JP6328039B2 - Vertical gear unit - Google Patents

Description

  The present invention relates to a vertically installed gear device.

  Patent Document 1 discloses a configuration example in which a drive unit including a vertical gear device is incorporated in a shovel car.

  In the gear device of the drive unit, the input shaft is disposed vertically above the output shaft. The gear device is externally fitted to the input shaft between the input shaft, a sun gear incorporated in the input shaft via a spline, a support member that supports the input shaft via a bearing, and the bearing and the sun gear. Color.

  In the above gear device, for example, the sun gear of the second stage planetary gear device is connected to the tip of the input shaft (the output shaft of the first planetary gear device) via a spline (that is, axially movable). In this case, the upward movement in the axial direction is regulated by a collar press-fitted into the input shaft.

Japanese Unexamined Patent Publication No. 2014-114952 (FIGS. 1, 2, and 4)

  The sun gear of the gear device incorporated in the configuration as described above is vertically placed and the movement upward in the axial direction is restricted by the collar. There is nothing wrong.

  However, for some reason, the sun gear may rise strongly together with the collar in the axial direction. In this case, the bearing may be damaged.

  The present invention has been made to solve such a problem, and even if a situation occurs in which the gear incorporated in the input shaft rises strongly for some reason, damage to the bearing is prevented. It is an object of the present invention to provide a vertical gear device that can be prevented.

  The present invention includes an input shaft, an output shaft, a gear incorporated in the input shaft so as to be movable in the axial direction, a support member that supports the input shaft via a bearing, the bearing, and the gear A collar that is externally fitted to the input shaft, and the input shaft is disposed vertically above the output shaft, and the gear is moved in the axial direction. A movement restricting member for restricting the movement, the movement restricting member being integrated with the support member, disposed between the gear and the collar, and opposed to the gear in the axial direction. Thus, the above problem is solved.

  In the present invention, a movement restricting member for restricting the axial movement of the gear is provided. The movement restricting member is integrated with a support member that supports the input shaft via a bearing, is disposed between a gear incorporated in the input shaft and a collar, and faces the gear in the axial direction. Therefore, even if a situation occurs in which the gear is strongly lifted toward the axial collar for some reason, this rise is restricted by the movement restricting member that is disposed facing the support member in a fixed state. The

  For this reason, it is possible to prevent the ascent of the gear from being transmitted to the collar and to prevent the bearing from being damaged.

  According to the present invention, even if a situation occurs in which the gear incorporated in the input shaft rises strongly for some reason, damage to the bearing can be prevented.

The front view of a partially broken drive unit to which a vertical gear device according to an embodiment of the present invention is applied FIG. 1 is an enlarged cross-sectional view of a broken portion. 2 is an enlarged cross-sectional view of the main part of FIG. Front view of the movement restricting member of FIG. A perspective view of an excavator in which a drive unit including the vertical gear device is incorporated.

  Hereinafter, an example of an embodiment of the present invention will be described in detail based on the drawings.

  First, an overall schematic configuration of an excavator car 100 in which a drive unit 10 including a vertically installed gear device according to an example of an embodiment of the present invention is incorporated will be described with reference to FIG.

  The shovel car 100 includes a lower traveling body (crawler) 102 and an upper revolving body 106 that is pivotably mounted on an upper portion of the lower traveling body 102. A turning internal gear 114 is fixed to the lower traveling body 102. The drive unit 10 is attached to the upper swing body 106. The turning internal gear 114 fixed to the lower traveling body 102 and the final output shaft 118 of the drive unit 10 attached to the upper turning body 106 are engaged with each other. Thereby, the upper turning body 106 can turn around the axis of the turning internal gear 114 by the reaction of the meshing. The upper swing body 106 has a driver's seat 104, and can operate the boom 108, the arm 110, and the attachment 112 while turning.

  The turning internal gear 114 of the shovel car 100 has a structure in which the upper turning body 106 is turned in a horizontal plane, and its axis is directed in the vertical direction. On the other hand, in the drive unit 10 on the upper swing body 106 side having the final output shaft 118 meshing with the turning internal gear 114 on the lower traveling body 102 side, the input shaft is vertically above the output shaft. A vertically-arranged gear device (first stage to third stage planetary gear units 14 to 16 described later) is incorporated.

  Here, “the input shaft is disposed above the output shaft in the vertical direction” means “the input shaft is positioned above the output shaft in the vertical direction”. . The axial directions of the input shaft and the output shaft do not have to coincide with the vertical direction. That is, the axial directions of the input shaft and the output shaft may be inclined with respect to the vertical direction.

  The overall schematic configuration of the drive unit 10 will be described with reference to FIGS. 1 and 2.

  The drive unit 10 includes a motor (drive source) 12 and first to third-stage vertically arranged planetary gear devices 14 to 16 from the upper side in the vertical direction O1. The first to third stage planetary gear units 14 to 16 all have a power transmission structure of a simple planetary gear mechanism, and the configuration for transmitting power is basically the same.

  Here, the schematic configuration from the first stage planetary gear unit 14 to the portion reaching the second stage planetary gear unit 15 will be mainly described.

  The first-stage planetary gear device 14 includes an input shaft 20, a sun gear 22 incorporated at the tip of the input shaft 20, a planetary gear 24 with which the sun gear 22 is externally meshed, and an internal gear with which the planetary gear 24 is internally meshed. A tooth gear 26, a carrier 30 that supports the planetary gear 24 so as to revolve around the sun gear 22, and an output shaft 40 integrated with the carrier 30 are provided.

  The input shaft 20 of the first stage planetary gear unit 14 is integrated with the motor shaft 12A of the motor 12 of the preceding stage. An outer spline 20B is formed at the tip (load side) of the input shaft 20. A sun gear 22 having an inner spline 22B formed on the inner periphery is incorporated in the outer spline 20B.

  The sun gear 22 of the first stage planetary gear unit 14 is formed of a helical gear. Note that a spur gear is employed for the sun gear 82 of the second stage planetary gear device 15 described later. The sun gear 22 has a tooth portion 22C and a shaft portion 22D that protrudes to the load side continuously to the tooth portion 22C. The sun gear 22 meshes with the planetary gear 24.

  The planetary gear 24 of the first stage planetary gear device 14 is supported by the carrier 30 and can revolve around the sun gear 22. The planetary gear 24 is in mesh with the internal gear 26. The internal gear 26 is integrated with the casing 60.

  The casing 60 is configured by connecting a plurality of casing bodies (a first casing body 61, a second casing body 62,...). In FIG. 2, among the plurality of casing bodies, the second casing that houses the gear mechanism of the first casing body 61 and the first stage planetary gear apparatus 14 disposed between the motor 12 and the first stage planetary gear apparatus 14. The casing body 62, the 3rd casing body 63 arrange | positioned between the 1st stage planetary gear apparatus 14 and the 2nd stage planetary gear apparatus 15 appears.

  The carrier 30 of the first stage planetary gear device 14 includes a first side portion 31, a second side portion 32, a connecting portion 33 that connects the first and second side portions 31, 32, and a connecting pin 34 that supports the planetary gear 24. Is provided. The output shaft 40 is integrated with the second side portion 32 of the carrier 30 via a bolt 37. For this reason, if the way of viewing is changed, it can also be understood that the output shaft 40 also constitutes a part of the carrier 30. The carrier 30 supports the planetary gear 24 so as to revolve around the sun gear 22.

  More specifically, the first side portion 31 of the carrier 30 is disposed on the side portion on the axially opposite load side of the sun gear 22 and the planetary gear 24, and the second side portion 32 is disposed on the sun gear 22 and the planetary gear 24. It is arrange | positioned at the side part of the axial direction load side. The connecting portion 33 integrally connects the first side portion 31 and the second side portion 32 (as a single member). The connecting pin 34 is composed of a member different from the first side portion 31 and the second side portion 32. The connecting pin 34 is press-fitted into the first pin hole 31A of the first side part 31 and the second pin hole 32A of the second side part 32, so that the first side part 31 and the second side part 32 are circumferentially moved. Are connected at multiple locations. The connecting pin 34 constitutes a support shaft of the planetary gear 24, and supports the planetary gear 24 via the needle bearing 25 so as to revolve around the sun gear 22.

  The support structure of the carrier 30 will be described. The carrier 30 is supported by a first main bearing 51 and a second main bearing 53. The outer ring 51 </ b> B of the first main bearing 51 is disposed on the inner periphery of the first central through hole 31 </ b> B formed at the radial center of the first side portion 31 of the carrier 30. On the other hand, a part of the first casing body 61 extends radially inward to the vicinity of the outer periphery of the input shaft 20, and a cylindrical bearing parallel to the input shaft 20 from the inner end portion 61 </ b> A of the extended portion. A placement portion 61B is formed. The inner ring 51 </ b> A of the first main bearing 51 is disposed on the bearing mounting portion 61 </ b> B of the first casing body 61. That is, the first casing body 61 is located on the radially inner side with respect to the first main bearing 51, and the carrier 30 is located on the radially outer side.

  On the other hand, the outer ring 53 </ b> B of the second main bearing 53 is disposed on the radially inner side of the bearing mounting portion 63 </ b> B formed on the inner periphery of the third casing body 63. The inner ring 53 </ b> A of the second main bearing 53 is disposed on the radially outer side of the output shaft 40 that can be regarded as constituting a part of the carrier 30 by being integrated with the carrier 30 via the bolt 37. Has been.

  In short, in the present embodiment, the first main bearing 51 has a casing (first casing body 61) disposed radially inside and a carrier (first side portion 31) disposed outside, and the second main bearing 53 is disposed. The carrier (output shaft 40) is arranged radially inside, and the casing (third casing body 63) is arranged outside. The carrier 30 is supported by the first main bearing 51 and the second main bearing 53 in such a support manner so as to be rotatable relative to the first casing body 61 and the third casing body 63.

  Reference numeral 52 denotes a sun gear bearing that supports the sun gear 22. The outer ring 52 </ b> B of the sun gear bearing 52 is disposed on the inner periphery of the second central through hole 32 </ b> B formed at the radial center of the second side portion 32 of the carrier 30. The inner ring 52 </ b> A of the sun gear bearing 52 is disposed on the outer periphery of the shaft portion 22 </ b> D of the sun gear 22.

  As described above, the carrier 30 of the first stage planetary gear unit 14 is integrated with the output shaft 40 (of the first stage planetary gear unit 14) via the bolt 37. The output shaft 40 also serves as the input shaft of the second stage planetary gear unit 15. Therefore, hereinafter, the output shaft 40 of the first stage planetary gear unit 14 will be referred to as the input shaft 40 when describing the second stage planetary gear unit 15 (the output shaft 40 of the first stage planetary gear unit 14 = The input shaft 40 of the second stage planetary gear unit 15).

  In the present embodiment, the present invention is applied to the structure that regulates the axial movement of the sun gear 82 incorporated at the tip of the input shaft 40 in the second stage planetary gear device 15.

  The second stage planetary gear unit 15 is connected in a manner that is movable in the axial direction to the input shaft 40, the output shaft (not shown), and the tip of the input shaft 40. The input shaft 40 is interposed between the sun gear 82 incorporated, the third casing body (support member) 63 that supports the input shaft 40 via the second main bearing 53, and the second main bearing 53 and the sun gear 82. An externally fitted collar 56.

  The second stage planetary gear unit 15 is also a vertical gear unit in which the input shaft 40 is disposed above the output shaft (not shown) in the vertical direction O1. The second-stage planetary gear device 15 has a movement restricting member 70 that restricts the movement of the sun gear 82 in the axial direction. The movement restricting member 70 is integrated with the third casing body 63, disposed between the sun gear 82 and the collar 56, and faces the sun gear 82 in the axial direction.

  Details will be described below.

  The input shaft 40 of the second stage planetary gear unit 15 includes a disk-shaped flange portion 42 integrated with the second side portion 32 of the carrier 30 via a bolt 37, and a load from the radial center of the flange portion 42. And a shaft portion 44 protruding and extending to the side. The shaft portion 44 has a step portion 44A having a load side facing surface.

  A third casing body 63 is located in the vicinity of the input shaft 40. The third casing body 63 includes a wall portion 63A extending radially inward, a bearing mounting portion 63B formed at the radially inner end of the wall portion 63A, and the bearing mounting portion 63B and the axial direction. And an oil seal arrangement part 63D arranged side by side.

  A second main bearing 53 is disposed between the input shaft 40 and the third casing body 63. That is, the third casing body 63 supports the input shaft 40 via the second main bearing 53. The second main bearing 53 includes an inner ring 53A that contacts the outer periphery of the input shaft 40 and the stepped portion 44A of the shaft portion 44, an outer ring 53B that contacts the bearing mounting portion 63B of the third casing body 63, and an inner ring 53A and an outer ring 53B. Rolling elements (balls in this example) 53D that roll between them. On the load side of the second main bearing 53, a collar 56 is disposed in contact with the inner ring 53A of the second main bearing 53.

  The collar 56 has an inner periphery 56A that is slightly smaller than the outer diameter d40 (56) of the portion of the input shaft 40 to which the collar 56 is externally fitted. The positioning of the two main bearings 53 on the input shaft 40 is performed. The collar 56 has a substantially rectangular shape with a cross section parallel to the axis extending in the axial direction, and is formed in a ring shape as a whole. The outer periphery 56B of the collar 56 forms a sliding contact surface of the oil seal 58, and two oil seals 58 are disposed between the outer periphery 56B of the collar 56 and the oil seal disposing portion 63D of the third casing body 63. ing. On the load side of the collar 56, the movement restricting member 70 is disposed with a gap δ (70-56) in the axial direction. Further, a contact member 74 is disposed on the load side of the movement restricting member 70. The movement restricting member 70 and the abutting member 74 will be described in detail later.

  A sun gear 82 is incorporated on the load side of the abutting member 74, that is, on the tip end (load side: lower side) of the input shaft 40.

  The sun gear 82 has an inner spline 82B on the inner periphery and a tooth portion 82C on the outer periphery. The inner spline 82B is engaged with an outer spline 44S formed at the tip of the input shaft 40. That is, the sun gear 82 is incorporated in the input shaft 40 (in a connecting manner that can move in the axial direction) via the outer spline 44S and the inner spline 82B. As described above, the sun gear 22 of the first stage planetary gear unit 14 is formed of a helical gear, but the sun gear 82 of the second stage planetary gear unit 15 employs a spur gear.

  Conventionally, the sun gear 82 has not been particularly restricted with respect to the movement toward the axially opposite load side. However, in the present embodiment, the movement restricting member 70 restricts the movement toward the axial antiload side. The movement restricting member 70 is integrated with the third casing body (supporting member) 63, is disposed between the sun gear 82 and the collar 56, and faces the sun gear 82 in the axial direction.

  As described above, the third casing body 63 has the wall portion 63A that extends to the inside in the radial direction. The movement restricting member 70 is fixed to the load side end surface 63A1 of the wall portion 63A of the third casing body 63 via a plurality of (six in this example) bolts 72, and is integrated with the third casing body 63. Yes. Reference numeral 70 </ b> H is a bolt hole of the bolt 72 formed in the wall portion 63 </ b> A of the third casing body 63.

  FIG. 3 shows a cross section (cross section parallel to the shaft) in a state in which the movement restricting member 70 is incorporated in the second stage planetary gear unit 15, and FIG. 4 shows a front view of the movement restricting member 70 alone. Has been. The cross section of the movement restricting member 70 shown in FIG. 3 corresponds to the cross section taken along the line III-III in FIG.

  The movement restricting member 70 is formed of a ring-shaped member having a cross section parallel to the shaft having a long rectangular shape in the radial direction and having a through hole 70P through which the input shaft 40 passes in the center in the radial direction. On the surface 70A of the movement restricting member 70 facing the sun gear 82, two grooves 70B are formed diagonally from the radially outer side to the inner side. More specifically, the groove 70B is drilled from a position outside the center in the radial direction, linearly goes inward in the radial direction (normal direction), and reaches the through hole 70P. This groove 70B is for facilitating the movement of the lubricant present in the vicinity of the movement restricting member 70 radially inward.

  In this embodiment, a contact member 74 is disposed between the sun gear 82 and the movement restricting member 70. In this embodiment, the contact member 74 is configured by a ring-shaped member that functions as a sliding bearing. The abutting member 74 is incorporated in the input shaft 40 with a clearance fit. However, the inner diameter of the inner circumference 74A of the corresponding member is D74, which is substantially the same as the outer diameter d40 (74) at the position where the abutting member 74 of the shaft portion 44 of the input shaft 40 is fitted. That is, the abutting member 74 is externally fitted to the input shaft 40 with a clearance fit, but does not have a clearance enough to move in the radial direction with respect to the input shaft 40 (diameter relative to the input shaft 40). Cannot move in the direction). Further, in this embodiment, no gap is provided between the load side end surface 74B of the contact member 74 and the anti-load side end surface 82E of the sun gear 82.

  Here, the size of the gap between the collar 56, the movement restricting member 70, and the abutting member 74 will be described. In this embodiment, the inner diameter D70 of the movement restricting member 70 is externally fitted to the movement restricting member 70 of the input shaft 40. It is larger by 2 · δ70 than the outer diameter d40 (70) of the portion that is formed. That is, there is a gap of δ 70 between the outer periphery of the input shaft 40 and the inner periphery of the movement restricting member 70, and the input shaft 40 and the movement restricting member 70 are not in contact with each other.

  A gap δ (70-56) in the axial direction is formed between the anti-load side end surface 70E of the movement restricting member 70 and the load side end surface 56F of the collar 56. That is, the movement restricting member 70 and the collar 56 are not in contact. A gap δ (70-74) in the axial direction is formed between the load-side end surface (surface facing the sun gear 82) 70A of the movement restricting member 70 and the anti-load-side end surface 74C of the contact member 74. That is, the movement restricting member 70 and the abutting member 74 are not in contact.

  The gap δ (70-74) between the movement restricting member 70 and the contact member 74 is larger than the gap δ (70-56) between the movement restricting member 70 and the collar 56.

  Next, the operation of this embodiment will be explained.

  The basic power transmission actions of the first to third stage planetary gear units 14 to 16 of the drive unit 10 are all the same. That is, when the motor shaft 12A of the motor 12 rotates, the input shaft 20 of the first stage planetary gear device 14 integrated with the motor shaft 12A rotates, and the sun gear 22 rotates. Then, the planetary gear 24 revolves around the sun gear 22 while rotating. The revolution of the planetary gear 24 rotates the entire carrier 30 via the connecting pin 34 that supports the planetary gear 24. The rotation of the carrier 30 is transmitted to an output shaft (input shaft of the second stage planetary gear device 15) 40 connected to the second side portion 32 of the carrier 30 via a bolt 37.

  The rotation of the input shaft 40 rotates the sun gear 82 via the outer spline 44S of the input shaft 40 and the inner spline 82B of the sun gear 82. Thereafter, the same operation as that of the first stage planetary gear unit 14 already described is performed in the second stage planetary gear unit 15 and the third stage planetary gear unit 16.

  Then, the final output shaft 118 located at the lowermost part of the third stage planetary gear unit 16 meshes with the turning internal gear 114 of the lower traveling body 102 of the excavator 100, and the upper turning body 106 turns by the reaction of the meshing. It can turn around the axis of the internal gear 114.

  Here, the sun gear 82 of the second stage planetary gear unit 15 is a spur gear, and is connected by a connection by the outer spline 44S and the inner spline 82B (connection by a connection mode movable in the axial direction). However, the second-stage planetary gear unit 15 is installed vertically, the input shaft 40 is assembled in the vertical direction O1, and the collar 56 is located above the sun gear 82. Therefore, in a normal operation state, the sun gear 82 does not rise and the problem of damage to the second main bearing 53 does not occur. Therefore, conventionally, no particular measures have been taken with respect to the rise of the sun gear 82.

  However, in particular, for applications such as the excavator car 100 where a load that is so strong that the output side rotation is suddenly stopped is frequently applied, a slight assembly error between the gears (such as the inclination of the shaft). A strong thrust load (force to increase) may occur in the sun gear 82 under the influence of the manufacturing error of the tooth surface and the like. The thrust load to be raised by the sun gear (82) sometimes pushes up the collar (56), and as a result, pushes up the entire input shaft (40) into which the collar (56) is press-fitted, and the bearing ( The second main bearing 53) may be damaged.

  However, in the present embodiment, the movement restricting member 70 that restricts the movement of the sun gear 82 in the axial direction is provided. The movement restricting member 70 is integrated with a third casing body 63 that supports the input shaft 40 via a second main bearing 53 via a bolt 72. The movement restricting member 70 is disposed between the sun gear 82 and the collar 56 and faces the sun gear 82 in the axial direction. Therefore, even if a situation occurs in which the sun gear 82 rises strongly toward the axial collar 56 for some reason, the movement restricting member that is disposed facing the third casing body 63 while being fixed thereto. This rise is regulated by 70. Accordingly, the thrust load (upward force) of the sun gear 82 is prevented from being transmitted to the collar 56, and the collar 56 does not rise. Therefore, the effect that the input shaft 40 rises together with the collar 56 does not occur, and the second main bearing 53 is prevented from being damaged.

  Here, in the present embodiment, a contact member 74 is disposed between the sun gear 82 and the movement restriction member 70. In this example, the abutting member 74 is constituted by a sliding bearing. For this reason, problems of excessive wear and heat generation hardly occur between the sun gear 82 rotating at a high rotation speed and the movement restricting member 70 in a fixed state.

  In the present embodiment, the gap δ (70-74) between the movement restricting member 70 and the abutting member 74 is more than the gap δ (70-56) between the movement restricting member 70 and the collar 56. Is set larger. For this reason, it is easy to supply the lubricant between the movement restricting member 70 and the abutting member 74, but on the other hand, it is possible to obtain an effect that the lubricant hardly reaches the vicinity of the collar 56. Since relative rotation occurs between the movement restricting member 70 and the abutting member 74, it is preferable that the lubricant is supplied in an abundance. On the other hand, the lubricant is not particularly required in the vicinity of the collar 56. Rather, in this configuration example, an oil seal 58 is disposed on the outer periphery of the collar 56 to prevent the lubricant from coming and going between the first stage planetary gear unit 14 side and the second stage planetary gear unit 15 side. It is said. From this point of view, it is rather undesirable for the lubricant to be supplied in the vicinity of the collar 56. In the present embodiment, the gap δ (70-74) between the movement restriction member 70 and the abutting member 74 is set larger than the gap δ (70-56) between the movement restriction member 70 and the collar 56. Therefore, it is possible to effectively suppress the lubricant from reaching the vicinity of the collar 56 due to the labyrinth effect.

  The labyrinth effect due to the presence of the movement restricting member 70 includes the gap δ (70-56) between the movement restricting member 70 and the collar 56 and the gap δ ( 70-74), which is an effect obtained correspondingly (only by the presence of the movement restricting member 70). Therefore, it can be said that the movement restricting member 70 further enhances the sealing performance between the first-stage planetary gear device 14 side and the second-stage planetary gear device 15 side.

  In the present embodiment, a groove 70 </ b> B is formed on the surface 70 </ b> A facing the sun gear 82 of the movement restricting member 70 from the radially outer side to the inner side. Accordingly, the sun gear 82 in terms of “the lubricant passage” can be obtained without increasing the gap between the sun gear 82 and the movement restricting member 70 in terms of “the distance the sun gear 82 moves in the axial direction”. And the movement restricting member 70 can be formed substantially larger. That is, it is preferable that the sun gear 82 does not move freely in the vertical direction. Therefore, the groove 70B is formed to suppress the axial movable distance of the sun gear 82 to be small. In addition, a good effect can be obtained in that more lubricant can be introduced between the movement restricting member 70 and the contact member 74.

  In the above embodiment, the movement restricting member has a groove, but the groove of the movement restricting member is not necessarily required. Further, the shape of the groove is not particularly limited. That is, since the effect of introducing the lubricant can be obtained as long as the groove is directed from the radially outer side to the inner side, the groove may have a shape different from the above example. For example, in the above example, the groove is linearly formed in the radial direction, but may be formed in a curved shape (for example, in an arc shape). Moreover, the groove | channel penetrated from a radial direction outer side edge part to an inner side edge part may be sufficient. Furthermore, in the above embodiment, two grooves are formed, but the number of grooves to be formed is not limited to two, and may be one or three or more.

  Moreover, in the said embodiment, although the contact member was comprised with the slide bearing, the specific structure of a contact member is not specifically limited to this. In other words, the abutting member does not necessarily need to be configured by a sliding bearing. For example, it may be configured by a thrust bearing having rolling elements such as balls and rollers in order to more actively reduce sliding resistance. Good. In addition, the contact member is not an essential component in the first place and may not be provided.

  Further, the size of the gap between the collar, the movement restricting member, and the contact member is not necessarily limited to the above example, and the magnitude relationship may be reversed depending on other surrounding configurations.

  In the above embodiment, the present invention has been applied to the (second stage) planetary gear device incorporated in the drive unit of the excavator car, but a specific application example of the vertical gear device of the present invention is as follows. However, the present invention is not limited to this example. For example, in the above example, the present invention may be applied to the first-stage or third-stage planetary gear device. The gear device is not necessarily a simple planetary gear device. For example, the gear device may be an eccentric oscillating planetary gear device in which the planetary gear oscillates and meshes with the internal gear. Furthermore, it may not be a planetary gear device, and may be a parallel shaft gear device or an orthogonal shaft gear device, for example. Further, the speed reduction device is not necessarily required, and a constant speed device (idler device) or a speed increase device may be used.

40 ... Input shaft 53 ... Second main bearing (bearing)
56 ... Collar 63 ... Third casing body (supporting member)
70 ... Movement restriction member 82 ... Sun gear (gear)

Claims (5)

Between the input shaft, the output shaft, a gear incorporated in a coupling manner movable in the axial direction to the input shaft, a support member that supports the input shaft via a bearing, and between the bearing and the gear A collar externally fitted to the input shaft,
The input shaft is a vertical gear device that is disposed vertically above the output shaft,
A movement restricting member for restricting the axial movement of the gear;
The movement restricting member is integrated with the support member, is disposed between the gear and the collar, and is opposed to the gear in the axial direction. In claim 1,
A vertical gear device, wherein a contact member is disposed between the gear and the movement restricting member. In claim 2,
A gap is formed between the movement regulating member and the collar, and a gap is formed between the movement regulating member and the abutting member,
A longitudinally mounted gear device, wherein a gap between the movement regulating member and the abutting member is larger than a gap between the movement regulating member and the collar. In any one of Claims 1-3,
An oil seal is disposed on the outer periphery of the collar. In any one of Claims 1-4,
A longitudinally-arranged gear device is characterized in that a groove facing from the radially outer side to the inner side is formed on a surface of the movement restricting member facing the gear.

Images