JPS6088248A - Power uniform-distributing gearing device employing conical shaft and gear thrust balancing device - Google Patents

Abstract

PURPOSE:To enable uniform application of a load on each planetary gear and to prevent the generation of vibration noise, by a method wherein a plurality of planetary gears, engaged with a central gear on an input shaft, are axially movably mounted on their respective conical shaft secured to a carrier formed integrally with an output shaft. CONSTITUTION:When a device is mounted to the reduction mechanism of a geared motor, 3 conical shafts 8 are secured at equal distances to one side of a carrier 6 formed integrally with an output shaft 7, and the forward end of each shaft 8 is fastened to a support plate 9. The support plate 9 is provided at the center of an internal surface with a spherical recess surface 10, and a thrust receiving plate 11 having a spherical projection surface 12 is attached in the recess surface 10. 3 spherical recess surfaces 13 are provided in the other side surface of the thrust receiving plate 11, a gear 5, engaged with each conical shaft 8 with a play, is energized by a spring 16 to press the gear against the recess surface 13 through a spherical seat metal 14. Further, the gear 5 is located so that it is engaged with a central gear 3 of a motor shaft (input shaft) 2 and a moving internal gear 4.

Description

[Detailed Description of the Invention] Technical Field This invention is applicable to, for example, the J of the Yu B1M Car Souni, the Uni Yu! This invention relates to a power equalization device that can equally distribute transmitted power to a plurality of tooth widths in a tooth width device in which a plurality of gears are meshed with a No. 11 gear.

BACKGROUND OF THE INVENTION Conventionally, as an example of this type of gear device, there is a geared motor speed reduction mechanism as shown in FIG.

In this reduction mechanism, a motor shaft 2 supported in a motor case 1 is interlocked with an external tooth if 3 as a thick gear, and three planetary teeth are provided between the external gear 3 and a fixed internal gear 4. lu
5, a carrier 6 rotatably supporting the loose tooth width 5 is interlocked with the output shaft 7. In this planetary gear arrangement, as shown in FIG. 2, the distance between the centers of each planetary gear 5 -i 11 , l# and the distance between each planetary gear 5 and the center of the external tooth 3, v+r ra l-2, are completely If they match, 5 out of 8 planetary teeth will be equally distributed, so each gear 3. /1.
5 teeth (if the difference is h), the 0 teeth are engaged on average with each M star gear 5, and 3.4°5 out of 8 teeth exhibits the expected strength.
&Q 1FIJ No noise is generated, but in reality, 11 above. It is difficult to make L2 completely coincident with each other because there is always an error in the bearing part of each coasting gear 5 and the tooth widths 3, 4, and 5, so this equal distribution is actually very difficult. The development of an effective motion equalization device is a major technical challenge.
be.

1] The object of the present invention is to provide (1 load) in each planet 1ψ1 that meshes with a plurality of gears that mesh with each other around the center tooth width; for example, as described above, that meshes with an external gear that has By configuring it so that it spreads evenly, it is possible to reduce vibration and noise by reducing the width of the tooth width mechanism, while also reducing vibration and noise by 4ft! be.

A1) The present invention achieves this object by assembling a plurality of gears 5 meshing with the central gear 3 so as to be movable in the axial direction on a circular shaft 8, respectively. The balancing device 1'1.18A, 188, 20.26.30, etc.3L35 is used so that the 111 force generated in the tooth width 5 group toward the small diameter end of the conical shaft becomes γi.
36 and 38 were set up. To outline the principle, if a rotational force is applied to a plurality of gears 5, then
Since a thrust is generated in the direction of the small diameter conical shaft in proportion to the size, the thrust is made equal (t5cJ), the rotational force acting on the gear 5 is also equal, and the power is equally distributed. Since a plurality of gears 5) are mounted on the circular shaft 8F, if these gears move toward the large diameter end of the circular shaft 8, the bearing clearance S becomes smaller, and the circular shaft 8F becomes smaller. el is smaller than the piece of gear 5 from the center line of gear 5,
is moved against the driving direction as shown by arrow A in FIG. 12, and the power share increases. Conversely, if the gear 5 moves toward the smaller diameter of the circular shaft ε3, the bearing clearance S increases,
Since C2 of the gear 5 from the center line of the circular shaft 8 becomes more sensitive, the teeth 115 escape in the driving direction as shown by the arrow A in FIG. 14, so that the power sharing is reduced. In this invention, the Jlt force changes in proportion to the size of the power sharing, using the Saga, which has a small tooth width of 5, ? l"J small gear 5 LJ (force balancing device pushes toward the large diameter end of the conical shaft, gear 5 moves toward the large diameter end of the conical shaft, In addition, the large gear 5 of the power valve 113, that is, the gear 5 with a large thrust, is pushed toward the small diameter end of the conical shaft by the force balancing device 11L, so that the gear 5 is pushed toward the small diameter end of the conical shaft 1111. The C1 power is equally distributed by making the thrust of the plurality of gears 5 equal, thereby reducing the power sharing.

EXAMPLE Hereinafter, a first embodiment of the present invention in which the present invention is embodied in a 7-gear overnight speed reduction mechanism shown in FIG. Three circular shafts 8 are attached to one side of the rear 6.
It sticks at 11 intervals, and the tip of A is Q: ni L; L! 4'r
! 5.6 The receiving plate 9 is fixed as shown in Figure 6. This receiving plate 9 is provided with a spherical concave surface 10. The force receiving plate 11 has a spherical convex surface 12 on the spherical concave surface 10 side of the receiving plate 9 as shown in FIG. A spherical concave surface 13 on the opposite side of the convex surface 12
There are three spherical washers 1 on the four spherical surfaces 13.
4 is fitted, and this is brought into contact with the tooth Φ5. A washer 15 is installed on the opposite side of the gear 5, and a coil spring 16 for removing play is installed between the gear 5 and the rear wheel 6.

In such a configuration, if there is a difference in the thrust toward the small diameter end of the conical shaft of the three gears 5, the thrust receiving plate 11 will swing freely, and the gear 5) with the larger thrust will move toward the small diameter end of the conical shaft. Moving toward the end, the gear 5 with the smaller thrust is pushed toward the large diameter end of the envelope 111.

As mentioned above, if the round shaft 8 is moved toward the small diameter end of the shaft 8, the power sharing will be reduced by 1, and the force will also be smaller. As C moves toward the large diameter end of the circular shaft 8, the moving horn component 11] increases and i
The ff force is also large, and when the 111 forces become equal, the power sharing becomes equal, and the power is equally distributed.

Furthermore, the variation in power sharing due to the axial movement of the gear 5 will be explained in detail based on FIGS. 9 to 14.

The position e of vA115, which is not shown in FIG. 9, is indicated by the arrow El in FIG.
] The center of the gear 5 is eQ from the center of the circular shaft 8 in the drive direction shown by A (proceeds by 5).

At the position of the mountain 5 shown in FIG. 11, where the zigzag 15 gear 5 has moved to the large diameter end of the conical shaft 8, the bearing clearance S becomes smaller and the conical gear 5 moves in the drive direction shown by the arrow in FIG. axis 8
The distance from the center of gear 5 to the center of gear 5 becomes el and becomes small. Since the gear 5 moves against the driving direction,
The power sharing increases, and the 111 force generated in the gear 5 due to the round shaft with a small diameter becomes smaller.

As shown in Figure 13 (di I position, that is, Minami Junior High School 5)
has moved to the small i end of the circle J axis 8. The distance between the centers of 31 and 31 becomes C2 (it becomes less crowded. Yamanaka 5 moves in the driving direction! Therefore, the mh force 11.1 decreases and I'll'
The thrust force generated in the direction of the small diameter end of the circular shaft 8 becomes smaller.

Furthermore, since the gear 5 drives the conical shaft 8 in the bearing direction indicated by the arrow △ in FIGS. Contact occurs through an oil film.

In the first embodiment, the number of gears 5 is 3 C, and the bearing 1 has a tooth width of 5.
7. This is the case when a sliding bearing is adopted, but the first
In the second embodiment shown in FIGS. 5 to 24, the number of gears 5 is four, a thrust ball bearing (q sword roller bearing) is adopted as the bearing 17 of the gear 5, and 111 force balancing is performed. The device is a combination of levers 18a, 18b, and 20 with the center as a fulcrum.

At No. 164, the 111 force generated in the gear 5 toward the small diameter end of the circular shaft is transmitted by the spherical washer 14 to the first levers 18a and 18b shown in FIGS. 19 and 20.

The first levers 18a and 18b have a spherical convex surface 19 provided in the center as shown in FIG. 18, and are fitted into the spherical concave surface 21 of the second lever 2o as shown in FIGS. This 2
0 is a spherical convex surface 22 provided at the center as shown in FIGS. 16 and 17, and a receiving plate 23 shown in FIGS. 23 and 24 is fixed to the Kirelia 6 via a circular shaft 8. It is inserted into the spherical concave surface 24 of .

Therefore, in Fig. 15, Yamanaka 5) Δ's 41 force gear 5
The 18 force of B is balanced by the first lever '1ε1△, and the thrust force of the gear 5C and the it force of the float 5D are the first lever 1
813 will be balanced. And J of gear 5△
lt force and the JIF force of the gear 5] - acts on the connection part 2 (C1 (spherical uneven surface 21.19) between the lever 18Δ and the second lever 20, and the thrust of Yamanaka 5C The force added to the thrust of the gear 5D is applied to the connecting portion 20b (spherical uneven surface 2'l, 19) between the first lever 18B and the second lever 20.
), and the second lever 20 has a medium-heat spherical convex surface 22.
Since it is supported by the receiving plate 23, the force acting on the connecting part 20a of the negative horn and the force acting on the connecting part 20b of the other part j are balanced. Yi no Sung, 4 ffQ
5A, 58, 50, 51) can be balanced, and the power is equally distributed.

Note that 25 shown in FIG. 16 is a disc spring for removing play.

Shown in Figures 25 and 26? +The third embodiment is gear 5
In this case, the thrust generated by the gear 5(,1) is received by the -i('U lever 26 through the spherical washer 14, and this lever 26 is 6 through a cone 8 (supported by the spherical concave surface 29 of the shaft 28, the circle 1 formed on the two gears 5
It is possible to balance the thrust of the small shaft toward the small diameter end, and the power is equally distributed.

In the fourth embodiment C shown in FIGS. 27 and 28, the thrust generated in six gears 5 is divided into three gears 30 and a thrust receiving plate 31 supported swingably ( I decided to divide the balance from 2. Of the 6 gears 5, 2 gears 11 (
force (J each equal to − by 30, the sum h1
A force acts on the center of 30, and the sum of the 4 forces is
Catch it at three places on the 9th board 31. The IWjj receiving plate 31 has its spherical convex surface 32 shaped like a cone 1111 with respect to the carrier 6.
+8 is supported by the spherical concave surface 34 of the fixed receiving plate 33, so it can swing. Therefore, 6
The thrust forces of the gears 5 can be equally covered, and the dynamic JW arrangement is performed.

In the fifth embodiment shown in FIG. 29, the thrust generated in the gear 5 is received by a piston 35, and the piston 35 is fitted into a cylinder 36. The cylinder 3G is fixed to a receiving plate 37 which is fixed to the key 1/rear 6 via a C-circular shaft 8.

In this configuration, the circular J-shaped axis generated in the gear 5 is oriented toward the small diameter end.
The force of perspiration is transmitted to the piston 35 and causes the fluid filled in the cylinder 36 to generate fluid pressure. cylinder 36
The fluid inside can communicate with the fluid inside the cylinder 36 corresponding to the other tooth 1] 5 through the communication pipe 38, so that the fluid pressure inside each cylinder 36 is equal and the horns are also equal. Equal distribution of power is performed.

In this fifth embodiment, a thrust ball bearing needle roller bearing 111 is adopted as the bearing 17 of the mountain shaft 5. 2
51; L Listening to remove slack A:>'7: Yes.

The sixth embodiment shown in FIGS. 30 and 31 is an application of the present invention to a gear device other than the 'M star gear 41'4, in which the 1st gear is fixed at the input @2, the +13 and output shaft 7
A plurality of intermediate gears 5 are meshed between the movable internal gears 4 fixed to the movable internal gears 4, and the intermediate gears 5 are rotatably supported on the fixed support shaft 8. As shown in FIG. It is possible to apply the third embodiment, fourth embodiment, and eleventh embodiment to this gear device.

In each of the above embodiments, the reduction gear device is used as an example, but the input shaft and the output horn shaft can also be used as a speed increase mechanism.

Furthermore, only in the above embodiment, it is also possible to configure the following J.

(B) In the above embodiment, the external gear 3 is formed directly on the motor shaft 2 to interlock the external gear 3 as the center tooth 12 from the Tanabata shaft 2, but the motor shaft 2 and the external gear 3 are It is possible to interpose another interlocking machine between the two. Incidentally, the same applies to the case of interlocking the rear 6 and the output shaft.

(b) Although the m-star gear chain structure is exemplified as a one-stage one, it can also be applied to a two-stage or higher reduction gear.

(c) The direction of the taper of the support shaft 8 can be reversed.

(d) The bearing structure using the spherical convex surface and the spherical concave surface in each of the above embodiments includes a combination with a circular surface ball.

(E) The number of gears 5 is arbitrary as long as it is 2 or more - FLL - and is determined by the number of wheels (the number t of levers).

Effects As mentioned above, according to the present invention, the central tooth! 11
3) +1ili115 that mesh with each other can be moved in the axial direction l\\ to the round shaft 8 earth.
ノ, the circle J axis generated in the south center 5 ICY towards the small diameter end σ)
The JU force is transferred to the above 11 [force balancing device IVi11, 18Δ
1813, 20, 26, 30, 35, 36, 38. In addition to preventing vibration and noise as much as possible, the entire device can be made compact, and it is possible to provide a gear device that has practical effects and can provide power equal distribution performance. ! i@ is an excellent invention.

[Brief explanation of drawings]

Fig. 1 is a sectional view showing a conventional speed reduction mechanism of gear A7-9, Fig. 2 is a schematic diagram showing only the planetary float mechanism part,
Go to Figure 3. Figure 1/i shows the first embodiment, Figure 3 is a front view showing the planetary gear mechanism, Figure 4 is its longitudinal sectional view, and Figure 5
The figure is a front view of the receiving plate, Fig. 6 is a sectional view of the receiving plate, Fig. 7 is an iE side view of the thrust receiving plate, Fig. 8 is a sectional view of the 41f force receiving plate, and Fig. 9 is a round shaft. A partial cross-sectional view showing the center position of the planetary gear above. Figure 10 is a view from the X1-X'I line...i side of Figure 9. Figure 1'1 shows the planetary gear on the conical shaft being circular. A partial cross-sectional view showing the state in which the cover 1 has been moved toward the large diameter end, Figure 12 is a cross-sectional view taken along the line X2-X2 in Figure 11, and Figure 13 is a partial cross-sectional view showing the state in which the cover has been moved toward the large diameter end. 14 is a sectional view taken along the line X3 in FIG. 13, and FIGS. 15 to 271 show the second embodiment.
The figure shows a front view of the planetary gear mechanism, Figure 16 is a sectional view taken along the line Y1-Y'I in Figure 15, and Figure 17 is a Y2 line in Figure 15.
- Y22 line cross section, 8f118 is Y3-Y3 in Figure 15
3-line sectional view, Figure 19 is a front view of the first lever, Figure 20 is a sectional view of the first lever, Figure 21 is a front view of the second lever, and Figure 22 is a front view of the first lever.
The figure is a sectional view of the second lever, and Figure 23 is a front view of the receiving plate.
Fig. 4 is a sectional view of the receiving plate, Fig. 25 is a front view of the assembly state of the lever and the receiving plate at d5 in the third embodiment, Fig. 26 is a vertical sectional view from the outside, and Fig. 27 is a front view of the assembled state of the lever and the receiving plate. FIG. 28 is a sectional view taken along line 7-Z in FIG. 27, FIG. 29 is a partial sectional view showing the 1ith embodiment, Negative! Figure 30 is a schematic diagram of the gear device according to the sixth embodiment, and Figure 31 is a partial sectional view thereof. Motor case 1, Tanabata shaft (man-powered shaft) 2, external gear (center gear) 3 , fixed internal toothed medium (1st moving float) 4, planetary gear (intermediate gear) 5, = 1' , thrust receiving plate 1
1, spherical convex surface '12, spherical concave surface 13, spherical washer 14, washer 15, playback coil spring 16, bearing 17, to first lever 18, 18B, spherical convex surface 19, second lever 20, spherical concave surface 21, Spherical convex surface 22, receiving plate 23, spherical concave surface 24, play take-up 1111 spring 25, lever 26, spherical convex surface 27, receiving plate 28, spherical concave surface 29, 30.11 [force receiving plate 31, spherical convex surface 32, receiving plate] Plate 33, spherical four-sided 3/11 piston 3! ′
], cylinder 36, receptacle 37, communication pipe 38, driving force f
Direction Δ for 1, S between ri'Ill and 1iEi, GO from one side,
01, (!2゜Patent applicant Fujihen) Juki Co., Ltd. Shinsho Ko - Go Mutsumi Kazuyo Attorney Patent attorney On +U ++1,1 Gi No. 24
Figure 1i23 Figure Heat 211 et al. 30w1 31st [

Claims (1)

[Scope of Claims] 1. A central gear, a plurality of gears, and a circular shaft formed on the group of gears. A power equal distribution gearing device using a round shaft and a gear thrust balancing device characterized by having a balancing device for thrust toward the small diameter end. 2. The balancing device uses the medium heat as a fulcrum. A circular shaft according to claim 1, which is supported in a swingable manner and is configured to receive the thrust of each planetary gear at a position corresponding to the planetary gear. Gear thrust balance I!
A power uniform gearing device using a gear. 3. Balance 01 corresponds to the three planetary gears and its J11
A power equal distribution gearing device using a round shaft and a gear thrust balancing device according to claim 2, which comprises one ilfl receiving force receiving force. 4. The balancing device is connected to a pair of first levers that receive the 111 force of the adjacent planetary gear among the four planetary gears, and is connected between these first levers and can swing around the center as a fulcrum. Second J: A power uniform gearing device using a circular shaft and a gear II horn balancing device according to claim 2. 5. Balance! The device consists of a cone 611 and a gear 111 as described in Claim 2, which corresponds to the two planetary gears and receives their thrust.
Power distribution Nanchu using force balancing device '1￥ iFJ
. 6. Balance I! A is a three-way lever that receives the llf horns of two planetary teeth T11 adjacent to the backs of six planetary gears, and is connected between these levers and has a fulcrum at the center (a swingable lltl receiving force 'l''i W'lClaim 1f11 A power distribution gearing device using the conical shaft and gear 111 force balance l!WFf according to claim 2.7. Claim 11 consisting of pistons and cylinders arranged to receive the conical shaft small diameter end direction t)ry force generated in a plurality of gears, and a communicating pipe configured to allow fluid in each cylinder to flow. A power uniform gearing device using the internally sized shaft described in item 1 and the tooth 1j 11f horn balancing V device.