JP3078973B2 - transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission which is connected to a motor shaft for reducing or increasing the speed of, for example, a geared motor.

[0002]

2. Description of the Related Art Transmissions that transmit drive by changing the rotation of a motor shaft have been used. In general, these transmissions change the speed using gears such as a planetary gear mechanism. Here, the gear backlash for put that circle smooth drive transmission meshing of the teeth are formed. However, on the one hand, the backlash causes a delay in the amount of rotation, so that the rotation tends to be transmitted incorrectly. Therefore, in the transmission, the gear is divided into two in the direction perpendicular to the axis of the rotation axis, meshed with the gear on the other side to check the backlash, and the backlash is eliminated by shifting the phase of both divided tooth bodies by the gap of the backlash. Technology has been proposed.

[0003]

However, in some transmissions, a lid is formed at the end of the assembling process to complete the transmission. In such a model, when the assembly is completed, the gear is already hidden inside the lid, so the operation of shifting the tooth body cannot be performed as described above, and the backlash of the gear formed on the lid body can be eliminated. Did not.

[0004] It is an object of the present invention to provide a transmission capable of removing the backlash of a gear formed on the lid from the outside after the transmission is fitted with a lid and closed.

[0005]

In order to solve the above-mentioned problems, the present inventor has proposed in the invention of claim 1 that the input shaft is formed on the input shaft.
The decentered publicly on the rotary shaft with respect to the axis of rotation of the sun gear
A planetary gear that rotates, wherein a first tooth body of the planetary gear is
At the input shaft side, it meshes with a part of the tooth body of the sun gear,
The second tooth body of the planetary gear is provided with an opening of the transmission on the output shaft side.
Part of the ring gear body attached to the lid closing the part
And the first of the planetary gears
The tooth body of the sun gear or the tooth body of the sun gear is aligned with the rotation axis of the input shaft.
In contrast, it is divided into two parts in the vertical direction.
That the relative phase of the divided two tooth bodies can be changed
In addition, the tooth body of the ring gear has a relative phase change between the two tooth bodies divided into two in a direction perpendicular to the rotation axis of the output shaft.
And a second adjusting mechanism provided on the lid.
The relative phase of the divided two tooth bodies changes from outside the transmission.
The configuration is such that it can be changed.

[0006]

According to the first aspect of the present invention, the ring gear mounted on the lid by operating the second adjusting mechanism from outside after the transmission is closed by mounting the lid. division of the
Of the planetary gear that meshes by changing the relative phase of the
The backlash between the teeth of the vehicle can be eliminated. Ma
In addition, the backlash between the sun gear in which the transmission is already disposed and the first tooth body of the planetary gear can be eliminated by operating the adjustment mechanism.

[0007]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the transmission according to the present invention will be described below in detail with reference to the drawings.

As shown in FIG. 1, an input shaft 2 of a speed-up gear 1 serving as a transmission is connected to a motor shaft (not shown) so that drive from a motor is transmitted and rotation is transmitted to an output shaft 3 side. I have. In the following description, the input shaft 2 side is referred to as a rear side, and the output shaft 3 side is referred to as a front side. The input shaft 2 is inserted through an insertion hole 5 formed in a base end 4 a of the input shaft frame 4, and is rotatably supported by a bearing 6. The input shaft frame 4 has a forwardly bulging portion 4b formed so as to cover the inserted input shaft 2 and the planetary gear 8 disposed in front of the input shaft 2. A mounting leg 9 is formed. Base end 4a of input shaft frame 4
A lid 10 is fixed by bolts 11 to close the insertion hole 5. An oil seal 12 is interposed between the lid 10 and the input shaft 2.

At the tip of the input shaft 2, a sun gear 15 bulging into a disk is formed. The sun gear 15 is divided into two front and rear parts in a direction perpendicular to the axis of the input shaft 2 to form sun gear divided bodies 15a and 15b.
As shown in FIGS. 1 and 4a and 4b, the front sun gear split 15a is formed integrally with the large diameter portion 16 of the sun gear 15, and the rear sun gear split 15b is formed with the small diameter of the sun gear 15 . It is rotatably fitted to the outer periphery of the portion 17. On the outer periphery of both sun gear divided bodies 15a and 15b, divided tooth bodies 1 are respectively provided.
8a, 18b are formed, and the two tooth bodies 18a, 18b
Have the same height (ring diameter).

As shown in FIGS. 4a, 4b and 6, the end face of the rear sun gear segment 15b has a slot 1 extending in the circumferential direction.
9 is provided at a position corresponding to the elongated hole 19 and a large-diameter portion 16 of the sun gear 15 (sun gear split body 15a).
A bolt hole 20 is screwed into the end face. An adjustment bolt 21 with a hexagonal hole is screwed into the bolt hole 20 via a washer 22 from outside the same long hole 19, and the divided tooth body 15 b is fastened to the large diameter portion 16. I have. That is, the sun gear divided body 15b rotates relatively to the sun gear divided body 15a, and can adjust the relative phase of the divided tooth body 15b with respect to the divided tooth body 15a.

An output shaft 3 is provided in front of the input shaft 2. The output shaft 3 is supported via a bearing 24 in a concave portion 23 formed on the inner peripheral side of the sun gear 15 at the base end. The output shaft 3 is supported by a bearing 26 of an output shaft frame 25 near its front end, and the front end protrudes outward from a through hole 25 a formed in the output shaft frame 25. Note that an oil seal 27 is interposed between the tip of the output shaft 3 and the through hole 25a. A large-diameter disk-shaped large-diameter trunk portion 3a is formed on the trunk portion of the output shaft 3, and the large-diameter trunk portion 3a is formed.
The planetary gear 8 is rotatably mounted on the outer periphery of the member a through a bearing 28. A thrust ring 29 is provided in front of the bearing 28.
Is interposed. The large-diameter trunk portion 3a is a large-diameter disc formed eccentrically with respect to the axis of the output shaft 3, and rotates the planetary gear 8 at a position eccentric with respect to the input shaft 2 and the output shaft 3. Has become. A pair of balance weights 30 and 31 are attached before and after the large-diameter trunk portion 3a of the output shaft 3 is sandwiched. The balance weights 30, 31 are boss-shaped cylinders formed with insertion holes 30a, 31a eccentric with respect to the axis of the output shaft 3, and at positions where they cancel each other with respect to the eccentric position of the large-diameter body 3a. The output shaft 3 is mounted so as to balance the rotation. A regulation pipe 33 for regulating the distance is mounted between the front balance weight 30 and the bearing 26 mounted on the output shaft frame 25.

A flange 34 bulging in a key shape in cross section is formed on the rear outer peripheral side of the planetary gear 8, and a disk-shaped gear body 35 is formed on the front outer peripheral surface. A first tooth body 36 is formed on the inner peripheral surface of the flange 34 along the circumferential direction. The inner diameter of the first tooth body 36 is the sun gear 1
5, the first tooth body 36 and the divided tooth bodies 18a and 18b of the sun gear 15 mesh with some of the tooth bodies as shown in FIG. ing. Here, since the planetary gear 8 rotates about an axis eccentric to the center axis of the input shaft 2 (the axis indicated by the line AA in FIG. 1), as shown in FIG. It is designed to mesh with only some of the divided tooth bodies 18a and 18b. Then, the planetary gear 8 orbits the outer periphery of the rotating sun gear 15 due to the shift of the rotation center. As shown in FIG. 4B, the divided tooth body 18a on the front side of the sun gear 15 is
A backlash p is formed between the two teeth 18a, 36 in a state where the tooth 36 comes into contact with the left wall surface 36a in the drawing. On the other hand, in a state where the rear divided tooth body 18b of the sun gear 15 is in contact with the right wall surface 36b in the drawing of the first tooth body 36, a backlash q is formed between the two tooth bodies 18b and 36. I have. Since the divided tooth bodies 18a and 18b are fixed with a relative shift by this phase,
As a result, the backlashes p and q of each other are canceled.

On the outer periphery of the gear body 35 on the front side of the planetary gear 8, a second tooth body 40 is formed along the circumferential direction. The second tooth body 40 meshes with the divided tooth bodies 39a and 39b of the ring gear 38 formed on the frame flange 37 of the output shaft frame 25. The ring gear 38 is mounted on the output shaft frame 25 behind the frame flange 37. As shown in FIGS. 1 and 5a and 5b, the ring gear 38 is divided into two parts in the direction perpendicular to the axis of the output shaft 3, and the inner peripheral surfaces of the two divided ring gear divided bodies 38a and 38b. Along each tooth 3
9a and 39b are formed. The front ring gear segment 38a is fixed to the frame flange 37 by bolts 42, and the rear ring gear segment 38b is rotatably mounted behind the front ring gear segment 38a. The tooth heights (ring diameters) of the divided tooth bodies 39a and 39b of the two ring gear divided bodies 38a and 38b are the same. The inner diameter of the teeth 39a and 39b of the ring gear 38 is larger than the outer diameter of the second tooth 40.

Here, the planetary gear 8 rotates about the axis eccentric with respect to the input shaft 2 as described above (A-
(A line), so as to always mesh with only a part of the divided tooth bodies 39a and 39b as shown in FIG. Then, the planetary gear 8 orbits the inner periphery of the fixed ring gear 38 due to the shift of the rotation center.

As shown in FIGS. 5A and 5B and FIG.
A long hole 43 as an adjusting mechanism extending in the circumferential direction is provided in the end face of the ring gear segment 38a on the side of the front side and the front side, and the output shaft frame 25 is located at a position corresponding to the long hole 43. A long hole 44 as an adjusting mechanism corresponding to the frame flange 37 is also provided. On the other hand, a bolt hole 45 as an adjustment mechanism is screwed into the ring gear segment 38b on the rear side. A hexagonal adjustment bolt 46 as an adjustment mechanism is screwed from the front of the output shaft frame 25 via a washer 49, and the rear side ring gear split 38a with respect to the output shaft frame 25 and the front ring gear split 38a. Body 38
b. That is, by operating the adjustment bolt 46, the divided tooth body 39b is
Is rotated in the circumferential direction along the long holes 43 and 44, so that the relative phases of the teeth of the two tooth bodies 39a and 39b can be adjusted.

As shown in FIG. 5B, in a state in which the divided tooth body 39a on the front side of the ring gear 38 is in contact with the left side wall 40a of the second tooth body 40 in the figure, there is a gap between the two tooth bodies 39a, 40. A backlash r is formed. On the other hand, a backlash s is formed between the two tooth bodies 39b and 40 in a state where the divided tooth body 39b on the rear side of the ring gear 38 is in contact with the right side wall 40b in the drawing of the second tooth body 40. . Double split tooth body 39
Since a and 39b are relatively shifted and fixed by this phase, the backlashes r and s of each other are offset as a result.

The output shaft frame 25 serving as a lid is mounted in front of the bulging portion 4b of the input shaft frame 4. Frame flange 3 formed rearward of output shaft frame 25
Reference numeral 7 is fitted to the bulging portion 4b of the input shaft frame 4 .
As shown in FIG. 2, the output shaft frame 25 is fastened together with the input shaft frame 4 from above by a fixing screw 47, and is fastened to the input shaft frame 4 from below by a rotation preventing bolt 48 from the front. . An oil inlet 50 for injecting lubricating oil is formed in an upper portion of the input shaft frame 4, and a drain 51 for draining oil is formed in a lower side of the input shaft frame 4.

Next, the operation of the speed increasing gear 1 of this embodiment will be described. The input shaft 2 is mounted on the input shaft frame 4, while the planetary gear 8 and the balance weights 30 and 3 are mounted on the output shaft 3.
1. After installing the restriction pipe 33 etc. in advance, the input shaft
Connect to 2 . At this stage, the planetary gears 8 are adjusted by adjusting the divided tooth bodies 18a and 18b of the sun gear 15 of the input shaft 2 as follows.
The backlash generated between the first tooth body 36 and the first tooth body 36 is eliminated. That is, the sun gear 15 and the first tooth body 36 of the planetary gear 8 are engaged with each other, and the divided tooth body 18b on the rear side of the sun gear 15 is rotated with the adjustment bolt 21 loosened. Then, the relative phases between the divided tooth bodies 18a and 18b are shifted, and the divided tooth body 18a on the front side contacts the left side wall 36a of the first tooth body 36. On the other hand, the rear divided tooth body 18b is the first
Abuts against the right side wall 36b of the tooth body 36 of the
The backlash between the teeth 36a and 18b is eliminated.

Next, the adjusting bolt 21 is tightened to fix the divided tooth bodies 18a and 18b. Finally, output shaft frame 2
5 is attached to the output shaft 3 through the through hole 25a, and the assembly is completed with the fixing screw 47 and the rotation preventing bolt 48. At this stage, the ring gear 38 attached to the output shaft frame 25
The relative phases of the divided tooth bodies 39a and 39b are not shifted,
The phases are almost the same. Therefore, the second of the planetary gear 8
With the tooth body 40 while having a backlash.

Next, after the assembling of the gearbox 1 is completed, by operating the adjusting bolt 46 having a hexagonal hole protruding from the output shaft frame 25, the two divided tooth bodies 3 of the ring gear 38 are operated.
The relative phases of 9a and 39b are shifted to eliminate the backlash between the planetary gear 8 and the second tooth body 40. That is, when the ring gear 38 and the second tooth body 40 of the planetary gear 8 are engaged with each other, the adjusting bolt 46 screwed to the rear divided body 38b is operated to rotate the rear divided body 38b in the circumferential direction. To do. Then, both divided tooth bodies 39a, 39b
And the front divided tooth body 39a contacts the left side wall 40a of the second tooth body 40. On the other hand, the rear divided tooth body 39b abuts on the right side wall 40b of the second tooth body 40, and there is no backlash between the two divided tooth bodies 39a and 39b with respect to the tooth body 40. Next, the divided body 3 in the loosely fitted state
8b with the adjustment bolt 46 to separate the two divided bodies 38a, 38
8b and the output shaft frame 25 are fastened together. With such a configuration, the following effects can be obtained. (I) The backlash between the ring gear 38 and the second tooth body 40 of the planetary gear 8 can be eliminated from the outside after the output shaft frame 25 is mounted and the assembling of the gearbox 1 is completed. Therefore, even with the speed increaser 1 in which the ring gear 38 and the output shaft frame 25 to be mounted last are integrated, the problem of backlash can be solved. Also, the ring gear 3
Since it is not necessary to mount 8 before the output shaft frame 25, components such as a mounting bracket for the ring gear 38 are not required, and the assembling process is simplified, so that the manufacturing cost is reduced. (Ii) a planetary gear mechanism of a type in which only one planetary gear 8 meshes with the sun gear 15 and the ring gear 36;
It is easier to assemble than a type having a plurality of planetary gears. (Iii) The lubricating oil injected from the oil inlet 50 is stored below the inside of the transmission to lubricate the planetary gear mechanism.
Since the adjusting bolt 46 of the ring gear 38 is mounted on the side of the output shaft 3, this lubricating oil does not leak from the bolt hole 45.

Although the embodiment of the present invention has been described in detail, the present invention is not limited to the above-described embodiment, and may be embodied in other modes as described below. (1) The backlash between the sun gear 15 and the first tooth body 36 of the planetary gear 8 in the above embodiment is the same as the sun gear 15
The divided bodies 15a and 15b were formed to solve the problem. But,
As shown in FIG. 8, the first tooth body 3 of the planetary gear 8 is reversed.
6 may be divided into divided bodies 60a and 60b, and divided tooth bodies 61a and 61b may be formed on the divided bodies 60a and 60b, respectively, so as to mesh with the tooth bodies 62 formed on the outer periphery of the sun gear 15.

In the above embodiment, the divided teeth 18a and 18b of the sun gear 15 face outward, and the first teeth 36 formed on the flange 34 of the planetary gear 8 face inward. However, as shown in FIG. 9, the sun gear 15 is formed with a flange 63 bent in a channel shape in cross section, and the divided tooth body 6 is formed.
4a and 64b may be formed inward. The first tooth body 36 meshing with the divided tooth bodies 64a and 64b is formed outward with respect to the flange 34 of the planetary gear 8. In addition, the present invention can be implemented by changing the form of the gearbox 1 of the type in which the ring gear 38 and the output shaft frame 25 also serving as a closing cover are integrated and have one planetary gear 8. Is free. (2) In addition, the backlash elimination mechanism on the side of the sun gear 15 may not be necessarily provided, and the mounting position of the adjustment bolt 46 may not necessarily be on the side of the output shaft 3. The present invention can be freely modified and implemented without departing from the spirit thereof, for example, the input and output may be reversed.

[0023]

As described in detail above, according to the present invention , the input shaft
A planetary gear that revolves on a rotation axis that is eccentric to the rotation axis of the sun gear formed on the first planetary gear.
When the teeth mesh with a part of the teeth of the sun gear on the input shaft side
In both cases, the second tooth body of the planetary gear is shifted on the output shaft side.
Of the ring gear attached to the lid closing the opening of the machine
Said planetary teeth while being configured to mesh with a part of the body
The first tooth of the car or the tooth of the sun gear is connected to the rotation of the input shaft.
The first adjusting mechanism is divided into two parts in a direction perpendicular to the axis of rotation.
Can change the relative phase of the divided two teeth.
In addition, the tooth body of the ring gear is
A second adjusting device provided on the lid, wherein the relative phase of the two teeth divided into two in the direction perpendicular to the rotation axis can be changed;
The relative phase of the two teeth divided by the structure is outside the transmission.
The backlash can be eliminated even after the assembly by operating the second adjusting mechanism from the outside.

[Brief description of the drawings]

FIG. 1 is a cross-sectional plan view of a speed increaser according to an embodiment of the present invention.

FIG. 2 is a partially cutaway front view of the speed increaser of the same embodiment.

FIG. 3 is an exploded perspective view for explaining a member of a main part of the speed increaser in the same embodiment by disassembling and explaining the member.

FIGS. 4A and 4B are explanatory diagrams illustrating a main part of the adjustment mechanism in the same embodiment, where FIG. 4A is an enlarged sectional plan view of the adjustment mechanism, and FIG.

FIGS. 5A and 5B are explanatory views illustrating a main part of the adjustment mechanism in the same embodiment, where FIG. 5A is an enlarged sectional plan view of the adjustment mechanism and FIG.

FIG. 6 is a front view of the speed increasing device of the same embodiment as viewed from line BB.

FIG. 7 is a front view of the speed increaser of the same embodiment as viewed from the line CC.

FIG. 8 is a side sectional view of a main part for explaining another embodiment.

FIG. 9 is a side sectional view of a main part explaining another embodiment.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Gearbox as a transmission, 8 ... Planetary gear, 15 ... Sun gear, 18a, 18b ... Split tooth body, 43 ... Long hole as an adjusting mechanism, 19 ... Long hole as an adjusting mechanism, 20 ... Bolt hole as an adjusting mechanism , 21 ... Adjustment bolt as an adjustment mechanism, 25 ... Output shaft frame as a lid, 38 ... Ring gear, 39a, 39b ...
Divided teeth 43, long holes serving as an adjusting mechanism, 44 long holes serving as an adjusting mechanism, 45 bolt holes serving as an adjusting mechanism, 46 adjusting bolts serving as an adjusting mechanism.

Claims (1)

(57) [Claims] 1. A sun gear (1 ) formed on an input shaft (2).
5) Play that revolves on a rotating shaft eccentric to the rotating shaft
A star gear (8), a first tooth body of the planetary gear (8)
(36) is the tooth body of the sun gear (15) on the input shaft (2) side
And a second part of the planetary gear (8).
Of the transmission (1) on the output shaft (3) side.
Ring gear mounted on lid (25) for closing the mouth
(38) is configured to mesh with a part of the tooth body (39).
While the first tooth body (36) of the planetary gear (8) or
Is the tooth of the sun gear (15), the rotation of the input shaft (2)
The first adjusting mechanism is divided into two parts in a direction perpendicular to the axis.
(19, 20, 21)
The relative phase can be changed, and the tooth body (39) of the ring gear (38) is divided into two teeth in a direction perpendicular to the rotation axis of the output shaft (3). (39a, 3
The relative phase of 9b) can be changed, and is set on the lid (25).
To the second adjustment mechanism (43, 44, 45, 46)
Therefore, the relative positions of the divided two tooth bodies (39a, 39b)
A transmission characterized in that the phase can be changed from outside the transmission (1) .