CN115773338A - Reduction gear having a first planetary gear train stage - Google Patents
Reduction gear having a first planetary gear train stage Download PDFInfo
- Publication number
- CN115773338A CN115773338A CN202111052930.8A CN202111052930A CN115773338A CN 115773338 A CN115773338 A CN 115773338A CN 202111052930 A CN202111052930 A CN 202111052930A CN 115773338 A CN115773338 A CN 115773338A
- Authority
- CN
- China
- Prior art keywords
- gear
- ring
- shaft
- bearing
- sun gear
- 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.)
- Pending
Links
Images
Abstract
The invention relates to a reduction gear having a first planetary gear train stage having a first sun gear shaft, an internal toothing and a working gear, wherein the working gear has a planetary gear into which a cylindrical projection, in particular a pin, of a gear wheel designed to be inserted into a pinion is inserted, wherein the teeth of the planetary gear wheel mesh with the teeth of the first sun gear shaft, wherein the teeth of the gear wheel mesh with the teeth of the internal toothing, wherein the planetary gear wheel is connected to the gear wheel in a rotationally fixed manner by means of a key connection.
Description
Technical Field
The invention relates to a reduction gear having a first planetary gear train stage.
Background
As is known, planetary gear trains are rotary gear trains and have a working gear/rotary gear (Umlaufrad).
Disclosure of Invention
The object of the invention is therefore to enable the reduction gear to be produced more precisely, in particular to enable a longer service life of the bearings and toothed parts.
According to the invention, this object is achieved by a retarder according to the features given in claim 1.
The invention relates to a reduction gear having a first planetary gear train stage having a first sun gear shaft, an internal toothing, in particular of a first ring gear connected to a housing part or of a first ring gear formed integrally with the housing part, and a working gear, wherein the invention is characterized in that the working gear has a planetary gear into which a cylindrical projection, in particular a pin, of a gear designed to be inserted into the pinion is inserted, wherein a tooth of the planetary gear meshes with a toothing of the first sun gear shaft, wherein the tooth of the gear meshes with the toothing of the internal toothing, wherein the planetary gear is connected to the gear in a rotationally fixed manner by means of a key connection, and/or wherein the projection has a groove, in particular a flat key groove, in which a flat key is received, which also projects at least partially into the groove of the gear, in particular for connecting the planetary gear to the gear in a linear manner around the rotational axis of the working gear in the circumferential direction.
The advantage here is that by axially supporting the working gears on both sides, precise alignment of the working gears is achieved and thus also during operation. Because the bearings arranged axially on both sides of the outer part of the toothing prevent tilting of the working gear. The axially elongated embodiment also helps this. Since the pinion is inserted by the connection, the working gear is longer in the axial direction as a whole. Thus, the stability is further improved by the large bearing spacing. In addition, the different tip circle diameters of the gear and the planet gear not only enable different transmission ratios, but also contribute to further improving the stability of the working gear. Since the radial supports by the respective toothing, in particular the sun gear toothing and the internal toothing, are axially remote from one another, and therefore an additional leverage effect can be achieved, which enhances the stability.
In an advantageous embodiment, the first planet gear is shrink-fitted onto the projection and/or thermally bonded onto the projection, in particular such that the gear is connected with the first planet gear in a force-fitting manner. The advantage here is that an increased safety can be achieved. Since, in addition to the form-locking connection, a force-locking connection is also produced.
In an advantageous embodiment, the working gear is inserted onto a planet pin, wherein the planet pin is rotatably mounted axially on both sides by means of corresponding bearings received in the planet carrier of the reduction gear, in particular wherein the bearings are spaced apart from the gear and/or the planet gear in the axial direction. The advantage here is that the stability against tilting of the working gear is improved. Thus enabling higher accuracy.
In an advantageous embodiment, the input shaft of the gear unit is rotatably mounted by means of a bearing received in a bearing flange of the gear unit, wherein the bearing flange is connected, in particular bolted, to one or the housing parts of the gear unit, wherein the first sun gear shaft has a toothing, in particular a wedge-shaped toothing, which is inserted into a hollow region of the input shaft, in particular into a hollow shaft section, for the purpose of rotationally fixedly connecting the input shaft to the sun gear. The advantage here is that the input shaft is connected in a rotationally fixed manner to the first sun gear shaft via the tooth clutch. In this way, deviations from the ideal position of the input shaft occurring on the input side have only a small effect. The first sun gear shaft therefore drives the first transmission stage more precisely than when the tooth clutch is not present.
In an advantageous embodiment, the first sun gear shaft is rotatably supported at its end region facing away from the input shaft by means of a bearing, which is received in the second sun gear shaft, in particular wherein an inner ring of the bearing is inserted onto the first sun gear shaft and an outer ring of the bearing is received in the second sun gear shaft. The advantage here is that the coaxial alignment of the two sun gear shafts is possible, a coaxial two-stage reduction gear can be provided, the first sun gear shaft being able to be mounted in the second sun gear shaft and thus allowing the most compact possible design.
In an advantageous embodiment, the first planet carrier has an internal toothing into which a region of the second sun gear shaft with the external toothing is inserted, which region of the second sun gear shaft with the external toothing engages, in particular for rotationally fixedly connecting the first planet carrier to the second sun gear shaft, in particular wherein the first planet carrier is rotatably mounted by means of a bearing received in the housing part. The advantage here is that a further clutch is present for tolerance compensation. The inclined section introduced into the first gear stage via the input shaft is therefore nevertheless further decoupled from the second gear stage.
In an advantageous embodiment, the second sun gear shaft has a toothing which meshes with the toothing of a second planet gear which is rotatably mounted, in particular by means of a needle bearing, on a second planet gear pin in an end region of the second sun gear shaft facing away from the input shaft in the axial direction, wherein the second planet gear pin is received in the planet carrier, wherein the toothing of the second planet gear is meshed with the internal toothing of the second ring gear. The advantage here is that needle bearings for the planetary gears can be used in the second gear stage. Furthermore, the ring gear may be designed to extend less radially than the planet carrier.
In an advantageous embodiment, the second ring gear is connected to the support ring in a rotationally fixed manner, in particular by inserting the support ring at least partially into the ring gear, wherein the support ring has an external toothing which meshes with an internal toothing of the ring gear. The advantage here is that the ring gear is connected to the support ring by means of a tooth clutch, in particular also for decoupling the tilting forces, and the support ring can be inserted onto a finished alignment surface which is provided on an annular projection formed on the housing part. Thus, the support ring can be accurately aligned and hold the second ring gear in a desired position.
In an advantageous embodiment, a radially directed, annular projection, in particular a projection, is formed on the housing part, in particular with respect to the rotational axis of the second sun gear shaft, which projection has an alignment surface running in the circumferential direction, on which projection the support ring is slipped, in particular for aligning the support ring together with the second ring gear, in particular wherein the alignment surfaces are spaced apart from one another in the axial direction. In this case, it is advantageous to provide a surface that is as fine-machined as possible for the purpose of aligning the support rings and thus the second ring gear, and thus to be able to achieve a high degree of precision during production.
In one advantageous embodiment, the first sun gear shaft is oriented coaxially with the second sun gear shaft. The advantage here is that the reduction gear can be designed as a coaxial reduction gear. Furthermore, the first sun gear shaft can be mounted in the second sun gear shaft, so that the reduction gear can be designed very compactly. Advantageously, the relative rotational speed of the two sun gear shafts is less than the rotational speed of the first sun gear shaft relative to the housing part.
In an advantageous embodiment, a sleeve is connected to the second planet carrier, which sleeve radially surrounds the second ring gear, in particular wherein a clearance region is formed between the second ring gear and the sleeve. The advantage here is that the ring gear is radially surrounded by the rotating parts, i.e. the sleeve and the second planet carrier.
In an advantageous embodiment, the first bearing is inserted with its inner ring onto the cylindrical section of the housing part and its outer ring is received in the sleeve, and/or the second bearing, in particular the outer ring of the second bearing, is received in the sleeve, the inner ring of the second bearing being inserted onto the support ring, in particular wherein the support ring has a step, against which the second bearing rests. The advantage here is that the sleeve is supported by two bearings and therefore the second planet carrier is supported by the sleeve. In this way, a large axial distance between the two bearings and the planet carrier can be achieved, so that tilting can be avoided.
The sleeve can be designed as a hollow component, in particular as a substantially hollow cylinder.
In an advantageous embodiment, the support ring is limited in the axial direction by a spindle nut screwed onto a thread mounted on the housing part. The advantage here is that a precise and stable alignment of the support rings can be achieved.
In an advantageous embodiment, the shaft sealing ring received by the sleeve seals against the housing part, in particular the sealing lip of the shaft sealing ring bears against the finished surface of the housing part, in particular wherein the dust seal, in particular a dust seal designed as a V-ring, additionally seals the sleeve against the housing part. The advantage here is that the shaft sealing ring enables a simple, cost-effective sealing.
In an advantageous embodiment, the radial bore through the sleeve opens into a space region adjoining the first and second bearings, in particular wherein an axial bore formed in the sleeve intersects the radial bore and opens into a space region in which the tooth region of the second planetary gear is located. The advantage here is that the oil supply takes place via the radial bores. In operation, the radial bore is preferably sealed off from the surroundings by a closing plug.
Further advantages are given by the dependent claims. The invention is not limited to the combination of features of the claims. Other possible combinations of the features of the claims and/or of the individual claims and/or of the features of the description and/or of the drawings can be made possible for the person skilled in the art, in particular from the objects set forth and/or by comparison with the prior art.
Drawings
The invention will now be described in detail with reference to the schematic drawings:
fig. 1 shows a sectional view of a gear unit according to the invention.
Fig. 2 shows a perspective view of a multi-part operating gear of the gear unit.
List of reference numerals:
1. gear ring
2. Support ring
3. Second sun gear shaft
4. Shaft sealing ring
5. Dust seal, in particular V-ring
6. First planet carrier
7. Bearing assembly
8. Gear wheel
9. Flat key
10. Housing component
11. Planetary gear
12. Bearing assembly
13. First planetary gear pin
14. Input shaft
15. First sun wheel shaft
16. Bearing assembly
17. Bearing flange
18. Bearing assembly
19. Bearing assembly
20. Bearing assembly
21. Alignment surface
22. Alignment surface
23. Planetary gear pin
24. Planetary gear
25. Planet carrier
26. Shaft nut
27. Sleeve, in particular bearing bush
28. Closing plug
Detailed Description
As shown, the reducer has two planetary gear stages.
A bearing flange 17 is connected to the housing part 10 of the gear unit, in which bearing flange bearings are received, which rotatably support the input shaft 14.
The input shaft 14 has a hollow shaft section in which an inner wedge toothing is machined, which engages with an outer wedge toothing of a first sun gear shaft 15 of the first planetary gear stage inserted into the hollow shaft section.
The outer wedge toothing is arranged on a first axial end region of the first sun gear shaft 15.
The sun gear shaft 15 is rotatably mounted on its other axial end region, in particular facing away from the input shaft 14, by means of a bearing 18.
Here, the bearing 18 is received in the second sun gear shaft 3, wherein the second sun gear shaft 3 belongs to the second planetary gear train stage.
The teeth of the working gear, which consists of the gear wheel 8 and the planet gear wheel 11, mesh with this first sun wheel shaft 15.
The toothing of the planet gears 11 meshes here with the toothing of the first sun gear shaft 15.
The gear wheel 8 designed as a plug-in pinion is inserted into a recess of the planetary gear wheel 11 and is positively connected to the planetary gear wheel 11 by means of a flat key 9. Since the planet gears 11, which are designed as hollow, are inserted for this purpose into the cylindrical extensions of the gear wheels 8, wherein key grooves are formed in the cylindrical extensions, into which key grooves the flat keys 9 are inserted, which also project into the axial grooves of the planet gears 11.
The ring gear with the internal toothing is connected to the housing part 10 or is designed in one piece, in particular in one piece.
The teeth of the gear 8 mesh with the internal teeth of the ring gear, and the teeth of the planet gears 11 mesh with the teeth of the first sun gear shaft 15.
The teeth of the gearwheel 8, which are preferably designed as involute teeth, have a smaller outer diameter, in particular tip circle diameter, than the teeth of the planet gearwheel 11, which are preferably designed as involute teeth.
The inner diameter of the ring gear is smaller than the tip circle diameter of the tooth portion of the pinion gear 11. The internal toothing of the ring gear is therefore arranged radially spaced apart from the toothing of the planet gears 11, in particular at a small radial distance from the rotational axis of the first sun gear shaft 15.
The gear wheel 8 is hollow and is inserted onto a planet pin 13, which is mounted axially on both sides in the first planet carrier 6 by means of bearings 7, 12, in particular rolling bearings. The bearings 7 and 12 are arranged axially outside the toothing of the gear wheel 8 and the planet gear 11.
The first planet carrier 6 is supported on the one hand by a bearing 16 received in a bearing flange 17 and on the other hand by a bearing 19 received in the housing part 10.
The second sun gear shaft 3 has an external toothing, in particular a wedge toothing, on its axial end region assigned to the first sun gear shaft 15, with which the second sun gear shaft 3 is inserted into the axial end region of the first planet carrier 6 with the internal toothing.
The second sun gear shaft 3 has no direct support.
The second sun gear shaft 3 is inserted into the first planet carrier 6 at its first end region and is therefore indirectly supported by the bearing 19 of the first planet carrier 6.
The second sun gear shaft 3 has a toothing on its second axial end region, which acts as a sun toothing, which meshes with in particular three second planet gears 24, wherein each of the second planet gears 24 is rotatably mounted on a respective planet pin 23 by means of a bearing, in particular a needle bearing.
The planet pins 23 are received in a double-walled planet carrier 25.
The teeth of the planetary gear 24 also mesh with the second ring gear 1. For this purpose, the second ring gear 1 has an internal toothing which meshes with the toothing of the planet gears 24. Furthermore, the internal toothing of the second ring gear 1 is designed to be axially elongated, i.e. to protrude axially beyond the planet gears 24, so that the externally toothed region of the support ring 2 can be inserted into the second ring gear 1 and can therefore mesh with the internal toothing of the second ring gear 1. In this way, the second ring gear 1 can also be connected to the support ring 2 in a form-fitting manner in the circumferential direction, in particular in a rotationally fixed manner.
In order to align the support ring 2 with the ring gear 1, the support ring 2 is inserted onto annular projections which have finished alignment surfaces 21 and 22 on their radial outer sides. These annular projections are formed on a cylindrical region of the housing part 10 which covers, in the axial direction, a region surrounded by a region covered by the second sun gear shaft 3 in the axial direction.
In particular, the support ring 2 is arranged on the side of the second planet gears 24 facing the first sun gear shaft 15.
The inner ring of the bearing 20 is inserted onto the support ring 2, and the outer ring of the bearing is received in a sleeve 27, in particular a bearing sleeve, which is connected in a rotationally fixed manner to the planet carrier 25, in particular by means of bolts.
Also received in the sleeve 27 is the outer ring of the second bearing 20, which is inserted onto a cylindrical region of the housing part 10, in particular a bearing receiving region.
The sleeve 27 is arranged axially between the second planet gears 24 and the first sun gear shaft 15.
In this way, the second planet carrier 25 is rotatably supported by the sleeve 27 in that the sleeve 27 is supported on the one hand on the housing part 10 by the bearing 20 and on the other hand on the housing part 10 together with the support ring 2 by the further bearing 20.
The region covered by the sleeve 27 in the axial direction overlaps with the region covered by the second planetary gears 24 in the axial direction and is surrounded by the region covered by the second sun gear shaft 3 in the axial direction.
The seal received in the sleeve 27 comprises a shaft sealing ring 4, the sealing lip 4 of which is moved on the finished face of the housing part 10 and thus seals the sleeve 27 against the housing part 10. The sealing lip thus contacts the housing part 10. The sleeve 27 has a seat for the shaft sealing ring 4.
The finished face of the housing part 10 is arranged radially inside the sealing ring 3 and/or the sleeve 27.
The dust seal 5, which is preferably designed as a V-ring, seals the housing part 10 towards the sleeve 27.
The sleeve 27 has a radially through-going bore which is closed by a closure plug 28. Thus, in particular, oil can be replenished through the sleeve 27 when the closing plug is removed and the retarder is out of operation. However, when the speed reducer is operated, the sleeve 27 is a rotating member, and therefore, the replenishment of oil cannot be performed.
A bore, in particular a radial bore, which passes radially through the sleeve 27 opens out between the two bearings 20, so that the rolling bodies thereof can be supplied with lubricant.
The radial bores open into the axially directed bores, or the bores intersecting the radial bores open into a gap region, in particular an annular gap, which is arranged radially between the sleeve 27 and the second ring gear.
The additional recess through the support ring 2 allows the needle bearings of the second planet gears 24 and the toothing of the second planet gears 24 to be lubricated.
The sleeve 27 acts as an axial extension of the second planet carrier 25 and radially surrounds the second ring gear 1.
The gear wheel 8 is positively connected to the planet gear wheel 11 by means of a flat key 9, but the gear wheel 8, which is also designed as a pinion, is inserted with its cylindrical extension into the planet gear wheel 11, wherein the latter is shrink-fitted. Here, the gear wheel 8 is heated during manufacture before insertion, so that a temperature difference of more than 40 ℃ exists between the gear wheel 8 and the planet gear wheel 11.
In this way, the connection between the gearwheel 8 and the planet gearwheel 11 is not only positively, but also non-positively.
In a further exemplary embodiment according to the present invention, the sleeve 27 is formed integrally, in particular in one piece, with the second planet carrier 25.
Claims (15)
1. A reduction gear unit having a first planetary gear stage,
the first planetary gear train stage has a first sun gear shaft, an internal toothing, in particular of a first ring gear connected to the housing part or of a first ring gear formed integrally with the housing part, and a running gear,
it is characterized in that the preparation method is characterized in that,
the working gear has a planetary gear into which a cylindrical projection, in particular a pin, of a gear designed to be inserted into the pinion is inserted,
wherein the teeth of the planet gear are meshed with the teeth of the first sun gear shaft,
wherein the tooth part of the gear is meshed with the tooth part of the internal tooth part,
wherein the planet gears are connected in a rotationally fixed manner to the gear wheels by means of a key connection,
and/or wherein the projection has a groove, in particular a flat key groove, in which a flat key is received, which also projects at least partially into the groove of the gearwheel, in particular for connecting the planet gearwheel with the gearwheel in a linear manner in the circumferential direction about the rotational axis of the working gearwheel.
2. A decelerator according to claim 1 in which the decelerator is,
it is characterized in that the preparation method is characterized in that,
the first planet gears are heat shrink fitted onto the bosses and/or heat bonded onto the bosses,
in particular, the gear wheels are connected in a force-fitting manner to the first planetary gear.
3. A decelerator according to any preceding claim,
it is characterized in that the preparation method is characterized in that,
the working gears are inserted onto planet pins, which are rotatably mounted axially on both sides by means of corresponding bearings received in the planet carrier of the gear unit,
in particular, the bearings are spaced apart from the gear and/or the planet gear in the axial direction.
4. A decelerator according to any preceding claim,
it is characterized in that the preparation method is characterized in that,
the input shaft of the gear unit is rotatably supported by means of bearings received in bearing flanges of the gear unit,
wherein the bearing flange is connected, in particular by means of screws, to one or the housing parts of the gear unit,
the first sun gear shaft has a toothing, in particular a wedge-shaped toothing, which is inserted into a hollow region of the input shaft, in particular into a hollow shaft section, for the rotationally fixed connection of the input shaft to the sun gear.
5. A decelerator according to any one of the preceding claims,
it is characterized in that the preparation method is characterized in that,
the first sun gear shaft is rotatably supported on its end region facing away from the input shaft by means of a bearing, which is received in the second sun gear shaft,
in particular wherein the inner race of the bearing is inserted over the first sun gear shaft and the outer race of the bearing is received in the second sun gear shaft.
6. A decelerator according to any preceding claim,
it is characterized in that the preparation method is characterized in that,
the first planet carrier has an internal toothing into which the region of the second sun gear shaft with the external toothing is inserted, the region of the second sun gear shaft with the external toothing meshes with the internal toothing,
in particular for the non-rotatable connection of the first planet carrier to the second sun gear shaft,
in particular, the first planet carrier is rotatably mounted by means of bearings received in the housing part.
7. A decelerator according to any one of the preceding claims,
it is characterized in that the preparation method is characterized in that,
in an end region of the second sun gear shaft facing away from the input shaft in the axial direction, the second sun gear shaft has a toothing which meshes with the toothing of a second planet gear which is rotatably mounted on a second planet pin, in particular by means of a needle bearing,
wherein the second planet pins are received in the planet carrier,
wherein the tooth portions of the second planetary gear are meshed with the internal tooth portions of the second ring gear.
8. A decelerator according to any one of the preceding claims,
it is characterized in that the preparation method is characterized in that,
the second ring gear is connected with the support ring in a relatively non-rotatable manner,
in particular, a support ring is inserted at least partially into the ring gear, wherein the support ring has an external toothing which meshes with an internal toothing of the ring gear.
9. A decelerator according to any preceding claim,
it is characterized in that the preparation method is characterized in that,
a radially directed, annular projection, in particular a projection, is formed on the housing part, in particular with respect to the rotational axis of the second sun gear shaft, which projection has an alignment surface running around in the circumferential direction,
the support ring is fitted onto this projection, in particular for aligning the support ring with the second ring gear,
in particular wherein the alignment faces are spaced from each other in the axial direction.
10. A decelerator according to any one of the preceding claims,
it is characterized in that the preparation method is characterized in that,
the first sun gear shaft is oriented coaxially with the second sun gear shaft.
11. A decelerator according to any preceding claim,
it is characterized in that the preparation method is characterized in that,
a sleeve is connected to the second planet carrier, which sleeve radially surrounds the second ring gear,
in particular, a clearance region is provided between the second toothed ring and the sleeve.
12. A decelerator according to any preceding claim,
it is characterized in that the preparation method is characterized in that,
the first bearing is inserted with its inner race onto the cylindrical section of the housing part and with its outer race received in the sleeve,
and/or
A second bearing, in particular an outer ring of the second bearing, is received in the sleeve, the inner ring of the second bearing being inserted onto the support ring,
in particular, the support ring has a step, against which the second bearing rests.
13. A decelerator according to any preceding claim,
it is characterized in that the preparation method is characterized in that,
the support ring is limited in the axial direction by a spindle nut screwed onto a thread mounted on the housing part.
14. A decelerator according to any preceding claim,
it is characterized in that the preparation method is characterized in that,
a shaft sealing ring received by the sleeve seals against the housing components,
in particular the sealing lip of the shaft sealing ring abuts against the finished surface of the housing part,
in particular, the dust seal, in particular designed as a V-ring, additionally seals the sleeve against the housing part.
15. A decelerator according to any preceding claim,
it is characterized in that the preparation method is characterized in that,
a radial bore through the sleeve opens into a region of space adjacent the first bearing and the second bearing,
in particular, the axial bore formed in the sleeve intersects the radial bore and opens into a space region in which the tooth region of the second planetary gear is located.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111052930.8A CN115773338A (en) | 2021-09-06 | 2021-09-06 | Reduction gear having a first planetary gear train stage |
| PCT/EP2022/025337 WO2023030676A1 (en) | 2021-09-06 | 2022-07-20 | Transmission having a first planetary gear stage |
| DE102022002656.2A DE102022002656A1 (en) | 2021-09-06 | 2022-07-20 | Transmission with a first planetary gear stage |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111052930.8A CN115773338A (en) | 2021-09-06 | 2021-09-06 | Reduction gear having a first planetary gear train stage |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN115773338A true CN115773338A (en) | 2023-03-10 |
Family
ID=85388283
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111052930.8A Pending CN115773338A (en) | 2021-09-06 | 2021-09-06 | Reduction gear having a first planetary gear train stage |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN115773338A (en) |
-
2021
- 2021-09-06 CN CN202111052930.8A patent/CN115773338A/en active Pending
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US20050193851A1 (en) | Angle drive with power distribution | |
| JP2019533410A (en) | Input shaft structure with motor and reduction gear connected | |
| CN102927255A (en) | Planetary gear transmission device and assembly method thereof | |
| CN217814795U (en) | Reduction gear having a first planetary gear train stage | |
| CN218267040U (en) | Reduction gear having a first planetary gear stage | |
| CN214331371U (en) | Planetary gear train and planetary reducer capable of automatically eliminating gaps in radial direction | |
| TWI404872B (en) | Planetary reducer | |
| CN115773338A (en) | Reduction gear having a first planetary gear train stage | |
| CN115773337A (en) | Reduction gear having a second planetary gear stage | |
| KR100642307B1 (en) | A speed reducer having hollowness with a motor in midair | |
| US20010031683A1 (en) | Generator drive | |
| CN112460224A (en) | Method for producing a differential gear and differential gear | |
| CN105317965B (en) | Disconnect shaft assembly | |
| US10663062B2 (en) | High-precision rear-axle reduction gearbox for scooter | |
| CN114396461A (en) | Industrial robot hollow cycloid speed reduction all-in-one machine | |
| US20210088119A1 (en) | Toothing Arrangement | |
| CN214171298U (en) | Precise planetary gear speed reducer | |
| CN113619381A (en) | Door type driving device for driving axle of electric vehicle | |
| CN109563917B (en) | Planetary differential device and method for manufacturing same | |
| US7010995B2 (en) | Bevel gear with annular housing | |
| US11781619B2 (en) | Planetary transmission | |
| CN216842923U (en) | Industrial robot small tooth difference speed reduction all-in-one machine | |
| CN216200207U (en) | Single-support one-stage transmission planetary gear reducer | |
| CN211852686U (en) | RV speed reducer | |
| CN111156309B (en) | Mounting method of RV reducer |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication |