JP2006226499A - Reduction gear and lubricating method for reduction gear - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a reduction gear provided with a lubricant splashing up mechanism (lubricant supply mechanism) eliminating agitation loss of lubricant and capable of coping with various gear ratio with keeping compactness. <P>SOLUTION: A hollow input shaft 112 penetrating through a reduction gear mechanism K1 and rotating at high speed is provided. Centrifugal force is given to lubricant by rotation of a rotary member 126A inserted through an inside of the input shaft 112 and capable of rotating as one unit with the input shaft 112. Lubricant is splashed up by converting the centrifugal force to upward motion thrust force. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a reduction gear that decelerates input rotation and a method of lubricating the reduction gear.

  Conventionally, a reduction gear as shown in FIG. 4 has been disclosed (see, for example, Patent Document 1).

  In this speed reduction device 10, a high speed shaft 12 is located at the upper portion and a low speed shaft 14 is located at the lower portion, and both shafts 12 and 14 are arranged close to each other coaxially via bushes 16 so as to be independently rotatable. The high-speed shaft 12, the bush 16, and the low-speed shaft 14 are provided with through holes 12A, 14A, and 16A, respectively, which integrally form one lubricating oil (lubricant) path 20.

  In this state, when the high-speed shaft 12 rotates at a high speed and the low-speed shaft 14 rotates at a low speed, a negative pressure is generated in the through hole 12A, and the lubricating oil (lubricant) staying in the lower part of the apparatus is sucked up to the upper part of the apparatus. And supply and reflux.

JP 2000-161473 A

  However, since the speed reducer 10 described above is configured to suck the lubricant using the negative pressure generated due to the difference in rotational speed between the high speed shaft and the low speed shaft, the high speed shaft rotates at a considerably high rotational speed. In addition, a condition that the low-speed shaft rotates at a relatively slow rotation speed (high reduction ratio) is necessary, and it is difficult to increase the suction force.

  Although it is possible to put the lubricant in advance enough to fill the upper part of the device (above the part where lubrication is required), in this case the speed reduction mechanism is always immersed in the lubricant. Therefore, the driving loss increases because the lubricant rotates while stirring. In addition, there is a problem that the internal pressure of the apparatus tends to increase due to heat generated by the stirring resistance. Furthermore, the absolute amount of lubricant required becomes large, and considering waste oil treatment such as oil exchange, it is not preferable in terms of environment and cost.

  The present invention has been invented to solve these problems, and while maintaining compactness, it reduces the stirring loss of the lubricant and is sufficient regardless of the rotational speed and reduction ratio of the reduction gear. An object of the present invention is to provide a speed reducer that can obtain a satisfactory cooling effect.

  The present invention is a reduction gear having a high speed shaft and a speed reduction mechanism for reducing the rotation of the high speed shaft, the hollow shaft penetrating the speed reduction mechanism, being inserted into the hollow shaft, and the high speed shaft. These problems are solved by having a structure that has a lubricant lifting mechanism provided with a rotating member that rotates integrally.

  Thereby, even when the relative rotational speed difference between the high speed shaft and the low speed shaft is small, the lubricant can be efficiently supplied to the upper part of the apparatus.

  According to the present invention, efficient lubrication and cooling can be performed in various reduction gears. Further, the absolute amount of lubricant used can be reduced, and the cost and environmental load can be reduced.

  Exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings.

  FIG. 1 is an overall partial cross-sectional view of a geared motor GM100 including a reduction gear 110 that is an example of an embodiment according to the present invention. FIG. 2 is a cross-sectional view taken along line II-II in FIG.

  The geared motor GM100 includes a motor 122 that is a drive source and a reduction gear 110.

  The motor 122 is connected to the reduction gear 110 by a bolt or the like, and the motor shaft 124 (high-speed shaft) is installed vertically and faces the inside of the reduction gear 110.

  The reduction gear 110 includes an input shaft 112 (hollow shaft), a reduction mechanism K1 that reduces the rotation of the input shaft 112, and an output shaft 114 that transmits the rotation reduced by the reduction mechanism K1 to an unillustrated counterpart machine. And a lubricant lifting mechanism P1.

  The input shaft 112 is hollow, and the motor shaft 124 is inserted into the hollow portion. The internal teeth 112B provided on the inner peripheral surface of the input shaft 112 and the spline 124A directly cut by the motor shaft 124 are provided. Is engaged.

  An eccentric body 132 is integrally formed with the input shaft 112, and the rotation of the motor shaft 124 can be transmitted to the eccentric body 132 while being rotatably supported by the bearings 158 and 160.

  The eccentric body 132 supports the external gear 136 through an eccentric body bearing 134 so as to be swingable. The external gear 136 meshes with an external pin 130 that functions as an internal tooth of an internal gear integrated with the casing 128. The number of external pins 130 (internal teeth) is set to be slightly larger than the number of external teeth of the external gear 136.

  The external gear 136 is provided with a plurality of inner pin holes 136A, and the inner pins 138 and the inner rollers 142 are loosely fitted into the inner pin holes 136A.

  Both ends of the inner pin 138 are press-fitted into the first and second carrier bodies 144 and 146, and are further fixed by bolts 140 on the first carrier body 144 side. That is, the rotation of the external gear 136 can be transmitted to the first and second carrier bodies via the inner pin 138.

  The first carrier body 144 is supported by bearings 154 and 158, while the second carrier body 146 is supported by bearings 156 and 160, both of which are rotatable about the axis O1. The second carrier body 146 is formed integrally with the output shaft 114, and transmits power to a counterpart machine (not shown).

  Next, the lubricant lifting mechanism P1 will be described.

  The lubricant scooping mechanism P1 includes a recess 148, a second oil introduction hole 150 that guides the lubricant (lubricant) to the recess 148, a rotating member 126A that is accommodated in the recess 148, and the lubricant that has been lifted up. It is constituted by a lubricant passage 112C serving as a passage and an outlet 112A through which the lubricant is blown.

  The concave portion 148 has a substantially mortar shape and is formed integrally with the second carrier body 146, but may be formed of a separate member instead of being integrated. The second carrier body 146 is provided with a second oil introduction hole 150 that connects the recess 148 and the internal space 129 in which the lubricant is retained.

  A recess 124B is provided on the front end surface of the motor shaft 124 that is inserted into the input shaft 112, and one end of the rotating member shaft 126B is press-fitted into the recess 124B. The rotating member 126A is fixed to the other end of the rotating member shaft 126B. In this state, the rotating member 126A is accommodated in the recess 148.

  The rotating member 126A in the speed reducer 110 is a general immediate bevel gear (umbrella-shaped member), and has a plurality of irregularities constituting “teeth”, but is not necessarily limited to this shape. However, any shape that can impart centrifugal force to the lubricant by rotation is acceptable.

  Here, in the speed reducer 110 shown in FIG. 1, the shape of the mortar of the recess 148 and the shape of the rotating body formed by the tooth tip of the rotating member 126A are in a shape in which they face each other with a very narrow gap. However, the present invention is not necessarily limited to this. For example, a larger gap may be formed between the two.

  Since the rotating member shaft 126B is a member that is thinner than the hollow portion of the input shaft 112, a gap with the input shaft 112 is formed as a part of the lubricant passage 112C. Further, in the vicinity of the uppermost portion of the lubricant path 112C, a plurality of air outlets 112A are provided on the input shaft 112 so that the raised lubricant can be blown out. In this embodiment, the air outlet is provided only in the vicinity of the uppermost portion of the lubricant passage 112C, but it may be provided in the middle or further in both. It can be changed appropriately according to the purpose.

  The first carrier body 144 is also provided with a first oil guide hole 145 for supplying the lubricant blown from the blowout port 112A to the outside of the speed reducer (radially outside the input shaft 112). Yes.

  Reference numeral 152 denotes an oil gauge for confirming the amount of lubricating oil of the reduction gear 110.

  The arrows in the figure indicate the flow of the lubricant in the speed reducer. In addition, the lubricant is sealed in the internal space 129 of the reduction gear 110 to the extent that the vertical position of the reduction mechanism K1 is not reached.

  Next, the operation of the reduction gear 110 will be described.

  When the motor 122 is energized and the motor shaft 124 rotates, the input shaft 112 rotates accordingly. The rotation of the input shaft 112 is transmitted to the eccentric body 132, and the eccentric body 132 tries to swing and rotate the external gear 136 via the eccentric body bearing 134. However, the rotation of the external gear 136 is restricted by the presence of the external pin 130 that is in mesh with the internal gear, so that the external gear 136 only swings. This swing component is absorbed by the inner pin hole 136A, the inner pin 138 and the inner roller 142, and only the rotation component of the external gear 136 due to the difference in the number of external pins 130 and the number of external teeth of the external gear 136 is obtained. It is transmitted to the first and second carrier bodies 144 and 146 via the inner pin 138. That is, at this time, the rotation of the input shaft 112 is decelerated to (number of external gear teeth−number of external pins) / (number of external gear teeth) and output to the output shaft 114. Become.

  In this embodiment, from the viewpoint of securing the transmission capacity, the external gear 136 is configured as two, but is not limited thereto, and may be configured as one or three or more. Further, although the speed reduction mechanism K1 of the present embodiment is a one-stage speed reduction, a speed reduction mechanism having two or more levels may be configured.

  Next, the operation of the lubricant lifting mechanism P1 will be described.

  As the motor shaft 124 rotates, the rotating member shaft 126B fixed to the motor shaft 124 rotates, and the rotating member 126A also rotates. At this time, a lubricant is sealed in the internal space 129 of the reduction gear 110, and the lubricant also enters the recess 148 through the second oil guide hole 150, soaking the rotating member 126A. Accordingly, when the rotating member 126A rotates, the lubricant present in the recess 148 is applied with centrifugal force and moves outward in the radial direction of the rotating member (centrifugal force is applied), but the mortar-shaped recess 148. Therefore, the kinetic energy (centrifugal force) trying to move in the radial direction is converted into energy rising upward in the lubricant passage 112C (upward moving driving force in the hollow shaft). The lubricant that has passed through the lubricant passage 112C toward the upper side of the reduction gear 110 passes through the blowout port 112A provided in the input shaft 112, and then the bearing 158, and further, the eccentric body bearing 134 located at the lower part thereof, The external gear 136 and the like are lubricated and cooled. The lubricant that has passed through the first oil guide hole 145 provided in the first carrier body 144 mainly lubricates and cools the bearings 154 and sliding portions such as the inner pins 138 and the outer pins 130. Further, there is a lubricant that is supplied to the upper side of the bearing 154 through the gap between the input shaft 112 and the first carrier body (see arrow).

  As described above, the portion of the speed reduction mechanism K1 that requires a high level of lubrication / cooling is appropriately lubricated / cooled by the lubricant pumped up by the lubricant lifting mechanism P1, resulting in insufficient lubrication / cooling. It is possible to prevent damage to the speed reducer.

  Further, since the amount of the lubricant sealed in the internal space 129 of the reduction gear 110 is set at a position lower than that of the speed reduction mechanism K1 even during start-up and operation, the speed is reduced by the operation of the reduction gear. Without causing the members in the apparatus to stir the lubricant, it is possible to prevent problems such as a transmission loss, an increase in internal pressure, a temperature rise, and oil leakage that accompany the stirring.

  Further, since the power source of the lubricant lifting mechanism P1 is directly obtained from the rotation of the motor shaft 124 (high speed shaft), the lubricant is applied even when the reduction ratio is small and the difference in the rotational speed between the high speed shaft and the low speed shaft is small. It is possible to lift up without problems.

  Further, the lubricant that is lifted up by the lubricant lifting mechanism P1 is a path through which a member such as an input shaft, which is inherently present in this type of reduction gear, is hollow and through which the lubricant passes (lubricant path 112C). Therefore, there is no need to newly provide a path outside the reduction gear, and the compactness of the device itself can be maintained.

  In addition, since the absolute amount of lubricant that needs to be sealed inside the device can be reduced, the cost can be reduced, and the burden of waste oil treatment, which is a problem when changing oil, can be reduced. However, it has realized a friendly (ecological) device.

  Next, it demonstrates using FIG.

  FIG. 3 shows a geared motor GM300 including a reduction gear 310 that is an example of another embodiment of the present invention.

  Here, in order to avoid redundant description, the same or similar members as those of the geared motor GM100 (reduction gear 110) described above are denoted by the same reference numerals in the last two digits in FIG. Only the part will be described.

  The geared motor GM300 includes a motor 322 and a reduction gear 310, and the rotation of the motor shaft 324 can be reduced by the reduction mechanism K3 and transmitted to the output shaft 314.

  In the present embodiment, the present invention is applied to a simple planetary gear type reduction mechanism K3, and a hollow shaft that penetrates the reduction mechanism is constituted by an input shaft 312 and sun gears 370 and 376.

  An input shaft 312 is fixed to the motor shaft 324 by a key member 325, and the input shaft 312 can rotate integrally with the motor shaft 324. The input shaft 312 is a hollow shaft having a short length in the axial direction, and an internal tooth 313 is provided on the inner peripheral surface of the hollow portion. A first sun gear 370 meshes with the internal teeth 313 and is rotatable about the axis O3.

  On the other hand, a first internal gear 374 is fixed to the casing 328. Between the first internal gear 374 and the first sun gear 370, there is a first planetary gear 372 that meshes with both gears 370 and 374, and can revolve while rotating around the first sun gear 370. Has been.

  A first carrier pin 373 is inserted into the first planetary gear, and the revolution component of the first planetary gear 372 can be transmitted to the first carrier body 373. The first carrier body 373 meshes with the second sun gear 376. A second internal gear 375 is provided on the inner peripheral surface of the casing 328 corresponding to the second sun gear 376, and a second planetary gear 376 is provided between the second internal gear 375 and the second sun gear 376. A gear 378 is located and meshes with both gears 375 and 376. Further, a second carrier pin 379 is inserted into the second planetary gear 378 so that the revolution component of the second planetary gear 378 can be transmitted to the second carrier body 380. The second carrier body 380 is formed integrally with the output shaft 314.

  In the present embodiment, a simple planetary gear reduction mechanism having two stages is used. However, the present invention is not limited to this, and a single-stage structure or three or more stages may be used depending on the application.

  Next, the operation of geared motor GM300 (decelerator 310) will be described. Here, similarly, the same or similar members are given the same reference numerals in the last two digits, and repeated explanation is omitted as appropriate.

  When the motor 322 is energized and the motor shaft 324 rotates, the input shaft 312 and the first sun gear 370 rotate accordingly. When the first sun gear 370 rotates, the meshed first planetary gear 372 slowly revolves around the first sun gear 370 while rotating.

  The revolution component of the first planetary gear 372 is transmitted to the second sun gear 376 via the first carrier body 373, and revolves while rotating the second planetary gear 378. This revolution component is then transmitted to the output shaft 314 via the second carrier pin 379 and the second carrier body 380.

  The lubricant lifting mechanism P3 exhibits substantially the same operation as the lubricant lifting mechanism P1 described above, but in this embodiment, the two sun gears 370 and 376 are made hollow and the hollow portions are used as the lubricant passage 312C. Therefore, the lubricant can be blown out from the gap G1 between the first sun gear 370 and the second sun gear 376. Of course, it may be configured so that the lubricant does not blow out by closing the gap G1 if necessary.

  In all of the above embodiments, the rotating members are general quick bevel gears, and it is possible to scoop up the lubricant not only when the geared motor rotates in the normal direction but also when it reverses. . If the rotational direction is determined to be one direction depending on the use of the geared motor, for example, a propeller-shaped member or a bevel gear with an inclined tooth is used as the rotating member, so that the centrifugal force and the rise can be more efficiently applied to the lubricant. Power can be applied, and the lifting efficiency can be further increased.

  Moreover, although all the blower outlets are provided in the radial direction of the hollow shaft, they may be provided in the axial direction or in the oblique direction.

  The present invention can be applied to a speed increasing device as well as a speed reducing device.

Whole partial sectional view of geared motor GM100 using reduction gear 110 which shows an example of an embodiment of the present invention. Sectional view along the arrow II-II line in FIG. Whole partial sectional view of geared motor GM300 using reduction gear 310 showing an example of an embodiment of the present invention. The transmission of Patent Document 1 as a conventional example

Explanation of symbols

GM100 ... Geared motor 110 ... Deceleration device 112 ... Input shaft 112A ... Air outlet 112C ... Lubricant passage 114 ... Output shaft 122 ... Motor 124 ... Motor shaft 126A ... Rotating member 126B ... Rotating member shaft 130 ... Outer pin 132 ... Eccentric body 134 ... Bearing for eccentric body 136 ... External gear 138 ... Inner pin 142 ... Inner roller 144 ... First carrier body 145 ... First oil guide hole 146 ... Second carrier body 148 ... Recess 150 ... Second oil guide hole 152 ... Oil gauge 154, 156, 158, 160 ... Bearing K1 ... Deceleration mechanism P1 ... Lubricant lifting mechanism

Claims (8)

A speed reduction device having a high speed shaft and a speed reduction mechanism for reducing the rotation of the high speed shaft,
A hollow shaft passing through the speed reduction mechanism;
A speed reducer comprising a lubricant scooping mechanism that is inserted into the hollow shaft and includes a rotating member that rotates integrally with the high speed shaft. In claim 1,
The speed reducing device, wherein the rotating member is an umbrella-shaped member that rotates integrally with the high-speed shaft. In claim 1 or 2,
The lubricant lifting mechanism is
While having a recess for accommodating the rotating member,
A lubricant passage is formed by the recess and the hollow shaft. In claim 3,
The said recessed part is provided in the flange body which transmits the rotation decelerated by the said reduction gear to an output shaft. The reduction gear characterized by the above-mentioned. In any one of Claims 1 thru | or 4,
The speed reduction mechanism is a swinging internal meshing type reduction device having an eccentric body, an external gear that swings by the eccentric body, and an internal gear that meshes with the external gear, and
The speed reducer characterized in that the hollow shaft also serves as the eccentric body. In any one of Claims 1 thru | or 4,
The speed reduction mechanism is a simple planetary gear type speed reducer having a sun gear, an internal gear, a planetary gear provided between the sun gear and the internal gear, and meshing with both, and ,
The hollow shaft also serves as the sun gear. In any one of Claims 1 thru | or 6.
The speed reducing device, wherein the hollow shaft is provided with a blowout port for blowing out a part of the lubricant from the middle of the hollow shaft in the radial direction to the outside in the radial direction. In claim 7,
The said blower outlet is provided with two or more in the site | part from which the axial direction differs in the said hollow shaft. The speed reducer characterized by the above-mentioned.

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