JP2005121236A - Drive joint - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compact drive joint capable of transmitting large torque, and providing quiet driving by reducing transmission sound. <P>SOLUTION: A deformed protruding part 32b provided on a second coupling member is loosely fit in an inner side of a deformed recessed part 31d provided on a first coupling member, and an elastic body made spacer 33 and buffer layer 34 provided by filling synthetic rubber are interposed in a gap between the first and second coupling members. It is composed so that vibration following transmission is absorbed by vibrations of the spacer 33 and the buffer layer 34, and in transmission of large torque, the recessed part 31d and the protruding part 32b are brought into direct contact by deformation of the buffer layer 34 to bear the large torque. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a drive joint that connects a drive shaft and a driven shaft so that power can be transmitted.

  Recent automobiles are equipped with a number of auxiliary machines that operate by hydraulic pressure and assist driving operations, such as power steering devices and automatic transmissions. A pump is installed. As the hydraulic pump, various types of positive displacement pumps such as a vane pump and a gear pump are used. In general, the hydraulic pump is rotationally driven using a traveling engine as a drive source.

  However, a hydraulic pump for a power steering apparatus that assists the steering operation with hydraulic pressure is driven at a high speed during low-speed traveling and when it needs to generate a large steering assist force, and almost requires a steering assist force. It is desirable that the motor is driven at a low speed during high-speed traveling, and there is a problem that direct driving by the engine is disadvantageous. Conventionally, for example, as disclosed in Patent Document 1, output adjustment is easy. There is a configuration in which an electric pump using a simple electric motor as a drive source is used as a hydraulic pump for driving auxiliary equipment and is driven separately from the engine.

  As shown in FIG. 12, this conventional electric pump has an electric motor M having a drive shaft m (motor shaft) and a driven shaft a (pump shaft) and is driven by the electric motor M. A and a driven gear (not shown) meshed with the drive gear A, a pump housing B having a suction chamber and a discharge chamber (none shown) formed by meshing of the drive and driven gears, and the pump housing B and a housing support C formed integrally with the housing support C. The housing support C is provided with a discharge oil passage E communicating with the discharge chamber, and the pressure oil pressurized by the rotation of the drive and driven gear is discharged. The oil passage E is configured to be sent to the outside from the delivery port.

  In recent years, electric vehicles (EV) using an electric motor as a drive source instead of an engine have been put into practical use in order to prevent environmental deterioration due to exhaust gas. This electric vehicle may also be equipped with an auxiliary machine that operates by hydraulic pressure, and an electric pump using an electric motor as a drive source is used to generate the hydraulic pressure of these auxiliary machines.

  As described above, since a hydraulic pump used in a vehicle has a limited installation space, as disclosed in Patent Document 1 described above, an electric motor is integrally assembled on one side thereof. In order to connect the motor shaft as the drive shaft m and the pump shaft as the driven shaft a so as to be able to transmit power, such a unitized electric pump is used as shown in FIG. A drive joint J having a simple configuration is used.

  At the tips of the drive shaft m (motor shaft) and the driven shaft a (pump shaft) connected by the drive joint J, connection protrusions m1 and a1 having a rectangular cross section with an appropriate slenderness ratio are respectively provided. The center is projected along the axis. Further, the drive joint J is a short cylindrical member, and a fitting hole J1 having substantially the same rectangular cross section as the connection protrusion m1 is provided on one side, and the connection protrusion is provided on the other side. A fitting hole J2 having a rectangular cross section substantially the same as a1 is formed such that the centers thereof coincide with each other and the longitudinal directions thereof are substantially orthogonal.

  As shown in FIG. 13, the drive shaft m and the driven shaft a are connected to each other by using the drive shaft m and the end surface of the driven shaft a. The connecting projections m1 and a1 projecting from these end faces are aligned with the fitting holes J1 and J2, respectively, and as shown by arrows in the drawing, the fitting holes J1 and J2 are respectively aligned. This is done by fitting the connecting projections m1 and a1.

  The fitting holes J1 and J2 have a center on the axis of the drive joint J and have a rectangular cross section whose longitudinal directions are substantially orthogonal to each other, and the centers of the engagement protrusions m1 and a1 to be fitted to these are as follows. While aligning on the axis of the drive joint J, the centers of the engaging projections m1 and a1 coincide with the axes of the drive shaft m and the driven shaft a, respectively, so that the drive shaft m and the driven shaft a are coaxial. It can be properly aligned and connected together.

Similar connection can be realized by providing an engagement protrusion on the drive joint J side and a fitting hole on the drive shaft m or driven shaft a side. Such a drive joint is disclosed in Patent Document 2. It is disclosed.
Japanese Patent Publication No. 3-15592 Japanese Utility Model Publication No. 5-58882

  The drive joint J configured as described above has a simple structure including fitting holes or engaging projections on both sides of the cylindrical body, and the drive shaft m (motor shaft) and the driven shaft a (pump shaft) are coaxial. It is an excellent one that can be connected, and is generally made of metal. However, when a metal drive joint J is used, a transmission sound generated along with the transmission from the drive shaft m to the driven shaft a is generated. There is a problem of being big. This transmission sound is caused by the backlash of the fitting portion of the driven shaft a with the drive joint J accompanying the vibration of the driven shaft a. The drive joint J is made of resin, and the resin It can be reduced by absorbing the vibration using the elasticity of. However, the drive joint J made of resin has a small torque that can be transmitted, and when it is made the same size as that made of metal, there is a possibility that the resin drive joint J may be damaged by a large torque load, thereby enabling transmission of desired torque. For this reason, there is a problem that enlargement is inevitable.

  The present invention has been made in view of such circumstances, and is elastic to the gap between the concave section having a modified cross section and the convex section having a predetermined section that is loosely fitted inside the concave section. An object of the present invention is to provide a compact drive joint that can transmit a large torque by interposing a body and can significantly reduce the generation of transmission sound.

  A drive joint according to a first aspect of the present invention is a drive joint used for coaxially connecting a drive shaft and a driven shaft so that power can be transmitted. The drive joint is coaxially attached to one of the drive shaft and the driven shaft, and has a deformed cross section. A first connecting member having a concave portion, a second connecting member that is coaxially attached to the other, and has a convex portion having an irregular cross section that is loosely fitted inside the concave portion with a predetermined gap, and the gap And an interposed elastic body.

  A drive joint according to a second aspect of the invention is characterized in that the elastic body is configured by filling synthetic rubber into a gap formed between the first and second connecting members by the loose fitting.

  The drive joint according to a third aspect is characterized in that the first and second connecting members are press-formed products of a metal material.

  According to the drive joint according to the first aspect of the present invention, the first connecting member attached to one of the drive shaft and the driven shaft is provided with the recess having the irregular cross section, and the convex having the irregular cross section provided in the second connection member attached to the other is provided. Provided with an elastic body in the gap between the concave part and the convex part that are loosely fitted to each other, and vibration accompanying transmission from the drive shaft to the driven shaft is absorbed by the elastic body. On the other hand, at the time of transmission of large torque, the concave portion and the convex portion are brought into direct contact with the deformation of the elastic body when torque is transmitted, so that transmission of large torque and significant transmission noise Excellent effects are achieved, for example, a quiet operation by reduction is realized.

  According to the drive joint according to the second aspect of the present invention, the elastic body can be easily and surely provided by filling the gap between the two portions with the synthetic rubber while the convex portion is loosely fitted inside the concave portion. .

  According to the drive joint according to the third aspect of the present invention, the first and second connecting members are metal press-molded products, which can reliably transmit large torque under direct contact, and the first and first 2 The connecting member is configured at low cost.

  Hereinafter, the present invention will be described in detail with reference to the drawings illustrating embodiments thereof. 1 is a longitudinal side view of an electric pump using a drive joint according to the present invention, FIG. 2 is a cross-sectional view taken along line XX of FIG. 1, and FIG. 3 is a cross-sectional view taken along line YY of FIG.

  The electric pump shown in FIG. 1 has an electric motor 2 having a drive shaft 1 (motor shaft) and a driven shaft 4 (pump shaft) interlocked with the drive shaft 1 via a drive joint 3, and the electric motor 2 and a driven gear 6 meshed with the drive gear 5, a pump housing 7 having a suction chamber 71 and a discharge chamber 72 formed by meshing of the drive and driven gears 5 and 6, and the pump First and second housing supports 8 and 9 that support the housing 7 from both sides, and a bottomed cylindrical tank housing 10 that fits outside the second housing support 9 and the pump housing 7 are provided.

  The pump housing 7 accommodates the drive gear 5 and the driven gear 6 and has a cylindrical body portion 7 a having an oval gear chamber 70 that communicates with each other, and a pair of side plates that close both side open portions of the gear chamber 70. 7b and 7c, and is driven through the driven shaft 4 and a driven shaft (not shown) parallel to the driven shaft 4 in two sets of bearing holes formed in the side plates 7b and 7c. The gear 5 and the driven gear 6 are meshed with each other and supported rotatably, and the suction chamber 71 and the discharge chamber 72 are formed on both sides of the meshing position so that the hydraulic oil sucked into the suction chamber 71 is supplied. The drive and driven gears 5 and 6 are received between the teeth, sealed between the gear chamber 70 and the inner peripheral surface, and pumped to the discharge chamber 72.

  A suction port 73 that opens to the gear chamber 70 is provided at one place of the body portion 7a, a first discharge passage 74 that penetrates in the axial length direction is provided on the opposite side, and the discharge chamber is provided on one side plate 7b. Discharge ports 75 that open to 72 are respectively provided. The suction port 73 is connected to a rubber silencer 11 extending upward along the peripheral surface of the low pressure chamber, which will be described later, and sealed between a pair of meshing teeth of the drive and driven gears 5 and 6. The sound generated when the pressurized oil is returned to the suction chamber 71 can be eliminated.

  A second housing support 9 that supports the pump housing 7 is detachably attached to the motor housing of the electric motor 2, and the second housing support 9 is attached to the outer surface of the body portion 7 a as shown in FIG. 2. Are detachably attached to the first housing support 8 via four screw bodies 12, 12... Arranged along the same, and the pump housing 7 is fixedly fixed by attaching the second housing support 9. I am doing so.

  The second housing support 9 has a first communication hole 91 that communicates with the discharge port 75 and a second communication hole 92 that is drilled in parallel with the first communication hole 91. A plate wall portion 9a that is in contact with one end in the direction, and a cylindrical wall portion 9b that is connected to the outer peripheral portion of the plate wall portion 9a. The cylindrical wall portion 9b is provided with the first communication hole 91 and the discharge port 75 interposed therebetween. A bottomed noise damper cylinder 20 that communicates with the discharge chamber 72 and has a larger volume of the empty chamber 20a than the discharge chamber 72 is detachably attached.

  The first housing support 8 includes a substantially L-shaped second discharge oil passage 81 that communicates with the first discharge oil passage 74, a relief oil passage 82 that opens to the second discharge oil passage 81, and the relief oil passage. An annular oil return passage 83 communicating with the relief oil passage 82 via a relief valve 14 attached to the passage 82 and an insertion hole 84 through which the driven shaft 4 is inserted. The oil seal 15 is inserted into the insertion hole 84. Is provided. The oil return path 83 communicates with the low pressure chamber 16 defined in the tank housing 10 so that the relief hydraulic oil can be returned to the low pressure chamber 16.

  The relief valve 14 is a cartridge type including a valve body 14a that closes the relief oil passage 82, a valve spring 14b that urges the valve body 14a, and a valve housing 14c that holds the valve body 14a and the valve spring 14b. Yes, it is detachably inserted and held in the relief oil passage 82, and the valve body 14a is opened when the second discharge oil passage 81 is overpressured. Further, the valve housing 14c is in contact with the plate wall portion 9a of the second housing support 9 and is prevented from coming off.

  The tank housing 10 includes a clamp ring 17 abutted against the opening flange 10a, and four fixing bolts 40 passing through the clamp ring 17 in the axial length direction. It is detachably attached to the side.

The inside of the tank housing 10 is used as an oil tank that stores hydraulic oil. A circular partition plate 18 is inserted and fixed in the tank housing 10, and the pump housing 7, the second housing support 9 and the noise damper cylinder 20 are placed between the partition plate 18 and the first housing support 8. A return chamber 19 is defined between the partition plate 18 and the bottom portion 10b of the surrounding low-pressure chamber 16, respectively. The return chamber 19 is supplied with hydraulic oil stored in a sub tank (not shown) by its own weight, and further supplied from the return chamber 19 to the low pressure chamber 16 through three oil return holes 18a. Is done.
The oil return hole 18 is formed on the lower side in the radial direction of the partition plate 18 so that the oil in the return chamber 19 is decompressed and returned to the low pressure chamber 16 from the oil return hole 18a.

  Further, the plate wall portion 9a of the second housing support 9 is provided with a valve hole 95 that opens to the discharge chamber 72, and the valve hole 95 includes a valve body and a valve spring that biases the valve body. 41, when the electric motor 2 is stopped due to a failure or the like in a state where the pressure oil is supplied to the one-side working chamber of the hydraulic actuator, one of the hydraulic oils in the high-pressure side hydraulic path to which the pressure oil is supplied. The part can be returned from the discharge chamber 72 through the check valve 41 into the noise damper cylinder 20.

  The driven shaft 4 (pump shaft) that supports the drive gear 5 passes through the insertion hole 84 of the first housing support 8 and protrudes toward the electric motor 2, and is fixedly supported on the other side of the first housing support 8. The drive shaft 1 (motor shaft) of the electric motor 2 is abutted on the same axis, and the drive shaft 1 and the driven shaft 4 are connected by the drive joint 3.

  As shown in FIG. 1, the drive joint 3 includes a first connecting member 31 attached to the drive shaft 1 and a second connecting member 32 attached to the driven shaft 4. The drive shaft 1 and the driven shaft 4 that are connected by the drive joint 3 are connected protrusions 1a having a rectangular cross-section projecting from the respective tip ends that are coaxially opposed to each other so as to be centered on the shaft center. 4a.

  4 is a perspective view of the first connecting member, FIG. 5 is a longitudinal sectional view of the first connecting member, FIG. 6 is a perspective view of the second connecting member, and FIG. 7 is a longitudinal sectional view of the second connecting member. As shown in FIGS. 4 and 5, the first connecting member 31 includes a connecting cylinder 31 b that protrudes from one side of a disk-shaped substrate 31 a. A fitting hole 31c having substantially the same rectangular cross section as the connection protrusion 1a at the tip of the drive shaft is formed through the shaft center portion of the substrate 31a. The attachment of the first connection member 31 to the drive shaft 1 is illustrated in FIG. 4, the connecting projection 1 a of the drive shaft 1 is closely fitted into the fitting hole 31 c of the first connecting member 31 from the side opposite to the protruding side of the connecting cylinder 31 b. Yes. As shown in FIG. 4, the connecting cylinder 31b has a shape with six chevron projections that are substantially evenly arranged in the circumferential direction of the thin cylinder, and the inside of the connecting cylinder 31b is aligned with the fitting hole 31c. A recess 31d is formed in a flower-shaped cross-section having six petals.

  As shown in FIGS. 6 and 7, the second connecting member 32 includes a convex portion 32 b that protrudes from one side of a disc-like substrate 32 a. A fitting hole 32c having substantially the same rectangular cross section as the connection protrusion 4a at the tip of the driven shaft 4 is formed in the shaft center portion of the substrate 32a so as to penetrate to the end surface of the convex portion 32b. The second connecting member 32 is attached to the fitting projection 32a of the driven shaft 4 in the fitting hole 32c of the second connecting member 32 as shown by an arrow in FIG. It is tightly fitted from the opposite side. As shown in FIG. 6, the convex portion 32 b corresponds to the inner periphery of the concave portion 31 d of the first connecting member 31 on both end surfaces of the rectangular long axis that have an appropriate thickness and rim around the fitting hole 32 c. And a short rectangular protrusion at the center of both end faces in the short axis direction. FIG. 7 shows a cross section in the minor axis direction of the convex portion 32b and the fitting hole 32c.

  The first connecting member 31 and the second connecting member 32 configured as described above and attached to the drive shaft 1 and the driven shaft 4 respectively face the end surfaces on the side shown in FIGS. The drive joint 3 that connects the drive shaft 1 and the driven shaft 4 is configured by fitting the convex portion 32b of the second connecting member 32 inside the concave portion 31d.

  FIG. 8 is a cross-sectional view showing a state in which the first connecting member 31 and the second connecting member 32 are combined. As shown in the figure, the first connecting member 31 and the second connecting member 32 include a fitting hole 31c of the first connecting member 31 into which the connecting projection 1a at the tip of the drive shaft 1 is fitted, and a connecting projection at the tip of the driven shaft 4. The fitting hole 32c of the 2nd connection member 32 with which 4a is fitted is fitted so that both the centers may be orthogonally crossed, and the rectangle which protruded from the short-axis direction both end surface of the 2nd connection member 32 was provided. Positioning in the state where rectangular rod-shaped rubber spacers 33 are interposed in four rectangular spaces formed between both sides of the projection and the inner surface of the recess 31d of the first connecting member 31. Has been.

  At this time, the chevron-shaped protrusions on both sides in the longitudinal direction of the convex portion 32b of the second connecting member 32 are located at two locations that are radially opposite to each other inside the concave portion 31d having the flower-shaped cross section of the first connecting member 31. The first connecting member 31 and the second connecting member 32 are filled with a synthetic rubber in the gap except for the positions where the spacers 33, 33,... Are inserted in this state. In addition, the elastic buffer layer 34 is formed and integrated to form the drive joint 3 according to the present invention.

  The drive joint 3 configured as described above is arranged between the opposed portions of the drive shaft 1 and the driven shaft 4, and the connection protrusion 1 a at the tip of the drive shaft 1 is inserted into the fitting hole of the first connection member 31 as described above. The drive shaft 1 and the driven shaft 4 are used to connect the drive shaft 1 and the driven shaft 4 as shown in FIG. 1 by fitting the connection protrusion 4a at the tip of the drive shaft 4 to the fitting hole 32c of the second connection member 32. . At this time, since the fitting hole 31c and the fitting hole 32c are positioned so as to be orthogonal to each other with the centers thereof aligned as described above, the driving shaft 1 and the driven shaft 4 are fitted to each other as described above. By the alignment, they are correctly positioned and connected on the same axis.

  This connection is made by fitting one side of the drive joint 3 to the drive shaft 1 or the driven shaft 4 before fixing the electric motor 2 to the first housing support 8, and to the other side of the drive joint 3. The procedure is performed by fixing the electric motor 2 to the first housing support 8 while fitting the drive shaft 4 or the drive shaft 1. At this time, the alignment of the drive shaft 1 and the driven shaft 4 is simultaneously performed as described above. Since this is achieved, there is an effect that when the hydraulic pump and the electric motor 2 are integrated, they can be easily aligned.

  The drive joint 3 attached as described above performs an operation of transmitting the rotation of the electric motor 2 as a driving source to the driven shaft 4 via the driving shaft 1 so that the electric pump performs a pumping operation. In the electric pump, when the electric motor 2 is driven, the drive gear 5 and the driven gear 6 are rotated through the drive shaft 1 (motor shaft) and the driven shaft 4 (pump shaft), and the rotations of the drive and driven gears 5 and 6 are rotated. Accordingly, the hydraulic oil in the low pressure chamber 16 is sucked into the suction chamber 71 from the muffler tube 11, and each oil chamber defined by the space between the tooth portions and the gear chamber circumferential surface is opened to the discharge chamber 72. Then, pressure oil is generated, and this pressure oil is supplied into the noise damper cylinder 20 through the discharge port 75 and the first communication path 91. The noise damper cylinder 20 has a larger volume in the empty chamber 20a than the discharge chamber 72, so that the pressure oil pulsation is reduced.

  Since the noise damper cylinder 20 is thus provided to reduce the pulsation of the pressure oil, the vibration of the driven shaft 4 due to the pulsation can be reduced. The pressure oil in the noise damper cylinder 20 is supplied to the one-side working chamber of the hydraulic actuator machine via the second communication path 92, the first and second discharge oil paths 74 and 81. The hydraulic oil returned to the return chamber 19 from the oil return pipe 42 communicating with the other-side working chamber of the hydraulic actuator machine is decompressed from the oil return hole 18 a of the partition plate 18 and returned to the low pressure chamber 16.

  The drive joint 3 according to the present invention has a configuration in which the first connecting member 31 and the second connecting member 32 having the above-described shapes are fitted together via an elastic spacer 33 and a buffer layer 34. The vibration reduced by the noise damper chamber 20a is absorbed by the elastic deformation of the spacer 33 and the buffer layer 34, and the generation of sound due to the vibration can be effectively reduced.

  On the other hand, when the load of the hydraulic pump increases, the first connecting member 31 and the second connecting member 32 rotate relative to each other with a large deformation of the spacer 33 and the buffer layer 34 therebetween, and the second connecting member 32 The mountain-shaped protrusions on both sides in the longitudinal direction of the convex portion 32 b are in a state of being in direct contact with the inner surface of the concave portion 31 d of the first connecting member 31. FIG. 9 is a cross-sectional view showing this state.

  In such a state, torque transmission from the drive shaft 1 to the driven shaft 4 is borne by the contact portion between the concave portion 31d and the convex portion 32b, so that stable transmission of large torque is possible. Become. The first connecting member 31 having the shape as shown in FIGS. 4 and 5 and the second connecting member 32 having the shape as shown in FIGS. 6 and 7 can both be configured as a press-formed product of a metal material, which is a high machine. By using a metal material having sufficient strength, the value of rotational torque that can be transmitted under direct contact as described above can be increased.

  FIG. 10 is a diagram comparing torque transmission characteristics of the drive joint 3 according to the present invention and a conventional drive joint as shown in FIGS. 12 and 13. The conventional drive joint indicated by the broken line in the figure is damaged at the point P due to the increase in the transmission torque accompanying the increase in the input torque, and further torque transmission becomes impossible, whereas the book indicated by the solid line in the figure. In the drive joint 3 according to the invention, it is possible to reliably load a wide range of input torque without being damaged even under a load of transmission torque corresponding to the point P.

  FIG. 11 is a cross-sectional view showing another embodiment of the drive joint of the present invention, and shows a state in which the first connecting member 31 and the second connecting member 32 are combined as in FIG. The first connecting member 31 of the drive joint includes a recess 31d having the same shape as that of FIG. 8, but the second connecting member 32 is different from that of FIG. 8 and has a similar shape slightly smaller than the recess 31d. A convex portion 32b is formed, and the convex portion 32b is loosely fitted inside the concave portion 31d, and a synthetic rubber is placed in a gap formed between the two with a substantially uniform width. The buffer layer 34 is formed by filling.

  As described above, the shapes of the concave portion 31d of the first connecting member 31 and the convex portion 32b of the second connecting member 32 can be loosely fitted to each other, and a direct contact portion can be generated in a part thereof during relative rotation. The shape, that is, any irregular cross-section other than a circle may be used. Further, the elastic body interposed in the gap between the two is not limited to the rubber material as shown in the above embodiment, and may be any material rich in elasticity. In the above embodiment, the first connecting member 31 is attached to the motor shaft that is the drive shaft 1 and the second connecting member 32 is attached to the pump shaft that is the driven shaft 4. In other words, it goes without saying that the second connecting member 32 may be attached to the drive shaft 1 and the first connecting member 31 may be attached to the driven shaft 4.

  Furthermore, in the above embodiment, although the usage example to the hydraulic pump used as the hydraulic power source for the power steering apparatus has been described, the application range of the drive joint 3 according to the present invention is not limited to this, and the load fluctuation is not limited. In addition, it can be used in a wide range of applications where the mounting position is limited, and it is possible to achieve both large torque transmission and quiet operation.

It is a vertical side view of the electric pump which uses a drive joint concerning the present invention. It is sectional drawing of the XX line of FIG. It is sectional drawing of the YY line | wire of FIG. It is a perspective view of a 1st connection member. It is a longitudinal cross-sectional view of a 1st connection member. It is a perspective view of the 2nd connecting member. It is a longitudinal cross-sectional view of a 2nd connection member. It is a cross-sectional view which shows the state which combined the 1st connection member and the 2nd connection member. It is a cross-sectional view which shows the state at the time of large torque transmission. It is the figure which compared the torque transmission characteristic of the drive joint which concerns on this invention, and the conventional drive joint. It is a cross-sectional view showing another embodiment of the drive joint according to the present invention. It is a vertical side view which shows the conventional electric pump. It is a perspective view of the drive joint used conventionally.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Drive shaft 3 Drive joint 4 Driven shaft 31 1st connection member 31d Concave part 32 2nd connection member 32b Convex part 33 Spacer (elastic body)
34 Buffer layer (elastic body)

Claims (3)

  A drive joint used to connect a drive shaft and a driven shaft coaxially so that power can be transmitted, and is coaxially attached to one of the drive shaft and the driven shaft, and has a first connection member having a recess having a deformed cross section. A second connecting member that is coaxially attached to the other and has a convex portion having an irregular cross section that is loosely fitted inside the concave portion with a predetermined gap, and an elastic body interposed in the gap. A drive joint characterized by   The drive joint according to claim 1, wherein the elastic body is configured by filling a synthetic rubber into a gap formed between the first and second connecting members by the loose fitting. The drive joint according to claim 1 or 2, wherein the first and second connecting members are press-formed products of a metal material.

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