JP3914207B2 - Transmission - Google Patents

Description

The present invention relates to a transmission.

2. Description of the Related Art Conventionally, transmission devices that are used for machine tools, industrial machines, construction machines, agricultural machines, vehicle machines, and the like are known to be based on electrical control such as inverters and servo motors. Alternatively, there is a device that mechanically shifts gears, and a device that shifts gears using many gears is known (for example, see Patent Document 1).
JP-A-57-163755

  The conventional transmission has a problem that in the low speed range, the output is low and the output is insufficient, and the efficiency is poor. In addition, a transmission used in an internal combustion engine (such as an automobile) that does not use electric power has a problem in that control is difficult and the structure is complicated. Furthermore, when many gears are used, there is a problem that efficiency is lowered.

The transmission according to the present invention includes an input shaft and an output shaft that are rotatably supported on the same axis, and is rotatably fitted on the input shaft and the shaft. An eccentric shaft for transmission having an eccentric circumferential surface centering on a declination axis that intersects with the predetermined angle, and an outer periphery of the eccentric circumferential surface that is rotatable about the declination axis and revolves about the axis. A shift input ring member that is fitted, a speed change means that changes the revolution speed of the speed change input ring member by rotating the speed change eccentric shaft, and a shaft that is rotatable at the output shaft side end of the input shaft An output eccentric shaft portion that is supported by the eccentric shaft center and is integrated with the output shaft, and the output eccentric shaft portion that can rotate about the deflection shaft center and revolve around the shaft center. A cylindrical case that is externally fitted to the gear and is provided with a revolving force around the shaft center by the speed change input ring member. And a coupling member having a connecting member for connecting the cylindrical casing and the input shaft, and the locking input ring member and the cylindrical casing are mutually locked and locked together. The engaging portion is formed of a bevel gear , and a connecting member that connects the cylindrical casing and the input shaft is fitted on the cylindrical casing and is formed from the outer peripheral surface of the casing. A short cylindrical member that rotatably holds the projecting shaft portion, and a central portion that is connected to the input shaft and is inserted through a through hole of a long hole formed in the cylindrical casing so that the both end portions can be swung. a transmission shaft which is rotatably held on the short cylindrical member, Ru der those with.

According to the transmission of the present invention, idling of the transmission input ring member is prevented, and heat (friction heat) is not generated between the transmission input ring member and the joint member (rotating body).
In addition, a simple and compact structure can be configured, and handling and manufacture are easy, and a highly efficient transmission can be obtained in a wide range of transmission. That is, since gear shifting is not performed using a plurality of gears, power can be transmitted with extremely high efficiency, and high torque can be transmitted even at low speeds. Furthermore, the operation sound is quiet and the power transmission is smooth. The output shaft can be shifted to a desired rotational speed (rotation speed) with stepless and full-area constant output only by changing the rotational speed (rotation speed) of the shifting eccentric shaft by the speed change means.

FIG. 1 shows an embodiment of a transmission according to the present invention. This transmission is provided with an input shaft 1 and an output shaft 2 that are rotatably supported on the same axis L ₁ .
The transmission includes a transmission eccentric shaft 3 that is rotatably fitted to the input shaft 1 via a bearing, and a transmission input that is fitted to the transmission eccentric shaft 3 via a bearing (automatic centering roller bearing). A ring member 4, a transmission means Y that changes the revolution speed of the transmission input ring member 4 by rotating the transmission eccentric shaft 3, and an output that is rotatably supported at the end of the input shaft 1 on the output shaft 2 side. An output eccentric shaft portion 5 integrated with the shaft 2, a cylindrical casing 6 that is externally fitted to the output eccentric shaft portion 5 via a bearing (four-point contact ball bearing) 12, and the cylindrical casing 6 and the input shaft 1 And a joint member 8 having a connecting member 7 for connecting the two.

Specifically, the input shaft 1 and the output shaft 2 are both pivotally supported by a support member such as an external casing so as to be rotatable about the axis L ₁ . The proximal end side of the input shaft 1 is supported by the drive source 16 so that the input shaft 1 is rotationally driven, and the distal end side of the output shaft 2 is connected to a machine or the like that is driven to shift. In FIG. 1, the left side is the distal end side, and the right side is the proximal end side.

The transmission eccentric shaft 3 has an eccentric peripheral surface 50 formed at a part of the outer peripheral surface with a declination axis P intersecting with the shaft center L ₁ at a predetermined angle θ (θ = 2 to 5 °). It is a cylindrical member and is centered on the declination axis P. Moreover, it is attached to the input shaft 1 through a bearing so as to be fitted externally, and is rotatable about the axis L ₁ .
An outer flange portion 35 is formed on the base end side of the eccentric peripheral surface 50, and an inner ring 18 for a self-aligning roller bearing is fixed to a corner portion between the eccentric peripheral surface 50 and the outer flange portion 35. Further, a balance weight 10 is attached to a part of the outer flange portion 35.

  The transmission eccentric shaft 3 has a cylindrical portion 11 fitted on the input shaft 1 via a bearing at the base end portion, and the cylindrical portion 11 is inserted into the transmission means Y. Further, a thrust bearing 13 is interposed between the outer flange portion 35 and the outer casing of the transmission means Y, which is outside the cylinder portion 11.

The transmission input ring member 4 is an annular member that is externally fitted to the eccentric circumferential surface 50 of the transmission eccentric shaft 3 so as to be rotatable about the declination axis P and revolve around the axis L _1. The (inner peripheral surface) is an outer ring 19 for a self-aligning roller bearing. Therefore, it can be said that the self-aligning roller bearing 9 can be constituted by the inner ring 18 on the shift eccentric shaft 3 side and the outer ring 19 of the shift input ring member 4. The self-aligning roller bearing 9 may be a thrust self-aligning roller bearing.
A locking portion 51 that locks with the cylindrical casing 6 included in the joint member 8 is formed on the side surface on the distal end side of the transmission input ring member 4.

Next, the output eccentric shaft portion 5 is rotatably supported at the end portion of the input shaft 1 on the output shaft 2 side, and the output shaft is formed integrally with the output shaft 2 with the declination axis P as the center. 2 is a portion on the base end side.
Specifically, the output eccentric shaft portion 5 has a concave portion for insertion with a circular cross section that opens to the input shaft 1 side on the shaft center L ₁ , and the concave portion is provided at the tip portion of the input shaft 1 via a bearing. It is attached to the outside. Further, the output eccentric shaft portion 5 is provided with a balance weight 17 on the tip side thereof, and is connected (connected) integrally with the output shaft 2.

The joint member 8 is a universal joint having a cylindrical casing 6 that is externally fitted to the output eccentric shaft portion 5 via a bearing 12 and a connecting member 7 that connects the cylindrical casing 6 and the input shaft 1.
The cylindrical casing 6 is rotatable about a declination axis P about a declination axis P by a bearing 12 and about an axis L ₁ according to the rotation of the transmission input ring member 4. Revolving freely. That is, the cylindrical casing 6 and the transmission input ring member 4 are centered on the self-aligning roller bearing 9 on the eccentric peripheral surface 50 of the transmission eccentric shaft 3 and the declination axis P of the output eccentric shaft portion 5. The cylindrical casing 6 can be rotated around the axis L ₁ of the transmission input ring member 4 by a revolving operation around the axis L ₁ by the bearing 12 on the outer peripheral surface. at 51, the revolving force of the axis L ₁ around is applied.

Moreover, the latching | locking part 51 of the cylindrical casing 6 latched with the transmission input ring member 4 is formed in the base end surface. The shift input ring member 4 and the cylindrical casing 6 are formed with a locking portion 51 that is locked with each other and rotates together.
For example, as shown in FIG. 1, the locking portion 51 is configured by a bevel gear, and is configured not to cause the shifting input ring member 4 to idle when the cylindrical casing 6 rotates. In addition to the bevel gear, the pins may be fixed to each other and connected.

FIG. 2 is a cross-sectional view (as viewed in the direction of arrow V) in FIG. 1. The connecting member 7 of the joint member 8 will be further described with reference to FIGS. 1 and 2. The connecting member 7 includes the cylindrical casing 6 and the input shaft 1. A rotating member to be connected.
The connecting member 7 is fitted to the cylindrical casing 6 and has a short cylindrical member 61 that rotatably holds a shaft portion 60 (FIG. 1) that protrudes in an orthogonal direction from the outer peripheral surface of the cylindrical casing 6, and a central portion 62a. Is connected to the input shaft 1 (FIG. 2). A transmission shaft 62 is inserted through a through-hole 63 formed in the cylindrical casing 6 and both end portions 62b and 62b are rotatably held by a short cylindrical member 61 via bearings. And having.

  That is, in FIG. 1, a pair of shaft portions 60, 60 are integrally formed on the outer peripheral surface of the cylindrical casing 6 with a phase difference of 180 °. The short cylindrical member 61 is formed with four through holes 14 having a phase of 90 ° on the peripheral wall, and two of the through holes 14 and 14 facing each other at 180 ° are provided via bearings. The pair of shaft portions 60, 60 formed in the cylindrical casing 6 are rotatably held.

  In FIG. 2, the two (remaining) two through holes 14 and 14 facing each other at 180 ° are provided with both ends 62b and 62b of a linear transmission shaft 62 having a circular cross section through bearings. , Hold freely. Further, the transmission shaft 62 has a central portion 62 a connected to the input shaft 1, and the transmission shaft 62 is inserted through a spherical bulging portion 15 formed closer to the distal end side of the input shaft 1, and the input shaft 1. And are connected in an orthogonal direction. Although not shown, both ends of the transmission shaft 62 are prevented from coming off by snap rings or the like.

  The transmission shaft 62 passes through a through hole 63 formed in the peripheral wall of the cylindrical casing 6, and the size of the through hole 63 is larger than the diameter d of the transmission shaft 62. That is, it is a long hole having a dimension larger than the diameter d of the transmission shaft 62 in the swinging direction of the transmission shaft 62 due to the rotation of the input shaft 1. The clearance between the transmission shaft 62 and the through hole 63 is about 6 to 10 mm. That is, the relationship between the diameter d of the transmission shaft 62 and the diameter (major axis) D of the through hole 63 is 6 mm ≦ It is supposed that Dd ≦ 10mm.

Transmission means Y is a transmission eccentric shaft 3 is rotated in the axis L ₁ around, revolution speed of the axis L ₁ about the transmission input ring member 4 by the eccentric peripheral surface 50 of the transmission eccentric shaft 3 (rotational speed ). The speed change means Y shown in FIG. 1 uses an electromagnetic powder clutch (friction plate). This is a well-known one, but simply described. An electromagnet portion provided to rotate integrally with the input shaft 1 and a cylindrical portion 11 provided at the base end portion of the shift eccentric shaft 3 to be integrally rotatable. And a receiving iron core portion wound around.

  In this speed change means Y, if the electromagnetic powder clutch is in a non-energized state, even if the electromagnet portion rotates together with the input shaft 1, the speed change eccentric shaft 3 does not rotate. When the electromagnetic powder clutch is energized, the powder (iron powder) is coupled between the electromagnet portion and the force-receiving iron core portion, and the shift eccentric shaft 3 rotates in the same direction as the input shaft 1. Then, the rotational speed of the shift eccentric shaft 3 can be changed by adjusting the intensity of the current to change the degree of powder coupling, and as a result, the rotational speed of the output shaft 2 can be changed.

Next, the operation of this transmission will be described. When the electromagnetic powder clutch of the transmission means Y is in a non-energized state, even if the input shaft 1 rotates, the transmission eccentric shaft 3 does not rotate (is stationary). Therefore, at this time, the joint member 8 only rotates around the declination axis P by the rotation of the input shaft 1 and does not revolve around the axis L ₁ . That is, since the cylindrical casing 6 of the joint member 8 only rotates around the outer peripheral surface of the output eccentric shaft portion 5 (is idle), the output eccentric shaft portion 5 is in a stationary state, and thus the output shaft 2 is stationary. Yes. Since the transmission input ring member 4 is locked (connected in the rotational direction) by the cylindrical casing 6 and the locking portion 51, it rotates around the declination axis P.

When the electromagnetic powder clutch is energized from this non-energized state, the cylindrical portion 11 starts to rotate in the same direction as the input shaft 1, thereby rotating the transmission eccentric shaft 3 about the axis L ₁ . Then, the transmission input ring member 4 revolves around the axis L ₁ while rotating around the declination axis P, and a revolving force is applied from the transmission input ring member 4 to the cylindrical casing 6 of the joint member 8. Thus, the joint member 8 revolves around the axis L ₁ while rotating around the declination axis P. As a result, the output eccentric shaft portion 5 starts to revolve around the shaft center L ₁ , and thus the output shaft 2 starts to rotate (in the same direction as the input shaft 1).

  Then, as the current value of the electromagnetic powder clutch of the speed change means Y is increased, the rotational speed of the cylindrical portion 11 is increased (the rotational speed is increased), and the rotation of the cylindrical portion 11 and the input shaft 1 is synchronized (the same). The output shaft 2 has the same rotational speed as the input shaft 1 and the speed change operation is completed. And if the electric current value of an electromagnetic powder clutch is made small, rotation of the output shaft 2 will become slow according to it.

Next, the transmission shown in FIG. 3 has a configuration in which a gear is used instead of the joint member 8 which is a universal joint of the transmission explained in FIG. 1, and is rotatable on the same axis L _1. A pivoted input shaft 1 and output shaft 2 are provided.
This transmission includes an input gear 30 that rotates integrally with an input shaft ₁ around an axis L _1, a transmission eccentric shaft 3 that is externally fitted via a bearing so as to be rotatable on the input shaft 1, and a transmission eccentricity. A speed change input ring member 4 fitted on the shaft 3, a speed change means Y that rotates the speed change eccentric shaft 3 to change the revolution speed of the speed change input ring member 4, and the input shaft 1 on the output shaft 2 side. An output eccentric shaft portion 5 that is rotatably supported at the end portion and integrated with the output shaft 2, and a force receiving gear portion 32 that is externally fitted to the output eccentric shaft portion 5 via a bearing and meshes with the input gear 30. And a rotating body 34 having a force receiving portion 33 to which a revolving force about the axis L _{1 is applied} by the transmission input ring member 4.

The transmission eccentric shaft 3 is a cylindrical member having an eccentric peripheral surface 50 having an eccentric axis P intersecting the axis L ₁ at a predetermined angle θ (θ = 2 to 5 °) as an axis. The configuration is the same as that of the transmission. Further, the output eccentric shaft portion 5 is a portion having an outer peripheral surface having the declination axis P as an axis, and differs from FIG. 1 in that it is externally fitted to the input shaft 1 via a cylindrical spacer. Other configurations are the same as those in FIG. The input gear 30 is a bevel gear (crown gear) centered on the axis L ₁ , its teeth are directed toward the tip side (output shaft 2 side), and rotates integrally with the input shaft 1 around the axis L _1. The input shaft 1 is fixed to the key member or the like.

Transmission input ring member 4 is fitted over the member to the eccentric peripheral surface 50 of the transmission eccentric shaft 3 as freely revolve declination axis P around the rotating freely and axis L ₁ around, in the case of FIG. 1 In the same manner as described above, the inner peripheral surface portion is used as an outer ring 19 for a self-aligning roller bearing, and the self-aligning roller bearing 9 is configured with the eccentric peripheral surface 50 of the transmission eccentric shaft 3. A cylindrical portion 22 centering on the declination axis P is formed on the outer peripheral side of the transmission input ring member 4 via an annular flange portion 21, and a locking portion that locks the rotating body 34 on the tip surface thereof. 51 is formed. The cylindrical portion 22 is disposed radially outward of the input gear 30, and can function as a cover for the input gear 30.

The rotation member 34 includes a force-receiving gear portion 32, and a force receiving portion 33, force-receiving gear portion 32, outputs as freely revolve rotation freely and axis L ₁ around the declination axis P around The portion that is externally fitted to the eccentric shaft portion 5 and meshes with the input gear 30, and the force receiving portion 33 is connected around the shaft center L ₁ by the transmission input ring member 4 (connected by the locking portion 51). This is the part to which the revolving force is applied.
Further, as the force receiving gear portion 32, a bevel gear (crown gear) centering on the declination axis P is used, and a part of the periphery of the force receiving gear portion 32 meshes with the input gear 30. Yes.

The force receiving portion 33 is formed with a locking portion 51 that locks with the transmission input ring member 4. In other words, the shifting input ring member 4 and the rotating body 34 are formed with locking portions 51 that are locked with each other and rotate together.
For example, as shown in FIG. 3, the locking portion 51 is configured by a bevel gear, and is configured not to cause the transmission input ring member 4 to idle when the rotating body 34 rotates. In addition to the configuration with the bevel gear, the pins may be fixed and connected with each other.
The force receiving gear portion 32 and the force receiving portion 33 having the locking portion 51 are formed on the same annular surface of the rotating body 34, and the force receiving portion 33 is disposed on the outer diameter side to receive the force receiving portion 33. A force gear portion 32 is disposed on the inner diameter side.

Further, transmission means Y is may be due to the electromagnetic powder clutch in the transmission of FIG. 1, may be a transmission means Y and a friction wheel 23 which moves back and forth a plurality of helical gear and the axis L ₁ direction. Specifically, a variable speed input helical gear 24 that rotates integrally with the input shaft 1, a counter helical gear 25 that meshes with the variable speed input helical gear 24, and a friction wheel 23 that is coaxially fixed to the counter helical gear 25; And an output helical gear 26 that rotates integrally with the cylindrical portion 11 of the transmission eccentric shaft 3, a receiving helical gear 27 that meshes with the output helical gear 26, and a friction wheel attached to the receiving helical gear 27. And a force-receiving friction wheel 28 that abuts against the wheel 23.
Then, the rotational speed of the output helical gear 26 is changed by the forward / backward movement of the friction wheel 23 with respect to the force-receiving friction wheel 28, and the rotational speed of the eccentric shaft 3 is changed as in FIG. The revolution speed of the ring member 4 is changed.

The operation of the transmission shown in FIG. 3 will be described. (Similar to the transmission shown in FIG. 1) In the state where the friction wheel 23 of the transmission means Y is separated from the force-receiving friction wheel 28, the gear shifts even if the input shaft 1 rotates. The eccentric shaft 3 does not rotate. The input gear 30 is rotated by the rotation of the input shaft 1, the force-receiving gear portion 32 which meshes with the input gear 30 (not revolve the axis L ₁ around) which rotates the polarization axis P around. That is, since the rotating body 34 only rotates around the output eccentric shaft portion 5 (around the eccentric shaft center P), the output eccentric shaft portion 5 is in a stationary state, and thus the output shaft 2 is stationary.

From this state, when the shifting eccentric shaft 3 is rotated around the axis L ₁ by the transmission means Y, the shifting input ring member 4 rotates around the declination axis P while rotating around the axis L ₁ . Start a revolution. Then, the revolution force is applied to the rotating body 34 from the transmission input ring member 4 by the locking portion 51, the rotating body 34 is gradually revolves the axis L ₁ around while rotating the declination axis P around. As a result, the output eccentric shaft portion 5 revolves around the shaft center L ₁ and the output shaft 2 rotates (in the same direction as the input shaft 1). Then, if the shifting eccentric shaft 3 rotates integrally with the input shaft 1, the output shaft 2 becomes the same rotational speed as the input shaft 1 and the shifting operation is completed.
And if the rotational speed of the eccentric shaft 3 for speed reduction is made small, the rotational speed of the output shaft 2 will become slow according to it.

The present invention is not limited to the above-described embodiment. For example, although the transmission means Y is not shown, an outer casing member provided so as to be integrally rotatable with the cylindrical portion 11 of the eccentric shaft 3 for transmission, The outer casing member is provided so as to face the input shaft 1 so as to be rotatable integrally with the input shaft 1, and a pair or plural pairs of magnets of S and N poles attached to the outer casing member. It may be configured to approach and separate.
Alternatively, a pulley rotation drive type, a torque converter, or any other type can be used. It is desirable that the speed change by the speed change means Y is performed by servo control, a microcomputer or the like.

As described above, according to the present invention, in the transmission including the input shaft 1 and the output shaft 2 that are rotatably supported on the same axis L ₁ , the input shaft 1 is rotatably attached to the input shaft 1. A shift eccentric shaft 3 having an eccentric peripheral surface 50 centered on a declination axis P that is fitted and intersects the axis L ₁ at a predetermined angle θ, and is rotatable about the declination axis P and is axially rotatable. A transmission input ring member 4 fitted on the eccentric peripheral surface 50 so as to be revolved around L _1; and transmission means Y for rotating the transmission eccentric shaft 3 to change the revolution speed of the transmission input ring member 4; An output eccentric shaft portion 5 that is rotatably supported at an end portion of the input shaft 1 on the output shaft 2 side and that has a declination axis P as an axis and is integrated with the output shaft 2, and around the declination axis P cylindrical shape revolving force of the axis L ₁ around is imparted by fitted over and transmission input ring member 4 to the output eccentric shaft 5 as freely revolve rotation freely and axis L ₁ around the A joint member 8 having a casing 6 and a connecting member 7 for connecting the cylindrical casing 6 and the input shaft 1, and the transmission input ring member 4 and the cylindrical casing 6 are mutually locked and rotated together. An engaging portion 51 is formed, and the engaging portion 51 is configured by a bevel gear. Further, a connecting member 7 that connects the cylindrical casing 6 and the input shaft 1 is fitted to the cylindrical casing 6 and is cylindrical. A short cylindrical member 61 that rotatably holds a shaft portion 60 projecting from the outer peripheral surface of the cylindrical casing 6, and a long through-hole 63 formed in the cylindrical casing 6 with the central portion 62 a connected to the input shaft 1. The transmission shaft 62 having both ends 62b, 62b rotatably supported by the short cylinder member 61, which is freely swingable, prevents the shift input ring member 4 from slipping and Heat (friction heat) is generated between the input ring member 4 and the joint member 8. There is no.

In addition, the structure can be simple and compact, easy to handle and manufacture, and a highly efficient transmission can be obtained in a wide range of transmission. That is, since gear shifting is not performed using a plurality of gears, power can be transmitted with extremely high efficiency, and high torque can be transmitted even at low speeds.
In addition, the output shaft 2 can be shifted to a desired rotational speed steplessly and with a constant constant range of output only by changing the rotational speed of the shifting eccentric shaft 3 by the transmission means Y.
Moreover, the operation sound is quiet and the power transmission is smooth .
Further, since the locking portion 51 is configured by a bevel gear, the shifting input ring member 4 does not stop or rotate between the joint member 8 and prevents idling, Does not cause generation.

It is sectional drawing which shows one Embodiment of the transmission which concerns on this invention. It is sectional drawing of the principal part of FIG. It is sectional drawing which shows a transmission .

Explanation of symbols

1 the input shaft 2 the output shaft 3 transmission eccentric shaft 4 transmission input ring member 5 outputs the eccentric shaft part 6 the tubular casing 7 connecting member 8 joint member
50 Eccentric peripheral surface
51 Locking part
60 Shaft
61 Short cylinder member
62 Transmission shaft
62a center
62b end
63 Through-hole L ₁ shaft center P declination shaft center Y transmission means θ predetermined angle

Claims (1)

In a transmission having an input shaft (1) and an output shaft (2) rotatably supported on the same shaft center (L ₁ ), the input shaft (1) is rotatably fitted on the input shaft (1). And a transmission eccentric shaft (3) having an eccentric circumferential surface (50) having an eccentric shaft center (P) intersecting with the shaft center (L ₁ ) at a predetermined angle (θ), and the deflection angle A speed change input ring member (4) externally fitted to the eccentric peripheral surface (50) so as to be rotatable about the axis (P) and revolving around the axis (L ₁ ), and the speed change eccentric shaft ( 3) rotating means (Y) for rotating the speed change input ring member (4) by rotating it, and an end of the input shaft (1) on the output shaft (2) side rotatably supported by the shaft An output eccentric shaft portion (5) having the declination axis (P) as an axis and integral with the output shaft (2), and rotatable about the declination axis (P) and the shaft Heart (L ₁ ) A cylindrical casing (6) which is externally fitted to the output eccentric shaft portion (5) so as to be revolved around the shaft and to which a revolving force around the shaft center (L ₁ ) is applied by the transmission input ring member (4). ) And a coupling member (8) having a connecting member (7) for connecting the cylindrical casing (6) and the input shaft (1), and the transmission input ring member (4) and the cylindrical shape. The casing (6) is formed with a locking portion (51) that is locked and rotated together, and the locking portion (51) is constituted by a bevel gear ,
Further, a connecting member (7) for connecting the cylindrical casing (6) and the input shaft (1) is fitted on the cylindrical casing (6) and from the outer peripheral surface of the cylindrical casing (6). A short cylindrical member (61) that rotatably holds the projecting shaft portion (60), and a long hole formed in the cylindrical casing (6) with the central portion (62a) connected to the input shaft (1). And a transmission shaft (62) in which both end portions (62b) and (62b) are rotatably held by the short cylindrical member (61). Transmission.

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