JP2016049474A - Agitating shaft driving device and method for assembling the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To support an output shaft and an agitating shaft of a rotating device stably at a low cost.SOLUTION: In a driving device 62 for an agitating shaft 56 that couples the output shaft 39 of the rotating device 11 to the agitating shaft 56 to rotatably drive the agitating shaft 56, the output shaft 39 and the agitating shaft 56 are coupled to each other so as not to be relatively movable in a radial direction, and the output shaft 39 is supported by one output shaft ball bearing 64, and the agitating shaft 56 is supported by one frame base ball bearing 66.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a drive device for a stirring shaft and an assembling method thereof.

  In the fields of water treatment, chemicals, food production, etc., it is often necessary to agitate the liquid material in the tank. Patent Document 1 discloses a device that is suitable for use in such an application, and connects the stirring shaft to the output shaft of the speed reducer and rotationally drives the stirring shaft.

  In this device, the output shaft of the speed reducer is supported at two points (both ends supported) by a pair of bearings incorporated in the speed reducer casing. A gantry casing is connected to the lower part of the reduction gear casing. The stirring shaft is key-connected to the output shaft through a joint member, and is supported at two points (both-end support) by a pair of bearings incorporated in the gantry casing.

Japanese Patent Laying-Open No. 2004-1000077 (FIG. 1)

  However, the configuration in which the output shaft and the stirring shaft of the speed reducer are each supported by two bearings (a configuration in which the total is supported by four bearings) is costly.

  Therefore, in order to reduce costs, a structure has been proposed in which the stirring shaft is connected to the output shaft of the speed reducer without any play in the radial direction so that the stirring shaft is supported by only one bearing on the anti-reduction gear side. . According to this structure, the output shaft and the agitation shaft can be supported by only a total of three bearings, including the output shaft bearing of the reduction gear.

  However, when the output shaft and the agitation shaft of the speed reducer are supported by a total of three bearings in this way, sometimes abnormal noise or vibration occurs, the speed reducer bearing is damaged, etc. There was a problem that sometimes occurred.

  The present invention has been made in order to solve such a problem, and provides a drive device for a stirring shaft that can stably support the output shaft and the stirring shaft of a rotating device at low cost. That is the issue.

  The present invention provides a stirrer shaft drive device in which a stirrer shaft is connected to an output shaft of a rotating device, and the stirrer shaft is rotationally driven. The above-described problem is solved by supporting the output shaft with a single bearing and supporting the agitation shaft with a single bearing.

  Further, the present invention relates to a method for assembling a stirring shaft drive device in which an output shaft of a rotating device and a stirring shaft are connected to rotationally drive the stirring shaft, and a single bearing and a dummy bearing are provided on the output shaft. A step of incorporating, a step of removing the dummy bearing, a step of connecting the output shaft and the agitation shaft so as not to move relative to each other in a radial direction, and a step of supporting the agitation shaft by a single bearing. By including the configuration, the above-described problems are similarly solved.

  In the present invention, the output shaft and the stirring shaft of the rotating device are connected so as not to move relative to each other in the radial direction. The output shaft of the rotating device is supported by one bearing, and the stirring shaft is also supported by one bearing. That is, the output shaft and the stirring shaft that are connected so as not to be relatively movable in the radial direction are supported at two points by the two bearings. Therefore, the output shaft and the stirring shaft can be stably supported at a low cost.

  According to the present invention, the output shaft and the stirring shaft of the rotating device can be stably supported at low cost.

Sectional drawing which shows the principal part of the stirring apparatus to which the drive apparatus of the stirring shaft which concerns on an example of embodiment of this invention was applied. 1 is an enlarged cross-sectional view of the main part of FIG. Whole sectional drawing of the drive device of the stirring shaft which concerns on an example of other embodiment of this invention. The whole sectional view of the drive device of the stirring shaft concerning an example of other embodiments of the present invention. 1 is an overall cross-sectional view of a stirring device to which a driving device for a stirring shaft according to the embodiment of FIG. 1 is applied.

  Hereinafter, an example of an embodiment of the present invention will be described in detail based on the drawings.

  FIG. 5 is an overall cross-sectional view of a stirrer to which a drive device for a stirrer shaft according to an example of an embodiment of the present invention is applied, FIG. 1 is a cross-sectional view showing the main part of the stirrer, and FIG. FIG.

  First, the overall schematic configuration of the stirring device will be described.

  In the stirring device 10, a stirring shaft 56 is connected to an output shaft 39 (see FIG. 1) of the rotating device 11, and the stirring shaft 56 is driven to rotate. The stirring shaft 56 has a stirring blade body 56A to which the stirring blade 15 is fixed. Then, by rotating the stirring shaft 56 (stirring blade body 56A), the stirring blade 15 rotates integrally to stir the object to be stirred (not shown) in the tank 13.

  The rotating device 11 includes a motor 12 and a speed reducer 14 in this example. The rotating device 11 is installed and fixed on the upper portion of the tank 13 of the stirring device 10 via a gantry unit 16. Hereinafter, the configuration of the rotating device 11 will be described in order.

  The motor 12 of the rotating device 11 includes a motor shaft 18. The motor shaft 18 is connected to the input shaft 22 of the speed reducer 14 via the first key 20. The speed reducer 14 is a speed reducer having an eccentric oscillating planetary gear speed reduction mechanism, and two eccentric bodies 24 eccentric to the axis of the input shaft 22 are integrally formed on the outer periphery of the input shaft 22. Is formed. The eccentric phase of each eccentric body 24 is shifted by 180 degrees. An external gear 28 is incorporated on the outer periphery of the eccentric body 24 via rollers 26 so as to be swingable. The external gear 28 is in mesh with the internal gear 30.

  In this embodiment, the internal gear 30 includes an internal gear main body 30A integrated with the reduction gear casing 32, a pin member 30B supported by the internal gear main body 30A, and the pin member 30B so as to be rotatable. And a roller member 30 </ b> C that is externally fitted and constitutes the internal teeth of the internal gear 30. The number of internal teeth (the number of roller members 30C) of the internal gear 30 is slightly larger (only 1 in this example) than the number of external teeth of the external gear 28.

  The external gear 28 has a through hole 28A at a position offset from the respective axis C28. A plurality of through holes 28A are formed at equal intervals in the circumferential direction. The inner pin 34 passes through the through hole 28A. An inner roller 36 is rotatably fitted on the outer periphery of the inner pin 34. A part of the inner roller 36 and the through hole 28A are in contact with each other, and the dimension between the inner roller 36 and the through hole 28A, which is not in contact, is twice the eccentric amount of the eccentric body 24. The corresponding maximum gap is secured.

  The inner pin 34 is press-fitted and fixed to a carrier flange 38 disposed on the axial load side of the external gear 28. The carrier flange 38 is integrated with the output shaft 39.

  The motor casing 40 of the motor 12 of the stirring device 10 includes a motor main body casing 42 and a motor cover 44 connected to the load side of the motor main body casing 42.

  The speed reducer casing 32 of the speed reducer 14 of the stirring device 10 includes a speed reducer main body casing 48, an input side cover 50 connected to the anti-load side of the speed reducer main body casing 48, and a load side of the speed reducer main body casing 48. It has the output side cover 52 connected. The motor cover 44 of the motor 12 is also used as the input side cover 50 of the speed reducer 14 (motor cover 44 = input side cover 50 of the speed reducer 14). The speed reducer main body casing 48, the input side cover 50, and the output side cover 52 of the speed reducer 14 are coupled together by a first bolt 54.

  The unit casing 57 of the gantry unit 16 of the stirring device 10 includes a gantry body casing 58 that accommodates the stirring shaft 56, and a gantry cover 60 that is connected to the load side of the gantry body casing 58.

  Next, the structure of the drive device 62 of the stirring shaft 56 applied to the stirring device 10 will be described.

  If it demonstrates from an outline, the drive device 62 of the stirring shaft 56 which concerns on this embodiment will connect the stirring shaft 56 of the mount unit 16 to the output shaft 39 of the reduction gear 14 (of the rotation apparatus 11), and this stirring shaft 56 will be connected. It is configured to rotate. The output shaft 39 and the stirring shaft 56 are connected so as not to move relative to each other in the radial direction. The output shaft 39 of the speed reducer 14 is supported by an output shaft ball bearing 64 on the output side cover 52 of the speed reducer 14. The stirring shaft 56 is supported on the gantry cover 60 of the gantry unit 16 by one gantry ball bearing 66.

  More specifically, the output shaft 39 of the speed reducer 14 and the agitation shaft 56 of the gantry unit 16 are connected to the joint shaft 68 so as not to move relative to each other in the radial direction and the axial direction. In this embodiment, the joint shaft 68 is constituted by a cylindrical member having a single press-fit hole 68A. The core of the press-fit hole 68A is C68A. The output shaft 39 of the speed reducer 14 is press-fitted into the press-fit hole 68A from the side opposite to the load, and the stirring shaft 56 is press-fitted into the same press-fit hole 68A from the load side. Thereby, the shaft center C39 of the output shaft 39 coincides with the hole center C68A of the press-fit hole 68A, and the shaft center C56 of the stirring shaft 56 coincides with the hole center C68A of the same press-fit hole 68A. In this embodiment, the joint shaft 68, the output shaft 39, and the stirring shaft 56 are connected by the second key 70 (in the rotational direction) (the connection by the second key 70 is not necessary).

  The output side cover 52 constituting a part of the speed reducer casing 32 of the speed reducer 14 is entirely constituted by a cylindrical member. On the outer periphery of the end of the output side cover 52 on the side opposite to the load, a first outer flange portion 52A is formed to project outward in the radial direction. As described above, the output side cover 52 is connected to the main body casing 48 of the speed reducer 14 via the first bolt 54 at the first outer flange portion 52A. On the outer periphery of the load side end portion of the output side cover 52, a second outer flange portion 52B is formed to project outward in the radial direction. The output side cover 52 is connected to the gantry body casing 58 at the second outer flange portion 52B via a bolt (only the center line C55 is shown) inserted from the load side.

  Further, the first inner flange portion 52C protrudes inward in the radial direction at a position slightly on the axial load side of the inner periphery of the output side cover 52 on the side opposite to the load side than the first outer flange portion 52A. Is formed. A second inner flange portion 52D protrudes inward in the radial direction at a position on the inner side of the load side of the output side cover 52 and slightly on the side opposite to the axial direction from the second outer flange portion 52B. ing.

  The output shaft 39 of the speed reducer 14 is supported by the second inner flange portion 52D of the output side cover 52 via one output shaft ball bearing (one bearing) 64. Here, “supported by one bearing” means “supported by a bearing that receives a load but cannot receive a moment acting on the shaft (output shaft 39) alone”. doing. In other words, in terms of appearance, the configuration supported by a cross roller bearing, a four-point contact ball bearing, a double-row angular bearing, or the like that can receive the moment of the output shaft 39 independently even with a single bearing is here. Is not included in the concept of “supported by one bearing”.

  The output shaft ball bearing 64 includes an inner ring 64A, an outer ring 64B, and a rolling element 64C. The inner ring 64 </ b> A of the output shaft ball bearing 64 is sandwiched between the stepped portion 39 </ b> A of the output shaft 39 and the first collar 72 press-fitted into the output shaft 39, so that movement in the axial direction is restricted. The outer ring 64 </ b> B of the output shaft ball bearing 64 is restrained from moving in the axial direction by a retaining ring 78. The retaining ring 78 is sandwiched between the load side end portion 52D1 of the second inner flange portion 52D and the locking block 80 integrated with the second inner flange portion 52D via the second bolt 55, and the shaft Directional movement is constrained. With this configuration, the output shaft ball bearing 64 can receive a radial load and a thrust load acting on the output shaft 39. However, the moment acting on the output shaft 39 cannot be received alone.

  In this embodiment, no bearing or the like is particularly disposed on the first inner flange portion 52C of the output side cover 52. That is, in this embodiment, the first inner flange portion 52C functions as a reinforcing portion that increases the strength of the output side cover 52. The first inner flange portion 52C is utilized as an assembly flange of the bearing when the speed reducer 14 is used for other purposes. That is, the output side cover 52 is supported by a reduction gear whose output shaft is supported by two bearings (with two-point support), and the output shaft is supported by one bearing (with one-point support) as in this embodiment. It is shared (shared) with the reduction gear.

  Two oil seals 73 are arranged side by side between the outer periphery of the first collar 72 and the inner periphery of the locking block 80 on the axial load side of the output shaft ball bearing 64. The oil seal 73 seals between the reduction gear casing 32 (the output side cover 52 thereof) and the output shaft 39.

  On the other hand, the entire gantry body casing 58 of the gantry unit 16 is formed of a cylindrical member having a slightly larger diameter on the load side than on the non-load side. A first outer flange portion 58 </ b> A is formed on the outer periphery of the opposite end of the gantry body casing 58 so as to project outward in the radial direction. As described above, the gantry body casing 58 has the second outer side of the output side cover 52 of the speed reducer 14 via the bolt inserted from the load side (only the center line C55 is shown) in the gantry first outer flange portion 58A. It is connected to the flange portion 52B.

  On the outer periphery of the end of the gantry body casing 58 on the load side, a gantry second outer flange portion 58B is formed to project outward in the radial direction. A gantry cover 60 is connected to the gantry second outer flange portion 58B via a third bolt 61 inserted from the load side.

  The gantry cover 60 is formed of a substantially disk-shaped member, and has a through hole 60 </ b> A in the central portion in the radial direction. The through-hole 60A of the gantry cover 60 is formed with a thick peripheral wall, and a support portion 60A1 of the agitation shaft 56 is formed on the opposite side of the through-hole 60A, and a support portion 60A2 of the oil seal 65 is formed on the load side. ing. Specifically, the oil seal 65 is disposed between the second collar 74 incorporated on the outer periphery of the stirring shaft 56 and the inner periphery of the through hole 60A, and seals the inside of the gantry body casing 58.

  The agitation shaft 56 is rotatably supported by one pedestal ball bearing (one bearing) 66 disposed in a support portion 60A1 formed on the side opposite to the through hole 60A. “Supported by one bearing” means “bearing that receives a load but cannot receive a moment acting on the shaft (stirring shaft 56) alone, as in the meaning of the output shaft ball bearing 64. It is supported by. The gantry ball bearing 66 includes an inner ring 66A, an outer ring 66B, and a rolling element 66C. The inner ring 66 </ b> A of the gantry ball bearing 66 is sandwiched between the step portion 56 </ b> A formed on the stirring shaft 56 and the second collar 74, so that the movement in the axial direction is restricted. The second collar 74 is restrained from moving in the axial direction by coming into contact with a mounting block 84 for mounting the stirring blade body 56A (see FIG. 5) of the stirring shaft 56. The mounting block 84 is incorporated in the stirring shaft 56 via a fourth bolt 82 inserted from the load side.

  With this configuration, the gantry ball bearing 66 can receive a radial load and a thrust load acting on the stirring shaft 56. However, the moment acting on the stirring shaft 56 cannot be received alone.

  Next, the operation of this embodiment will be described. First, the operation of the stirring device 10 will be described.

  In the stirring device 10, when the motor shaft 18 of the motor 12 rotates, the input shaft 22 of the speed reducer 14 connected to the motor shaft 18 via the first key 20 rotates. When the input shaft 22 rotates, the external gear 28 swings and rotates through the eccentric body 24 and the rollers 26 arranged on the outer periphery of the eccentric body 24. This causes a phenomenon in which the meshing positions of the external gear 28 and the internal gear 30 are sequentially shifted, and each time the input shaft 22 rotates once, the external gear 28 (in a fixed state) The toothed gear 28 rotates (rotates) relative to the number of teeth (1 in this example).

  This relative rotation is transmitted to the carrier flange 38 via the inner roller 36 and the inner pin 34, and the output shaft 39 integrated with the carrier flange 38 rotates. The swinging component of the external gear 28 is absorbed by the gap between the inner roller 36 and the through hole 28A of the external gear 28.

  When the output shaft 39 of the speed reducer 14 rotates, the stirring shaft 56 connected to the output shaft 39 rotates.

  Here, the output shaft 39 and the agitation shaft 56 are connected so as not to move relative to each other in the radial direction by being press-fitted into the joint shaft 68. Specifically, the output shaft 39 is press-fitted into the press-fitting hole 68A of the joint shaft 68 from the non-load side, and the stirring shaft 56 is press-fitted into the same press-fitting hole 68A from the load side. Therefore, the shaft center C39 of the output shaft 39 is aligned with the hole center C68A of the press-fit hole 68A, and the shaft center C56 of the stirring shaft 56 is aligned with the hole center C68A of the same press-fit hole 68A. For this reason, there is no relative displacement in the radial direction between the axis C39 of the output shaft 39 and the axis C56 of the stirring shaft 56, and the output shaft 39 and the stirring shaft 56 are as if they are one shaft. Rotate like so.

  The output shaft 39 and the stirring shaft 56 that rotate as if they were one shaft are supported by one output shaft ball bearing 64 at the portion of the output shaft 39 and at the portion of the stirring shaft 56. Two points are supported by one frame ball bearing 66. Therefore, the output shaft 39 and the agitation shaft 56 can rotate in an extremely stable state with almost no vibration or the like due to the shift of the shaft centers C39 and C56.

  More specifically, in this regard, a conventional configuration in which the output shaft 39 of the speed reducer 14 is supported by two bearings and the stirring shaft 56 is supported by two bearings (the output shaft 39 and the output shaft 39). The configuration in which the stirring shaft 56 is supported at four points) requires a total of four bearings and is expensive.

  On the other hand, in order to suppress an increase in cost, the agitation shaft 56 is connected to the output shaft 39 of the speed reducer 14 without any play in the radial direction, so that one bearing is omitted and a three-point support structure with three bearings is provided. When it is adopted, although the cost can be reduced, there is a problem that the blur due to the deviation between the axis C39 of the output shaft 39 and the axis C56 of the stirring shaft 56 is more likely to occur. And until now, the fact that the rotation by the three-point support is not stable has been a disadvantage associated with the omission of one bearing for cost reduction.

  According to the drive device 62 of the stirring shaft 56 according to the present embodiment, it is possible to further reduce the cost by further reducing one bearing compared to the three-point support configuration. In addition, the output shaft 39 and the agitation shaft 56 that rotate substantially as “one shaft” by being connected so as not to move relative to each other in the radial direction are supported by a portion of the output shaft 39 with a single bearing, The stirring shaft 56 is supported by a single bearing. In short, the output shaft 39 and the stirring shaft 56 that rotate substantially as “one shaft” are supported at two points. For this reason, rather than a configuration in which one shaft is supported at three points, stable support is possible.

  Note that, as described above, the output shaft ball bearing 64 and the gantry ball bearing 66 as “one bearing” here “behaves a load but alone acts on the shaft (the output shaft 39 or the stirring shaft 56). It is a bearing that cannot receive the moment that is generated. If, for example, a cross roller bearing, a four-point contact ball bearing, a double-row angular bearing, or the like that can receive a load and independently receive the moment of the shaft is adopted as “one bearing”, each shaft 39 , 56 is improperly constrained, resulting in increased blurring and the possibility of smooth rotation.

  Since the output shaft ball bearing 64 and the gantry ball bearing 66 according to the present embodiment are bearings that cannot receive the moment of the shaft by themselves, they can sufficiently receive the merit of “two-point support”. Conversely, if there is a configuration that can receive the thrust load of the output shaft 39 and the stirring shaft 56 by some method, for example, a roller bearing or the like that can receive only a radial load may be used. Further, for example, a pair of tapered roller bearings, angular ball bearings, or the like may be used, with one bearing supporting the output shaft and one bearing supporting the stirring shaft. Since the tapered roller bearing and the angular ball bearing are bearings that cannot receive a moment acting on the shaft (the output shaft 39 or the stirring shaft 56) by themselves, they can be “one bearing” according to the present invention.

  3 and 4 show another embodiment of the present invention.

  In the embodiment of FIG. 3 as well, the output shaft 39 of the speed reducer 14 and the stirring shaft 56 are connected so as not to be relatively movable in the radial direction, as in the previous embodiment. In addition, the output shaft 39 of the speed reducer 14 is supported by one output shaft ball bearing 88, and the stirring shaft 56 is supported by one gantry ball bearing 66.

  However, in this embodiment, the arrangement position of one output shaft ball bearing 88 that supports the output shaft 39 of the speed reducer 14 is different from that of the previous embodiment, and in addition to the output shaft ball bearing 88, the output shaft Further, a dummy ball bearing 90 which is incorporated in the circuit 39 but does not receive a radial load during operation is further provided.

  Hereinafter, more specifically, the output side cover 52 of the speed reducer 14 in this embodiment is an output shaft cover having the same configuration as in the previous embodiment. That is, the first inner flange portion 52C protrudes radially inward from the inner periphery of the output side cover 52 at a position slightly on the axial load side than the first outer flange portion 52A. ing. In the previous embodiment, the first inner flange portion 52C functions as a reinforcing portion that increases the strength of the output-side cover 52. In this embodiment, the first inner flange portion 52C is connected to the output shaft 39. The "one output shaft ball bearing 88" that receives the load is arranged.

  In addition, a dummy ball bearing 90 is disposed as a dummy bearing on the second inner flange portion 52D of the output side cover 52 where the output shaft ball bearing 64 is disposed in the previous embodiment. “Dummy bearing” refers to a bearing that is incorporated in the output shaft but does not receive a radial load during operation. Here, “does not receive radial load during operation” means that even if it receives no radial load during operation or even receives a radial load during operation, it does not have a single bearing (in this example, the output This means that only a load of 1/3 or less of the radial load during operation received by the shaft ball bearing 88) is received. Specifically, in this embodiment, the dummy ball bearing 90 includes an inner ring 90A, an outer ring 90B, and a rolling element 90C, but the inner ring 90A or the outer ring 90B (in this example, the outer ring 90B) is a clearance fit. . Then, when a radial load is applied during operation from the output shaft 39 side, the dummy ball bearing 90 is not subjected to the load (operation in which the radial load during operation received by the dummy ball bearing 90 is received by the output shaft ball bearing 88). The dimension of the dummy ball bearing 90 (gap on the outer ring 90B side) and the like are set so that the radial load is 1/3 or less of the radial load at that time.

  With this configuration, the output shaft 39 of the speed reducer 14 can be maintained in a more stable state that is substantially equivalent to the two-point support during transport or assembly (when not in operation). Can be further enhanced.

  Since the inner ring 90A or the outer ring 90B (in this example, the outer ring 90B) is incorporated with a clearance fit, the dummy ball bearing 90 receives almost no radial load during operation. The agitation shaft 56 is effectively supported by the two-point support of the output shaft ball bearing 88 and the gantry ball bearing 66, and stable rotation without shaking is possible. In this embodiment, the dummy ball bearing 90 has the same configuration as that of the output shaft ball bearing 64 of the previous embodiment except that the outer ring 90B is a clearance fit. The output shaft ball bearing 88 and the dummy ball bearing 90 can be used.

  Since other configurations are the same as those of the previous embodiment, the same reference numerals are given to the members of the same or similar parts in the drawings, and the duplicated description is omitted.

  Next, the embodiment shown in FIG. 4 corresponds to a modification of FIG.

  In the modified example of FIG. 4, the dummy slide bearing 94 is disposed on the outer side (axial load side) of the speed reducer 14 than the oil seal 73 that seals the lubricant in the speed reducer 14. The output side cover 96 has a configuration similar to that of the output side cover 52 in the previous embodiment, and includes a first inner flange portion 96C and a second inner flange portion 96D. However, the locking block 80 existing in FIGS. 1 and 3 is not provided.

  The dummy sliding bearing 94 is made of resin, and the inner peripheral sliding surface 94A is opposed to the collar 95 fitted on the output shaft 39 with a slight gap. The dummy slide bearing 94 includes a step portion 96D1 formed on the second inner flange portion 96D of the output side cover 96 (a flange portion corresponding to the second inner flange portion 52D of the previous embodiment), and the second inner flange portion. Movement in the axial direction is restricted by a retaining ring 98 incorporated in 96D. The dummy slide bearing 94 is incorporated in the output shaft 39 when the speed reducer 14 is stored in stock or transported, but is removed when the speed reducer 14 is transported and installed on the stirring device 10. It has become so.

  Similarly to the previous embodiment, the output shaft ball bearing 88 has an inner ring 88A, an outer ring 88B, and a rolling element 88C, and supports the output shaft 39 as “one bearing”. However, in this embodiment, since the dummy slide bearing 94 is removed during operation, the dummy slide bearing 94 does not receive the thrust load of the output shaft 39 during operation as in the dummy ball bearing 90 of the previous embodiment. Can not. Therefore, a projection 96C1 projecting radially inward is provided on the axial load side of the first inner flange portion 96C of the output side cover 96 so as to contact the outer ring 88B of the output shaft ball bearing 88 and the inner ring 88C is made to be a carrier. By abutting against the lower end of the flange 38, the thrust load of the output shaft 39 can be received, and the output shaft ball bearing 88 is prevented from coming off.

  In other words, in this embodiment, the assembly of the drive device 62 of the stirring shaft 56 is performed as follows.

  a) The output shaft 39 of the speed reducer 14 is in a state where one output shaft ball bearing 88 and a dummy slide bearing 94 are initially incorporated. Stock storage and transportation of the speed reducer 14 are performed in this state. B) At the stage where the stirrer 10 is installed, the retaining ring 98 is removed from the second inner flange portion 96D and the dummy slide bearing 94 is removed at the stage where the speed reducer 14 is installed on the gantry unit 16 of the stirrer 10 To do. Since the dummy slide bearing 94 is arranged on the outer side in the axial direction of the speed reducer 14 than the oil seal 73 that seals the lubricant in the speed reducer 14, the dummy slide bearing 94 is reduced even if the dummy slide bearing 94 is removed. The lubricant in the machine 14 does not leak out. When assembling the reducer 14 to the gantry unit 16, c) by pressing both the output shaft 39 and the stirring shaft 56 of the reducer 14 from both sides in the axial direction of the press-fitting holes 68 </ b> A of the single joint shaft 68. The output shaft 39 and the stirring shaft 56 are coupled so as not to be relatively movable in the radial direction. D) The load side end portion of the stirring shaft 56 integrated with the output shaft 39 is supported by one pedestal ball bearing 66 arranged on the gantry cover 60 of the gantry unit 16.

  As a result, the output shaft 39 and the stirring shaft 56, which are finally connected so as not to move relative to each other in the radial direction, are connected by one output shaft ball bearing 88 at the output shaft 39 portion and one at the stirring shaft 56 portion. It can be assembled in a state where it is supported at two points by the gantry ball bearing 66.

  It should be noted that the steps c) and d) are reversed so that the output shaft 39 and the stirring shaft 56 are connected after the stirring shaft 56 is first supported by the mounting unit ball bearing 66 on the mounting unit 16. It may be.

  According to the present embodiment, the output shaft 39 of the speed reducer 14 is stock-stored or transported while being supported at two points by the output shaft ball bearing 88 and the dummy slide bearing 94, so that the speed reducer 14 is a single product. Can be handled in a stable state. Further, even if a somewhat shocking external force is applied to the output shaft 39 during conveyance or the like, the impact can be received by the output shaft ball bearing 88 and the dummy slide bearing 94. Therefore, it is possible to prevent the shocking external force from being applied to the meshing portion of the external gear 28 and the internal gear 30 of the speed reducer 14 as it is.

  Since the dummy slide bearing 94 is removed when the speed reducer 14 is in operation, the integrated output shaft 39 and stirring shaft 56 are completely supported by the output shaft ball bearing 88 and the gantry ball bearing 66 only. Therefore, stable support can be maintained.

  In the above embodiment, a ball bearing or a sliding bearing is adopted as the dummy bearing. However, in the present invention, the dummy bearing is basically compared with the original “one bearing” that supports the output shaft. Any member that is assembled so as not to receive a radial load during operation (even if it is received, “one bearing” is 1/3 or less of the radial load received during operation) may be used. That is, the specific configuration of the dummy bearing is not particularly limited.

  For example, even when a sliding bearing is used, the material is not necessarily a metal (since it is not intended to receive a load or moment), and a material other than metal, such as resin or rubber. It may be configured. In particular, as in the embodiment of FIG. 4, in the case of the dummy bearing removed at the time of assembly, it receives no load or moment during operation, so it absorbs more shock due to external load during inventory storage or transportation. In order to be able to do so, you may make it comprise with soft members, such as rubber | gum.

  In the above embodiment, the rotating device includes a reduction gear having an eccentric rocking planetary gear reduction mechanism, and the structure of the reduction mechanism is such that the output shaft does not fluctuate greatly. In general, when a planetary gear speed reduction mechanism is employed as the speed reduction mechanism, the fluctuation of the output shaft can be suppressed to some extent at the speed reduction mechanism. Therefore, when the rotating device according to the present invention includes a speed reducer, the speed reduction mechanism of the speed reducer (in the case of a multistage speed reducer, particularly as the speed reduction mechanism in the final stage) is an eccentric oscillation type, simple planetary It is preferable to employ a planetary gear reduction mechanism such as a mold. As a result, even if there is only one bearing that supports the output shaft, it is possible to prevent the output shaft from wobbling significantly, including during inventory storage or transportation.

  However, the speed reduction mechanism of the speed reducer is not necessarily a planetary gear speed reduction mechanism, and may be, for example, a parallel shaft gear speed reduction mechanism, an orthogonal shaft gear speed reduction mechanism, or the like. Alternatively, a speed reduction mechanism that does not have a gear, such as a pulley mechanism or a traction drive mechanism, may be used (the type of speed reduction mechanism is not limited). In particular, in the case where a dummy bearing is provided, the support function of the dummy bearing can avoid the problem of wobbling during inventory storage and transportation, so that various speed reduction mechanisms can be freely employed.

  In addition, the rotating device is not limited to the configuration of a motor and a speed reducer, and may be a rotating device that includes only a motor and does not include a speed reducer.

DESCRIPTION OF SYMBOLS 10 ... Stirring device 11 ... Rotating device 12 ... Motor 14 ... Reduction gear 16 ... Mounting unit 39 ... Output shaft 52 ... Output side cover 56 ... Stirring shaft 60 ... Mounting shaft cover 62 ... Stirring shaft drive device 64 ... Output shaft ball bearing 66 ... Trading ball bearings 68 ... Joint shaft 90 ... Dummy ball bearings 94 ... Dummy sliding bearings

Claims (5)

In the stirrer shaft drive device for connecting the stirrer shaft to the output shaft of the rotating device and rotating the stirrer shaft,
The output shaft and the agitation shaft are connected so as not to be relatively movable in the radial direction,
The output shaft is supported by a single bearing, and the stirring shaft is supported by a single bearing. In claim 1,
In addition to the one bearing that supports the output shaft of the rotating device, a dummy bearing that is incorporated in the output shaft is included, and the dummy bearing may or may not receive a radial load during operation. A stirring shaft driving device characterized in that it is a member that receives only a radial load equal to or less than 1/3 of the radial load during operation received by the one bearing. In claim 2,
The stirrer shaft drive device, wherein the dummy bearing has an inner ring or an outer ring incorporated with a clearance fit. In claim 2 or 3,
The stirrer shaft drive device, wherein the dummy bearing is disposed outside the rotation device rather than an oil seal that seals the lubricant in the rotation device. In the assembling method of the drive device for the stirring shaft for connecting the output shaft of the rotating device and the stirring shaft to rotationally drive the stirring shaft,
Incorporating one bearing and a dummy bearing into the output shaft;
Removing the dummy bearing;
Connecting the output shaft and the agitation shaft in a radially unmovable manner;
Supporting the agitation shaft with a single bearing;
A method for assembling a stirring shaft driving device.

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