operation from affecting the transmission effect.

The following description specifically describes the working process of the single-stage cycloidal reducer of the present invention:

after the single-stage cycloidal speed reducer is assembled, the pin gear housing 100 stably accommodates all other components, and a main input shaft 410 and a secondary input shaft 420 in an input shaft assembly 400 sequentially pass through a first flange 210, a first cycloidal gear 310, a second cycloidal gear 320 and a second flange 220, wherein the first flange 210 is fixedly connected with the second flange 220 to form a flange assembly 200, and the first cycloidal gear 310 and the second cycloidal gear 320 are clamped in the middle. At this time, the first and second cycloidal gears 310 and 320 are engaged with the pin gear 131 provided in the pin gear housing 100, as shown in fig. 8, and the first and second cycloidal gears 310 and 320 have a phase difference of 180 °, and the number of the pin gear 131 is 1 more than the number of the cycloidal gear teeth of the first and second cycloidal gears 310 and 320.

The input shaft assembly 400 is connected with an external motion device needing speed reduction through an input interface 419 of the main input shaft 410, and the main input shaft 410 and the auxiliary input shaft 420 are driven to rotate by input motion and drive the first cycloidal gear 310 and the second cycloidal gear 320 in the cycloidal gear assembly 300 to move. At this time, the first and second cycloidal gears 310 and 320 perform a planar motion of revolution and rotation due to characteristics of a tooth profile curve and limitation of the pin 131, and as the main input shaft 410 rotates one turn, the first and second cycloidal gears 310 and 320 rotate one tooth in a direction opposite to the rotation direction of the main input shaft 410, so that the rotation motion of the main input shaft 410 is decelerated to the rotation motion of the first and second cycloidal gears 310 and 320, and the deceleration of the motion is completed. The motion of the gerotor assembly 300 is then output through the first flange 210 and the second flange 220 of the flange assembly 200 to achieve a low speed motion.

In summary, the single-stage cycloidal speed reducer provided by the utility model comprises a pin gear shell, wherein the outer contour of the pin gear shell is cylindrical and forms a shell of the single-stage cycloidal speed reducer; the flange assembly is sleeved in the pin gear shell and rotates relative to the pin gear shell so as to output decelerated motion; the cycloidal wheel assembly is sleeved in the pin gear shell and arranged between the flange assemblies, and the cycloidal wheel assembly is meshed with a pin gear pin arranged in the pin gear shell; and the input shaft assembly is sleeved in the cycloid wheel assembly and matched with the cycloid wheel assembly to reduce the received motion and then output through the flange assembly, the single-stage cycloid speed reducer takes the shell as a pin gear shell to accommodate the flange assembly, the cycloid wheel assembly and the input shaft assembly, the compact connection among the assemblies is realized, and meanwhile, the mutual matching realization of speed reduction transmission is ensured, the whole device is high in power density and low in structural complexity, the whole volume is reduced, so that the effects of reducing the production cost and improving the market application occupancy rate are achieved, and good social benefits can be generated.

It is to be understood that the invention is not limited to the above-described embodiments, and that modifications and variations may be made by those skilled in the art in light of the above teachings, and all such modifications and variations are intended to be included within the scope of the invention as defined in the appended claims.

Claims

1. A single stage cycloidal reducer comprising:

the flange assembly is sleeved in the pin gear shell and rotates relative to the pin gear shell to output the decelerated motion;

the input shaft assembly is sleeved in the cycloidal gear assembly and is matched with the cycloidal gear assembly to decelerate the received motion and then output through the flange assembly.

2. The single stage cycloidal reducer of claim 1 wherein said flange assembly comprises:

the first flange is sleeved in one end of the pin gear shell;

the second flange is sleeved in the other end of the pin gear shell;

3. The single stage cycloidal reducer of claim 2 further comprising:

4. The single stage cycloidal reducer of claim 3 wherein said pin gear housing comprises:

5. The single stage cycloidal reducer of claim 2 wherein said cycloidal wheel assembly comprises:

the first cycloidal gear and the second cycloidal gear are eccentrically arranged.

6. The single stage cycloidal reducer of claim 5 wherein said input shaft assembly comprises:

one end of the main input shaft is connected with a movement device needing to be decelerated, the other end of the main input shaft sequentially penetrates through the first flange, the first cycloid wheel, the second cycloid wheel and the second flange, and the main input shaft is matched with the first cycloid wheel and the second cycloid wheel to decelerate the received movement and then outputs the decelerated movement through the first flange and the second flange;

the auxiliary input shafts sequentially penetrate through the first flange, the first cycloid wheel, the second cycloid wheel and the second flange and surround the main input shaft to be uniformly arranged so as to be matched with the first cycloid wheel and the second cycloid wheel to decelerate received movement and then to be output through the first flange and the second flange.

7. The single stage cycloidal reducer of claim 6 wherein said primary input shaft comprises:

8. The single stage cycloidal reducer of claim 7 wherein said second bearing location and said third bearing location are symmetrically offset 180 ° with respect to a central axis of said main input shaft forming an eccentric shaft arrangement and an eccentricity between said second bearing location and said third bearing location is equal to an eccentricity between said first cycloidal gear and said second cycloidal gear.

9. The single stage cycloidal reducer of claim 6 wherein the secondary input shaft comprises:

and the eighth bearing position is close to the seventh bearing position and corresponds to the second flange so as to install an eighth bearing, the inner ring of the eighth bearing is sleeved outside the eighth bearing position, and the outer ring of the eighth bearing is sleeved in the second flange so as to realize that the second flange is sleeved outside the auxiliary input shaft.

10. The single stage cycloidal reducer of claim 9 wherein said sixth bearing location and said seventh bearing location are symmetrically offset 180 ° with respect to a central axis of said secondary input shaft forming an eccentric shaft arrangement and an eccentricity between said sixth bearing location and said seventh bearing location is equal to an eccentricity between said first cycloidal gear and said second cycloidal gear.