CN210318396U - Friction transmission planetary speed increasing device suitable for high input rotating speed - Google Patents
Friction transmission planetary speed increasing device suitable for high input rotating speed Download PDFInfo
- Publication number
- CN210318396U CN210318396U CN201920954787.3U CN201920954787U CN210318396U CN 210318396 U CN210318396 U CN 210318396U CN 201920954787 U CN201920954787 U CN 201920954787U CN 210318396 U CN210318396 U CN 210318396U
- Authority
- CN
- China
- Prior art keywords
- planet
- wheel
- sun
- outer ring
- planet wheel
- 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
- Retarders (AREA)
Abstract
The utility model provides a friction drive planet speed increaser suitable for high input speed, including input shaft, web, output shaft, shell and planetary gear train, wherein: the input shaft and the web plate are assembled into a whole in a rigid connection mode to drive the outer ring to rotate; the outer ring, the planet wheel and the sun wheel are installed in an extrusion mode, the outer ring, the planet wheel and the sun wheel and a planet carrier form a planet wheel train together, the planet carrier is in transmission through friction force, the planet carrier is in rigid connection with the shell, a bearing installation hole is formed in the planet carrier, the inner diameter of the bearing installation hole is larger than the outer diameter of a planet wheel bearing, and a slope effect is generated during movement to increase transmission torque; the output shaft is rigidly connected with the sun gear, and the axes are overlapped. The utility model discloses the moment that can transmit promotes along with the rotational speed increase, and the even central line of sun gear atress does not squint.
Description
Technical Field
The utility model relates to a friction drive planet speed increasing device who is suitable for high input speed especially is applied to the acceleration rate field that needs transmission moment to rise and increase along with input speed.
Background
In the prior art, in order to obtain a high step-up ratio, a planetary transmission is generally used instead of a parallel gear transmission.
Japanese patent laid-open No. 4-203421 discloses a planetary gear mechanism, but it has the following disadvantages: the service life of the planetary gear train bearing is reduced due to noise and vibration generated by the engagement of the planetary gear mechanism under the condition of high-speed rotation; in order to reduce the problems of gear meshing noise and vibration, the machining precision and the assembling precision of the gear must be improved, so that the problem of higher production cost is caused.
Japanese patent laying-open No. 11-502596 discloses a friction drive planetary gear train using a deformable outer race, but has the following disadvantages: the outer ring, the planet wheel and the sun wheel are easy to slip at a high rotating speed, and power and torque cannot be effectively transmitted; in order to avoid the slipping phenomenon under the condition of high rotating speed, the pressing force of the outer ring to the planet wheel needs to be increased, and the pressing force can cause the friction loss to be aggravated when the planet wheel rotates at low speed; meanwhile, in order to prevent slipping at a high rotating speed and ensure proper pressing force at a low rotating speed, the requirements on the processing precision and the special assembly process of the outer ring and the planet wheel are high.
US2344078 discloses a friction drive planetary gear in which the centre line of the planet wheel and the planet wheel shaft is located at the pitch diameter, and when the planet wheel meshes with the sun wheel, the transmission of torque is ensured by adjusting the contact width of the planet wheel and the sun wheel. But the disadvantages are also obvious: as the rotational speed increases, the torque that the planetary gear train can transmit gradually decreases, because the centrifugal force on the planet gears reduces the friction between the sun gear and the planet gears.
Danish patent DK 171047B 1 and chinese patent ZL 02808233.8(WO2002/064997a1) disclose a friction drive planetary gear that automatically adjusts the torque transmitting capacity of the planetary gear according to the rotational speed. The device is designed with one or more planet wheels, and the inner hole of the planet wheel is larger than the outer diameter of the support shaft of the planet wheel. In motion, the sun gear centerline is closer to the planet support shaft centerline than to the planet centerline, so that an eccentric mechanism is formed at the planet gear. Along with the increase of the rotating speed of the planetary gear train, the planetary gear deforms under the action of centrifugal force, a slope effect is formed by the planetary gear and the planetary gear shaft eccentric mechanism, and the increase of the transmission torque is realized. However, the invention limits that at least one planet wheel inner hole is matched with the outer diameter of the planet wheel shaft without a movable gap, which can cause uneven stress on the sun wheel.
Chinese patent CN 1432721a discloses a supercharger which uses a friction drive planetary device in which the outer ring has an eccentric amount relative to the sun wheel, and one or more planetary wheels are not mounted on the planetary wheel shaft but around the sun wheel through an elastic mechanism, and the planetary wheels can move in the radial and normal directions relative to the sun wheel. However, the invention limits at least one planet wheel to be fixedly arranged on the planet wheel shaft, and the stress of the sun wheel can be uneven.
SUMMERY OF THE UTILITY MODEL
The utility model provides a friction drive planet speed increaser that is suitable for high input speed, aim at:
1. the invention solves the problems that in the prior friction transmission planetary speed increasing device, one or more planetary gears are concentrically and fixedly arranged on a planetary carrier and are inconsistent with other eccentrically arranged planetary gears, so that a sun gear is subjected to the action of a rotating bending moment during operation, the center of the sun gear deviates along with different rotating speeds, and the stress is uneven under the high-speed condition.
2. The stable operation of the planetary gear system under the condition of ultrahigh rotating speed is ensured, and the vibration and noise of the device are effectively inhibited;
3. when the planetary gear train runs at a high speed, the transmitted torque automatically increases along with the increase of the rotating speed without slipping, so that the work requirement of work machinery (such as a centrifugal machine) arranged on an output shaft of the planetary gear train is met, and meanwhile, when the planetary gear train runs at a low speed, the friction torque is lower, and large driving loss is not generated.
In order to achieve the above object, the utility model adopts the following technical scheme:
a friction drive planetary speed increasing device suitable for high input rotating speed is characterized in that: the planetary gear train comprises an input shaft, a web plate, an output shaft, a shell and a planetary gear train, wherein:
the input shaft and the web plate are assembled into a whole in a rigid connection mode to drive the outer ring to rotate;
the outer ring, the planet wheel and the sun wheel are installed in an extrusion mode, the outer ring, the planet wheel and the sun wheel and a planet carrier form a planet wheel train together, the planet carrier is in transmission through friction force, the planet carrier is in rigid connection with the shell, a bearing installation hole is formed in the planet carrier, the inner diameter of the bearing installation hole is larger than the outer diameter of a planet wheel bearing, and a slope effect is generated during movement to increase transmission torque;
the output shaft is rigidly connected with the sun gear, and the axes are overlapped.
And an installation groove is formed in the circumferential direction of one end of the outer ring, and the web plate is installed in the groove.
The central axis of the outer ring is coincident with the central axis of the sun wheel.
The planet wheel quantity is 3 at least, and all planet wheel central axis are equal with the distance between the sun gear central axis, and around the even distribution of sun gear circumferential direction.
The planet wheels are identical in terms of geometry, tolerances, materials and mounting on the planet carrier.
All the mounting holes in the planet carrier are identical in size and tolerance.
The planet wheel and the planet wheel supporting shaft are of an integrated structure or are rigidly connected into a whole.
The sun wheel is provided with a shaft shoulder.
The inner diameter of the bearing mounting hole is larger than the outer diameter of the planet wheel bearing and is replaced by the inner diameter of the planet wheel bearing which is larger than the outer diameter of the planet wheel supporting shaft, or the inner diameter of the bearing mounting hole is larger than the outer diameter of the planet wheel supporting shaft.
The utility model has the advantages that:
1. the utility model discloses well all planet wheel geometric dimensions, material and mounting means are unanimous, and planet wheel system is the during operation under the high input rotational speed condition, and all planet wheels act on the radial force on the sun gear unanimous with normal force size, and along the unanimous distribution of circumferencial direction, do not form the rotatory moment of flexure that acts on the sun gear along its central line, and the skew does not take place for the sun gear the central axis when static and motion.
2. The utility model discloses in through the unanimous installation of planet wheel, make the planet wheel act on the power equipartition on the planet carrier and join in marriage and be zero, only produce pure torque to the planet carrier.
3. The utility model discloses well all planet wheels and support shaft unanimous, simple structure, easy manufacturing, the cost is lower.
Drawings
FIG. 1 is a schematic view of a first example assembly of the present invention;
FIG. 2 is a schematic view of an installation mode of an input shaft, a web plate and a planetary gear train outer ring;
FIG. 2A is a front cross-sectional view of the input shaft, web and outer race of the planetary gear set;
FIG. 3 is a schematic diagram of the relative position relationship of the components of the planetary gear train when the planetary gear train is at rest;
FIG. 4 is a schematic diagram of the relative position relationship of the components of the planetary gear train during movement;
FIGS. 5A, 5B and 5C are partial cross-sectional views of a planet support shaft at a planet carrier mounting location in different examples;
fig. 6 is a force analysis diagram of the sun gear when the planetary gear train is in operation.
Description of reference numerals: i-an input shaft; an O-output shaft; 2a, 2b, 2 c-planet; 4-outer ring; 5a, 5b, 5 c-a planet wheel support shaft; 7-a planet carrier; 8-sun gear; 20a, 20b, 20 c-planet wheel bearings; 21-a web; 22-bearing mounting holes; aa-a-sun central axis; ac-c-the planet central axis.
Detailed Description
Some specific embodiments of the invention will be described in detail below, by way of example and not by way of limitation, with reference to the accompanying drawings. The same reference numbers in the drawings identify the same or similar elements or components. Those skilled in the art will appreciate that the drawings are not necessarily drawn to scale.
Referring to fig. 1, 2 and 3, the present invention provides a friction drive planetary speed increasing device suitable for high input speed, which is characterized in that: including input shaft I, web 21, output shaft O, shell 1 and planetary gear train, wherein:
the input shaft I and the web plate 21 are assembled into a whole in a rigid connection mode to drive the outer ring 4 to rotate;
the outer ring 4, the planet wheels 2a, 2b and 2c and the sun wheel 8 are mounted in an extrusion mode, the planet wheels and the planet carrier 7 form a planet wheel train together, the planet carrier 7 is in transmission through friction force, the planet carrier 7 is in rigid connection with the shell 1, a bearing mounting hole 22 is formed in the planet carrier 7, the inner diameter of the bearing mounting hole 22 is larger than the outer diameter of the planet wheel bearings 20a, 20b and 20c, and a slope effect is generated during movement to increase transmission torque;
the output shaft O is rigidly connected with the sun gear 8, and the axes are overlapped.
And one end of the outer ring 4 is circumferentially provided with an installation groove, and the web plate 21 is installed in the groove.
The central axis of the outer ring 4 is coincident with the central axis of the sun wheel 8.
The number of the planet wheels 2a, 2b and 2c is at least 3, and the distances between the central axes of all the planet wheels 2a, 2b and 2c and the central axis of the sun wheel 8 are equal and are evenly distributed around the circumference of the sun wheel 8.
The geometry, tolerances, materials and mounting on the planet carrier 7 of the planet wheels 2a, 2b, 2c are identical.
All the mounting holes 22 of the planet carrier 7 have the same dimensions and tolerances.
The planet wheels 2a, 2b and 2c and the planet wheel supporting shafts 5a, 5b and 5c are of an integral structure or are rigidly connected into a whole.
The sun wheel 8 is provided with shoulders 23, 24.
The bearing mounting hole 22 has an inner diameter larger than the outer diameter of the planet wheel bearings 20a, 20b, 20c, and is replaced by the planet wheel bearings 20a, 20b, 20c having an inner diameter larger than the outer diameter of the planet wheel support shafts 5a, 5b, 5c, or by the bearing mounting hole 22 having an inner diameter larger than the outer diameter of the planet wheel support shafts 5a, 5b, 5 c.
In the first embodiment of the present invention, the outer diameter of the planetary gear train outer ring 4 is determined according to the maximum torque of the input shaft to be transmitted by the planetary gear train. And determining the inner diameter of the outer ring 4 and the outer diameter of the sun gear 8 according to the speed ratio required to be realized by the planetary gear train, thereby determining the transmission ratio of the planetary gear train. Preferably, the gear ratio of the gear train is maintained between 8 and 12, and the calculation formula of the gear ratio is as follows:
the pressing force among the outer ring 4, the planet wheels 2a, 2b, 2c and the sun wheel 8 is mainly determined by the start-up non-slip of the planetary gear train, the rotating speed range of the planetary gear train during movement and the torque which needs to be transmitted by the planetary gear train.
Referring to fig. 2 and 2A, as shown in fig. 2 and 2A, a slot is formed at one end of the outer ring 4, and a web 21 is installed in the slot of the outer ring 4 to ensure that the torque transmitted from the input shaft I to the web 21 is transmitted to the outer ring 4. Under the condition of high rotating speed, the radial deformation of the outer ring 4 and the web plate 21 caused by the action of centrifugal force can be inconsistent, and the deformation displacement of the web plate 21 and the outer ring 4 in the radial direction is not limited by the grooving. The web 21 for transmitting torque may be in-line, "cross-line" or other form of lightweight construction. The input shaft I is rigidly connected to the web 21 by means of a spline connection, an interference connection or a threaded connection.
Referring to fig. 3, as shown in fig. 3, all the planetary gears 2a, 2b, 2c in the planetary gear train are uniformly distributed in the circumferential direction around the central axis Aa-a of the sun gear 8, and the materials, dimensions and tolerances of all the planetary gears 2a, 2b, 2c are the same. The planet wheels 2a, 2b, 2c are rigidly connected to a planet wheel support shaft 5a, 5b, 5 c. The planet wheel supporting shafts 5a, 5b and 5c are arranged in the bearing mounting holes 22 on the planet carrier 7 through the same planet wheel bearings 20a, 20b and 20c, and the sizes and various tolerances of the bearing mounting holes 22 on the planet carrier 7 are also completely the same, so that the condition that the radial resultant force borne by the sun wheel 8 is not zero due to different supporting modes or dimensional tolerances of one or more planet wheels is avoided.
When the planetary gear train is static, the central axis Aa-a of the sun wheel 8 and the central axis of the outer ring 4 are coincident, and the distances between the central axes Ac-c of all the planetary wheels 2a, 2b and 2c and the central axis Aa-a of the sun wheel 8 are the same.
Referring to FIG. 4, as shown in FIG. 4, the input shaft I and the web 21 drive the outer ring 4 to rotate under the friction force
And
under the action of the planetary gear train, the planetary gear train enters a motion state, and the planetary carrier 7 is rigidly connected with the shell 1 and always kept fixed. The planet wheel 2a and the planet wheel support shaft 5a are rigidly assembled into a whole, the planet wheel support shaft 5a and the planet wheel bearing 20a are installed in the bearing installation hole 22 of the planet carrier 7 together, and because the outer diameter of the planet wheel bearing 20a is smaller than the inner diameter of the bearing installation hole 22 on the planet carrier 7, the planet wheel system is enabled to displace due to inertia effect (the outer ring 4 also generates certain deformation therewith) when moving, the displacement direction is radially far away from the central axis of the sun wheel 8 and forms an angle theta direction with the horizontal position, and the azimuth angle theta of the displacement is different along with the different rotating speeds. At a certain speed, the planet wheel 2a moves to the position shown in fig. 4, the outer wall of the planet wheel bearing 20a contacts with the inner wall of the bearing mounting hole 22, and the planet carrier 7 generates a reaction force F for the planet carrier wheel shaft 5a to inhibit the inertia movement thereof2aBecause the resultant force of the planet wheels in the motion state is 0, the following are obtained:
from the above formula, in the numerical value FRca,aIs equal to FRcb,aAnd F2aSum of radial components, i.e.
FRca，a＝FRcb，a+F2a×sin(θ) (4)
The sun wheel 8 is now pressed by the planet wheels numerically in the same way as FRca,aEqual and opposite in direction. Compared with the planetary gear train which is static, the pressing force applied to the sun gear 8 is larger, so that the friction force generated on the contact surface of the sun gear and the planetary gear is larger, and the transmitted torque is increased.
When the planetary gear train moves, the planetary gears 2a are still uniformly distributed on the circumference around the sun gear 8, the central axis Aa-a of the sun gear 8 is not deviated, and the central axis of the sun gear 8 and the central axis of the outer ring 4 are still coincident. All planet wheel centre axes Ac-c are at the same distance from the sun wheel 8 centre axis Aa-a, but the distance has changed relative to the distance at which the planetary gear train is stationary.
The variable distance a between the planet wheels 2a and the central axis of the sun wheel 8 enables the planet wheel system to generate a slope effect at the planet wheels 2a when in motion, thereby realizing that the transferable torque automatically increases along with the increase of the rotating speed.
The geometrical dimensions, material properties (interference, friction coefficient) and the maximum variable distance a of the outer ring 4, the planet wheels 2a and the sun wheel 8 in the planetary gear train determine the magnitude of each acting force acting on the planet wheel supporting shaft in the slope effect and determine the maximum torque which can be transmitted by the planetary gear train.
Referring to fig. 5A, fig. 5A shows how the planetary gear 2a is mounted on the planetary carrier 7 in this example. The planet wheel 2a and the planet wheel support shaft 5a are superposed in central line and are integrally machined or rigidly assembled into a whole in an interference connection mode. The planet wheel supporting shaft 5a is supported by a planet wheel bearing 20a, and the bearing 20a is mounted in a bearing mounting hole 22 in the planet carrier 7. The inner diameter of the bearing mounting hole 22 is larger than the outer diameter of the bearing 20a, and the difference is a, so that the distance between the central axis of the planet wheel 2a and the central axis of the sun wheel 8 can be changed when the planetary gear train moves.
Referring to fig. 5B, fig. 5B shows a second example of the present invention, in which the planetary gear 2a is mounted on the planet carrier 7. The planet wheel 2a and the planet wheel support shaft 5a are superposed in central line and are integrally machined or rigidly assembled into a whole in an interference connection mode. The planet wheel support shaft 5a is supported by bearing planet wheels 20a, and the planet wheel bearings 20a are mounted in bearing mounting holes 22 in the planet carrier 7. The bearing mounting hole 22 has an inner diameter corresponding to the outer diameter of the bearing 20a to form an interference fit. The inner diameter of the planet wheel bearing 20a is larger than the outer diameter of the planet wheel supporting shaft 5a, the difference is a, and the distance between the central axis of the planet wheel 2a and the central axis of the sun wheel 8 can be changed when the planetary gear train moves.
Referring to fig. 5C, fig. 5C shows a third example of the present invention, in which the planetary gear 2a is mounted on the planet carrier 7. The planet wheel 2a is coincident with the planet wheel supporting shaft 5a in central line, and is supported and mounted on the planet wheel supporting shaft 5a by a planet wheel bearing 20 a. The inner hole of the planet wheel 2a and the outer ring of the planet wheel bearing 20a form interference fit, and the inner hole of the planet wheel bearing 20a and the outer surface of the planet wheel supporting shaft 5a form interference fit. The planet wheel supporting shaft 5a is mounted in a bearing mounting hole 22 in the planet carrier 7. The inner diameter of the bearing mounting hole 22 is larger than the outer diameter of the planet wheel supporting shaft 5a, the difference is a, and the distance between the central axis of the planet wheel 2a and the central axis of the sun wheel 8 can be changed when the planetary gear train moves.
Referring to fig. 6, as shown in fig. 6, in the planetary gear train motion state, the radial force of the three planetary wheels acting on the sun gear 8 is
And friction force
Because the sizes, materials and installation modes of the three planet wheels are completely consistent and are uniformly distributed in the circumferential direction along the central axis of the sun wheel, the three radial forces have the same size, and the included angles are 120 degrees.
According to the law of friction, the relationship between radial force and friction force is
When the planetary gear train is at rest, the friction force acting on the sun gear through the planetary gear is
When the planetary gear train is static, the resultant of the radial forces acting on the sun gear through the planetary gears is
The torque input to the sun gear through the planet gear in the motion state of the planetary gear train is
The resultant force acting on the sun gear through the planet wheel in the motion state of the planetary gear train is
When the planetary gear train is stationary, the radial force acting between the outer ring 4, the planet wheels 2a, 2b, 2c and the sun wheel 8 is determined by the geometrical dimensions of the outer ring 4, the planet wheels 2a, 2b, 2c and the sun wheel 8 and the amount of compression between them. The magnitude of each radial force can be calculated by a theoretical formula or obtained by a finite element analysis method.
When the planetary gear train moves, the rotation speed, the geometric dimension, the mutual compression amount and the friction coefficient of the outer ring 4, the planetary gears 2a, 2b and 2c and the sun gear 8 and the change a of the distance difference value of the central axes of the planetary gears and the sun gear determine the interaction radial force and the friction force among the outer ring 4, the planetary gears 2a, 2b and 2c and the sun gear 8. The magnitude of each radial force and friction force can be calculated by a theoretical formula or obtained by a finite element analysis method.
The foregoing description is intended to be illustrative rather than limiting, and it will be appreciated by those skilled in the art that many modifications, variations or equivalents may be made without departing from the spirit and scope of the invention as defined in the appended claims.
Claims (9)
1. The utility model provides a friction drive planet speed increaser suitable for high input rotational speed which characterized in that: including input shaft (I), web (21), output shaft (O), shell (1) and planetary gear train, wherein:
the input shaft (I) and the web plate (21) are assembled into a whole in a rigid connection mode to drive the outer ring (4) to rotate;
the outer ring (4), the planet wheels (2a, 2b and 2c) and the sun wheel (8) are mounted in a compression mode, the planet wheels and a planet carrier (7) form a planet wheel train together, the planet carrier (7) is in rigid connection with the shell (1) through friction transmission, a bearing mounting hole (22) is formed in the planet carrier (7), the inner diameter of the bearing mounting hole (22) is larger than the outer diameter of the planet wheel bearings (20a, 20b and 20c), and a slope effect is generated during movement to increase transmission torque;
the output shaft (O) is rigidly connected with the sun gear (8), and the axes are overlapped.
2. A friction drive planetary step up gear adapted for high input rotational speeds as in claim 1 wherein: and an installation groove is formed in the circumferential direction of one end of the outer ring (4), and the web plate (21) is installed in the groove.
3. A friction drive planetary step up gear adapted for high input rotational speeds as in claim 1 wherein: the central axis of the outer ring (4) is coincident with the central axis of the sun wheel (8).
4. A friction drive planetary step up gear adapted for high input rotational speeds as in claim 1 wherein: the number of the planet wheels (2a, 2b and 2c) is at least 3, the distances between the central axes of all the planet wheels (2a, 2b and 2c) and the central axis of the sun wheel (8) are equal, and the planet wheels are evenly distributed around the circumference of the sun wheel (8).
5. A friction drive planetary step up gear adapted for high input rotational speeds as in claim 1 wherein: the planet wheels (2a, 2b, 2c) are mounted in the same way on the planet carrier (7) as well as on the same geometry and tolerances and materials.
6. A friction drive planetary step up gear adapted for high input rotational speeds as in claim 1 wherein: all the mounting holes (22) on the planet carrier (7) are identical in size and tolerance.
7. A friction drive planetary step up gear adapted for high input rotational speeds as in claim 1 wherein: the planet wheels (2a, 2b, 2c) and the planet wheel supporting shafts (5a, 5b, 5c) are of an integral structure or are rigidly connected into a whole.
8. A friction drive planetary step up gear adapted for high input rotational speeds as in claim 1 wherein: the sun wheel (8) is provided with shaft shoulders (23, 24).
9. A friction drive planetary step up gear adapted for high input rotational speeds as in claim 1 wherein: the inner diameter of the bearing mounting hole (22) is larger than the outer diameter of the planet wheel bearing (20a, 20b, 20c), and is replaced by the inner diameter of the planet wheel bearing (20a, 20b, 20c) being larger than the outer diameter of the planet wheel supporting shaft (5a, 5b, 5c), or the inner diameter of the bearing mounting hole (22) being larger than the outer diameter of the planet wheel supporting shaft (5a, 5b, 5 c).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920954787.3U CN210318396U (en) | 2019-06-24 | 2019-06-24 | Friction transmission planetary speed increasing device suitable for high input rotating speed |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920954787.3U CN210318396U (en) | 2019-06-24 | 2019-06-24 | Friction transmission planetary speed increasing device suitable for high input rotating speed |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN210318396U true CN210318396U (en) | 2020-04-14 |
Family
ID=70146098
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201920954787.3U Active CN210318396U (en) | 2019-06-24 | 2019-06-24 | Friction transmission planetary speed increasing device suitable for high input rotating speed |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN210318396U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111692296A (en) * | 2020-07-10 | 2020-09-22 | 浙江贝托传动科技有限公司 | Planetary gear reducer with self-adaptive fastening planet carrier |
| CN111795123A (en) * | 2019-06-24 | 2020-10-20 | 北京稳力科技有限公司 | Friction drive planetary speed increasing device suitable for high input speed |
| CN111998039A (en) * | 2020-09-16 | 2020-11-27 | 浙江超级电气科技有限公司 | A high-precision planetary reducer and connector |
-
2019
- 2019-06-24 CN CN201920954787.3U patent/CN210318396U/en active Active
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111795123A (en) * | 2019-06-24 | 2020-10-20 | 北京稳力科技有限公司 | Friction drive planetary speed increasing device suitable for high input speed |
| CN111692296A (en) * | 2020-07-10 | 2020-09-22 | 浙江贝托传动科技有限公司 | Planetary gear reducer with self-adaptive fastening planet carrier |
| CN111998039A (en) * | 2020-09-16 | 2020-11-27 | 浙江超级电气科技有限公司 | A high-precision planetary reducer and connector |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN210318396U (en) | Friction transmission planetary speed increasing device suitable for high input rotating speed | |
| CN101080579B (en) | Bearing assembly for supporting a drive shaft in a housing | |
| JP5903834B2 (en) | Friction roller speed reducer and electric vehicle drive device | |
| WO2012165395A1 (en) | Friction drive-type wave transmission | |
| JP5138535B2 (en) | Booster / decelerator | |
| US4563915A (en) | Wobble type axial speed reducer apparatus | |
| US9200698B2 (en) | Roller-type friction transmission unit | |
| CN111795123A (en) | Friction drive planetary speed increasing device suitable for high input speed | |
| US7441634B2 (en) | Friction drive device | |
| EP3101298B1 (en) | Divided holder, one-way clutch, and joint for power-generating device | |
| CN202418458U (en) | Stepless speed reducer with friction-pair planetary transmission | |
| JP5893206B2 (en) | Automatic pressing friction transmission speed reducer | |
| CN109458449B (en) | Power takeoff with adjustable center distance | |
| JP2016200218A (en) | Planetary roller type power transmission device | |
| CN115552149B (en) | Friction transmission device | |
| CN211778831U (en) | Homothetic differential speed reducer | |
| JP5310667B2 (en) | Traction drive mechanism | |
| CN102252075A (en) | Friction pair planet driven continuously variable transmission | |
| CN111895058A (en) | Forming design method of speed reducer | |
| JP4311452B2 (en) | Power transmission device | |
| CN111590553A (en) | Novel harmonic reducer and driver | |
| JP2009057993A (en) | Continuously variable transmission | |
| CN116292612B (en) | An adaptive preload compensation mechanism for tapered roller bearings | |
| CN112460226B (en) | A harmonic reducer and driver | |
| JP3220154U6 (en) | Multi Crankshaft Cycloid Pin Gear Reducer |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |