JP4651022B2 - Decelerator - Google Patents

Description

  The present invention relates to a speed reducer, and more particularly to a speed reducer that decelerates power input from an input shaft and transmits the reduced power to an output shaft that receives a thrust load from a counterpart machine.

  2. Description of the Related Art Conventionally, a speed reducer is known as a device that decelerates rotation serving as a power source such as a motor and transmits it to a counterpart machine.

  These reduction gears are devised in various structures or structures in order to cope with various counterpart machines.

  For example, as shown in FIG. 5, a speed reducer 20 described in Patent Document 1 is known as a speed reducer that receives a thrust load. The speed reducer 20 decelerates the power input from the input shaft (not shown) using the speed reduction element 23 and increases the torque, and transmits the power to the other machine (not shown) via the output shaft 40. ing. At this time, depending on the type of the counterpart machine, due to its structure, the reduction gear operates, and at the same time, a thrust load (an axial load of the output shaft 40) may be applied to the output shaft 40. In order to cope with this, in the speed reducer 20, the output shaft 40 is rotatably supported on the casing 70 by the tapered roller bearing 30, and the anti-load side 40A of the output shaft 40 is also supported by the tapered roller bearing 31. The bearings 30 and 31 are configured to receive a thrust load.

  Furthermore, there is a structure in which the reducer itself does not deal with such a load in the thrust direction and does not apply a thrust load to the output shaft of the reducer by devising the counterpart machine in structure. It was.

JP 2003-106413 A

  However, when the thrust load becomes a value above a certain level, there is a limit to support the large thrust load with the tapered roller bearing as described above, and the wear of the bearing becomes severe. On the other hand, if the capacity of the bearing is increased, the compactness is lost accordingly.

  It may be possible to configure the counterpart machine itself so that no thrust load is generated on the output shaft of the reducer, but it is often difficult for the reducer manufacturer to change the design of the counterpart machine. .

  The present invention has been made to solve these problems, and can cope with a large thrust load from the counterpart machine side on the reduction gear side, and is compact in the configuration of the entire apparatus including the counterpart machine. It is possible to provide a speed reducer that can maintain the above and has high ease of assembly or maintenance.

The present invention relates to a speed reducer that decelerates power input from an input shaft and transmits the power reduced to an output shaft. The output shaft includes a flange portion, and the casing of the speed reducer has the output. An output shaft cover through which the shaft passes is fixed, and a radial bearing that supports a radial load of the output shaft between the flange portion and the output shaft cover in the axial direction of the output shaft, and the output shaft of which the thrust bearing is arranged to support the thrust load, the radial bearing is constituted by a second radial bearing located at the first radial bearing and the output shaft cover side positioned in the flange portion, wherein between the first radial bearing and the second radial bearing and a thrust bearing is disposed, and wherein said thrust bearing second radial bearing, wherein In a state where the force shaft cover detached from the casing, and has a configuration that is disposed to be attached or removed from the load side of the casing.

  This makes it possible to withstand a large thrust load on the reducer side (without any effort on the counterpart machine) while maintaining compactness compared to a reduction gear with the same transmission capacity using a tapered roller bearing. It becomes possible.

  Further, since both the radial bearing and the thrust bearing are present on the counterpart machine side (load side) in the speed reducer, assembly or maintenance can be performed simply by removing the output shaft cover.

  A compact speed reducer capable of withstanding a large thrust load can be provided.

  Also, the reducer is easy to assemble and maintain.

  Hereinafter, an example of an embodiment according to the present invention will be described in detail with reference to the accompanying drawings.

  FIG. 1 shows an application example of a speed reducer 120 according to the present invention.

  The speed reducer 120 according to the present invention is connected to a motor 110 as a power source by a bolt or the like (not shown). The reduction gear 120 and the motor 110 constitute a geared motor GM100. Further, a bevel gear 142 can be rotated integrally with the output shaft 140 by key connection with the output shaft 140 of the speed reducer 120 and is prevented from coming off in the axial direction by a bolt (not shown). The bevel gear 142 meshes with a gear 144 provided on the counterpart machine 190. By this meshing, the rotation of the output shaft of the speed reducer 120 is orthogonally transmitted to the counterpart machine 190. At this time, due to the meshing of the bevel gear 142 provided on the output shaft 140 and the gear 144 provided on the counterpart machine 190, a load (thrust load S1 or thrust load S2) in the direction of the arrow shown in FIG. To do.

  Next, the configuration of the speed reducer of the present invention will be described in more detail with reference to FIGS.

  2 is a cross-sectional view of the X portion of the speed reducer excluding the bevel gear 142 in FIG. 1, and FIG. 3 is an enlarged view of a substantially central portion of FIG.

  2, a roller 123 and a carrier pin 122 are members that transmit power after the rotation of the motor 110 is decelerated to the carrier 124. The carrier 124 corresponds to the flange portion of the output shaft 140. As a mechanism for decelerating the rotation of the motor 110, a planetary gear type mechanism in which the external gear is eccentrically oscillated and internally meshed with the internal gear is preferable. The roller 123 is rotatably fitted on the carrier pin 122. The rotation component of the carrier pin 122 is transmitted to the output shaft through the carrier 124. The output shaft 140 is accommodated in the casing 170, and a part of the output shaft 140 protrudes from an output shaft cover 174 fixed to the casing 170. The output shaft cover 174 is fixed to the casing 170 by bolts 172. Reference numeral 171 denotes a rib provided in the casing 170.

  The output shaft 140 is rotatably supported by the casing 170 via a first radial bearing 126. Further, the output shaft 140 is rotatably supported by the output shaft cover 174 via the second radial bearing 130 at a portion different from the first radial bearing 126 in the axial direction of the output shaft 140. That is, the first radial bearing 126 is disposed on the flange portion (carrier 124) side of the output shaft 140, and the second radial bearing 130 is disposed on the output shaft cover side of the output shaft 140. A first intermediate support member 132 is provided between the first radial bearing 126 and the casing 170. The first intermediate support member 132 and the casing 170 are fixed by welding. However, welding is not an essential component in the present invention.

  On the other hand, a thrust bearing 128 is disposed between the first radial bearing 126 and the second radial bearing 130 (details will be described later). The thrust bearing 128 is in contact with the second intermediate support member 134, and its axial position is restricted. Further, the second intermediate support member 134 is fixed to the first intermediate support member 132 by a bolt 136. In addition, each member of the code | symbol 150,152,154 has the 1st radial bearing 126, the thrust bearing 128, the 2nd radial bearing 130 between the carrier (flange part of the output shaft 140) 124 and the output shaft cover 174. The reference numeral 150 represents a first position restricting member, the reference numeral 152 represents a second position restricting member, and the reference numeral 154 represents a third position restricting member.

  Reference numeral 180 denotes an oil seal.

  Next, the description of the periphery of each bearing will be described in more detail with reference to FIG.

  The first radial bearing 126 includes an inner ring 126A, an outer ring 126B, and 126C. The inner ring 126A is fixed to the output shaft 140, and is configured to be rotatable with the rotation of the output shaft 140. On the other hand, the outer ring 126 </ b> B is in contact with the first intermediate support member 132. With this configuration, the reaction force of the radial load received by the output shaft 140 can be received by the casing 170 via the first radial bearing 126 and the first intermediate support member 132.

  Further, a second radial bearing 130 is disposed on the counterpart machine side 190 of the output shaft 140. The second radial bearing 130 is configured as a self-aligning roller bearing in FIG. 2, but is not limited to this. By configuring as a self-aligning roller bearing in this way, it is possible to absorb the mounting error of the output shaft 140 and the deflection of the shaft when assembled to the counterpart machine 190. The second radial bearing 130 includes an inner ring 130A and an outer ring 130B, and 130C and 130D. The inner ring 130 </ b> A is fixed to the output shaft 140 and is configured to be rotatable integrally with the rotation of the output shaft 140. On the other hand, the outer ring 130 </ b> B is in contact with the output shaft cover 174. With this configuration, the output shaft cover 174 can receive the radial load received by the output shaft 140 via the second radial bearing.

  Further, a thrust bearing 128 is disposed between the first radial bearing 126 and the second radial bearing 130. The thrust bearing 128 includes two housings 128B and 128C, a ball holder 128A located at the center of the two housings 128B and 128C, and balls 128D and 128E. The two housings 128B and 128C have their axial positions regulated by fixing the second intermediate support member 134 to the first intermediate support member 132 with bolts 136. On the other hand, the sphere holder 128A is fixed to the output shaft 140 and is configured to be integrally rotatable.

  That is, when a thrust load S1 is applied from the counterpart machine side 190 to the motor 110 side, the thrust load S1 is transmitted to the ball 128D and the housing 128B via the ball cage 128A, and further, the first intermediate support member. The thrust load S <b> 1 is supported by being transmitted to the casing 170 through 132. When a thrust load S2 is applied in the opposite direction with respect to the output shaft 140, the thrust load S2 is transmitted to the ball 128E and the housing 128C via the ball cage 128A, and further, the second intermediate support member. 134 and the bolt 136 are transmitted to the casing 170, and the thrust load S2 is supported.

  Next, the operation of the speed reducer according to this embodiment will be described.

  When the motor 110 is energized and the roller 123 and the carrier pin 122 rotate through a speed reduction unit (not shown), the carrier 124 also starts to rotate. At the same time, the output shaft 140 also starts to rotate. Since the rotation of the output shaft 140 is transmitted to the gear 144 provided in the counterpart machine 190 via the bevel gear 142, the mesh between the bevel gear 142 and the gear 144 of the counterpart machine 190 causes the output shaft 140 to move to the counterpart machine. A large thrust load S1 is received from the 190 side to the motor 110 side.

  However, in the reduction gear 120 according to this embodiment, such a large thrust load S1 is transmitted to the ball 128D and further to the housing 128B via the ball cage 128A of the thrust bearing 128 provided on the output shaft 140. It is transmitted to the subsequent first intermediate support member 132 and casing 170, and is received by the entire reduction gear. In addition, when a radial load is applied to the output shaft 140, the radial load is supported by the first radial bearing 126 and the second radial bearing 130. In this way, by bearing the roles of the bearing that receives various loads applied to the output shaft 140 in the radial direction and further the bearing that receives in the thrust direction, it can receive a large load both in the radial direction and in the thrust direction. Is possible. Further, as in the present embodiment, different parts of the output shaft 140, that is, the first radial bearing 126 positioned on the flange (carrier 124) side and the second radial bearing 130 positioned on the output shaft cover 174 side. By arranging two radial bearings as described above, it is possible to share the radial load borne by each bearing and to receive the radial load efficiently.

  In addition, the thrust bearing 128 is well utilized in the conventional dead space (space generated between the casing 170, the output shaft 140, and the output shaft cover 174 in this embodiment) provided in this type of speed reducer. Since the arrangement is made, the entire thrust bearing 128 does not cause an increase in the size of the reduction gear, and the compactness is not greatly sacrificed.

  Furthermore, in the present embodiment, the output shaft 140 is provided with a carrier (flange portion) 124, and the output shaft cover 174 through which the output shaft 140 passes is provided in the casing of the speed reducer, and the flange in the axial direction of the output shaft 140 is provided. A radial bearing 126, 130 that supports the radial load of the output shaft 140 and a thrust bearing 128 that supports the thrust load of the output shaft are arranged between the output shaft cover 174 and the output shaft cover 174 to constitute a reduction gear. Yes. With this configuration, when assembling these bearings 126, 128, 130, etc., it is possible to easily assemble them by sequentially assembling from the motor 110 side to the counterpart machine 190 side with the output shaft cover 174 removed. is there. Similarly, during maintenance, it can be easily disassembled by sequentially removing it from the counterpart machine with the output shaft cover removed. Therefore, even if a thrust bearing 128 or the like is newly provided, the reducer can be assembled and maintained. Can also be maintained well.

  In addition, by using the first intermediate support member 132 and the second intermediate support member 134, the load generated on the output shaft 140 is efficiently supported, and various sizes can be obtained by appropriately changing the size of the support member. A radial bearing or a thrust bearing with a large capacity can be used, and a bearing can be selected according to the counterpart machine.

  Moreover, although demonstrated as a structure provided with two radial bearings, one may be sufficient and three or more may be arrange | positioned and comprised.

If it is desired to remove and replace only the thrust bearing from the output shaft cover, a reduction gear as shown in FIG. 4 may be configured as a reference example.

  In the description of FIG. 4, the same or similar parts as those of the speed reducer 120 described above are given the same reference numerals in the last two digits, and redundant description is omitted in the configuration and operation.

In the speed reducer 220, the output shaft 240 is rotatably supported by the casing 270 via a first radial bearing 226. The output shaft 240 is rotatably supported by the casing 270 via a second radial bearing 230 at a portion different from the first radial bearing 226 in the axial direction. That is, the first radial bearing 226 is disposed on the flange portion (carrier 224) side of the output shaft 240, and the second radial bearing 230 is disposed on the output shaft cover 274 side of the output shaft 240. A first intermediate support member 232 is provided between the first radial bearing 226 and the casing 270. The first intermediate support member 232 and the casing 270 are fixed by welding. A second intermediate support member 234 is provided between the second radial bearing 230 and the casing 270. The second intermediate support member 234 and the casing 270 are fixed by welding .

  On the other hand, a thrust bearing 228 is disposed between the second radial bearing 230 and the output shaft cover 274. The thrust bearing 228 is in contact with the second intermediate support member 234 and the output shaft cover 274, and its axial position is restricted. In addition, each member of the reference numerals 250, 252, and 254 includes a first radial bearing 226, a thrust bearing 228, and a second radial bearing 230 between the carrier (the flange portion of the output shaft 240) 224 and the output shaft cover 274. The reference numeral 250 is a first position restricting member, the reference numeral 252 is a second position restricting member, and the reference numeral 254 is a third position restricting member. That is, when a thrust load S1 is applied from the counterpart machine side to the motor side, the thrust load S1 is transmitted from the thrust bearing 228 to the casing 270 via the second intermediate support member 234, and the thrust load S1 is supported. ing. When a thrust load S2 is applied in the opposite direction to the output shaft 240, the thrust load S2 is transmitted to the output shaft cover 274 and the bolt 272 via the thrust bearing 228 and further supported by the casing 270. It is supposed to be configured.

  In the present embodiment, the thrust bearing 228 is disposed adjacent to the output shaft cover 274. With this configuration, the assembly workability is further improved. Further, even when the thrust bearing 228 is worn due to repeated large thrust loads, it is possible to easily replace only the thrust bearing by simply removing the output shaft cover 274.

  The present invention can be widely applied to a speed reducer such as a speed reducer of an inward swing meshing mechanism and a speed reducer of a simple planetary gear mechanism.

The figure which shows the specific usage example of the reduction gear which concerns on this invention Sectional drawing of the output shaft vicinity used as the principal part of invention of the reduction gear concerning this invention Enlarged view of the substantially central portion in FIG. Sectional view around the output shaft of the reducer shown as a reference example Cross-sectional view of a reduction gear considering the conventional thrust load

Explanation of symbols

GM100 ... Geared motor 110 ... Motor 120 ... Reducer 122 ... Carrier pin 123 ... Roller 124 ... Carrier 126 ... First radial bearing 128 ... Thrust bearing 130 ... Second radial bearing 132 ... First intermediate support member 134 ... Second intermediate Support member 136 ... Bolt 140 ... Output shaft 141 ... Bolt hole 170 ... Casing 171 ... Rib 172 ... Bolt 180 ... Oil seal 190 ... Counter machine

Claims (2)

In the decelerator that decelerates the power input from the input shaft and transmits the decelerated power to the output shaft.
The output shaft is provided with a flange portion, and an output shaft cover through which the output shaft passes is fixed to a casing of the speed reducer, and
A radial bearing that supports the radial load of the output shaft and a thrust bearing that supports the thrust load of the output shaft are disposed between the flange portion and the output shaft cover in the axial direction of the output shaft,
The radial bearing is composed of a first radial bearing located on the flange portion side and a second radial bearing located on the output shaft cover side,
The thrust bearing is disposed between the first radial bearing and the second radial bearing; and
The speed reducer, wherein the thrust bearing and the second radial bearing are arranged to be attachable or detachable from a load side of the casing in a state where the output shaft cover is detached from the casing. Oite to claim 1,
An intermediate support member that receives at least one of a radial load from the radial bearing and a thrust load from the thrust bearing is disposed between the radial bearing or the thrust bearing and the casing. And reducer.

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