CN110268180B

CN110268180B - Speed reducer

Info

Publication number: CN110268180B
Application number: CN201880010399.8A
Authority: CN
Inventors: 小浜田卓
Original assignee: Nissei Corp
Current assignee: Nissei Corp
Priority date: 2017-03-17
Filing date: 2018-03-12
Publication date: 2023-03-10
Anticipated expiration: 2038-03-12
Also published as: CN110268180A; JP6756649B2; JP2018155345A; WO2018168765A1

Abstract

The invention provides a speed reducer, which can prevent the whole speed reducer from falling from a fixed part. A reduction gear (1) is provided with: a sleeve main member (28) and a sleeve guide member (30) having cylindrical internal teeth (60A, 60B); planetary gears (22A, 22B) having external teeth (38A, 38B) that mesh with internal teeth (60A, 60B) of the sleeve main member (28); a first carrier member (24) and a second carrier member (26) that support the planetary gears (22A, 22B) and rotatably support the sleeve main member (28) and the sleeve guide member (30); a fixing portion (2) for fixing the first bearing member (24); and a bolt (84) disposed on the fixing portion (2), wherein a groove (80) is formed in the first bearing member (24), and the bolt (84) reaches the inside of the groove (80).

Description

Speed reducer

Technical Field

The invention relates to a sleeve rotating type speed reducing device.

Background

As a double-pipe rotary reduction gear, a gear described in japanese patent application laid-open No. 2010-216551 (patent document 1) is known.

In this reduction gear, the tool box 3 is coupled to the rotary sleeve 317 of the reduction gear 310, and the reduction gear 310 (first support block 314) is fixed to the fixing portion 308 by a thick bolt 328. The thick bolts 328 are disposed only on the lower side so as to avoid the pinion 304 and the like. The pinion 304 is engaged with a bevel gear 307, and the bevel gear 307 is fixed to an input shaft 311 of a reduction gear 310 by a small bolt 305.

The first support block 314 and the second support block 315, which support the external gear 312 of the reduction gear 310 and rotatably support the rotation sleeve 317, are coupled by an inner pin 323 and a thin bolt 316 integrally formed with the first support block 314.

Further, a disc 319 that overlaps with the end face of the first support block 314 in the rotation axis direction of the reduction gear 310 (rotation sleeve 317) is fixed to the rotation sleeve 317, and when the inner pin 323 or the thin bolt 316 is damaged by an accident such as collision, the disc 319 is suspended from the end face of the first support block 314, and the rotation sleeve 317 or the tool box 3 is prevented from falling off.

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open No. 2010-216551

Disclosure of Invention

Problems to be solved by the invention

However, in the above-described reduction gear device, when the thick bolt 328 is broken by an accident such as a strong impact applied to the rotation sleeve 317, the first support block 314 comes off from the fixed portion 308 together with the rotation sleeve 317. Even if the circular plate 319 integrated with the rotary sleeve 317 is hung on the first support block 314, such falling-off cannot be prevented, and as a result, the entire reduction gear 310 falls down.

In addition, when such a slip-off occurs, the bevel gear 307 may be hung from the fixing portion 308. However, since the total weight of the tool box 3 and the speed reducer 310 is applied to the small bolt 305, the small bolt 305 is also damaged, and as a result, the possibility that the entire speed reducer 310 falls is high.

A main object of the present invention is to provide a reduction gear device capable of preventing the entire reduction gear from falling from a fixed portion.

Means for solving the problems

To achieve the above object, a first aspect of the present invention includes: a sleeve having a cylindrical inner surface; an inner contact member having an outer surface that is in contact with the inner surface of the sleeve; a bearing member that supports the inner contact member and rotatably supports the sleeve; a fixing portion that fixes the carrier member; and a slip-off prevention member disposed on one of the fixing portion and the receiving member, wherein a recess is formed in the other of the fixing portion and the receiving member, and the slip-off prevention member reaches the inside of the recess.

In a second aspect of the present invention, in the above-described invention, the carrier member is fixed to the fixing portion by a fastening member, and the slip-off preventing member is disposed on a side opposite to the fastening member with respect to a rotation center axis of the socket.

In the third aspect of the present invention, in addition to the above-described invention, the slip-off preventing member is provided in plurality and arranged in a circumferential direction.

In a fourth aspect of the present invention, in the above invention, the concave portion is a circumferential groove.

In a fifth aspect of the present invention, in the above-described invention, the slip-off preventing member is a bolt, and a bolt hole into which the bolt is inserted is provided in the one of the fixing portion and the receiving member.

In the sixth aspect of the present invention, in addition to the above-described invention, a gap is provided between the slip-off preventing member and the recess.

Effects of the invention

The main effect of the present invention is to provide a reduction gear device capable of preventing the entire reduction gear from falling from a fixed portion.

Drawings

FIG. 1 is a longitudinal sectional view of the reduction gear of the invention;

fig. 2 isbase:Sub>A sectional view taken along linebase:Sub>A-base:Sub>A of fig. 1.

Detailed Description

Hereinafter, embodiments and modifications of the present invention will be described based on the drawings as appropriate. The present invention is not limited to the following embodiments and modifications.

Fig. 1 isbase:Sub>A longitudinal sectional view ofbase:Sub>A reduction gear 1 of the present invention, and fig. 2 isbase:Sub>A sectional view taken along linebase:Sub>A-base:Sub>A of fig. 1.

The reduction gear 1 includes a fixing portion 2 and a reduction gear 4 fixed thereto.

The fixing portion 2 includes a fixing portion case 10 as an outer shell thereof. A motor, not shown, as a driving source is attached above the fixed portion 2, and a motor shaft, which is an output shaft of the motor, is coupled to a coupling shaft 12 disposed in the fixed portion case 10. The coupling shaft 12 is rotatably supported around its own shaft via

bearings

14, 14.

A pinion 16 is formed by straight cutting at the tip end of the coupling shaft 12.

The speed reducer 4 includes: a crankshaft 20 as an input shaft thereof; two

planetary gears

22A, 22B as the internal connection member; a first carrier member 24 and a second carrier member 26 as carrier members; a sleeve main member 28 and a sleeve guide member 30 as a sleeve (output portion) to be rotated.

The first bearing member 24 and the second bearing member 26 are cylindrical block-shaped members each having a central hole of the same size, and the central holes are connected to each other at intervals and continuously. The crankshaft 20 passes through the center holes with its center axis aligned with the center axis of the center holes. The coincident central axis (central axis C in fig. 1) intersects with the central axis of the coupling shaft 12 of the fixing portion 2 in a state where the angle on the reducer 4 side becomes an obtuse angle.

A bevel gear 32 is fixed to an end of the crankshaft 20 on the fixed portion 2 side. Bevel gear 32 meshes with pinion 16 of coupling shaft 12.

Two disk-shaped

eccentric portions

34A and 34B are formed at the center of the crankshaft 20 so as to be eccentric with respect to the central axis C. The center axis of the eccentric portion 34A on the fixed portion 2 side is arranged at a position of 180 ° with respect to the center axis C of the eccentric portion 34B on the opposite side.

The crankshaft 20 is rotatably supported by

bearings

36A, 36B. The bearing 36A on the side of the fixing portion 2 is fixed in the central hole of the first carrier member 24, and the bearing 36B 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 each having an

external tooth portion

38A and 38B and a central hole.

The eccentric portion 34A of the crankshaft 20 is positioned in the center hole of the planetary gear 22A, and the planetary gear 22A is rotatably supported around the eccentric portion 34A by interposing the needle bearing 40A between the eccentric portion 34A and the center hole of the planetary gear 22A. The planetary gear 22A can revolve by eccentric rotation of the eccentric portion 34A caused by rotation about the central axis C of the crankshaft 20.

Similarly, the eccentric portion 34B of the crankshaft 20 is positioned in the center hole of the planetary gear 22B, and the needle bearing 40B is interposed between the eccentric portion 34B and the center hole of the planetary gear 22B, whereby the planetary gear 22B is rotatably supported around the eccentric portion 34B. The planetary gear 22B can revolve by the eccentric rotation of the eccentric portion 34B.

In a portion between the outer tooth portion 38A and the center hole in the planetary gear 22A, 6 pin holes 42A are arranged at equal intervals in the circumferential direction. Each pin hole 42A has a central axis parallel to the central axis C.

Similarly, in a portion between the outer tooth portion 38B and the center hole in the planetary gear 22B, 6 pin holes 42B are arranged at equal intervals in the circumferential direction. Each pin hole 42B has a central axis parallel to the central axis C.

In the first bearing member 24, 6 pin holes 44 are arranged at equal intervals in the circumferential direction at a portion between the outer curved surface and the central hole. Each pin hole 44 has a central axis parallel to the central axis C.

Similarly, in the portion between the outer curved surface and the central hole in the second bearing member 26, 6 pin holes 46 are arranged at equal intervals in the circumferential direction. Each pin hole 46 has a central axis parallel to the central axis C.

In addition, in a state where the pin holes 46 corresponding to the pin holes 44 are aligned, a total of 6 columnar carrier pins 48 pass through the

pin holes

44 and 46, respectively, whereby the first carrier member 24 and the second carrier member 26 are coupled with a gap therebetween. The

pin bores

44, 46 have an inner diameter that corresponds to the outer diameter of the carrier pin 48.

The

planetary gears

22A and 22B are disposed between the first carrier member 24 and the second carrier member 26.

The corresponding carrier pin 48 passes through each

pin hole

42A, 42B of the

planetary gears

22A, 22B. A cylindrical metal 49 is disposed radially outward of each carrier pin 48 and in each

pin hole

42A, 42B. The inner diameters of the pin holes 42A, 42B are larger than the outer diameter of the metal 49. Therefore, the metal 49 and the carrier pin 48 are restricted in such a manner as to allow revolution of the

planetary gears

22A, 22B, and to be restricted in a given manner with respect to movement of the

planetary gears

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

eccentric portions

34A, 34B.

A bolt hole 50 is formed in a lower portion of the first carrier member 24 (a portion opposite to the coupling shaft 12 with respect to the central axis C) on a surface of the fixed portion 2 side in parallel with the central axis C. On the other hand, a bolt hole 52 is opened in the lower portion of the fixed portion case 10. The first carrier member 24, and thus the reduction gear 4, is fixed to the fixing portion 2 by bolts 54 (fastening members) common to the bolt holes 52 and 50.

The sleeve main member 28 is a cylindrical member having a central hole. The central axis of the sleeve main part 28 and thus of the central bore coincides with the central axis C.

Internal tooth portions

60A, 60B that mesh with the

external tooth portions

38A, 38B of the

planetary gears

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

planetary gears

22A, 22B, and the number of internal teeth of the sleeve main member 28 is larger than the number of external teeth of the

planetary gears

22A, 22B. On the other hand, a second bearing member 26 is disposed on the inner surface of the central hole at a portion opposite to the fixed portion 2.

A cover 62 covering the central hole of the sleeve main member 28 is attached to the surface of the sleeve main member 28 opposite to the fixed portion 2 by a plurality of bolts 64.

A plurality of coupling portions 66 for coupling a tool box or the like, not shown, are provided on the outer surface portion of the sleeve main member 28.

The sleeve guide 30 is a cylindrical member having a center hole, and the center axis thereof and the center axis of the center hole coincide with the center axis C.

A cross roller 70 is interposed between the ferrule guide member 30 and the first bearing member 24, and the first bearing member 24 rotatably supports the ferrule guide member 30. The first carrier member 24 (inner ring), the cross rollers 70, and the sleeve 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 in the peripheral edge portion of the collar guide member 30. On the other hand, on the surface of the sleeve main member 28 on the fixing portion 2 side, a bolt hole 74 parallel to the central axis C is opened so as to correspond to the bolt hole 72. Bolts 76 are inserted into each pair of bolt holes 72 and 74, and the sleeve guide member 30 and the sleeve main member 28 are coupled to each other.

A groove 80 (concave portion) that is recessed radially inward from the other outer curved surface portion is formed in a portion of the outer curved surface of the first receiving member 24 that is located closer to the fixing portion 2 than the ferrule guide member 30, that is, a portion that is disposed in the fixing portion housing 10. The groove 80 circles around the outer curved surface of the first carrier part 24. A gap exists between the stationary part housing 10 and the ferrule guide member 30.

A plurality of bolt holes 82 orthogonal to the central axis C are arranged at equal intervals in the circumferential direction at the radial outer portion of the groove 80 in the fixed portion housing 10. The bolt holes 82 are provided vertically (fig. 1 or 2) and horizontally (fig. 2).

Further, a bolt 84 as a slip-off prevention member is inserted into each bolt hole 82. Each bolt 84 is inserted so that its head portion is radially outward and its tip portion is radially inward and protrudes from the inner surface of the fixed portion housing 10. The width of the tip of each bolt 84 (the dimension in the direction of the central axis C) is smaller than the width of the groove 80. The tip of each bolt 84 reaches the inside of the groove 80. A gap is present between the tip of each bolt 84 and the groove 80.

Next, an operation example of the reduction gear transmission 1 will be described.

When the coupling shaft 12 is rotated by driving of the motor, the crankshaft 20 rotates around the central axis C via the bevel gear 32, and the

eccentric portions

34A, 34B rotate eccentrically.

The

planetary gears

22A and 22B move relatively within the

internal gear portions

60A and 60B of the sleeve main member 28 between the first carrier member 24 and the second carrier member 26 while the movement range is restricted by the carrier pins 48.

The sleeve main member 28 rotates at a reduced speed around the central axis C at a reduction ratio corresponding to the difference between the number of outer teeth and the number of inner teeth of the

planetary gears

22A and 22B. The rotation of the sleeve main member 28 is guided by a sleeve guide member 30 coupled thereto.

By the rotation of the sleeve main member 28, the tool box and the like connected thereto rotate.

When the bolt 54 for fixing the reduction gear 4 to the fixing portion 2 is broken due to an accident such as a collision against a tool box, the reduction gear 4, the tool box, or the like is prevented from falling as follows.

That is, when the reduction gear 4 is to be separated from the fixing portion 2, the tip end portions of the bolts 84 come into contact with the grooves 80 (mainly, the surface on the fixing portion 2 side) of the first carrier member 24, and the bolts 84 support the first carrier member 24 and thus the reduction gear 4.

Next, the operation and effect of the reduction gear 1 will be described.

The reduction gear 1 includes: a sleeve main member 28 and a sleeve guide member 30 having cylindrical

internal teeth

60A and 60B;

planetary gears

22A, 22B having

external teeth portions

38A, 38B that mesh with the

internal teeth portions

60A, 60B of the sleeve main member 28; a first carrier member 24 and a second carrier member 26 that support the

planetary gears

22A, 22B and rotatably support the sleeve main member 28 and the sleeve guide member 30; a fixing portion 2 for fixing the first carrier member 24; and a bolt 84 disposed on the fixing portion 2, wherein 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 the entire reduction gear 4 falls from the fixing portion 2 due to an accident, the bolt 84 is hung in the groove 80, and the fall can be prevented.

The first carrier member 24 is fixed to the fixing portion 2 by the 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 sleeve main member 28. Therefore, the movement of the speed reducer 4 at the start of the fall with the bolt 54 (broken portion) as the center is effectively suppressed.

In addition, the bolts 84 are provided in plural and arranged in the circumferential direction. Therefore, when the bolt 54 is broken, the reduction gear 4 is supported by the bolts 84 from all directions, and the reduction gear 4 is more reliably prevented from falling.

The recess into which the tip end of each bolt 84 is inserted is a circumferential groove 80. Therefore, the groove 80 can be formed at low cost by a lathe, and the bolt 84 can be added easily by omitting a new formation of the recess by the groove 80.

The retaining members of the reduction gear 4 are bolts 84, and bolt holes 82 into which the bolts 84 are inserted are provided in the fixing portion 2. Therefore, the detachment and attachment of the retaining member are easy, and the manufacture, maintenance, and the like of the retaining member are easy.

Further, a gap is provided between each bolt 84 and the groove 80. Therefore, the impact on the first bearing member 24 is not directly transmitted to the bolts 84, and the occurrence of a situation in which the bolts 84 are damaged first is prevented, and the reduction gear 4 is more reliably prevented from coming off.

Finally, a modification of the reduction gear transmission 1 will be described.

The number of bolts 84 as the slip-off preventing member may be 3 or less (including one), or may be 5 or more. The plurality of bolts 84 may be disposed at unequal intervals in the circumferential direction, or may not be aligned on the same imaginary circle. The slip-off prevention member may be a pin pressed into the pin hole or a protrusion formed on the inner surface of the fixed portion housing 10.

Instead of the circumferential groove 80, a hole or the like opened at each of the facing portions of the tip end of the bolt 84 may be formed in the recess.

A part or all of the bolts 84 may be disposed so as to be connected to the grooves 80 without a gap.

The bolt 84 may be fixed to the first bearing member 24, and the groove 80 into which the bolt 84 is inserted is formed in the fixing portion housing 10.

The first carrier member 24 may be disposed outside the fixed portion case 10.

The number of the

planetary gears

22A, 22B, the number of the

eccentric portions

34A, 34B, or the eccentric angle may be increased or decreased.

The number and form of the various bearings can be variously changed by increasing or decreasing the number of the bearings 14, or by using the

needle bearings

40A and 40B as ball bearings.

The configuration of the various members such as the sleeve main member 28 and the

internal teeth

60A and 60B being separate members, the sleeve main member 28 being integrally formed with the sleeve guide member 30, the cap 62 and the bolt 64 being omitted, or the motor shaft being formed with a pinion without using the coupling shaft 12 may be variously modified.

The structure of the speed reducer 4 is not limited to the above-described structure. For example, the sleeve rotation type speed reducer may include a sun gear, a plurality of planetary gears (internal connection members) meshing with the sun gear, an internal gear meshing with the plurality of planetary gears, and a coupling member rotatably holding the planetary gears.

Description of the symbols

1 reduction gear, 2 fixed part, 4 reduction gear, 22A, 22B planetary gear (inscription part), 24 first carrier part (part of carrier part), 26 second carrier part (part of carrier part), 28 sleeve main part (part of sleeve), 30 sleeve guide part (part of sleeve), 38A, 38B external tooth part (external surface of inscription part), 54 bolt (fastening part), 60A, 60B internal tooth part (internal surface of sleeve), 80 groove (recess), 82 bolt hole, 84 bolt (disengagement-preventing part).

Claims

1. A reduction gear device is characterized by comprising:

a sleeve having a cylindrical inner surface;

an inner contact member having an outer surface that is in contact with the inner surface of the sleeve;

a bearing member that supports the inner contact member and rotatably supports the sleeve;

a fixing portion that fixes the carrier member; and

a slip-off prevention member disposed on one of the fixing portion or the carrier member,

a recess is formed in the other of the fixing portion or the carrier,

the slip-off prevention member reaches the inside of the recess,

the anti-slip part is provided with a plurality of anti-slip parts which are arranged along the circumferential direction,

the bearing member includes a first bearing member and a second bearing member, the central holes of the first bearing member and the second bearing member are connected with an interval therebetween and continuously,

the recess is a circumferential groove which surrounds the outer curved surface of the first bearing part by one turn.

2. Deceleration device according to claim 1,

the bearing component is fixed on the fixing part through a fastening component,

the slip-off prevention member is disposed on the opposite side of the fastening member with respect to the rotation center axis of the sleeve.

3. Deceleration device according to claim 1 or 2,

the anti-falling part is a bolt,

a bolt hole into which the bolt is inserted is provided in the one of the fixing portion or the carrier.

4. Deceleration device according to claim 1 or 2,

a gap is provided between the drop stop member and the recess.