KR20090119713A - Output structure of reducer - Google Patents

Abstract

PURPOSE: An output unit structure of a reducer for connecting the reducer to a driven device is provided to connect the reducer and the driven machine at high accuracy by alleviating the size management and component management in manufacturing the device. CONSTITUTION: An output unit structure of a reducer comprises an inner wheel member(54), a transmission member(56), and an outer wheel member(58). The inner wheel member constitutes the inner wheel of bearing. The inner wheel member is connected with the output member of the reducer. The transmission member constitutes the driver of the bearing. The outer wheel member constitutes the external wheel of the bearing. The bearing receives the bidirectional axle load of the driven shaft connected to the inner wheel member.

Description

Output structure of reducer

The present invention relates to a structure of an output unit of a reducer for connecting the reducer to a counterpart machine (driven machine).

The reducer decelerates the rotation of a drive source such as a motor and transmits it to the driven shaft of the counterpart machine. Therefore, on the output side of the reducer, it is necessary to connect the main body casing (fixed system) of the reducer to the connecting casing of the counterpart machine. In addition, it is necessary to connect the output member of the reduction gear (rotary system) with the driven shaft of the counterpart machine.

3, the speed reducer 2 disclosed by patent document 1 is shown.

A pair of bearings 6 and 8 are disposed on the inner circumference 4A of the main body casing 4 of the reducer 2, and the output member 10 is provided through the pair of bearings 6 and 8. Is rotatably supported by the body casing 4.

Under this basic configuration, the main body casing (fixed) of the reducer 2 is made using a rabbet portion E1 formed on the outer periphery 4B of the main body casing 4 of the reducer 2. System 4 is connected to the connecting casing 14 of the counterpart machine 12. In addition, in this specification, an "in-long part" means the fitting part which provides the reference | standard of the mounting position of each member when two members contact. That is, the induction part E1 formed in the outer periphery 4B of the main body casing 4 of the reducer 2 fits with the inner periphery 14A of the connection casing 14 of the counterpart machine 12, and the reducer 2 The axial centering and the axial positioning of the main body casing 4 and the coupling casing 14 of the mating machine 12 are performed.

Moreover, the output member (rotometer) 10 supported by the main body casing 4 via the bearings 6 and 8 is comprised as an output shaft of a solid in the example concerning this patent document 1, and is not shown in figure. It is connected to the driven shaft (not shown) of the counterpart machine 12 via a key.

[Patent Document 1] Japanese Patent Publication No. 2006-226347

However, in such an output part structure, since the outer periphery of the main body casing of a speed reducer functions as an intern part, accurate processing is required, for example. In addition, since the inner circumference of the main body casing also constitutes the bearing surface of the bearing, precise machining is also required. Bearings supporting the output member, whether using general-purpose products or internal materials, need to have appropriate size control for all of the inner ring, outer ring, and rolling element, including clearance control. . In addition, the outer periphery of the output member, of course, requires precise machining.

In other words, if the outer circumference and inner circumference of the main casing of the reducer, the outer circumference and inner circumference of the bearing outer ring, the diameter of the rolling element, the outer circumference and inner circumference of the bearing inner ring, and the outer circumference of the output member are not properly managed, Accumulation prevents the shaft core of the main body casing of the reducer and the connecting core of the partner machine or the shaft center of the output member of the reducer from the driven shaft of the counterpart machine. Therefore, strict control is required for the manufacturing of each of the above parts, and the number of parts is also high, and the manufacturing cost is likely to increase.

SUMMARY OF THE INVENTION The present invention has been made to solve such a conventional problem, and reduces the number of parts and reduces the dimensional control during manufacturing, thereby connecting the reducer and the counterpart with a low cost and accurate dimensional accuracy. It is the task to make it possible.

The present invention provides a structure of an output unit of a reducer configured to be mounted on a driven machine, the inner ring member constituting the inner ring of the bearing, the rolling member constituting the rolling element of the bearing, and the outer ring of the bearing. And an inner ring member connected with the driven shaft side of the counterpart machine as an output member of the reducer, wherein the outer ring member includes an inner circumference of the main casing of the reducer and an inner circumference of the connecting casing of the counterpart machine. It functions as an in-long part that provides a criterion when fitting and mounting, and the bearing is connected to the inner ring member and the driven shaft connected to the inner ring member by the inner ring member, the transmission member, and the outer ring member. The problem was solved by receiving the load.

According to the present invention, the output side constitutes a huge bearing as a whole, and the inner ring of the bearing functions as an output member, and the outer circumference of the outer ring functions directly as an induction portion of both the main casing of the reducer and the connecting casing of the counterpart machine. Therefore, the number of parts can be reduced, the number of parts requiring precise dimension management can be reduced, and accurate dimensional accuracy can be maintained at low cost.

According to the present invention, the size control and the part management at the time of manufacture are alleviated, and the reducer and the counterpart machine can be connected with low cost and accurate dimensional accuracy.

EMBODIMENT OF THE INVENTION Hereinafter, an example of embodiment of this invention is described in detail, referring drawings.

1 is a cross-sectional view showing the structure of an output unit of a reducer according to an example of the embodiment of the present invention. In this example, the form in which the speed reducer 22 integrated with the motor 20 is connected to the counterpart machine (driven machine) 24 is shown.

The motor 20 is connected to the first main body casing 28 of the reducer 22 via a bolt (not shown in the center line only) in the flange portion 26A of the motor casing 26. The motor shaft 32 of the motor 20 is connected to the joint shaft 36 provided with the friction fastening mechanism 34. The joint shaft 36 is supported by the first main body casing 28 of the reducer 22 via the ball bearing 40. In the hollow portion 36A of the joint shaft 36, a sun gear 38 corresponding to the input shaft of the reduction gear 22 is press-fitted.

The reduction gear 22 is provided with the reduction gear part 30 of the simple planetary gear mechanism. The reduction unit 30 includes the sun gear 38, a plurality of planetary gears 42 rotating while rotating around the sun gear 38, and internal gears in which the planetary gears 42 internally engage. 44). The planetary gear 42 is supported by the planetary pin 45 via the needle bearing 43. The planetary pin 45 is supported by the carrier 48. For this reason, the carrier 48 rotates in synchronism with the revolution of the planetary gear 42. In this example, the carrier 48 is composed of the carrier plate 48A and the carrier pin 48B, and fastened and fixed to the inner ring member 54 described later through the bolt 60. That is, in this reducer 22, the output member is comprised by the carrier 48 and the inner ring member 54, and rotation of the carrier 48 is withdrawn from the inner ring member 54 as the output rotation of the reducer 22. As shown in FIG. do. However, the internal gear 44 is integrated with the second main body casing 46 of the reducer 22.

The reduction gear 22 inserts a bolt (not shown) into the bolt insertion hole 49 of the 2nd main body casing 46, in the state which connected the motor 20, and connects the casing 50 of the counterpart machine 24. It is fastened to and fixed to.

Hereinafter, the structure of the output part of this reducer 22 is demonstrated in detail.

This output section structure has a large bearing 52 as its main component. The large bearing 52 has an inner ring member 54 constituting the inner ring of the large bearing 52 and a transmission member constituting the rolling element of the large bearing 52 ( 56 and an outer ring member 58 constituting the outer ring of the large bearing 52.

The inner ring member 54 of the large bearing 52 is a substantially cylindrical block, and is connected to the carrier 48 of the reduction unit 30 through the bolt 60 as described above, and the carrier Together with 48, it functions as an "output member" of the reducer 22. In this embodiment, the output shaft block 62 is attached to the inner ring member 54 via the bolt 64 from the left side of the drawing, and the key (key) is placed on the side of the driven shaft (not shown) of the counterpart machine 24. Only the grooves 62A are connected through the structure (not shown) to transfer power. However, in place of the power transmission in which the output shaft block 62 is installed, for example, the driven shaft of the counterpart machine 24 is directly connected to the inner ring member 54 by using the bolt hole 66 of the bolt 64. You may make it. The inner ring member 54 is formed with a V groove 54A having an opening degree of 90 degrees through which the transmission member 56 is fitted, and the V groove 58A having an opening degree of 90 degrees corresponding to the outer ring member 58 described later. ) Is formed.

The transmission member 56 of the large bearing 52 is comprised by the roller (not shown) of the same diameter and axial length, and rotates the said roller 90 degrees, and the said inner ring member 54 is changed. The V groove 54A is sandwiched between the V groove 54A and the V groove 58A of the outer ring member 58. Thereby, the large bearing 52 comprises what is called a cross roller bearing as a whole. In the cross roller bearing, there is only one surface of the raceway plane (the plane perpendicular to the axis O1 including the center of the transmission member 56) T1 of the transmission member 56. Both axial loads can be picked up. However, this transmission member 56 is provided one by one through the insertion hole 71 which penetrated in a radial direction to a part of outer ring member 58. As shown in FIG.

The outer ring member 58 of the large bearing 52 also serves as a function of the end casing of the reducer 22. The outer circumference 58B of the outer ring member 58 has a simple cylindrical shape without a step. In this embodiment, the outer circumference 58B of the outer ring member 58 has a simple cylindrical shape without a step, so that the outer circumference of the outer ring member 58 is formed by a so-called centerless grinding machine (centerless grinder). (58B) is to be ground. As a centerless grinding machine, it is well known to support the work (the outer ring member 58 in this example) with a work rest (not shown) and grind using two grindstones. Do.

The outer circumference 58B of the outer ring member 58 engages with the reducer side induction portion E2 and the counterpart machine 24 that fit with the inner circumference 46A (part of) of the second main body casing 46 of the reducer 22. It functions as a relative machine side inward part E3 fitting with (in part) the inner circumference 50A (part of) of the connecting casing 50. That is, the respective shaft centers O1 of the second main body casing 46 and the large bearing 52 coincide with the functions of the reduction gear side induction part E2 and the counterpart side induction part E3. . Moreover, 50 C of end surfaces of the connection casing 50 of the counterpart machine 24 contact the end surface 46C of the flange part 46B of the 2nd main body casing 46, and the connection casing 50 is carried out. The axial positioning on the outer circumference 58B of the outer ring member 58 is performed. However, the flange part 46B of the 2nd main body casing 46 is not formed in the whole circumferential direction of the said 2nd main body casing 46, It is an aspect called what is called an "ear part", It extends slightly in the axial direction and protrudes in the radial direction in four places of the circumferential direction, and is formed.

As is clear from FIG. 1, in this embodiment, most of the outer circumference 58B of the outer ring member 58 is fitted with the connecting casing 50 of the mating machine 24. In other words, most of the outer circumference 58B of the outer ring member 58 functions as an induction portion of the connecting casing 50 of the mating machine 24.

When viewed from the relation with the transmission member 56, in the outer periphery 58B of the outer ring member 58, among the reduction gear side induction part E2 and the relative machine side induction part E3, the relative machine side induction part E3 is shown. The page is set long. In addition, the track plane T1 of the said transmission member 56 is accommodated in the radial direction inner side of the said elongate set machine side induction part E3.

In this embodiment, however, the output section is formed so as to form a large bearing as a whole, and the inner ring member 54 and the outer ring member 58 are not formed of so-called "bearing steel". Therefore, the transfer surface of the transmission member 56 (the V groove 54A of the inner ring member 54 and the V groove 58A of the outer ring member 58) needs a separate hardening treatment. Therefore, in the vicinity of these V-grooves 54A and 58A, the material becomes hard, so that each hole such as the pin hole 47 and the bolt hole 66 of the planetary pin 45 is in this hardened vicinity. In order to avoid processing, the consideration is made so as not to be a "through hole", and as a result, each hole is easily and precisely formed in the soft part. As a result, as a result, the inner ring member 54 has a cross section P1 perpendicular to the axis (all of which is solid) in which no hole is formed.

Here, reference numeral 70 in FIG. 1 denotes an oil seal disposed between the inner ring member 54 and the outer ring member 58 in order to seal the inside and the outside of the reducer 22.

Next, the operation of the geared motor having the output unit structure will be described.

When the output shaft 32 of the motor 20 rotates, the sun gear 38 which is an input shaft of the reducer 22 rotates via the joint shaft 36. In this speed reducer 22, since the internal gear 44 of the speed reducer 30 is in a fixed state, the idle component of the planetary gear 42 is drawn out from the carrier 48. The carrier 48 is integrated with the inner ring member 54 of the large bearing 52 via the bolt 60, and the inner ring member 54 is connected via the output shaft block 62 and the bolt 64. As a result, the output shaft block 62 is rotated so that the driven shaft of the counterpart machine rotates through a key (not shown).

Here, since the inner ring member 54 is supported by the outer ring member 58 through the cross roller type transmission member 56, both the radial load and the bidirectional axial load can be picked up. The axial vibration (moment component) of the inner ring member 54 is also applicable.

In addition, since the carrier 48 (carrier plate 48A and carrier pin 48B) is integrated with this inner ring member 54 which is stably supported, the bearing of the outer circumference of the carrier plate 48A can be omitted. It is supposed to be done.

In addition, since the cross roller-type transmission member 56 is constituted by "rollers" sandwiched differently from each other by 90 degrees, there is little rattling (gap between the inner ring member 54 and the outer ring member 58). The inner ring member 54 and the outer ring member 58 can be fitted with high mounting accuracy. In addition, since there is only one surface of the raceway plane T1 of the transmission member 56, it is also possible to design a thinner axial thickness of the large bearing 52 if necessary.

Since the outer ring member 58 is ground by a centerless grinding mill utilizing the fact that its outer circumference 58B has a simple cylindrical shape without a step, it is possible to perform an extremely close circle processing. . In addition, the outer ring member 58 is connected to the flange portion 46B of the second main body casing 46 of the reducer 22 and the connecting casing 50 of the mating machine 24 at the outer circumference 58B close to the full circle. Is fitting in. Here, the reducer side induction part E2 with which the 2nd main body casing 46 of the reducer 22 is fitted, and the relative machine side induction part E3 with which the connection casing 50 of the mating machine 24 is fitted. In the meantime, the relative machine side intern part E3 is set longer (actually to almost the entire surface of the outer circumference 58B). Accordingly, the outer ring member 58 is eventually fitted and supported over almost the entire surface of the outer circumference 58B close to the full circle. In particular, in this embodiment, instead of the reduction gear side induction part E2 to which the "decelerator 22" is fitted, the side of the relative machine side induction part E3 to which the "relative machine 24" is fitted is lengthened. Since it is set, it is fitted and supported by the massively large member called a counterpart machine. Therefore, the rigidity of the connecting casing of the counterpart machine can be used as a support base as it is, and further higher rigidity can be ensured.

Further, in this way, the circumferential surface T1 of the transmission member 56 is disposed in the radially inner side of the relative machine side inward portion E3 of the outer ring member 58 which is stably supported with high rigidity. Because of this, it is transmitted from the transmission member 56 side (compared to the structure in which the transmission surface of the transmission member 56 is radially inward at a position deviated from the axial position of the induction portion due to a short axial dimension of the induction portion). Moment loads such as radial loads, thrust loads, or vibrations can be extremely stable.

In this embodiment, the number of machined surfaces requiring strict dimensional control can be kept to a minimum without the need for a detailed comparison with the conventional example described above. Do.

In addition, in the said Example, although the said big bearing 52 comprised the cross roller bearing as a whole, in this invention, it is not necessary to necessarily comprise a cross roller bearing as a whole. For example, as shown in FIG. 2, the first transmission member 156A capable of receiving an axial load on one side in the axial direction as the "electric member" between the inner ring member 154 and the outer ring member 158, and the first The second rolling member 156B is disposed apart from the first rolling member 156A in the axial direction and is capable of receiving the axial load on the other side in the axial direction, so that the large bearing 152 is (first and first). The track bearings T101A and T101B of the two transmission members 156A and 156B may constitute an angular bearing. Also in this case, the large bearing 152 is formed entirely by the inner ring member 154, the first and second transmission members 156A and 156B, and the outer ring member 158. The axial load of both directions of the driven shaft (not shown) of the counterpart machine 124 connected to the inner ring member 154 can be received, and the above-described effects can be obtained.

In this case, in the case of the bearing structure having two raceway planes T101A and T101B of the transmission member 156 in this manner, both of the raceway planes T101A and T101B have both long set portions ( In this embodiment, what is necessary is just to exist inside the radial direction of the mating member side intern part E103. As a result, the track surfaces T101A and T101B are separated in the axial direction, and in particular, good support characteristics can be obtained with respect to the axial vibration of the inner ring member 154.

The rest of the configuration is almost the same as in the previous embodiment, and thus, duplicate explanation is omitted by attaching the same reference numerals to the lower two digits in FIG. 2 to the same or functionally identical parts as those shown in FIG.

In the above embodiment, however, the outer circumference of the outer ring member is made to have a simple cylindrical shape without a step, and is ground by a centerless grinding machine (using this simple shape), whereby the outer circumference of the outer ring member constituting the in-long portion is highly precise. The road was to be processed. In the present invention, however, the shape of the outer circumference of the outer ring member does not necessarily have to be a simple cylindrical shape without a step. For example, the fitting of the connecting casing of the mating machine is stopped in the axial direction of the outer ring member. In this case, a step may be formed. That is, in this invention, it does not specifically limit about how much the connection casing of a counterpart machine and the main body casing of a reducer are fitted with respect to the outer periphery of an outer ring member. Even in the case of a cylindrical shape without a step, the entire outer circumference does not necessarily have to be an in-long part.

The shape of the inner ring member is not limited to the above shape, and the formation of each hole may be a through hole (for example, when there is a margin in the radial direction). In this case, the axial length of the inner ring member can be further shortened.

In addition, the structure of the specific deceleration part of a reducer is also not limited to the said structure.

The present invention can be widely used as a structure of an output section of various reducers.

1 is a cross-sectional view of a speed reducer showing an example of an embodiment of the present invention.

2 is a cross-sectional view of a speed reducer showing an example of another embodiment of the present invention.

3 is a cross-sectional view of a speed reducer illustrating an example of a structure of an output unit of a conventional speed reducer.

[Description of the code]

20: motor 22: reducer

24: partner machine 26: motor casing

28: first body casing 30: reduction unit

32: motor shaft 36: joint shaft

38: sun gear 42: planetary gear

44: internal gear 46: second body casing

48: carrier 50: connecting casing

52: large bearing 54: inner ring member

54A: V groove 56: Electric member

58: outer ring member 58A: V groove

60, 64: bolt 62: output shaft block

T1: track plane

E2: Inlong part of reducer

E3: Inner side of counterpart machine

Claims (5)

In the output structure of the reducer configured to be mounted on the driven machine, An inner ring member constituting the inner ring of the bearing, A transmission member constituting the rolling element of the bearing; An outer ring member constituting the outer ring of the bearing, The inner ring member is connected to the driven shaft side of the mating machine as an output member of the reducer, The outer ring member functions as an in-long part that provides a reference when fitting to the inner circumference of the main casing of the reducer and the inner circumference of the connecting casing of the counterpart machine, And the bearing receives, by the inner ring member, the transmission member, and the outer ring member, axial loads in both directions of the inner ring member and the driven shaft connected to the inner ring member. The method according to claim 1, An outer circumference of the outer ring member has a simple cylindrical shape without a step, wherein the output unit structure of the speed reducer. The method according to claim 1 or 2, Either one of the reducer side interns to which the main body casing of the reducer fits on the outer circumference of the outer ring member, and the other machine side inlets to which the coupling casing of the mating machine fits on the outer circumference of the outer ring member is different. And a plane perpendicular to the axis of the output member including the center of the transmission member is located radially inward of the in-long portion of the long set side. The method according to any one of claims 1 to 3, An output structure of a speed reducer, wherein the large bearing is a cross roller bearing having only one surface in a plane perpendicular to an axis of the output member including the center of the transmission member. The method according to any one of claims 1 to 3, The large bearing is a first transmission member that is capable of receiving an axial load on one side in the axial direction as the transmission member, and is disposed away from the first transmission member in the axial direction, and the axial load on the other side in the axial direction is applied. The output part structure of the speed reducer provided with the 2nd transmission member which can be received, and the bearing which has the plane which is perpendicular to the axis | shaft of the said output member including the center of the said 1st, 2nd transmission member, exists in two surfaces. .

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