JPS58184341A - Heavy load transmission planet gear system - Google Patents

Abstract

PURPOSE:To prevent overload by maintaing such gearing state where one end face of a planet gear is shifted from one end face of sun gear in order to produce such force as to buffer the movement of the planet gear due to the couple in the undesirable direction. CONSTITUTION:The right end of a fixed sun gear 5 is set further right than the right end of a planet gear 7 while the left end of the planet gear 8 is set further left than the left end of an inverted sun gear 6. Under such gearing state, the planet gears 7, 8 will produce the reaction force against the motion to the right thus to buffer the motion of the planet gears 7, 8 in the undesirable axial direction. Consequently the increase of load or the breakdown of gear due to the contact between the gear side faces or the erroneous gearing can be prevented.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a planetary gear device for high load transmission.

A method using planetary gears is known as a reduction mechanism that can obtain a large reduction ratio. In a capstan gear device as shown in Fig. 1, around tooth i2 fixed at @1,
When the internal gear 4 is rotated in the same direction and at almost the same speed as the planetary gear 3 by allowing it to freely move on the shaft 1 while meshing with the planetary gear 3 or the internal gear 4, the shaft 1 becomes very For slow-rotating machines, the rotational moment l of shaft 1 can be made very large. However, when decelerating t-g with a speed ratio of about 1710, achieving this in a small space depends on whether the outer diameter iLn of the gear 3 is made small or δ, but in order to have a transmission force above a certain level, K is ,・Module t--It cannot be made extremely small, and as a result, the outer diameter of the spacer 3 cannot be made smaller beyond a certain level. In other words, unless the overall size of this device is increased to a certain level, the speed ratio of 1/IOQ cannot be achieved.Conversely, this I# is not the same as e#, which is similar to a moving vehicle that leads to an increase in the size of the machine. It won't happen.

In addition, in the so-called planetary gear-equipped handle speed reduction mechanism shown in side and front views in FIGS. The two gears 7.8 are adapted to integrally move on a pin 10 protruding from a drive lever 9 which moves freely on The ratio is quite remarkable. In this device, gear 5.6
The smaller the difference in the number of teeth in each combination of gears 7 and 8, the larger the reduction ratio can be obtained, so it is advantageous to be able to completely eliminate the above-mentioned drawbacks of the capstan gear device shown in Fig. 1. On the other hand, there are some disadvantages as well. That is, when the load torque of the shaft 1 becomes large, a force is applied to push the two gears 7 and 8 at the input end to the right, and the end faces of the gear 6 and the gear 7 come into contact, causing tm The load applied to the drive lever becomes even greater. In particular, as shown in FIG. 3A, it has the same configuration as the speed reduction device shown in FIG. In order to allow the drive lever 9 to move on the shaft 1 in the case of an input by the coupling 12IC, and the tooth M7 is connected to the driven sun gear 6
IiAw to prevent contact or engagement with
A spring 1 is installed between the bead 10 on the J lever 9 and the gear 8.
When the third gear is inserted, the gear 7 roughly moves to the right in Figure 3A and engages with the driven sun gear 6.
The gears may become distorted, the gears may wear out, and the swage of gear 7.8 may come off. If we analyze the reason for this, we get the following.

In FIG. 3A, the drive lever 9 is aW(
When rotating clockwise), fixed sun gear 5 (18T)
Planetary gear 7 (17T) rotates while rotating. Along with this, the gear 8 (16T) which is caulked to the planetary gear 7 (17T) also rotates in aw. gear 8
The rotation of the driven sun gear 6 (which rotates with the gear OW) is transmitted to the shaft 1 via the key.
Reference numeral 14 in the figure indicates a planetary gear 7.8 driven by a spring 13.
This is a spacer that limits the leftward movement of.

Assuming that the tilting drive slot 11 is driven for toner agitation in, for example, the current 1-family device of the reconnaissance company, then) f-
cojilJtjK LF)・1-1□0. Karka,
IpT&, b) Zy is received as a total reaction. Since this torque becomes the load torque for causing the 116 to rotate on its own axis, the point on the tooth surface that contacts the tooth M8 or the awT wheel 6 is As shown in Figure 3B, A2B20! The trajectory of

Finally, pX# car 8 receives a force F2. This is all bin IO
Considering point 02 on the axis of (gear 80 center of gravity), 02
Above and above B2? , a force that differs only in its point of action, and a force whose vector is the same as tsoox are in equilibrium, so
Each of these forces is F2'.

If we divide it into F2, '2' and F2 become an aW couple of 8 wheels, and II'2' is a gear 8kF! It becomes a force that moves in the direction.

This corner force and moving force also act on the gear 7, or are balanced by the fixed sun gear 5. Considering the same way in Fig. 30, which is a partially enlarged view of the tab 9 as seen in the direction of the arrow G in Fig. 3A, Fl'' and Fl are the COW corner forces when viewed from the right side of the gear 7, and F2' and Combined with the corner force of F2, it is a force that moves F1' in the F'1 direction, and Fl'
+ The component forces f, , f2 of Fj are on a fishing platform. However, fl' and f21 contribute as a force to separate the planetary gear from the sun wheel.

After all, in Figure 3D seen from above in Figure 3A,
2 is the OW corner force of the planetary gear. If this corner force is tυ, then U increases in proportion to TK. Since the couple U [acts constantly, the drive lever 9 is
When rotated at W, the meshing surfaces of the gears 8 and 7 change one after another, and the planetary gears generate a spring due to the play between the bearings of the pin 10 and the planetary gear 7.8 and the deformation of the pin 10. The theory is that it moves toward the drive lever 9 against the force 13.

The above is a general understanding; in reality, the situation becomes more complicated as described below. In other words, Fl and F2 are developed as if they act on the entire width of each of the seven teeth, but this is only the case at the beginning when the drive lever 9 receives the load T. Actually, as mentioned above, gear 7.8 receives the OW couple ■, so the third
As shown in Fig. 5, which is an enlarged plan view showing the engaged state of Fig. 4, which is a view similar to Fig. A, the third
The points of action of fl and f shown in Figure D are not the full width, but are shifted to Sl and S, respectively. FIG. 4 shows a case where the right end of the planetary gear 7 is further to the right than the right end of the sun fixed gear 5, and the left end of the driven sun gear 6 is further to the left of the left end of the planetary gear 8. However, although the gear end faces in the layout shown in Figure 3A are flush,
The state shown in FIG. 4 is reached. Furthermore, Figure 6 is similar to Figure 4.
The fifth figure shows the mechanical equilibrium figure in the illustrated state.

Moreover, FIG. 7 shows a case in which the right end of gear 5 is further to the right than the right end of gear 7, and the left end of gear 8 is further to the left of the left end of gear 6, contrary to the case of FIG. In the figure shown in the figure, the present invention provides for the planetary gear 7 to be in such a meshing state.
．． By generating a reaction force sound to the rightward movement force applied to the shaft 8, all of the above-mentioned drawbacks of the prior art are attempted to be overcome. In addition, Fig. 8 and Fig. 9 are respectively 5th
Similarly to Fig. 6, the interlocking pattern 1 in Fig. 7! 1- is an enlarged plan view and a dynamic equilibrium diagram.

Next, the conventional device (A) shown in FIGS. 4, 5, and 6, and the device i based on the present invention shown in FIGS. 7, 8, and 9.
In order to soften the ratio between i (B) and r, (B) assumes that the gear 7.8 is in a symmetrical position relative to the gear 5.6. In other words, the position 11 * I of the center of gravity G of the planetary gears (7, 8) in the dynamic equilibrium diagrams (Figs. 6 and 9)
t + bI, h2Fi body) and (B) are respectively reversed, and the inclination angle variation ζA of the planetary tooth j [7, 8.

Let ζB (=ζ).

First, in (a)), the left end B2 of gear 8 is moved by gear 6? The power to become? When received (df2 in Figure 3D)
), the reaction force is a component of the force N acting on the gear 7 811 (acting in one direction normal to the tooth surface). At this time, another component force P of N acts to the right. SK for this component force P.

On day 2, a static frictional force μF acts. This equilibrium state in the horizontal and vertical directions can be determined by considering the component force 'lt at point G in the mechanical equilibrium rotational force. In other words, the OW force direction couple UA and the rightward force RA are as follows.

U□-'(4+z20μ(ht-h2)) PhtR
A=P-2μF≧0 (B) The mini corner force in the OW direction at K and the force RB in the left direction can be found in the same way, but UB=UA (=U) RB=:RA9,
The couple is the same as η), or the direction of the force that tries to move the planetary gears (7, 8) completely is completely opposite (from the rightward force to the leftward force).

Now, when trying to further rotate the drive lever 9,
When an even larger load torque T is applied, the couple ■ also increases, so the inclination angle ζ of 5OrI′i increases when the contact point B2 between gears 8 and 6 moves to the next tooth straightness. Move to the right.

In other words, if the rotation angle seat of the drive lever is 0, then if dζ/dθ is positive, then the planetary gears (7, 8)? It tries to move in the r-stone direction (the force during movement is static friction force of 2 μF). If you use the load torque T'i, you will be disappointed. However, since T fluctuates, according to this formula, when cl dζ/d when the face appears from the thorny side
θ also becomes negative, and now the planetary gear (7°8) must become a fist that returns to the left. However, in this case, if a load torque T that exceeds the level of friction is applied, the above-mentioned static friction force of 2 μP prevents movement. Actually, it is a planetary gear (7° pin IO)
Since the compression spring 13 constantly applies a force to the left, it is possible to return to the left (this must be done only when the load torque T is also greatly reduced).

From the above-mentioned force relationship (in reality, it would be a much more complicated equation, so I won't go into further theoretical explanations), in Buddha) and (B), even though they are the same as a couple, RA,
Since the RBO direction is exactly opposite, it is considered that (B) moves less to the right. Actually the floating gear (7, 8) t-
Even if we measure the total load torque when moving in two, in the case of body) 36 edges f + 1 l IK, but in the case of (B) u
It was 180Kffm.

The function is the same even if there is only one planetary gear (7, 8), but in the case of two, the load torque applied to one or the other is divided into three equal parts, so the pressure on the tooth surface and the axial direction as described above are The move to ll71! reduced. However, the toner supply pipe was closed and the current product (horizontal After 35 to 40 hours, the gear end face was scraped and the entire tooth surface was worn away. In addition, in the test of the experimental plan, 2 out of 8 units had broken planetary gears. i1 (caulking removed)
It becomes. As mentioned above, there is only one report of planetary gear damage in the market, but I witnessed another one when I went to the market, so it is estimated that there are potentially more. There seems to be no room for this. the current,
Continuous test of the same condition of countermeasure type H-continue b 1
No abnormality occurred even after 000 hours.

As explained above, the end face position f' of the sun gear and the planetary gear is
If the meshing position of the sun gear and planetary gear [k is determined so that the relationship shown in t-X Figs. It is possible to prevent contact between certain gear sides, increase of load due to mis-meshing of gears, and damage to gears, etc. In addition, it is particularly effective in a reduction gear device as shown in Fig. 3A, in which a spring is inserted between the lever 9 and the planetary gears (7, 8), and it is difficult to restrict the rightward movement of the planetary gears. Can produce sound.

Although the meshing relationships shown in FIGS. 7, 8, and 9 are preferred meshing states according to the present invention, if the gears 8 and 6 are in the meshing state shown in FIG. gear 5
Even if the meshing state with the mesh is in the meshing state shown in FIG.
This is more effective than the one shown in Figure 5. Therefore, any meshing state of at least one of the gears is included as an embodiment of the present invention if it is in a state that helps to buffer movement of the planetary gear in an undesirable direction.

[Brief explanation of the drawing]

Figure 1 is an explanatory diagram of a capstan gear device, which is well-known as a reduction mechanism, and Figures 2 (a) and (b) are the same well-known planetary geared handle speed reducer! A side view and a front view of the device, and FIG. 3A are specific examples of the speed reduction device as shown in FIG. 2. Side view showing 31st. Figure 3B is a partially enlarged view of Figure 3A viewed from the direction of arrow H, the 30th factor is a partially enlarged view of Figure 3A viewed from the direction of arrow G, and Figure 3D is a plan view of the planetary gear portion of Figure 3A. Fig. 4 is a diagram showing the planetary gear of the device shown in Fig. 3A slightly moved to the right, Fig. 5 is an enlarged plan view showing the gear mesh shape Mk of Fig. 4, and Fig. 6 is a view of the device shown in Fig. 4. Dynamic equilibrium diagram, FIG. 7 is the same cause as in FIG. 4 of the vjt according to the present invention, FIG. 8 is an enlarged plan view showing the meshing state of both sides in FIG. 7, and FIG. 8 is the dynamic equilibrium of the device shown in FIG. 7. Figure. DESCRIPTION OF SYMBOLS 1... Driven shaft, 5... Fixed sun gear, 6... Driven sun gear, 7... Planetary gear, 8... Planetary gear, 9
... Drive lever, IO... Support shaft (bin), 12...
・Coupling, 13...Spring, 14...Spacer. Agent: Patent Attorney Makoto Kon 13- Procedural amendment dated August 2, 1980 Kazuo Wakasugi, Commissioner of the Japan Patent Office 1, Indication of the case 1981 Patent Wanriki 65225 No. 2, Name of the invention High load transmission planet Gear device 3, relationship with the case of the person making the amendment Patent applicant No. 1-3-6 Nakamagome, Ota-ku, Tokyo
Ei) (674) Ricoh Co., Ltd. Representative: Takeshi Inue 4, Agent: 107 8, Contents of amendment: 250-

Claims (1)

[Claims] In order to receive a couple in a speed reduction device in which a planetary gear consisting of two gears is supported by a support shaft of a drive lever and rotates around a fixed sun gear and a driven sun gear fixed to a side drive shaft. In order to generate a force that cushions the movement of the planetary gear in an unfavorable direction, the high gear is configured such that one end surface of the planetary gear is kept in the shape of a tooth with one end surface of the sun gear offset. Planetary gear system for load transmission.