JP2017106586A - Speed reduction device and conveying device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a speed reduction device that can be easily detached.SOLUTION: A speed reduction device comprises two speed reduction mechanisms including a front speed reduction mechanism and a rear speed reduction mechanism. The rear speed reduction mechanism comprises a rear output shaft 122. The rear output shaft 122 comprises: a hollow part 142 in which a driving shaft 124 of a mating machine is inserted; a pressure medium chamber 144 provided radially outside the hollow part 142, and in which a pressure medium is housed; and pressure adjustment means 164 that adjusts the pressure of the pressure medium housed in the pressure medium chamber 144.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a speed reducer and a transport device.

  The gear motor is used for a roller drive of a belt conveyor and a suspension of a large movable device such as a crane, and its application range is wide. A gear motor generally includes a motor and a reduction gear, and is used with a drive shaft of a counterpart machine attached to an output shaft of the reduction gear.

  In the reduction gear described in Patent Document 1, the drive shaft of the counterpart machine is inserted into the hollow portion of the output shaft and is key-connected.

JP 2013-155813 A

  As described above, when the output shaft of the speed reducer and the drive shaft of the counterpart machine are key-connected, fretting occurs between the output shaft of the speed reducer and the drive axis of the counterpart machine when used for a long time. It may take time to remove the device.

  The present invention has been made in view of such circumstances, and an object thereof is to provide a speed reducer that can be easily removed.

  In order to solve the above-described problem, a reduction gear according to an aspect of the present invention is a reduction gear including an output shaft, the output shaft including a hollow portion into which a drive shaft of a counterpart machine is inserted, and a radial direction of the hollow portion A pressure medium chamber provided outside and containing a pressure medium; and pressure adjusting means for adjusting a pressure of the pressure medium accommodated in the pressure medium chamber.

  Another aspect of the present invention is a transport device. This device is a transport device that includes a plurality of drive shafts, a gear motor connected to each drive shaft, and a connecting member that connects the drive shaft and the output shaft of the gear motor. A hollow portion to be inserted, a pressure medium chamber that is provided radially outside the hollow portion and accommodates a pressure medium, and a pressure adjusting unit that adjusts the pressure of the pressure medium accommodated in the pressure medium chamber.

  Note that any combination of the above-described constituent elements, and those obtained by replacing the constituent elements and expressions of the present invention with each other among methods, apparatuses, systems, etc. are also effective as an aspect of the present invention.

  According to the present invention, it is possible to provide a speed reducer that can be easily detached.

It is sectional drawing of the gear motor which concerns on 1st Embodiment. FIG. 2 is an enlarged cross-sectional view showing an enlarged periphery of an end portion of a rear output shaft of FIG. It is a perspective view which shows the conveying apparatus which concerns on 2nd Embodiment. FIG. 4 is a plan view showing one of a plurality of gear motors in FIG. 3 and its periphery. It is an expanded sectional view which expands and shows the edge part periphery of the side far from the other party machine of the rear stage output shaft of the rear stage deceleration mechanism of the reduction device of the gear motor which concerns on a modification.

  Hereinafter, the same or equivalent components and members shown in the respective drawings are denoted by the same reference numerals, and repeated descriptions thereof are omitted as appropriate. In addition, the dimensions of the members in each drawing are appropriately enlarged or reduced for easy understanding. Also, in the drawings, some of the members that are not important for describing the embodiment are omitted.

(First embodiment)
First, the process of reaching the speed reduction device according to the present embodiment will be described.
One of the methods for connecting the drive shaft of the counterpart machine and the output shaft of the speed reducer is key connection. The key connection has a problem that fretting easily occurs between the drive shaft and the output shaft or between these and the key. Fretting is a phenomenon in which minute relative slip is repeatedly generated between two members due to vibration or the like, resulting in surface damage. As fretting progresses, the drive shaft of the counterpart machine and the output shaft of the speed reducer may stick together, and it may take much time to remove the speed reducer from the counterpart machine.

  Another method for connecting the drive shaft of the counterpart machine and the output shaft of the speed reducer is mechanical friction fastening using bolts. This mechanical frictional engagement can prevent or prevent the occurrence of slippage between the drive shaft and the output shaft, and can suppress the occurrence of fretting. However, the conventional mechanical frictional engagement requires a relatively large number of bolts, and therefore it takes time to mount the speed reducer on the counterpart machine and to remove the speed reducer from the counterpart machine.

  Based on the above knowledge, the present inventor has obtained the reduction gear according to the present embodiment. This will be specifically described below.

  FIG. 1 is a cross-sectional view of a gear motor 10 including a reduction gear 14 according to an embodiment. The gear motor 10 includes a motor 12 and a speed reducer 14.

  The motor 12 is an electric motor. A tip 26a of the motor shaft 26 that is an output shaft of the motor 12 on the side of the speed reduction device 14 extends to the inside of the speed reduction device 14, and serves as a front stage input shaft 32 that is an input shaft of a front stage speed reduction mechanism (described later) of the speed reduction device 14. Also works.

  The reduction gear 14 is an orthogonal reduction gear, and is located between the motor 12 and a counterpart machine (not shown). The speed reducer 14 transmits the rotation of the motor 12 to the counterpart machine. At this time, the speed reducer 14 converts the rotational speed and torque provided to the speed reducer 14 by the motor 12 into the rotational speed and torque necessary for the counterpart machine, and gives the drive shaft 124 of the counterpart machine.

  The reduction gear device 14 includes a two-stage reduction mechanism including a front-stage reduction mechanism 16 and a rear-stage reduction mechanism 18, and a casing 74.

  The front stage reduction mechanism 16 is a kind of planetary gear reduction mechanism called an eccentric swing meshing type. The front stage reduction mechanism 16 includes a front stage input shaft 32, external gears 60 and 62, eccentric bodies 64 and 66, roller bearings 68 and 70, an internal gear 72, a front stage output shaft 76, and a carrier flange 78. , And an inner pin 80.

  On the outer periphery of the front input shaft 32, eccentric bodies 64 and 66 whose axis is shifted from the front input shaft 32 are fixed or fitted. The eccentric bodies 64 and 66 are eccentric with a phase difference of 180 degrees from each other. In FIG. 1, the eccentric bodies 64 and 66 are integrally formed, but may be formed separately and may be separately fixed or fitted to the front input shaft 32. Or you may comprise the eccentric bodies 64 and 66 and the front | former stage input shaft 32 integrally.

  Two external gears 60 and 62 are fitted on the outer circumferences of the eccentric bodies 64 and 66 through roller bearings 68 and 70 so as to be swingable. The external gears 60 and 62 are in mesh with the internal gear 72, respectively.

  The internal gear 72 includes a cylindrical internal tooth pin 72a that constitutes an internal tooth, a holding pin 72b that passes through the internal tooth pin 72a and rotatably holds the pin, and rotatably supports the holding pin 72b. , And an internal gear main body 72c integrated with the casing 74.

  On the opposite side of the external gears 60, 62 from the motor 12, a carrier flange 78 configured integrally with a front output shaft 76 that is an output shaft of the front speed reduction mechanism 16 is disposed. A plurality of inner pins 80 extending substantially parallel to the front-stage input shaft 32 are fitted in through holes 78 a formed along the circumferential direction of the carrier flange 78.

  In the external gear 60, a plurality of through holes having the same diameter are formed at equal intervals at positions offset from the axis. The inner pins 80 extending from the carrier flange 78 are inserted into these through holes, respectively. Corrugated teeth are formed on the outer periphery of the external gear 60, and these teeth move while contacting on the internal tooth pin 72a of the internal gear 72. The toothed gear 60 can swing. The external gear 62 is the same except that there is a phase difference of 180 degrees with respect to the external gear 60.

  The rear stage reduction mechanism 18 includes a rear stage input shaft 128, a bevel pinion 130, a rear stage output shaft 122, and a bevel gear 132.

  The rear-stage input shaft 128 and the front-stage output shaft 76 are arranged coaxially with each other and are integrated to form a connecting shaft 82 that connects the front-stage reduction mechanism 16 and the rear-stage reduction mechanism 18. The connecting shaft 82 is rotatably supported by a pair of tapered roller bearings 170 and 172 incorporated in the casing 74.

  The bevel pinion 130 is formed at the tip of the rear input shaft 128 opposite to the motor 12. The bevel gear 132 is fixed to the rear output shaft 122 by key connection. A first key recess 122 a is formed on the outer peripheral surface of the rear output shaft 122, and a corresponding second key recess 132 a is formed on the inner peripheral surface of the bevel gear 132. The first key 134 is fitted into the first key recess 122a and the second key recess 132a.

  The rear output shaft 122 is rotatably supported by a pair of tapered roller bearings 146 and 148 incorporated in the casing 74, and penetrates the casing 74. The rear output shaft 122 is substantially orthogonal to the connecting shaft 82. The rear output shaft 122 is connected to the drive shaft 124 as described later.

  A lubricant is present inside the casing 74. The lubricant lubricates the meshing portion of the gear and the bearing of the reduction gear 14. The lubricant also serves as a coolant.

  Two oil seals (seal members) 152 are arranged side by side in the gap between the casing 74 and the rear output shaft 122 on the opposite side of the tapered roller bearing 146 from the tapered roller bearing 148. Two oil seals (seal members) 154 are arranged side by side in a portion of the gap between the casing 74 and the rear output shaft 122 on the opposite side of the tapered roller bearing 148 from the tapered roller bearing 146. The oil seal 152 and the oil seal 154 prevent the lubricant from leaking from the gap between the casing 74 and the rear output shaft 122.

  FIG. 2 is an enlarged cross-sectional view showing the periphery of the end of the rear output shaft 122 far from the counterpart machine. The rear output shaft 122 includes a main body portion 140 having a cylindrical outer peripheral surface, and a hollow portion (hollow portion) 142 penetrating the main body portion 140 in the axial direction (that is, the direction in which the main body portion 140 and thus the rear output shaft 122 extends). A pressure medium chamber 144 in which oil is stored; an opening 150 communicating with the pressure medium chamber 144; and a pressure adjusting means 164 for adjusting the pressure of a pressure medium such as oil stored (filled) in the pressure medium chamber 144. And having.

  A drive shaft 124 is inserted into the hollow portion 142. The pressure medium chamber 144 is a space provided in the main body 140, that is, a space provided on the radially outer side of the hollow portion 142. In the present embodiment, the pressure medium chamber 144 is formed in a cylindrical shape surrounding the hollow portion 142 at the end of the main body 140 on the side opposite to the counterpart machine.

  The opening 150 communicates the pressure medium chamber 144 with the outside of the main body 140. In the present embodiment, the opening 150 communicates the pressure medium chamber 144 with the axial end surface of the main body 140 on the side opposite to the counterpart machine. Therefore, the opening 150 opens on the axial end surface opposite to the counterpart machine. In particular, the opening 150 is formed in a ring shape over the entire circumference of the end surface in the axial direction of the main body 140.

  The pressure adjusting means 164 includes a piston member 156, a spacer 166, a washer 168, and an advancing / retreating means 158 for advancing / retreating the piston member 156. The piston member 156 is a ring-shaped member and is made of, for example, rubber. The piston member 156 is fitted to the ring-shaped opening 150 over the entire circumference. The spacer 166 is a ring-shaped member having a substantially L-shaped cross section, and abuts against the piston member 156 over the entire circumference. The washer 168 is provided between the spacer 166 and a nut 162 (described later) so as to surround the hollow portion 142.

  The advancing / retreating means 158 includes a cylindrical extending portion 141 extending from the main body 140 to the opposite side of the counterpart machine, a female screw 160 provided on the outer periphery of the extending portion 141, and a female screw 160 surrounding the hollow portion 142. And a nut 162 to be attached (screwed). The extending portion 141 is continuous with the inner portion 140 a of the main body 140 surrounded by the pressure medium chamber 144. Therefore, the inner diameter of the extending portion 141 is substantially the same as the inner diameter of the main body portion 140, and the inner peripheral surface of the extending portion is continuous with the inner peripheral surface of the inner portion 140a. Further, the outer diameter of the extending part 141 is smaller than the outer diameter of the main body part 140.

  When the nut 162 is screwed and tightened, the nut 162 presses the piston member 156 against the counterpart machine side through the washer 168 and the spacer 166. When the piston member 156 is pressed against the nut 162 and moves to the counterpart machine side, the pressure medium in the pressure medium chamber 144 is compressed, and the pressure of the pressure medium rises. When the pressure of the pressure medium rises, the inner portion 140a of the main body 140 surrounded by the pressure medium chamber 144 receives pressure from the pressure medium and contracts radially inward. As a result, the inner peripheral surface of the inner portion 140a of the main body 140 and the outer peripheral surface of the drive shaft 124 are strongly pressed against each other, and the main body 140 and, consequently, the rear output shaft 122 and the drive shaft 124 of the counterpart machine are frictionally fastened. Further, when the pressure of the pressure medium rises, the outer portion 140b of the main body 140 surrounding the pressure medium chamber 144 receives pressure from the pressure medium and expands outward in the radial direction.

  On the other hand, when the nut 162 is loosened, the pressure of the pressure medium in the pressure medium chamber 144 decreases, and the inner part 140a of the main body part 140 contracted by the pressure of the pressure medium returns to its original state. The inner peripheral surface and the outer peripheral surface of the drive shaft 124 are not pressed against each other, and the frictional engagement between the main body 140 and the subsequent output shaft 122 and the drive shaft 124 of the counterpart machine is released.

  The pressure medium chamber 144 is formed so as to overlap only partly with the tapered roller bearing 146 or not to overlap with the tapered roller bearing 146 as shown in FIG. 2 when viewed from the radial direction. That is, the pressure medium chamber 144 is formed so as not to overlap the tapered roller bearing 146 over the entire length when viewed from the radial direction. Therefore, even if the outer portion 140b of the main body 140 is expanded by receiving pressure from the pressure medium, the tapered roller bearing 146 is hardly or not affected by the influence.

  The pressure medium chamber 144 is preferably provided so as to overlap with at least a part of the oil seal 154 when viewed from the radial direction. In other words, the oil seal 154 is arranged so that at least a part of the oil seal 154 overlaps the pressure medium chamber 144 when viewed from the radial direction. In FIG. 2, the pressure medium chamber 144 is provided so as to overlap the entire length of the oil seal 154 when viewed from the radial direction. In this case, when the outer portion 140b of the main body 140 is expanded by receiving pressure from the pressure medium, the main body 140 (that is, the rear output shaft 122) and the oil seal 154 are more closely attached.

  In addition to the opening 150, an air vent passage 145 that connects the pressure medium chamber 144 and the outside of the main body 140 is formed in the main body 140. Accordingly, when the pressure medium is filled from the opening 150, the air in the pressure medium chamber 144 is released from the air vent passage 145, so that the pressure medium can be filled so that no air remains in the pressure medium chamber 144. A closing plug 149 is attached to the opening of the air vent passage 145. As a result, the pressure medium chamber 144 and the air vent passage 145 are sealed.

  The operation of the gear motor 10 configured as described above will be described. When the motor 12 is driven, the front stage input shaft 32 of the front stage speed reduction mechanism 16 that is integral with the motor shaft 26 rotates. When the front input shaft 32 rotates, the outer circumferences of the eccentric bodies 64 and 66 perform an eccentric motion, and the external gears 60 and 62 swing through the roller bearings 68 and 70. Due to this swinging, a phenomenon occurs in which the meshing positions of the external teeth of the external gears 60 and 62 and the internal pin 72a of the internal gear 72 are sequentially shifted.

  The difference in the number of teeth between the external gears 60 and 62 and the internal gear 72 is set to “1” in the present embodiment. Further, since the internal gear 72 is integral with the casing 74, the rotation of the internal gear 72 is restricted. For this reason, every time the front stage input shaft 32 makes one rotation, the external gears 60 and 62 rotate (rotate) by an amount corresponding to the difference in the number of teeth with respect to the internal gear 72 whose rotation is restricted. This rotation is transmitted to the carrier flange 78 via the inner pin 80 inserted in the through hole of the external gears 60 and 62. As a result, due to the rotation of the front input shaft 32, the carrier flange 78 and the front output shaft 76 integral with the carrier flange 78 rotate at a rotational speed reduced to 1 / (the number of teeth of the external gear). Further, the rear input shaft 128 integrated with the front output shaft 76 rotates. When the rear stage input shaft 128 rotates, the bevel pinion 130 formed at the tip of the rear stage input shaft 128 rotates, and the bevel gear 132 engaged with the bevel pinion 130 rotates. When the bevel gear 132 rotates, the rear output shaft 122 connected to the bevel gear 132 via the first key 134 rotates, and the drive shaft 124 of the counterpart machine connected to the rear output shaft 122 is driven as described above. .

  According to the reduction gear 14 according to the present embodiment described above, the rear output shaft 122 and the drive shaft 124 of the counterpart machine are frictionally fastened. Therefore, fretting as in the case where the rear output shaft 122 and the drive shaft 124 of the counterpart machine are key-connected can be suppressed. In addition, the drive shaft 124 can be fastened to the rear output shaft 122 by tightening one nut, and similarly, the drive shaft 124 can be detached from the rear output shaft 122 by loosening one nut. That is, according to the reduction gear 14 according to the present embodiment, it can be removed from the counterpart machine relatively easily.

  Further, according to the reduction gear device 14 according to the present embodiment, the opening 150 opens at the axial end surface of the rear output shaft 122. That is, the opening 150 opens at the end surface of the main body 140 in the axial direction, which is the direction in which the speed reducer 14 (that is, the gear motor 10) is attached to or removed from the counterpart machine. Therefore, workability is improved as compared with the case where the opening 150 opens on the side surface of the main body 140. Further, the opening 150 particularly opens at the axial end surface of the rear output shaft 122 opposite to the counterpart machine (the side far from the counterpart machine). For this reason, the counterpart machine does not interfere with the work, and the workability is further improved.

  Further, according to the reduction gear device 14 according to the present embodiment, the pressure medium chamber 144 does not overlap with the tapered roller bearing 146 only partially when viewed from the radial direction. Formed. Thereby, even if the pressure portion of the pressure medium in the pressure medium chamber 144 rises and the outer portion 140b of the main body 140 of the rear output shaft 122 surrounding the pressure medium chamber 144 expands radially outward, the tapered roller bearing 146 is not affected by the expansion of the outer portion 140 b of the main body 140. Therefore, according to the speed reducer 14 according to the present embodiment, the tapered roller bearing 146 is prevented from failing due to the outer portion 140b of the main body 140 receiving pressure from the pressure medium and expanding radially outward. it can.

  Further, according to the reduction gear device 14 according to the present embodiment, the pressure medium chamber 144 is provided so as to overlap at least a part of the oil seal 154 when viewed from the radial direction. In other words, the oil seal 154 is arranged so that at least a part of the oil seal 154 overlaps the pressure medium chamber 144 when viewed from the radial direction. As a result, when the pressure of the pressure medium in the pressure medium chamber 144 rises and the outer portion 140b of the main body 140 of the rear output shaft 122 surrounding the pressure medium chamber 144 expands radially outward, the outer side of the main body 140 The part 140b and the oil seal 154 are more closely attached, and the sealing performance by the oil seal 154 is improved.

(Second Embodiment)
FIG. 3 is a perspective view showing the transport apparatus 2 according to the second embodiment. FIG. 4 is a plan view showing one of the plurality of gear motors 10 of FIG. 3 and its periphery. In FIG. 4, the gear motor 10 is shown in cross section.

  The conveying device 2 includes a conveyor belt 110, a driving roller 116, a first frame 118, a second frame 119, one or more driven rollers (not shown), and a plurality of gear motors 10.

  The driving roller 116 and the driven roller are arranged substantially side by side in the horizontal direction. The conveyor belt 110 is wound around these rollers. One end of each shaft of the driving roller 116 and the driven roller (the shaft of the driven roller is not shown) is rotatably attached to the first frame 118 via a bearing (not shown), and the other end is attached to the second frame 119. It is rotatably attached to a bearing via a bearing (not shown). The first frame 118 and the second frame 119 are fixed to the floor of the building where the transport device 2 is arranged. The gear motor 10 is fixed to the first frame 118 by a fixing means (torque arm) (not shown).

  The drive shaft 124, which is the shaft of the drive roller 116, has an exposed portion that passes through the first frame 118 and is therefore exposed on the opposite side of the first frame 118 from the drive roller 116. The exposed portion of the drive shaft 124 is connected to the rear output shaft 122 of the rear speed reduction mechanism 18 of the speed reducer 14 of the gear motor 10 as in the first embodiment.

  According to the transport device 2 to which the gear motor 10 according to the present embodiment is applied, the gear motor 10 can be attached to the transport device 2 relatively easily, and the gear motor 10 can be detached from the transport device 2 relatively easily. Thereby, for example, when the gear motor 10 breaks down, it can be replaced with a new gear motor 10 in a relatively short time, and the stop time of the transport device 2 can be suppressed to a short time. The greater the number of gear motors 10 included in the transport device 2, the greater the effect.

  The configuration and operation of the gear motor 10 including the speed reduction device 14 according to the embodiment and the conveyance device 2 including the gear motor 10 have been described above. It is to be understood by those skilled in the art that these embodiments are exemplifications, and that various modifications can be made to combinations of the respective components, and such modifications are within the scope of the present invention.

(Modification 1)
FIG. 5 is an enlarged cross-sectional view showing the periphery of the end portion of the rear output shaft 122 of the rear stage reduction mechanism of the gear motor reduction device according to the modification of the first embodiment on the side farther from the counterpart machine. FIG. 5 corresponds to FIG. The opening 250 communicates the pressure medium chamber 144 and the outside of the main body 140. In this modification, the opening 250 communicates the pressure medium chamber 144 with the axial end surface of the main body 140 on the side opposite to the counterpart machine. Therefore, the opening part 250 opens in the axial direction end surface on the opposite side to the counterpart machine. In particular, the opening 250 is formed in a cylindrical shape.

  The pressure adjusting means 264 includes a piston member 256 and an advancing / retreating means 258 for moving the piston member 256 back and forth. The piston member 256 is a columnar member and fits into the opening 250. An O-ring 270 is fitted on the outer periphery of the piston member 256.

  The advance / retreat means 258 includes a screw hole 260 communicating with the opening 250 and a bolt 262 attached (screwed) to the screw hole 260. The bolt 262 is configured integrally with the piston member 256. The bolt 262 may be configured separately from the piston member 256.

  When the bolt 262 is screwed and tightened, the piston member 256 formed integrally with the bolt 262 moves to the counterpart machine side. When the piston member 256 moves to the counterpart machine side, the pressure medium in the pressure medium chamber 144 is compressed, and the pressure of the pressure medium increases. When the pressure of the pressure medium rises, the inner portion 140a of the main body 140 surrounded by the pressure medium chamber 144 receives pressure from the pressure medium and contracts radially inward. As a result, the inner peripheral surface of the inner portion 140a of the main body 140 and the outer peripheral surface of the drive shaft 124 are strongly pressed against each other, and the main body 140 and, consequently, the rear output shaft 122 and the drive shaft of the counterpart machine are frictionally fastened.

  On the other hand, when the bolt 262 is loosened, the pressure of the pressure medium in the pressure medium chamber 144 decreases, and the inner part 140a of the main body part 140 contracted by the pressure of the pressure medium returns to its original state. The inner peripheral surface and the outer peripheral surface of the drive shaft 124 are not pressed against each other, and the frictional engagement between the main body 140 and the subsequent output shaft 122 and the drive shaft 124 of the counterpart machine is released.

  According to the speed reduction mechanism according to this modification, it is possible to achieve the same effects as the effects achieved by the speed reduction device 14 according to the embodiment.

(Modification 2)
In the first and second embodiments, the case where the pressure adjusting means includes the piston member and the advancing / retreating means for advancing / retreating the piston member has been described in the embodiment, but the present invention is not limited thereto. The pressure adjusting means may be a pump that supplies the pressure medium to the pressure medium chamber 144. In this case, the pressure of the pressure medium in the pressure medium chamber 144 can be increased by sending the pressure medium from the pump to the pressure medium chamber 144.

(Modification 3)
In the first and second embodiments, the case where the speed reduction device 14 is an orthogonal speed reduction device has been described. However, the type of the speed reduction mechanism is not particularly limited. For example, the speed reduction device 14 may be a parallel axis speed reduction device.

(Modification 4)
In the second embodiment, when the rear output shaft 122 of the gear motor 10 includes a hollow portion 142, a pressure medium chamber 144, and a pressure adjusting means 164 (hereinafter collectively referred to as a “connecting member”), that is, Although the case where the connecting member that connects the rear output shaft 122 and the drive shaft 124 of the drive roller 116 is configured integrally with the rear output shaft 122 of the gear motor 10 has been described, the present invention is not limited thereto. For example, the connecting member may be configured integrally with a joint that is separate from the rear output shaft 122 and the drive shaft 124. For example, the connecting member may be configured integrally with the drive shaft 124 of the counterpart machine. In this case, the drive shaft 124 has a hollow structure, the rear output shaft 122 has a solid (solid) structure, and the rear output shaft 122 is inserted into the hollow portion of the drive shaft 124 and frictionally fastened.

  Any combination of the above-described embodiments and modifications is also useful as an embodiment of the present invention. The new embodiment generated by the combination has the effects of the combined embodiment and the modified examples.

  DESCRIPTION OF SYMBOLS 10 Gear motor, 14 Deceleration apparatus, 16 Front stage deceleration mechanism, 18 Rear stage deceleration mechanism, 122 Rear stage output shaft, 142 Hollow part, 144 Pressure medium chamber, 164 Pressure adjustment means.

Claims (10)

A reduction gear comprising an output shaft,
The output shaft includes a hollow portion into which a drive shaft of a counterpart machine is inserted, a pressure medium chamber that is provided on a radially outer side of the hollow portion and that stores a pressure medium, and a pressure medium that is stored in the pressure medium chamber And a pressure adjusting means for adjusting the pressure of the speed reducer.   The speed reducing device according to claim 1, wherein the pressure adjusting unit includes a piston member that fits into an opening communicating with the pressure medium chamber, and an advancing / retreating unit that advances and retracts the piston member.   The speed reducer according to claim 2, wherein the opening portion opens to an axial end surface of the output shaft.   The speed reducer according to claim 2 or 3, wherein the advance / retreat means includes a female screw provided on an outer periphery of the output shaft, and a nut attached to the female screw.   The speed reducer according to any one of claims 2 to 4, wherein the opening is configured in a ring shape over the entire circumference of the axial end surface of the output shaft.   The speed reducer according to any one of claims 2 to 4, wherein the advance / retreat means includes a screw hole communicating with the opening and a bolt attached to the screw hole.   A bearing disposed between the casing and the output shaft, wherein the pressure medium chamber overlaps only with a part of the bearing or does not overlap with the bearing when viewed from a radial direction; The speed reducer according to any one of claims 1 to 6, characterized in that:   7. An oil seal disposed between a casing and the output shaft, wherein the pressure medium chamber overlaps at least a part of the oil seal when viewed from a radial direction. A reduction gear according to any one of the above. A transport device comprising a plurality of drive shafts, a gear motor connected to each drive shaft, and a connecting member that connects the drive shaft and the output shaft of the gear motor,
The connecting member includes a hollow portion into which the drive shaft is inserted, a pressure medium chamber that is provided radially outside the hollow portion, and stores a pressure medium, and a pressure of a pressure medium stored in the pressure medium chamber And a pressure adjusting means for adjusting the pressure.   The conveying device according to claim 9, wherein the connecting member is configured integrally with an output shaft of a gear motor.

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