CN211975797U - Steel ring type friction transmission stepless speed changer - Google Patents
Steel ring type friction transmission stepless speed changer Download PDFInfo
- Publication number
- CN211975797U CN211975797U CN202020347438.8U CN202020347438U CN211975797U CN 211975797 U CN211975797 U CN 211975797U CN 202020347438 U CN202020347438 U CN 202020347438U CN 211975797 U CN211975797 U CN 211975797U
- Authority
- CN
- China
- Prior art keywords
- input
- friction
- output
- friction ring
- assembly
- 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.)
- Expired - Fee Related
Links
- 230000005540 biological transmission Effects 0.000 title claims abstract description 50
- 229910000831 Steel Inorganic materials 0.000 title claims abstract description 24
- 239000010959 steel Substances 0.000 title claims abstract description 24
- 230000007246 mechanism Effects 0.000 claims abstract description 43
- 238000003825 pressing Methods 0.000 claims description 19
- 239000000463 material Substances 0.000 abstract description 4
- 238000012856 packing Methods 0.000 abstract description 3
- 230000033228 biological regulation Effects 0.000 description 4
- 230000009347 mechanical transmission Effects 0.000 description 4
- 238000005096 rolling process Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 125000004122 cyclic group Chemical group 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 230000003252 repetitive effect Effects 0.000 description 1
Images
Landscapes
- Friction Gearing (AREA)
Abstract
The utility model relates to a steel ring formula friction drive buncher, including input flange assembly, output flange assembly, middle roller assembly is located between input flange assembly and the output flange assembly, and input flange assembly, the axial department of output flange assembly installs the loading system, the packing force through the loading system realizes the friction drive power between middle roller assembly and input output flange assembly, install the vice mechanism of friction between middle roller assembly and input output flange assembly, and the one end clamp of vice mechanism of friction is established between a terminal surface and the input flange assembly of middle roller assembly, the other end clamp of vice mechanism of friction is established between another terminal surface and the output flange assembly of middle roller assembly; the utility model discloses under fixed life-span, structure size, gear ratio, material and state condition, can improve transmission moment of torsion, increase the vice area of contact of friction.
Description
Technical Field
The utility model belongs to the technical field of continuously variable transmission, especially, relate to a steel ring formula friction drive continuously variable transmission who leans on middle friction pulley transmission and speed governing.
Background
A transmission is a mechanism used to vary the speed and torque from a power transmission and control device, such as an engine, and to fix or change the gear ratio of an output shaft to an input shaft in steps. A continuously variable transmission is a transmission that can achieve continuous changes in gear ratio to achieve the best match of the drive train to the engine operating conditions. In order to realize stepless speed change, three modes of liquid transmission, electric transmission and mechanical transmission can be adopted according to the transmission mode, but most of the mechanical transmission stepless speed changers adopting mechanical transmission in the market at present are provided, and the main reason that the mechanical transmission stepless speed changer adopting friction transmission can not transmit large torque is determined by the service life requirement of a product (a friction pair), but the structural design can not meet the mechanical property and fails. When the friction pair structure is shaped, the transmission torque is reduced to ensure or meet the service life requirement of the stepless speed changer, otherwise, when the service life requirement is specified, the friction pair structure is improved to improve the transmission torque. Such as: application No.: 2016102074282, a friction ring is arranged between an input and output flange and a column cone (gyro wheel), which ensures the vulnerable replacement and maintenance in practical application; the upper part of the inner end surface of the friction ring is abutted to the conical surface of the input conical section and the conical surface of the output conical section in a point contact mode, the contact mode enables the contact area of the friction ring to be small, the contact stress can be correspondingly increased, and the torque of the transmission is not improved.
At present, the friction pair of the automobile continuously variable transmission adopts a special steel belt and a special chain to meet the requirements of mechanics and service life, but the requirements of production technology and quality are very high, the mechanism is complex, the cost is high, and the failure rate is high.
Disclosure of Invention
An object of the utility model is to overcome the not enough of prior art existence, and provide one kind under fixed life-span, structure size, gear ratio, material and state condition, for improving the transmission moment of torsion, increase vice area of contact of friction for the steel ring formula friction drive buncher of purpose.
The utility model aims at accomplishing through following technical scheme, this kind of steel ring formula friction drive continuously variable transmission includes input flange assembly, output flange assembly, middle roller assembly is located input flange assembly with between the output flange assembly, just the axial department of input flange assembly, output flange assembly installs loading system, and the packing force through loading system realizes the friction drive power between middle roller assembly and input output flange assembly install the vice mechanism of friction between middle roller assembly and input output flange assembly, just the one end clamp of the vice mechanism of friction is established between a terminal surface and the input flange assembly of middle roller assembly, the other end clamp of the vice mechanism of friction is established between another terminal surface and the output flange assembly of middle roller assembly.
Preferably, the input flange assembly comprises an input flange and a first pressure rail, and the first pressure rail is mounted on the input flange; the output flange assembly comprises an output flange and a second pressure rail, and the second pressure rail is arranged on the output flange; and the first pressure rail and the second pressure rail are distributed oppositely.
Preferably, the pressurizing mechanism includes a central shaft, an input bearing, an output bearing, a disc spring, and a flange nut, the input bearing is installed at an axial end of the input flange, the output bearing is installed at an axial end of the output flange, the input and output bearings are respectively installed at two ends of the central shaft, and the disc spring is installed on the central shaft located at the input bearing end and is pressed by the flange nut.
Preferably, the middle roller assembly comprises a support, a gyro wheel and a guide shaft, the gyro wheel is arranged on the guide shaft and can axially move repeatedly, the guide shaft is circumferentially and uniformly arranged on the support and is inclined, and two ends of the guide shaft are connected with the support through bearings.
Preferably, the friction pair mechanism includes an input friction ring and an output friction ring, a radial end surface of the input friction ring is clamped between an end surface of the tourbillon and an annular groove provided on the first pressure rail, a radial end surface of the output friction ring is clamped between an end surface of the tourbillon and an annular groove provided on the second pressure rail, and the input friction ring and the output friction ring are pressed tightly between the annular grooves of the first pressure rail and the second pressure rail and the tourbillon by a pressing mechanism.
Preferably, the number of the friction pair mechanisms is equal to that of the gyros and the friction pair mechanisms are arranged in a one-to-one correspondence manner, the input friction ring and the output friction ring are arranged in a crossed manner, and the diameter of the output friction ring is smaller than that of the input friction ring.
Preferably, the first pressure rail and the second pressure rail are respectively provided with a circle of rack on the radial inner end surface, the input flange and the output flange are respectively provided with a circle of convex teeth and pressing blocks which are alternately arranged on the radial outer end surface, the convex teeth are meshed with the racks, and the pressing blocks are pressed on the inner radial wall of the pressure rail.
Preferably, the gyro wheel is rhomboid, two conical surfaces of the gyro wheel are respectively contacted with the input friction ring and the output friction ring, and the diameters of the input friction ring and the output friction ring are both larger than the cross section diameter of the conical surface of the gyro wheel.
Preferably, the input friction ring and the output friction ring are of steel ring type, and the inner end faces of the input friction ring and the output friction ring, which are in contact with the conical surface of the gyro wheel, are planes and are matched with the conical surface of the gyro wheel.
Preferably, the groove surfaces of the annular grooves of the first pressure rail and the second pressure rail are both arc-shaped, the outer end surfaces of the input friction ring and the output friction ring which are in contact with the annular grooves are both arc-shaped, and the outer end surfaces are positioned in the annular grooves and matched with the annular grooves.
The utility model has the advantages that: the friction pair mechanism with the steel ring type structure is additionally arranged between the input and output flange assembly and the middle roller body assembly, the contact area between the friction pair mechanism and the gyro wheel and between the friction pair mechanism and the pressing rail is increased, the problem that the large-torque transmission force cannot be transmitted due to the service life of the friction pair of the continuously variable transmission is solved, in order to effectively transmit power, the phenomenon that the structures cannot slip is guaranteed through the pressing force of the pressurizing mechanism, and therefore the whole transmission can achieve the effect of increasing the transmission torque.
Drawings
Fig. 1 is a schematic perspective view of the present invention.
Fig. 2 is a schematic view of the structure of the present invention.
Fig. 3 is a schematic view of the sectional structure a-a of fig. 2.
Fig. 4 is a schematic view of a connection structure between the gyro wheel and each pressure rail of the present invention.
Fig. 5 is an exploded view of the input flange assembly according to the present invention.
Fig. 6 is a schematic perspective view of the friction ring of the present invention.
The reference numbers in the drawings are respectively: 1. an input flange assembly; 2. an output flange assembly; 3. a middle roller assembly; 4. a pressurizing mechanism; 5. a friction pair mechanism; 6. an annular groove; 7. a rack; 8. a convex tooth; 9. briquetting; 11. an input flange; 12. a first rail pressing; 21. an output flange; 22. a second rail pressing; 31. a support; 32. A top wheel; 33. a guide shaft; 34. a bearing; 41. a central shaft; 42. an input bearing; 43. an output bearing; 44. a disc spring; 45. a flange nut; 51. inputting a friction ring; 52. and outputting the friction ring.
Detailed Description
The present invention will be described in detail with reference to the accompanying drawings: as shown in fig. 1, the utility model discloses an input flange assembly 1, output flange assembly 2, middle roller assembly 3 is located input flange assembly 1 with between output flange assembly 2, and input flange assembly 1, the axial department of output flange assembly 2 installs loading system 4, realizes the friction drive power between middle roller assembly 3 and the input output flange assembly through the packing force of loading system 4, install friction pair mechanism 5 between middle roller assembly 3 and the input output flange assembly, and the one end clamp of friction pair mechanism 5 is established between an terminal surface of middle roller assembly 3 and input flange assembly 1, the other end clamp of friction pair mechanism 5 is established between another terminal surface of middle roller assembly 3 and output flange assembly 2; the friction pair mechanism with the steel ring type structure is additionally arranged between the input and output flange assembly and the middle roller body assembly, the contact area between the friction pair mechanism and the gyro wheel and between the friction pair mechanism and the pressing rail is increased, the problem that the large-torque transmission force cannot be transmitted due to the service life of the friction pair of the continuously variable transmission is solved, in order to effectively transmit power, the phenomenon that the structures cannot slip is guaranteed through the pressing force of the pressurizing mechanism, and therefore the whole transmission can achieve the effect of increasing the transmission torque.
As shown in fig. 2 and 3, the power transmission sequence of the steel ring type friction transmission continuously variable transmission is as follows: the power is input from the central shaft 41 and is connected with the input flange 11, the input flange 11 is provided with the first pressure rail 12, the input friction ring 51 revolves in the annular groove 6 of the first pressure rail 12, the input friction ring 51 and one conical surface of the gyro wheel 32 mutually roll and frictionally transmit the power, the other conical surface mutually rolls and frictionally transmit the power to the second pressure rail 22 with the output friction ring 52, and the second pressure rail 2 is arranged on the output flange 21 and is power output by the output flange 21.
The speed regulation mode is as follows: the speed regulation mode of the continuously variable transmission is the speed regulation of the working diameter of the intermediate wheel; the two conical surfaces of the gyro wheel 32 are respectively in pressure contact with the input friction ring 51 and the output friction ring 52, and when the gyro wheel 32 moves towards the axial direction of the guide shaft 33, the diameters of contact surfaces of the gyro wheel 32, the input friction ring 51 and the output friction ring 52 are changed, so that the speed regulation purpose is achieved.
A pressurizing mode: in order to transmit power by effective rolling friction between the input friction ring 51 and the output friction ring 52 and the gyro wheel 32 and the two pressure rails, and prevent slipping; the input flange 11 and the output flange 21 are connected together by the central shaft 41 and the flange nut 45, are separated from each other by the bearing 34, and the disc spring 44 provides an axial pressing force to clamp the gyro wheel 32 between the input friction ring 51 and the output friction ring 52.
The motion mode of the friction pair is as follows: the two friction rings respectively roll in the annular grooves of the two pressure rails and revolve together, and simultaneously rotate around the central shaft 41, the friction force between the input friction ring 51 and the gyro wheel 32 drives the gyro wheel 32 to rotate around the guide shaft 33, and the friction force drives the output friction ring 52 to revolve with the output flange assembly.
The input flange assembly 1 comprises an input flange 11 and a first pressure rail 12, wherein the first pressure rail 12 is installed on the input flange 11; the output flange assembly 2 comprises an output flange 21 and a second pressure rail 22, and the second pressure rail 22 is installed on the output flange 21; and the first pressure rail 12 and the second pressure rail 22 are distributed oppositely, so that the middle roller body assembly 3 and the friction pair mechanism 5 can be clamped between the first pressure rail and the second pressure rail. As shown in fig. 5, a circle of rack 7 is respectively disposed on the radial inner end surfaces of the first pressure rail 12 and the second pressure rail 22, a circle of convex teeth 8 and a circle of pressing blocks 9 which are alternately arranged are respectively disposed on the radial outer end surfaces of the input flange 11 and the output flange 21, the convex teeth 8 are meshed with the rack 7 to enable the flanges and the pressure rails to realize meshing power transmission, the pressing blocks 9 are pressed on the inner radial walls of the pressure rails to enable the two oppositely arranged pressure rails to provide axial pressure, and the flange and the pressure rails are separated to be convenient to disassemble and maintain, and the cost is not too high when parts are replaced.
The pressurizing mechanism 4 comprises a central shaft 41, an input bearing 42, an output bearing 43, a disc spring 44 and a flange nut 45, wherein the input bearing 42 is installed at the axial end of the input flange 11, the output bearing 43 is installed at the axial end of the output flange 21, the input bearing and the output bearing are respectively installed at two ends of the central shaft 41, the disc spring 44 is installed on the central shaft 41 at the input bearing end and is pressed tightly through the flange nut 45; the friction force (i.e. friction pair) between the middle rolling body and the input and output structure of the mechanical stepless speed changer is used for transmitting power, the pressing force of the pressurizing mechanism is used for ensuring that the middle rolling body and the input and output structure cannot slip, and the magnitude of the friction force (F) is related to the pressing force (Q) and the friction coefficient (mu): f ═ μ Q. Therefore, the continuously variable transmission generally (with a determined structure size, materials and state) increases the pressing force to increase the friction force and transmit more power (torque). As the pressing force increases, the contact stress of the contact surface between the friction pairs increases, and the life of the friction pairs decreases (which can be concluded from the allowable contact stress calculation and the number of cyclic stresses). In order to ensure an increase in the transmission torque of the continuously variable transmission over a predetermined service life, the contact area of the friction partners must be increased, although the contact pressure must be increased, so that the service life cannot be reduced and the contact stress cannot be increased.
Middle roller assembly 3 includes support 31, top wheel 32, guiding axle 33, top wheel 32 installs but axial repetitive motion is gone up to guiding axle 33, just guiding axle 33 is the equipartition of circumference and arranges on the support 31 to along 41 axial distributions of center pin and be the slope form, just the both ends of guiding axle 33 with connect through bearing 34 between support 31, support 31 can be the axis removal of center pin 41 relatively, thereby drive top wheel 4 and remove the speed governing purpose that reaches buncher relatively guiding axle 33 axis.
The friction pair mechanism 5 comprises an input friction ring 51 and an output friction ring 52, a radial end surface of the input friction ring 51 is clamped between an end surface of the gyro wheel 32 and the annular groove 6 arranged on the first pressure rail 12, a radial end surface of the output friction ring 52 is clamped between an end surface of the gyro wheel 32 and the annular groove 6 arranged on the second pressure rail 22, and the input friction ring 51 and the output friction ring 52 are pressed between the annular grooves 6 of the first pressure rail 12 and the second pressure rail 22 and the gyro wheel 32 through a pressurizing mechanism 4; the outer end surfaces of the input friction ring 51 and the output friction ring 52 are in pressure contact with the annular groove 6 and revolve, and at the same time, rotate about the center line of the central shaft 41, the inner end surfaces of the input friction ring 51 and the output friction ring 52 are in pressure contact with the two end surfaces of the gyro wheel 32, and as the gyro wheel 32 moves along the axis of the guide shaft, the diameters of the contact surfaces also change.
The number of the friction pair mechanisms 5 is equal to that of the gyro wheels 32, and the friction pair mechanisms are arranged in a one-to-one correspondence manner, and the input friction ring 51 and the output friction ring 52 are arranged in a cross manner, so that the spatial arrangement is more compact, and the stability is better; the diameter of the output friction ring 52 is smaller than the diameter of the input friction ring 51.
As shown in fig. 4 and 6, the top wheel 32 is in a pyramid shape, two conical surfaces of the top wheel contact with the input friction ring 51 and the output friction ring 52 respectively, and the diameters of the input friction ring 51 and the output friction ring 52 are both larger than the cross-sectional diameter of the conical surface of the top wheel 32.
The input friction ring 51 and the output friction ring 52 are of steel ring structures, and are simpler than other structures (chains or steel belts and the like), lower in cost and high in reliability in view of mechanics and manufacturing cost; the inner end surface of the top wheel 32, which is contacted with the conical surface of the top wheel, is a plane and is matched with the conical surface of the top wheel 32; the groove surfaces of the annular grooves 6 of the first pressure rail 12 and the second pressure rail 22 are both arc-shaped, the outer end surfaces of the input friction ring 51 and the output friction ring 52 which are contacted with the annular grooves 6 are both arc surfaces, and the outer end surfaces are positioned in the annular grooves 6 and are matched with each other.
The "allowable contact stress" of the friction pair is also determined when the mechanical continuously variable transmission requires a specified service life, and in order to increase the transmission torque and not exceed the "allowable contact stress", the contact area of the friction pair must be increased.
The contact form of the pyramid gyro wheel without the friction ring and the pressure rail is the external contact of a cylinder and a plane. If one wants to reduce the contact stress (i.e. increase the transmission torque), the combined radius of curvature and the contact width of the friction pair contact surface must be increased according to the "hertzian equation". When the outer rings of the input friction ring 51 and the output friction ring 52 are contacted with the annular groove 6 of the pressure rail, the outer diameter of the friction rings is far larger than the diameter of the section of the conical surface of the diamond-cone gyro wheel, so that the comprehensive curvature radius is higher than that of the friction rings which are not adopted; meanwhile, the contact width of the contact surface is increased by the semi-circular arc contact form and is changed into an inner contact form (the hole is in contact with the shaft), and the comprehensive curvature radius of the contact surface is deduced to be increased according to the Hertz formula, so that the contact area is increased, and the contact stress is reduced; the inner ring surfaces of the input friction ring 51 and the output friction ring 52 are in contact with the outer diameter of the pyramid surface of the pyramid gyro wheel, the existing plane and cylinder contact mode is changed into an inner contact (hole and shaft) mode, and the comprehensive curvature radius is greatly increased by calculation according to the Hertz formula, so that the contact area is increased, the contact stress is reduced, and the transmission torque is increased.
The present invention is not limited to the above embodiments, and any change is made on the shape or material composition, and all the structural designs provided by the present invention are all the deformation of the present invention, which should be considered within the protection scope of the present invention.
Claims (10)
1. The utility model provides a steel ring formula friction drive buncher, includes input flange assembly (1), output flange assembly (2), middle roller assembly (3), its characterized in that: the middle roller assembly (3) is located between the input flange assembly (1) and the output flange assembly (2), a pressurizing mechanism (4) is installed at the axial positions of the input flange assembly (1) and the output flange assembly (2), friction transmission power between the middle roller assembly (3) and the input and output flange assembly is achieved through pressing force of the pressurizing mechanism (4), a friction pair mechanism (5) is installed between the middle roller assembly (3) and the input and output flange assembly, one end of the friction pair mechanism (5) is clamped between one end face of the middle roller assembly (3) and the input flange assembly (1), and the other end of the friction pair mechanism (5) is clamped between the other end face of the middle roller assembly (3) and the output flange assembly (2).
2. The steel ring type friction drive continuously variable transmission of claim 1, wherein: the input flange assembly (1) comprises an input flange (11) and a first pressure rail (12), wherein the first pressure rail (12) is installed on the input flange (11); the output flange assembly (2) comprises an output flange (21) and a second pressure rail (22), and the second pressure rail (22) is installed on the output flange (21); and the first pressure rail (12) and the second pressure rail (22) are distributed oppositely.
3. The steel ring type friction drive continuously variable transmission of claim 2, wherein: the pressurization mechanism (4) comprises a central shaft (41), an input bearing (42), an output bearing (43), a disc spring (44) and a flange nut (45), wherein the input bearing (42) is installed at the axial end of the input flange (11), the output bearing (43) is installed at the axial end of the output flange (21), the input bearing and the output bearing are respectively installed at two ends of the central shaft (41), the disc spring (44) is installed on the central shaft (41) located at the input bearing end, and the central shaft is tightly pressed through the flange nut (45).
4. The steel ring type friction drive continuously variable transmission of claim 3, wherein: middle roller assembly (3) are including support (31), top wheel (32), guiding axle (33), but top wheel (32) are installed but axial reciprocating motion on guiding axle (33), just guiding axle (33) are the equipartition of circumference and are arranged on support (31) and be the slope form, just the both ends of guiding axle (33) with connect through bearing (34) between support (31).
5. The steel ring type friction drive continuously variable transmission of claim 4, wherein: the friction pair mechanism (5) comprises an input friction ring (51) and an output friction ring (52), the radial end face of the input friction ring (51) is clamped between the end face of the gyro wheel (32) and an annular groove (6) formed in the first pressure rail (12), the radial end face of the output friction ring (52) is clamped between the end face of the gyro wheel (32) and the annular groove (6) formed in the second pressure rail (22), and the input friction ring (51) and the output friction ring (52) are tightly pressed between the annular grooves (6) of the first pressure rail (12) and the second pressure rail (22) and the gyro wheel (32) through a pressurizing mechanism (4).
6. The steel ring type friction drive continuously variable transmission of claim 5, wherein: the number of the friction pair mechanisms (5) is equal to that of the gyro wheels (32) and the friction pair mechanisms are arranged in a one-to-one correspondence manner, the input friction ring (51) and the output friction ring (52) are arranged in a crossed manner, and the diameter of the output friction ring (52) is smaller than that of the input friction ring (51).
7. The steel ring type friction drive continuously variable transmission of claim 2, wherein: the inner end faces of the first pressure rail (12) and the second pressure rail (22) in the radial direction are respectively provided with a circle of rack (7), the outer end faces of the input flange (11) and the output flange (21) in the radial direction are respectively provided with a circle of convex teeth (8) and pressing blocks (9) which are alternately arranged, the convex teeth (8) are meshed with the rack (7), and the pressing blocks (9) are tightly pressed on the inner radial wall of the pressure rail.
8. The steel ring type friction drive continuously variable transmission of claim 5, wherein: the gyro wheel (32) is in a pyramid shape, two conical surfaces of the gyro wheel are respectively contacted with the input friction ring (51) and the output friction ring (52), and the diameters of the input friction ring (51) and the output friction ring (52) are both larger than the diameter of the cross section of the conical surface of the gyro wheel (32).
9. The steel ring type friction drive continuously variable transmission of claim 8, wherein: the input friction ring (51) and the output friction ring (52) are of steel ring type, and the inner end faces of the input friction ring and the output friction ring, which are in contact with the conical surface of the gyro wheel (32), are planes and are matched with the conical surface of the gyro wheel (32).
10. The steel ring type friction drive continuously variable transmission of claim 5, wherein: the groove surfaces of the annular grooves (6) of the first pressure rail (12) and the second pressure rail (22) are arc-shaped, the outer end surfaces of the input friction ring (51) and the output friction ring (52) which are contacted with the annular grooves (6) are arc surfaces, and the outer end surfaces are positioned in the annular grooves (6) and are matched with each other.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020347438.8U CN211975797U (en) | 2020-03-19 | 2020-03-19 | Steel ring type friction transmission stepless speed changer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020347438.8U CN211975797U (en) | 2020-03-19 | 2020-03-19 | Steel ring type friction transmission stepless speed changer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN211975797U true CN211975797U (en) | 2020-11-20 |
Family
ID=73394551
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202020347438.8U Expired - Fee Related CN211975797U (en) | 2020-03-19 | 2020-03-19 | Steel ring type friction transmission stepless speed changer |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN211975797U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111396522A (en) * | 2020-03-19 | 2020-07-10 | 吉安市瑞鹏飞精密科技有限公司 | Steel ring type friction transmission stepless speed changer |
-
2020
- 2020-03-19 CN CN202020347438.8U patent/CN211975797U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111396522A (en) * | 2020-03-19 | 2020-07-10 | 吉安市瑞鹏飞精密科技有限公司 | Steel ring type friction transmission stepless speed changer |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101550995B (en) | Stepless speed change device of circularly arranged cone pulleys | |
| EP1045999B1 (en) | A continuously variable transmission device | |
| CN102725561B (en) | Full toroidal traction drive | |
| CN101479503B (en) | Toroidal type stepless transmission and stepless transmission | |
| WO2004070233A1 (en) | Traction drive type continuously variable transmission | |
| US9243694B2 (en) | Continuously variable transmission | |
| US7632208B2 (en) | Continuously variable transmissions | |
| CN211975797U (en) | Steel ring type friction transmission stepless speed changer | |
| US4167124A (en) | Variable-speed chain drive unit | |
| CN111396522A (en) | Steel ring type friction transmission stepless speed changer | |
| EP0400187B1 (en) | Infinitely variable traction roller transmission | |
| JP6507225B2 (en) | Conical disk type continuously variable transmission | |
| CN110857024A (en) | Power assembly for electric automobile | |
| CN115163757B (en) | Cycloidal pin gear planetary reducer | |
| CN111692306B (en) | Rolling type stepless speed changer | |
| JPS61112854A (en) | Speed reduction device with end face can | |
| JPH1163140A (en) | Continuously variable transmission equipped with idle pulley | |
| CN209943450U (en) | Stepless speed variator | |
| WO2011053187A1 (en) | Infinitely variable transmission, variable-speed drive, gear ratio range limiter and planetary gear | |
| JP7207636B2 (en) | Continuously variable transmission applied to gearbox with continuously variable transmission | |
| CN216200230U (en) | Novel stepless speed change device | |
| CN114483898B (en) | Speed regulating device of stepless speed changer | |
| US5051106A (en) | Transverse axis infinitely variable transmission | |
| CN110645328A (en) | Spherical surface structure stepless speed change device | |
| CN213479118U (en) | Device for improving bearing capacity of small-tooth-difference transmission output mechanism |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20201120 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |