WO2018168765A1

WO2018168765A1 - Speed reduction device

Info

Publication number: WO2018168765A1
Application number: PCT/JP2018/009494
Authority: WO
Inventors: 卓小浜田
Original assignee: 株式会社ニッセイ
Priority date: 2017-03-17
Filing date: 2018-03-12
Publication date: 2018-09-20
Also published as: JP6756649B2; CN110268180B; CN110268180A; JP2018155345A

Abstract

[Problem] To provide a speed reduction device with which the entire speed reducer can be prevented from falling out of a securing section. [Solution] A speed reduction device equipped with: a casing main member 28 having cylindrical internal tooth sections 60A, 60B, and a casing guide member 30; planetary gears 22A, 22B having external tooth sections 38A, 38B for meshing with the internal tooth sections 60A, 60B of the casing main member 28; a first carrier member 24 and a second carrier member 26 for supporting the planetary gears 22A, 22B and rotatably supporting the casing main member 28 and the casing guide member 30; a securing section 2 to which the first carrier member 24 is secured; and bolts 84 arranged on the securing section 2. A groove 80 is formed in the first carrier member 24, and the bolts 84 extend to the interior of the groove 80.

Description

Reduction gear

The present invention relates to a casing rotation type speed reducer.

As a casing rotation type speed reducer, one described in JP 2010-216551 A (Patent Document 1) is known.
In this speed reducer, the tool magazine 3 is connected to the rotary casing 317 of the speed reducer 310, and the speed reducer 310 (first support block 314) is fixed to the fixing portion 308 with a thick bolt 328. The thick bolt 328 is disposed only on the lower side in order to avoid the pinion 304 and the like. The pinion 304 meshes with a bevel gear 307 fixed by a small bolt 305 with respect to the input shaft 311 of the speed reducer 310.
The first support block 314 and the second support block 315 that support the external gear 312 of the speed reducer 310 and rotatably support the rotary casing 317 include an inner pin 323 and an inner pin 323 formed integrally with the first support block 314. They are connected by thin bolts 316.
A disc 319 is fixed to the rotary casing 317 so as to overlap the end surface of the first support block 314 in the rotational axis direction of the speed reducer 310 (rotary casing 317). When the thin bolt 316 is broken, the disc 319 is placed on the end surface of the first support block 314 so that the rotary casing 317 or the tool magazine 3 is prevented from falling off.

JP 2010-216551 A

However, in the above-described reduction gear, when the thick bolt 328 is damaged due to an accident such as a strong impact applied to the rotating casing 317, the first support block 314 is dropped together with the rotating casing 317 from the fixed portion 308. Such drop-off cannot be prevented even if the disc 319 integrated with the rotary casing 317 hits the first support block 314, and the entire speed reducer 310 eventually falls.
Further, there is a possibility that the bevel gear 307 may be hooked on the fixed portion 308 when dropping. However, since the total weight of the tool magazine 3 and the speed reducer 310 reaches the small bolt 305, there is a high possibility that the small bolt 305 will also be damaged and the entire speed reducer 310 will eventually fall.
A main object of the present invention is to provide a speed reducer that can prevent the entire speed reducer from falling from a fixed portion.

To achieve the above object, the invention according to claim 1 supports a casing having a cylindrical inner surface, an inscribed member having an outer surface inscribed in the inner surface of the casing, and the inscribed member. A carrier member that rotatably supports the casing; a fixing portion to which the carrier member is fixed; and a retaining member disposed on one of the fixing portion or the carrier member. A recess is formed on the other of the carrier members, and the retaining member reaches the inside of the recess.
According to a second aspect of the present invention, in the above invention, the carrier member is fixed to the fixing portion by a fastening member, and the retaining member is opposite to the fastening member with respect to the rotation center axis of the casing. It is arrange | positioned at the side.
According to a third aspect of the present invention, in the above invention, a plurality of the retaining members are provided and arranged in the circumferential direction.
According to a fourth aspect of the present invention, in the above invention, the concave portion is a circumferential groove.
According to a fifth aspect of the present invention, in the above invention, the retaining member is a bolt, and a bolt hole into which the bolt is inserted is provided in the one of the fixing portion or the carrier member. To do.
The invention described in claim 6 is characterized in that, in the above invention, a gap is provided between the retaining member and the recess.

The main effect of the present invention is to provide a speed reducer that can prevent the entire speed reducer from falling from the fixed portion.

It is a longitudinal cross-sectional view of the speed reducer which concerns on this invention. FIG. 2 is a sectional view taken along line AA in FIG. 1.

Hereinafter, embodiments according to the present invention and modifications thereof will be described based on the drawings as appropriate. Note that the present invention is not limited to the following embodiments and modifications.

FIG. 1 is a longitudinal sectional view of a reduction gear 1 according to the present invention, and FIG. 2 is a sectional view taken along line AA in FIG.
The speed reduction device 1 includes a fixed portion 2 and a speed reducer 4 fixed to the fixed portion 2.

The fixed portion 2 includes a fixed portion case 10 as an outer shell. A motor as a drive source (not shown) is attached above the fixed portion 2, and a motor shaft as an output shaft of the motor is connected to a joint shaft 12 disposed in the fixed portion case 10. The joint shaft 12 is supported via

bearings

14 and 14 so as to be rotatable around its own axis.
A pinion 16 is formed at the tip of the joint shaft 12 by direct cutting.

The reduction gear 4 includes a crankshaft 20 as an input shaft, two

planetary gears

22A and 22B as inscribed members, a first carrier member 24 and a second carrier member 26 as carrier members, and a rotating casing. A casing main member 28 and a casing guide member 30 are provided as (output unit).

The first carrier member 24 and the second carrier member 26 are cylindrical block-shaped members each having a central hole of the same size, and are connected in a state where the central holes are continuous with a space therebetween. The crankshaft 20 is passed through these central holes in a state where the central axis thereof coincides with the central axis of the central hole. The coincident center axis (center axis C in FIG. 1) intersects with the center axis of the joint shaft 12 of the fixed portion 2 in a state where the angle on the speed reducer 4 side is an obtuse angle.
A bevel gear 32 is fixed to an end portion of the crankshaft 20 on the fixed portion 2 side. The bevel gear 32 meshes with the pinion 16 of the joint shaft 12.
Two disc-shaped eccentric portions 34 A and 34 B that are eccentric with respect to the central axis C are formed in the central portion of the crankshaft 20. The central axis of the eccentric part 34A on the fixed part 2 side is disposed at a position of 180 ° with respect to the central axis C with respect to the central axis of the eccentric part 34B on the opposite side.
The crankshaft 20 is rotatably supported by

bearings

36A and 36B. The bearing 36 A on the fixed portion 2 side is fixed in the central hole of the first carrier member 24, and the bearing 36 B on the opposite side is fixed in the central hole of the second carrier member 26.

The

planetary gears

22A and 22B are disk-shaped members having

outer teeth

38A and 38B and a central hole, respectively.
An eccentric part 34A of the crankshaft 20 is located in the central hole of the planetary gear 22A, and the planetary gear 40A is interposed between the eccentric part 34A and the central hole of the planetary gear 22A. 22A is supported so as to be rotatable around the eccentric portion 34A. The planetary gear 22 A can revolve by the eccentric rotation of the eccentric portion 34 A caused by the rotation around the central axis C of the crankshaft 20.
Similarly, the eccentric portion 34B of the crankshaft 20 is located in the central hole of the planetary gear 22B, and the needle bearing 40B is interposed between the eccentric portion 34B and the central hole of the planetary gear 22B. The planetary gear 22B is supported so as to be able to rotate around the eccentric portion 34B. The planetary gear 22B can revolve due to the eccentric rotation of the eccentric portion 34B.
Six pin holes 42A are arranged at equal intervals in the circumferential direction at a portion between the outer tooth portion 38A and the central hole in the planetary gear 22A. Each pin hole 42A has a central axis parallel to the central axis C.
Similarly, six pin holes 42B are arranged at equal intervals in the circumferential direction at a portion between the outer tooth portion 38B and the central hole in the planetary gear 22B. Each pin hole 42B has a central axis parallel to the central axis C.

Six pin holes 44 are arranged at equal intervals in the circumferential direction at a portion between the outer curved surface and the central hole in the first carrier member 24. Each pin hole 44 has a central axis parallel to the central axis C.
Similarly, six pin holes 46 are arranged at equal intervals in the circumferential direction at a portion between the outer curved surface and the central hole in the second carrier member 26. Each pin hole 46 has a central axis parallel to the central axis C.
Then, a total of six cylindrical carrier pins 48 are passed through the

pin holes

44 and 46 in a state where the corresponding pin holes 46 and the corresponding pin holes 46 are matched, whereby the first carrier member 24 and the second carrier The member 26 is connected with an interval. The inner diameters of the

pin holes

44 and 46 coincide with the outer diameter of the carrier pin 48.
Planetary gears 22 A and 22 B are disposed between the first carrier member 24 and the second carrier member 26.
The corresponding carrier pins 48 pass through the pin holes 42A and 42B of the

planetary gears

22A and 22B. A cylindrical metal 49 is disposed on the outer side in the radial direction of each carrier pin 48 and in each

pin hole

42A, 42B. The inner diameters of the pin holes 42 A and 42 B are larger than the outer diameter of the metal 49. Therefore, the metal 49 and the carrier pin 48 are restricted so as to remain in a predetermined manner with respect to the movement of the

planetary gears

22A and 22B and the relative rotation with respect to the

eccentric portions

34A and 34B while allowing the

planetary gears

22A and 22B to revolve. ing.
Bolt holes 50 are opened in parallel to the central axis C on the surface of the fixed part 2 side in the lower part of the first carrier member 24 (the part opposite to the joint shaft 12 with respect to the central axis C). On the other hand, a bolt hole 52 is formed in the lower portion of the fixed portion case 10. Then, the first carrier member 24 and thus the speed reducer 4 are fixed to the fixing portion 2 by the bolt 54 (fastening member) common to the bolt hole 52 or the bolt hole 50.

The casing main member 28 is a cylindrical member having a central hole. The central axis of the casing main member 28 or its central hole coincides with the central axis

C. Inner teeth

60A and 60B that mesh with the

outer teeth

38A and 38B of the

planetary gears

22A and 22B are formed on the inner surface of the center hole on the fixed portion 2 side. The inner diameter of the central hole is larger than the outer diameter of the

planetary gears

22A and 22B, and the number of inner teeth of the casing main member 28 is larger than the number of outer teeth of the

planetary gears

22A and 22B. On the other hand, a second carrier member 26 is disposed on the inner side of the central hole on the side opposite to the fixed portion 2.
A cover 62 that covers the central hole of the casing main member 28 is attached to the surface of the casing main member 28 opposite to the fixed portion 2 by a plurality of bolts 64.
A plurality of connecting portions 66 for connecting a tool magazine or the like (not shown) are provided on the outer surface portion of the casing main member 28.

The casing guide member 30 is a cylindrical member having a central hole, and the central axis and the central axis of the central hole coincide with the central axis C.
A cross roller 70 is interposed between the casing guide member 30 and the first carrier member 24, and the first carrier member 24 rotatably supports the casing guide member 30. The first carrier member 24 (inner ring), the cross roller 70, and the casing guide member 30 (outer ring) can be regarded as a cross roller bearing.
A plurality of bolt holes 72 parallel to the central axis C are arranged at equal intervals in the circumferential direction on the peripheral edge of the casing guide member 30. On the other hand, a bolt hole 74 parallel to the central axis C is opened on the surface of the casing main member 28 on the fixed portion 2 side so as to correspond to the bolt hole 72. Bolts 76 are inserted into the respective pairs of bolt holes 72 to 74, and the casing guide member 30 is connected to the casing main member 28.

A groove on the outer curved surface of the first carrier member 24 that is closer to the fixed portion 2 than the casing guide member 30 and is recessed inward in the radial direction from the other outer curved surface portion. 80 (concave portion) is formed. The groove 80 goes around the outer curved surface of the first carrier member 24. A gap exists between the fixed case 10 and the casing guide member 30.
A plurality of bolt holes 82 orthogonal to the central axis C are arranged at equal intervals in the circumferential direction on the radially outer portion of the groove 80 in the fixed portion case 10. The bolt holes 82 are provided on the top and bottom (FIGS. 1 and 2) and on the left and right (FIG. 2).
Each bolt hole 82 is provided with a bolt 84 as a retaining member. Each bolt 84 is inserted so that the head portion protrudes from the inner surface of the fixed portion case 10 at the radially outer side and the distal end portion at the radially inner side. The width of the tip of each bolt 84 (the dimension in the direction of the central axis C) is made smaller than the width of the groove 80. The tip of each bolt 84 reaches the inside of the groove 80. A gap exists between the tip of each bolt 84 and the groove 80.

Next, an operation example of such a reduction gear 1 will be described.
When the joint shaft 12 is rotated by driving the motor, the crankshaft 20 is rotated around the central axis C via the bevel gear 32, and the

eccentric portions

34A and 34B are eccentrically rotated.
Then, the

planetary gears

22A and 22B move in the

inner teeth

60A and 60B of the casing main member 28 while the movement range is regulated by the carrier pins 48 between the first carrier member 24 and the second carrier member 26. Run relatively.
The casing main member 28 is decelerated and rotated around the central axis C at a reduction ratio corresponding to the difference between the number of external teeth and the number of internal teeth of the

planetary gears

22A and 22B. The rotation of the casing main member 28 is guided by a casing guide member 30 connected thereto.
By rotation of the casing main member 28, a tool magazine or the like connected to the casing main member 28 is rotated.

When the bolt 54 that fixes the speed reducer 4 to the fixed portion 2 is broken due to an accident such as a collision with the tool magazine, the speed reducer 4 or the tool magazine is prevented from dropping as follows.
That is, when the speed reducer 4 tries to move away from the fixing portion 2, the front end portion of each bolt 84 comes into contact with the groove 80 (mainly the surface on the fixing portion 2 side) of the first carrier member 24, and each bolt 84 is in the first The carrier member 24 and thus the speed reducer 4 is supported.

Then, the effect of the reduction gear 1 is demonstrated.
The reduction gear 1 is a planetary gear having casing main members 28 and casing guide members 30 having cylindrical

inner teeth

60A and 60B and

outer teeth

38A and 38B meshing with the

inner teeth

60A and 60B of the casing main member 28. The first carrier member 24 and the first carrier member 24 and the second carrier member 26 that support the casing main member 28 and the casing guide member 30 so as to be rotatable while supporting the planet gears 22A and 22B and the

planetary gears

22A and 22B are fixed. A fixing portion 2 and a bolt 84 disposed in the fixing portion 2, and a groove 80 is formed in the first carrier member 24, and the bolt 84 reaches the inside of the groove 80. . Therefore, even if a fall of the reduction gear 4 as a whole from the fixed portion 2 occurs due to an accident, the bolt 84 is caught in the groove 80, so that such a fall can be prevented.
The first carrier member 24 is fixed to the fixed portion 2 by a bolt 54, and the upper bolt 84 is disposed on the opposite side of the bolt 54 with respect to the rotation center axis C of the casing main member 28. Therefore, the movement at the time of the fall start of the reduction gear 4 centering on the volt | bolt 54 (damage part) is suppressed effectively.
Further, a plurality of bolts 84 are provided and are arranged in the circumferential direction. Therefore, the reduction gear 4 is supported by each bolt 84 from various directions when the bolt 54 is broken, and the reduction gear 4 is more reliably prevented from dropping.

In addition, the recess into which the tip of each bolt 84 is inserted is a circumferential groove 80. Therefore, the groove 80 can be formed with a lathe at low cost, and the addition of the bolt 84 can be easily performed by omitting the new formation of the recess by using the groove 80.
Moreover, the retaining members of the speed reducer 4 are the respective bolts 84, and the bolt holes 82 for inserting the respective bolts 84 are provided in the fixing portion 2. Therefore, the retaining member can be easily attached and detached, and the retaining member can be easily manufactured and maintained.
Further, a gap is provided between each bolt 84 and the groove 80. Therefore, the impact with respect to the 1st carrier member 24 is not transmitted directly to each volt | bolt 84, the situation where the volt | bolt 84 is damaged previously is prevented, and the reduction gear 4 is prevented from coming off more reliably.

Finally, a modified example of the reduction gear 1 will be described.
The number of bolts 84 as a retaining member may be three or less (including one), or may be five or more. Further, the plurality of bolts 84 may be arranged at unequal intervals in the circumferential direction, or may not be arranged on the same virtual circle. The retaining member may be a pin that is press-fitted into the pin hole, or may be a protrusion formed on the inner surface of the fixed portion case 10.
Instead of the circumferential groove 80, the recess may be a hole or the like that is opened at each opposed portion of the tip of the bolt 84.
A part or all of the bolts 84 may be arranged so as to contact the groove 80 without a gap.
The bolt 84 may be fixed to the first carrier member 24, and the groove 80 in which the bolt 84 enters may be formed in the fixed portion case 10.
The first carrier member 24 may be disposed outside the fixed part case 10.

The number of the

planetary gears

22A and 22B, the number of the

eccentric portions

34A and 34B, or the eccentric angle may be increased or decreased.
The number and type of various bearings can be changed in various ways, such as increasing or decreasing the number of bearings 14 or using

needle bearings

40A and 40B as ball bearings.
The casing main member 28 and its

internal teeth

60A and 60B are separated from each other, the casing main member 28 and the casing guide member 30 are integrally formed, the cover 62 and its bolt 64 are omitted, the shaft The configuration of various members may be variously changed such that 12 is not used and a pinion is formed on the motor shaft.
The configuration of the speed reducer 4 is not limited to the above. For example, a reduction gear of a casing rotation type having a sun gear, a plurality of planetary gears (inscribed members) meshing with the sun gear, an internal gear meshing with the sun gears, and a connecting member that rotatably holds the planetary gears. May be.

1 ... Reduction gear, 2 ... Fixing part, 4 ... Reduction gear, 22A, 22B ... Planetary gear (inscribed member), 24 ... First carrier member (part of carrier member), 26 ... 2 Carrier member (a part of carrier member), 28 ..Case main member (a part of casing), 30 ..Case guide member (a part of casing), 38 A, 38 B. Outer surface), 54... Bolt (fastening member), 60 A, 60 B... Internal toothed portion (inner surface of casing), 80.

Claims

A casing having a cylindrical inner surface;
An inscribed member having an outer surface inscribed in the inner surface of the casing;
A carrier member that supports the inscribed member and rotatably supports the casing;
A fixing portion to which the carrier member is fixed;
A retaining member disposed on one of the fixed part or the carrier member;
With
A recess is formed in the other of the fixed part or the carrier member,
The speed reducing device, wherein the retaining member reaches the inside of the recess.
The carrier member is fixed to the fixing portion by a fastening member,
The speed reducer according to claim 1, wherein the retaining member is disposed on the opposite side of the fastening member with respect to a rotation center axis of the casing.
The speed reducer according to claim 1 or 2, wherein a plurality of the retaining members are provided and arranged in the circumferential direction.
The reduction gear according to any one of claims 1 to 3, wherein the recess is a circumferential groove.
The retaining member is a bolt,
The speed reducer according to any one of claims 1 to 4, wherein a bolt hole into which the bolt is inserted is provided in the one of the fixing portion or the carrier member.
The speed reducer according to any one of claims 1 to 5, wherein a gap is provided between the retaining member and the recess.