JP7011382B2 - Rubber coupling - Google Patents

Description

The present invention relates to a rubber coupling that connects a drive side shaft portion on the transmission side of a vehicle and a driven side shaft portion on the differential gear side in series.

The rubber coupling that connects the drive side shaft on the transmission side of the vehicle and the driven side shaft on the differential side in series absorbs the rotational vibration (pulsation) of the engine and absorbs the vibration caused by the back crash of the differential gear. A function of suppressing and smoothly transmitting rotation is required, and a function of absorbing the eccentricity between the driven side shaft portion and the driven side shaft portion and the axial displacement is required.

By the way, in Patent Document 1, a bolt (connecting element) in the circumferential direction connecting the drive system and the driven system is provided in the circumferential direction of the elastic body, and these connecting elements are connected to each other by a cord to generate a rotational driving force. It is transmitted from the driven side to the driven side, and the eccentricity and the axial displacement are adjusted by the deflection of the elastic body.

Jikkenhei 5-64537 Gazette

However, if the connecting elements are connected by a cord, the manufacturing cost is high, and it is difficult to control the degree of damping of the vibration due to the vibration of the engine or the torque fluctuation due to the backlash of the transmission. Further, it is necessary to separately provide a mechanism for absorbing the axial displacement.

Therefore, the present invention was conceived in view of such circumstances, and its purpose is to absorb rotational pulsation and vibration caused by torque fluctuations due to engine vibration and transmission backlash, and to transmit power, as well as axial displacement between the transmission and the differential gear. Is to provide a rubber coupling that can absorb.

According to one aspect of the present invention, in a rubber coupling for connecting a drive side shaft portion on the transmission side of a vehicle and a driven side shaft portion on the differential gear side in series, the drive side shaft portion and the driven side are connected. A coupling body disposed between the shaft portion, a plurality of through holes provided in the coupling body along the circumferential direction and penetrating in the axial direction, and a tubular outer bush arranged in the through holes. And the support rubber arranged in the through hole to support the outer bush displaceably, and slidably provided in the outer bush and fastened to the drive side shaft portion or the driven side shaft portion. A rubber coupling is provided that features an inner slider and.

According to the present invention, it is possible to absorb rotational pulsations and vibrations to transmit power, and also to absorb axial displacement between the transmission and the differential gear.

It is a side sectional view of the rubber coupling which concerns on one Embodiment of this invention. FIG. 3 is a cross-sectional view taken along the line AA of FIG. It is a perspective view of a rubber coupling. It is a front view of a rubber coupling. It is a schematic explanatory drawing of the power transmission system to which a rubber coupling is applied. It is an enlarged view of the main part of the rubber coupling which concerns on other embodiment.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

[First Embodiment]
FIG. 5 shows an example in which the rubber coupling according to the present invention is applied to the power transmission system of a vehicle. 3 is an enlarged perspective view of the rubber coupling of FIG. 5, and FIG. 4 is a front view of the rubber coupling of FIG. 5 as viewed from the axial direction.

As shown in FIG. 5, the power of the engine 1 is input to the transmission 2 and transmitted from the transmission 2 to the differential gear 4 via the propeller shaft 3.

The propeller shaft 3 includes a first propeller shaft 3a connected to the transmission 2, a second propeller shaft 3b connected to the differential gear 4, and a universal joint 5 connecting the first propeller shaft 3a and the second propeller shaft 3b. To prepare for. The first propeller shaft 3a has a drive side shaft portion 6a connected to the transmission 2, a driven side shaft portion 7a connected to the universal joint 5, a drive side shaft portion 6a, and a driven side shaft portion 7a in series. It is provided with a rubber coupling 8 to be connected. Further, the second propeller shaft 3b includes a drive side shaft portion 6b connected to the universal joint 5, a driven side shaft portion 7b connected to the differential gear 4, a drive side shaft portion 6b, and a driven side shaft portion 7b. Is provided with a rubber coupling 8 for connecting in series.

The rubber coupling 8 absorbs rotational pulsation and vibration caused by vibration of the engine 1 and torque fluctuation due to backlash of the transmission 2 to transmit power, and also absorbs axial displacement between the transmission 2 and the differential gear 4. Is for.

As shown in FIGS. 3 and 4, the rubber coupling 8 is formed in a substantially disk shape and is fastened to the drive side shaft portion 6a and the driven side shaft portion 7a. Further, on the drive side shaft portion 6a and the driven side shaft portion 7a, fastening flanges 9 for fastening to the rubber coupling 8 are formed so as to extend radially outward in the radial direction. Specifically, the fastening flanges 9 are formed at intervals of 120 ° in the circumferential direction. Further, the drive side shaft portion 6a and the driven side shaft portion 7a are arranged so that the positions of the fastening flange 9 in the circumferential direction are displaced by 60 °, and are fastened to the rubber coupling 8 described later at alternating positions in the circumferential direction. Will be done.

FIG. 1 is a side sectional view of the rubber coupling 8. Since the rubber coupling 8 provided on the second propeller shaft 3b is the same as that of the first propeller shaft 3a, the description thereof will be omitted.

As shown in FIGS. 1 and 2, the rubber coupling 8 has a coupling main body 10 disposed between the drive side shaft portion 6a and the driven side shaft portion 7a, and the coupling main body 10 in the circumferential direction. A plurality of through holes 11 provided along the line and penetrating in the axial direction, a tubular outer bush 12 arranged in the through hole 11, and a through hole 11 arranged to support the outer bush 12 in a displaceable manner. A support rubber 13 and an inner slider 14 slidably provided in the outer bush 12 and fastened to the drive side shaft portion 6a or the driven side shaft portion 7a are provided.

The coupling body 10 is formed of a metal such as iron or die-cast in a disk shape. Further, a hole H for weight reduction is formed in the center of the coupling body 10. The coupling body is not limited to the above. For example, the coupling body may have a metal plate embedded in a rubber, a metal cord embedded in the rubber, or another one.

Six through holes 11 are formed in the outer peripheral portion of the coupling main body 10 at intervals of 60 ° in the circumferential direction. The through holes 11 are not limited to six places. For example, the through holes 11 may be a plurality of four or more places.

The outer bush 12 is formed in a tubular shape having a diameter sufficiently smaller than that of the through hole 11. The outer bush 12 is made of metal and is formed longer in the axial direction than the through hole 11.

The support rubber 13 is formed of vulcanized rubber. The support rubber 13 may be made of another soft resin. The support rubber 13 is filled between the tubular fitting member 17 fitted in the through hole 11 and the outer bush 12, and is integrated with the fitting member 17 and the outer bush 12. As a result, the fitting member 17, the outer bush 12, and the support rubber 13 can be unitized, and can be manufactured in parallel with the coupling main body 10. If the support rubber 13 is to be formed directly on the coupling body 10, a metal portion of the coupling body is formed by press working, machining, or the like, and then a plurality of support rubbers 13 are formed on the metal portion. At the same time, the outer bush 12 must be provided. In particular, molding of vulcanized rubber requires time and specialized equipment, so that there is a possibility that the size of the equipment and the production efficiency become problems. However, by forming the support rubber 13 between the outer bush 12 and the fitting member 17 and unitizing it, the support rubber 13 can be efficiently formed even if the equipment is small, and the metal portion and the support rubber portion of the coupling body can be formed efficiently. Can be manufactured in parallel, and the rubber coupling 8 can be efficiently manufactured.

The inner slider 14 is inserted into the inner bush 15 slidably provided in the outer bush 12 and the inner bush 15, and the inner bush 15 is fastened to the drive side shaft portion 6a or the driven side shaft portion 7a. A fastener 16 is provided.

The inner bush 15 is formed in a cylindrical shape that loosely fits with the outer bush 12, and is formed longer in the axial direction than the outer bush 12. Further, the inner bush 15 is made of metal and has a nylon coating 18 on the outer peripheral surface. The nylon coating 18 enhances the lubricity between the inner bush 15 and the outer bush 12.

The nylon coating 18 may be applied to the inner peripheral surface of the outer bush 12. Further, instead of the nylon coating 18, a surface treatment such as a coating of another lubricating material or a plating treatment may be performed.

Further, a lubricating oil such as grease is applied to the outer peripheral surface of the inner bush 15 coated with the nylon coating 18. As a result, the friction between the inner bush 15 and the outer bush 12 is further reduced.

Further, boots 19 for holding the lubricating oil are provided on the outer periphery of the inner bush 15 extending in the axial direction from the outer bush 12.

The boot 19 is made of metal, is formed in a cylindrical shape that covers the outer periphery of the inner bush 15, and is formed in a bellows shape. Further, the boot 19 is formed so that one end in the axial direction abuts on the outer bush 12 and the other end abuts on the enlarged diameter portion 20 of the inner bush 15 described later or the head portion 21 of the fastener 16 described later. It covers the sliding surface 14a of the inner bush 15 extending in the axial direction from the outer bush 12. As a result, the boot 19 suppresses or prevents foreign matter such as muddy water, sand, and dust from adhering to the sliding surface 14a of the inner bush 15. Then, the possibility that muddy water infiltrates between the inner bush 15 and the outer bush 12 to generate rust can be reduced, and the space between the inner bush 15 and the outer bush 12 due to foreign matter entering between the inner bush 15 and the outer bush 12 can be reduced. It is possible to reduce the increase in sticking and sliding resistance. Further, the outflow of the lubricating oil can be suppressed or prevented, and a lubricating oil pocket can be formed at the bent portion of the bellows of the boot 19. As a result, the sliding performance of the sliding portion can be well maintained for a long period of time. Further, the boot 19 is formed in a bellows shape to form a spring that can be expanded and contracted in the axial direction.

Further, the inner bush 15 has a diameter-expanded portion 20 for receiving the driven side shaft portion 6a or the driven side shaft portion 7a at one end. The enlarged diameter portion 20 is formed to have a diameter larger than the inner diameter of the outer bush 12, and also functions as a stopper for the outer bush 12. Further, the inner bush 15 is arranged along the circumferential direction of the coupling body 10 so that the axial positions of the enlarged diameter portions 20 are alternately opposite to each other.

The fastener 16 is composed of a bolt 16a and a nut 16b. The fastener 16 is inserted from the other end of the inner bush 15 to one end side and fastened to the fastening flange 9 of the driven side shaft portion 6a or the driven side shaft portion 7a. The head portion 21 of the fastener 16 is formed to have a diameter larger than the inner diameter of the outer bush 12, and also functions as a stopper for the outer bush 12.

The inner slider 14 is provided with an inner bush 15 and a fastener 16, but is not limited to this. The inner slider 14 may have the inner bush 15 and the fastener 16 integrally formed.

Next, the operation of this embodiment will be described.

As shown in FIG. 5, when the driving force from the engine 1 is transmitted to the driving side shaft portion 6a of the first propeller shaft 3a via the transmission 2, the driving force of the driving side shaft portion 6a is applied to the fastener 16 and the inner. It is transmitted to the support rubber 13 via the bush 15 and the outer bush 12. At this time, the rotation of the engine 1 is accompanied by pulsation, but since the support rubber 13 absorbs the pulsation, the force transmitted from the support rubber 13 to the coupling body 10 is averaged. Further, the force transmitted from the coupling body 10 to the driven side shaft portion 7a side is further averaged through the other support rubber 13, and the pulsation is further absorbed. As a result, the driven side shaft portion 7a is smoothly rotated in contrast to the driving side shaft portion 6a accompanied by pulsation, and the driving feeling can be kept good. Further, even when the impact due to the backlash on the differential gear 4 side is transmitted to the rubber coupling 8, the impact can be absorbed by the support rubber 13, and the driving feeling can be kept good.

Further, when the differential gear 4 moves up and down by traveling on the unevenness of the road surface, the distance between the rubber coupling 8 and the differential gear 4 fluctuates. In this case, the driven side shaft portion 7a moves in the axial direction, but the inner bush 15 fastened to the driven side shaft portion 7a slides with respect to the corresponding outer bush 12 and becomes the drive side shaft portion 6a. Since the outer bush 12 corresponding to the fastened inner bush 15 slides with respect to the inner bush 15, it is possible to absorb the axial movement of the driven side shaft portion 7a.

Further, even with the flexible coupling described in Cited Document 1, it is possible to absorb the axial movement of the driven side shaft portion 7a by deforming it, but for that purpose, it is necessary to adjust the hardness of the flexible coupling. Therefore, it is extremely difficult to achieve both the performance of absorbing pulsations and impacts in the rotational direction and the performance of absorbing the axial movement of the driven side shaft portion 7a. However, in the rubber coupling 8 according to the present embodiment, the absorption performance such as pulsation in the rotational direction and the absorption performance of the axial movement can be set independently and separately, so that both performances can be easily compatible. Can be done.

Further, the boot 19 that receives the load in the compression direction due to the movement of the driven side shaft portion 7a elastically degenerates. Therefore, when the position of the driven side shaft portion 7a is returned to the original position, the boot 19 acts to return the coupling body 10 to the axial center position of the inner bush 15. As a result, the rubber coupling 8 can always be prepared for the next operation, and the desired performance can be stably exhibited.

In this way, a plurality of rubber couplings 8 are provided on the coupling main body 10 arranged between the drive side shaft portion 6a and the driven side shaft portion 7a and the coupling main body 10 along the circumferential direction. A through hole 11 penetrating in the axial direction, a tubular outer bush 12 arranged in the through hole 11, a support rubber 13 arranged in the through hole 11 to support the outer bush 12 in a displaceable manner, and an outer. An inner bush 15 slidably provided in the bush 12, and a fastener 16 inserted into the inner bush 15 for fastening the inner bush 15 to the drive side shaft portion 6a or the driven side shaft portion 7a. Be prepared. Therefore, it is possible to obtain both the rotational performance that absorbs pulsations and vibrations in the rotational direction and the axial performance that absorbs the axial displacement between the transmission 2 and the differential gear 4. From this, it is possible to reduce or eliminate the need to separately provide a mechanism (for example, spline engagement, etc.) for absorbing the axial displacement in the propeller shaft 3, and power transmission between the transmission 2 and the differential gear 4 of the vehicle. The system can be simplified and the reliability of the power transmission system can be improved.

Further, since the nylon coating 18 is applied to the outer peripheral surface of the inner bush 15, the sliding resistance between the inner bush 15 and the outer bush 12 can be reduced by simple processing.

Further, the inner bush 15 is formed longer in the axial direction than the outer bush 12, lubricating oil is applied to the outer periphery of the inner bush 15, and lubricating oil is held on the outer periphery of the inner bush 15 extending from the outer bush 12. Boots 19 for this shall be provided. Therefore, it is possible to suppress or prevent foreign matter such as sand and dust from adhering to the outer periphery of the inner bush 15, and it is possible to keep the lubricating oil on the outer periphery of the inner bush 15 for a long time, so that the inner bush 15 and the outer bush 12 can be kept. The sliding resistance between them can be stably suppressed to a low level.

Further, since the boot 19 constitutes a spring that can be expanded and contracted in the axial direction, the coupling body 10 can be returned to the center position in the axial direction of the inner bush 15, and the axial direction between the transmission 2 and the differential gear 4 can be obtained. Displacement can be absorbed permanently and stably.

Since the cylindrical fitting member 17 is fitted into the through hole 11 and the support rubber 13 is provided between the fitting member 17 and the outer bush 12, the outer bush 12 and the support rubber 13 can be unitized and the support rubber 13 can be unitized. The metal portion of the coupling body 10 and the supporting rubber portion can be manufactured in parallel, and the rubber coupling 8 can be efficiently manufactured.

[Second Embodiment]
Next, a second embodiment of the present invention in which the boots 19 and the support rubber 13 are modified will be described. Since the configurations other than the boots and the support rubber are the same as those in the first embodiment, the same reference numerals are given and the description thereof will be omitted.

As shown in FIG. 6, the boot 30 is formed of vulcanized rubber and is integrally formed with the support rubber 31. Specifically, the boot 30 is formed so as to extend axially outward from both ends of the support rubber 31 formed between the outer bush 12 and the fitting member 17 on the outer bush 12 side and have a bellows shape. Is formed in. Further, the boot 30 is formed so that the tip thereof abuts on the enlarged diameter portion 20 of the inner bush 15 or the head portion 21 of the fastener 16, and the sliding of the inner bush 15 extending axially from the outer bush 12 Covers surface 14a.

As described above, even if the boot 30 is integrally formed with the support rubber 31, it is possible to suppress or prevent foreign matter such as sand and dust from adhering to the outer periphery of the inner bush 15, and the inner bush 15 can be kept lubricated for a long time. The sliding resistance between the inner bush 15 and the outer bush 12 can be stably suppressed to a low level.

The configurations of each of the above embodiments can be partially or wholly combined, as long as there is no particular contradiction. The embodiment of the present invention is not limited to the above-described embodiment, and all modifications, applications, and equivalents included in the idea of the present invention defined by the scope of claims are included in the present invention. Therefore, the present invention should not be construed in a limited manner and can be applied to any other technique belonging to the scope of the idea of the present invention.

6 Drive side shaft part 7 Driven side shaft part 8 Rubber coupling 10 Coupling body 11 Through hole 12 Outer bush 13 Support rubber 14 Inner slider

Claims (6)

In a rubber coupling that connects the drive side shaft on the transmission side of the vehicle and the driven side shaft on the differential gear side in series.
A coupling body disposed between the drive side shaft portion and the driven side shaft portion, and
A plurality of through holes provided in the coupling body along the circumferential direction and penetrating in the axial direction,
A cylindrical outer bush arranged in the through hole and
A support rubber arranged in the through hole to support the outer bush in a displaceable manner,
An inner slider provided in the outer bush so as to be slidable in the axial direction and to be fastened to the drive side shaft portion or the driven side shaft portion.
Equipped with
The inner slider is formed longer in the axial direction than the outer bush.
Lubricating oil is applied to the outer circumference of the inner slider.
Boots for holding the lubricating oil are provided on the outer periphery of the inner slider extending from the outer bush.
The boot was integrally formed with the support rubber.
A rubber coupling that features that. The rubber coupling according to claim 1, wherein the inner peripheral surface of the outer bush or the outer peripheral surface of the inner slider is coated with a lubricant. The rubber coupling according to claim 2, wherein the lubricant is nylon. The rubber coupling according to claim 1, wherein the inner peripheral surface of the outer bush or the outer peripheral surface of the inner slider is plated. The rubber coupling according to any one of claims 1 to 4, wherein the boot constitutes a spring that can be expanded and contracted in the axial direction. One of claims 1 to 5 , wherein a cylindrical fitting member is fitted in the through hole, and the support rubber is provided between the fitting member and the outer bush. The rubber coupling described in.

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