JP2002340043A - Coupling - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent oil leakage and the like by suppressing an expansion of a rotary case due to a thermal expansion of oil filled inside. SOLUTION: A coupling 1 is of a sealed type that comprises the rotary case 3 and an inner shaft 5, and connects power from either the rotary case 3 and the inner shaft to the other interruptively. A rotor 25 for closing an open side of the rotary case 3 is fixedly inserted in the rotary case 3, and an expansion suppressing means 31 for suppressing a radial expansion of the rotary case 3 is arranged. The expansion suppressing means 31 is formed of a material with a coefficient of thermal expansion smaller than that of the rotary case 3 and substantially same as that of the rotor 25.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a coupling for interrupting power.

[0002]

2. Description of the Related Art FIG. 3 shows a conventional coupling described in Japanese Patent Application Laid-Open No. 10-329562.

The coupling 301 is arranged in a four-wheel drive rear-wheel-side power transmission system, and includes a rotating case 303, an inner shaft 305, and a multi-plate main clutch 30.
7, ball cam 309, pressure plate 311,
Cam ring 313, multi-plate pilot clutch 31
5, an armature 317, an electromagnet 319, a controller and the like.

[0004] The rotating case 303 is entirely formed of steel, and is connected from the transfer to the transmission via a propeller shaft.

[0005] The inner shaft 305 is rotatably supported in the rotating case 303 by a ball bearing 321 and a needle bearing 323, and a drive pinion shaft is spline-connected.

[0006] The main clutch 307 includes a rotating case 303.
The pilot clutch 315 is disposed between the rotating case 303 and the cam ring 313.

The ball cam 309 is arranged between the cam ring 313 and the pressure plate 311, and the pressure plate 311 is spline-connected to the rotating case 303.

The electromagnet 319 includes a ball bearing 33.
6 and a rotor 3 which constitutes a part of the rotating case 303
25 is rotatably mounted. The rotor 325 is inserted from one side in the axial direction of the rotating case 303, and is fixed to one side of the rotating case 303 via a screw portion 335 between them, and closes one side of the rotating case 303. .

An X-ring 327 is disposed between the rotor 325 and the inner shaft 305, and an O-ring 329 is disposed between the rotor 325 and the rotating case 303. The leakage of oil sealed between the inner shaft 305 and the inner shaft 305 is prevented. The oil is injected from an oil hole 331 formed on the other side of the rotary case 303.

The controller excites the electromagnet 319, controls the excitation current, and stops the excitation.

When the electromagnet 319 is excited, a magnetic loop 333 is formed in the magnetic circuit, the armature 317 is attracted, and the pilot clutch 315 is pressed and fastened. When the pilot clutch 315 is engaged, the transmission torque between the rotating case 303 and the inner shaft 305 is applied to the ball cam 309, and the main clutch 307 is pressed and engaged via the pressure plate 311 by the generated cam thrust force. You.

When the coupling 301 is connected in this manner, the driving force of the engine is transmitted to the rear wheels, and the vehicle is driven in a four-wheel drive state, so that the running performance on rough roads and the stability of the vehicle body are improved.

Further, when the exciting current of the electromagnet 319 is controlled, the cam thrust force of the ball cam 309 changes due to the slip of the pilot clutch 315, and the main clutch 3
The coupling force of 07 is changed, and the magnitude of the driving force sent to the rear wheels is adjusted.

When the excitation of the electromagnet 319 is stopped,
The pilot clutch 315 is released and the ball cam 30 is released.
9, the main thrust force is released, the main clutch 307 is released, the connection of the coupling 301 is released, and the vehicle enters the two-wheel drive state.

During these operations, the oil is supplied by the main clutch 307, the ball cam 309, the pilot clutch 315, and the cam ring 3 by the centrifugal force of the coupling 301.
Circulate 13 to lubricate and cool them

[0016]

According to the conventional structure, oil is sealed between the rotating case 303 and the inner shaft 305 in the coupling 301, and the rotating case 303 is thermally expanded by the oil. Acts to expand. If this expansion occurs, the screw portion 335 between the rotating case 303 and the rotor 325 is loosened, and the loosening of the screw portion 335 may cause oil leakage or loosen the connection between the rotor 325 and the rotating case 303. There is.

For this reason, it is conceivable to increase the coupling force between the rotating case 303 and the inner shaft 305 by lengthening the screw portion 335. In this case, however, the entire coupling 301 becomes longer in the axial direction. Therefore, the space for storage is increased and the mountability is reduced.

When the rotating case 303 expands,
This affects the clearance between the main clutch 307 and the pilot clutch 315, and may also affect the intermittent operation of the power.

Accordingly, an object of the present invention is to provide a coupling capable of preventing oil leakage and loosening between a rotor and a rotating case even if oil thermally expands, and capable of satisfactorily interrupting power. And

[0020]

According to a first aspect of the present invention, there is provided a closed type coupling having an outer rotating member and an inner rotating member, wherein power from one of the outer rotating member and the inner rotating member is interrupted. A cover member for closing the opening side of the outer rotating member is inserted and fixed to the outer rotating member, and expansion suppressing means for suppressing radial expansion of the outer rotating member is provided. It is characterized by being formed of a material having a thermal expansion coefficient smaller than that of the member and having a thermal expansion coefficient equivalent to that of the cover member.

In the present invention, the means for suppressing the expansion of the outer rotating member is made of a material having a coefficient of thermal expansion smaller than that of the outer rotating member and having the same coefficient of thermal expansion as the cover member. Even if an attempt is made to expand, the expansion suppressing means suppresses the radial expansion of the outer rotating member. Therefore, oil is sealed in the outer rotating member,
Even if the oil thermally expands, the outer rotating member does not expand beyond a certain level, so that oil leakage can be prevented and loosening between the cover member and the outer rotating member can be prevented.

Further, since there is no oil leakage, the lubrication and cooling efficiency of the main clutch, the pilot clutch and the like with oil can be improved, and the durability can be improved.

In addition, it is not necessary to increase the length of the screw portion to prevent oil leakage, so that the size is reduced and the mountability is improved.

Further, since the expansion of the outer rotating member is within a certain range, there is no effect on the operation of the main clutch, the pilot clutch and the like disposed inside, so that the power can be connected and disconnected reliably.

Further, since the expansion of the outer rotating member is suppressed, the outer rotating member can be formed of a lightweight metal such as aluminum, so that the weight of the entire coupling can be reduced.

According to a second aspect of the present invention, there is provided the coupling according to the first aspect, wherein the expansion suppressing means is a lock nut having a double nut structure. Can be obtained.

Further, the lock nut used as the expansion suppressing means can be easily attached, the assemblability is improved, and the expansion of the outer rotating member can be suppressed with a simple structure.

Further, since the lock nut is inexpensive, the cost can be reduced.

According to a third aspect of the present invention, there is provided the coupling according to the first or second aspect, wherein the expansion suppressing means is integrated with the cover member. The same operation and effect as those of the above configuration can be obtained.

Since the expansion suppressing means is integrated with the cover member, expansion of the outer rotating member is suppressed together with the cover member. For this reason, the expansion of the outer rotating member can be reliably suppressed. Further, it is not necessary to increase the strength of the expansion suppressing means itself more than necessary, and an inexpensive material can be used.

According to a fourth aspect of the present invention, there is provided the coupling according to any one of the first to third aspects, wherein the expansion suppressing means has a tapered surface covering the outer peripheral surface of the outer rotating member. Therefore, the same operation and effect as those of the first to third aspects can be obtained.

Further, since the expansion suppressing means is provided with a tapered surface, the expansion of the outer rotating member can be suppressed with a simple structure.

Since the tapered surface is easy to mold,
The expansion suppressing means can be easily manufactured.

According to a fifth aspect of the present invention, there is provided the coupling according to any one of the first to third aspects, wherein the expansion suppressing means has a crank portion that covers an outer peripheral surface of the outer rotating member. Therefore, the same operation and effect as those of the first to third aspects can be obtained.

Further, since the expansion suppressing means is provided with the crank portion, the structure for suppressing the expansion of the outer rotating member is simplified.

[0036]

DESCRIPTION OF THE PREFERRED EMBODIMENTS [First Embodiment] A coupling 1 (first embodiment of the present invention) will be described with reference to FIG.

[0037] The coupling 1 is defined in claims 1, 2, 3, and 4.
The rear differential and engine (transfer) that are separated during two-wheel drive in a four-wheel drive vehicle
It is located between the sides. The left and right directions are the left and right directions of the vehicle, and the left side of FIG. 1 corresponds to the front (engine side) of the vehicle. In addition, members and the like without reference numerals are not shown.

The coupling 1 and the rear differential are arranged in this order in the front-rear direction, and are accommodated in a differential carrier.

The coupling 1 includes a rotating case 3 (outer rotating member), an inner shaft 5 (inner rotating member), a multi-plate type main clutch 7, a ball cam 9 (cam mechanism), a pressure plate 11, a cam ring 13, and a multi-plate type. Pilot clutch 15, armature 17, electromagnet 19,
It consists of a controller.

The rotating case 3 has a front power transmission shaft 21 made of a shaft steel material, a cylindrical member 23 made of an aluminum alloy, and a rear power transmission shaft 21 made of an iron-based alloy (magnetic material). It is composed of a rotor 25 (cover member) and the like.

The power transmission shaft 21 is fastened to the front end of the cylindrical member 23 by a bolt 35, and closes the front side of the cylindrical member 23. The power transmission shaft 21 is provided with a spline portion 27, and a shaft is connected to the spline portion 27. The shaft protrudes forward from the differential carrier, and is connected to the transfer side via a companion flange, a joint, a propeller shaft, and the like connected to the spline portion. The driving force of the engine is transmitted to the rotating case 3 via these power transmission systems.

The rotor 25 is screwed into a rear opening of the cylindrical member 23. For this reason, on the outer peripheral surface of the rotor 25, a threaded portion 2 that is screwed with the threaded portion on the inner peripheral surface of the cylindrical member 23 is provided.
9 are formed. The rear opening of the cylindrical member 23 is closed by the rotor 25 being screwed to the cylindrical member 23. Further, between the rotor 25 and the cylindrical member 23,
The O-ring 33 is arranged to ensure the sealing between them, thereby preventing oil leakage at this portion.

A lock nut 31 as a means for suppressing expansion of the rotating case 3 (cylindrical member 23) is screwed into the screw portion 29 of the rotor 25 from the rear side. This lock nut 31
Is screwed from the rear side to form a double nut structure.

At the end of the lock nut 31 on the side of the cylindrical member 23, a tapered surface 31a is formed.
At the rear end of the cylindrical member 23, a tapered surface 23a corresponding to the tapered surface 31a is formed. When the lock nut 31 is screwed into the screw portion 29, these tapered surfaces 31a, 2a
3a is in a state of collision. In this case, lock nut 3
The taper surface 31a of the cylindrical member 23 is
And presses against the tapered surface 23a.

The lock nut 31 is formed of a material having a smaller coefficient of thermal expansion than the cylindrical member 23 of the rotating case 3 and having a coefficient of thermal expansion equivalent to that of the rotor 25. Since the rotor 25 is formed of an iron-based alloy, the lock nut 31 can be formed of a similar iron-based alloy. By doing this,
The thermal expansion of the lock nut 31 is smaller than the thermal expansion of the cylindrical member 23. When the cylindrical member 23 thermally expands, the tapered surface 31a of the cylindrical member 23 presses the tapered surface 31a. Radial expansion can be suppressed.

The inner shaft 5 penetrates the rotating case 3 from behind. The inner shaft 5 has a front portion supported by the rotating case 3 by a ball bearing 37 and a rear portion supported by the rotor 25 by a needle bearing 39. The inner shaft 5 rotates in the rotating case 3. An X-ring 41 having an X-shaped cross section is provided between the inner shaft 5 and the rotating case 3 and between the inner shaft 5 and the rotor 25 on the outer side in the axial direction of the ball bearing 37 and the needle bearing 39. 43
Are arranged to prevent oil leakage.

A drive pinion shaft is connected to a spline 63 formed on the inner periphery of the inner shaft 5. A drive pinion gear is formed integrally with the drive pinion shaft, and the drive pinion gear meshes with a ring gear on the rear differential side. The rotation of the inner shaft 5 is transmitted to the rear differential via these power transmission systems.

The rotating case 3 is sealed by the O-ring 33 and the X-rings 41 and 43, and oil is injected into the inside of the rotating case 3 from an oil hole 45. After the oil is injected, the check hole 47 is press-fitted into the oil hole 45, and the power rotary shaft 21 is further covered to seal the oil hole 45.

A radially central portion of the inner shaft 5 is provided with a capacity increasing space 65 for increasing the amount of oil enclosed in the rotating case 3. Capacity increase space 65
As in the other parts inside the rotating case 3, the oil and the air that have been injected are stored therein. Further, the capacity increasing space portion 65 communicates with the main clutch 7 through a plurality of radial flow paths formed in the inner shaft 5.

The main clutch 7 is disposed between the rotating case 3 (cylindrical member 23) and the inner shaft 5, and its outer plate 69 is connected to a spline portion 71 formed on the inner periphery of the cylindrical member 23. The inner plate 73 is connected to a spline portion 75 formed on the outer periphery of the inner shaft 5.

The ball cam 9 is mounted on the pressure plate 1
1 and the cam ring 13.

The inner circumference of the pressure plate 11 is connected to a spline portion 75 of the inner shaft 5.
The main clutch 7 is pressed between the rotary case 3 (cylindrical member 23) by the thrust force of the ball cam 9 and is engaged.

The cam ring 13 is slidably disposed on the outer periphery of the inner shaft 5, and a thrust bearing 77 and a washer 79 which receive a cam reaction force of the ball cam 9 are disposed between the cam ring 13 and the rotor 25. ing.

The pilot clutch 15 is mounted on the rotating case 3
The outer plate 81 is disposed between the (cylindrical member 23) and the cam ring 13. The outer plate 81 is connected to a spline portion 71 formed on the inner circumference of the cylindrical member 23, and the inner plate 85 is formed on the outer circumference of the cam ring 13. Connected to the spline portion 87.

The armature 17 is disposed between the pressure plate 11 and the pilot clutch 15 and has an outer periphery movably connected to a spline portion 71 of the cylindrical member 23.

The core 89 of the electromagnet 19 penetrates through an appropriate air gap into a ring-shaped recess 91 formed in the rotor 25 and is supported on the rotor 25 by a double-sided sealed ball bearing 93. . The lead wire 101 of the electromagnet 19 is drawn out of the differential carrier through the grommet 97 and is connected to a battery mounted on the vehicle.

The rotor 25, the pilot clutch 15 and the armature 17 form a magnetic path of the electromagnet 19.

The rotor 25 is separated radially outward and inward by a stainless steel ring 99 which is a non-magnetic material.
At 1, 85, a plurality of notches and a bridge portion connecting these notches are provided in the circumferential direction at radial positions corresponding to the ring 99. These rings 99
The notch prevents the magnetic force from being short-circuited on the magnetic path.

The controller detects the turning traveling from the vehicle speed, the steering angle, the lateral G, and the like, or performs the excitation of the electromagnet 19, the control of the excitation current, the stop of the excitation, and the like according to the road surface condition and the like.

When the electromagnet 19 is excited, a magnetic loop 101 is formed in the above-described magnetic path, the armature 17 is attracted, and the pilot clutch 15 is pressed against the rotor 25 to be engaged.

When the pilot clutch 15 is engaged,
Transmission torque is applied to the ball cam 9 via the cam ring 13 connected to the rotating case 3 via the pilot clutch 15 and the pressure plate 11 on the inner shaft 5 side, and the pressure plate 11 receives the generated cam thrust force to move the pressure plate 11 to the left. And presses the main clutch 7 to engage it.

When the coupling 1 is connected, the driving force of the engine is transmitted from the inner shaft 5 to the rear differential via a propeller shaft on the rear differential side, etc., and is distributed from the rear differential to the left and right rear wheels, so that the vehicle is driven by four wheels. As a result, running performance on rough roads and the stability of the vehicle body are improved.

At this time, if the exciting current of the electromagnet 19 is controlled, the slip of the pilot clutch 15 changes, the cam thrust force of the ball cam 9 changes, and the coupling force of the main clutch 7 changes, and the driving force sent to the rear wheels changes , The driving force distribution ratio between the front and rear wheels can be controlled. For example, when such a control of the driving force distribution ratio is performed during the turning, the controllability and stability of the vehicle can be greatly improved.

When the excitation of the electromagnet 19 is stopped, the pilot clutch 15 is released, the cam thrust force of the ball cam 9 is lost, the main clutch 7 is released, the connection of the coupling 1 is released, and the rear differential side is disconnected.
The vehicle enters a front-wheel drive two-wheel drive state.

Further, since the cylindrical member 23 of the rotating case 3 is made of an aluminum alloy, the magnetic force of the electromagnet 19 is prevented from leaking to the cylindrical member 23 side.
Since the magnetic force is efficiently guided to 7, the pilot clutch 15 obtains a predetermined pilot torque, and the coupling 1 obtains a predetermined connection torque.

The oil sealed in the rotating case 3 is
Circulates inside by the centrifugal force of the electromagnetic coupling 1,
The main clutch 7, the ball cam 9, the pilot clutch 15, the spline portions 71, 75, 87, the thrust bearing 77, the washer 79, the sliding surface between the inner periphery of the cam ring 13 and the outer periphery of the inner shaft 5, the X rings 41, 43, and the like. These are sufficiently lubricated and cooled.

The oil in the capacity increasing space 65 flows into the main clutch 7 from the radial flow path of the inner shaft 5 by centrifugal force, and is given to the sliding surface between the outer plate 69 and the inner plate 73. Lubrication and cooling effects are further improved.

Each inner plate 73 of the main clutch 9 is provided with an oil hole 103 to promote the movement of oil to the sliding surface of each plate 69, 73, and to improve their lubrication and cooling effects. Let me.

Thus, the electromagnetic coupling 1 is configured.

As described above, the cylindrical member 2 of the rotating case 3
A lock nut 31 is screwed into a screw portion 29 of the rotor 25 to be screwed to the nut 3 to form a double nut structure, and the radial expansion of the cylindrical member 23 is suppressed. Therefore, even if the oil enclosed therein thermally expands, the rotating case 3 (cylindrical member 23) does not expand to a certain degree or more, so that oil leakage can be prevented, and the rotor 25 and the rotating case 3 Is not loosened.

Further, the lock nut 31 is formed of a material having the same coefficient of thermal expansion as that of the rotor 23, and performs the same degree of thermal expansion as the rotor 23. Therefore, the connection between the lock nut 31 and the rotor 23 is not loosened, and the lock nut 31 can stably maintain the connection state with the rotor 23.

Further, since there is no oil leakage as described above, the main clutch 7, the ball cam 9, the pilot clutch 15, the spline portions 71, 75, 87, the thrust bearing 77, the washer 79, the cam ring 13,
Since the oil is sufficiently supplied to the pressure plate 11 and the X-rings 41 and 43, lubrication and cooling thereof can be performed smoothly, and durability is improved.

Further, it is not necessary to increase the length of the screw portion 29 of the rotor 25 to prevent oil leakage, so that the size is reduced and the mountability is improved.

Further, since the expansion of the rotating case 3 is within a certain range, the operation of the main clutch 7, the ball cam 9, the cam ring 13, the pressure plate 11, the pilot clutch 15 and the like is not affected, and the intermittent power supply is ensured. Can be done.

Further, since the expansion of the rotating case 3 is suppressed, the cylindrical member 23 can be formed of a lightweight metal such as aluminum, so that the weight of the entire coupling can be reduced.

Further, the lock nut 3 is used as expansion suppressing means.
Because of the use of 1, the mounting is easy and the assembling property is improved.

The lock nut 31 has a tapered surface 31a.
Abuts against the tapered surface 23a of the cylindrical member 23 to suppress the expansion of the cylindrical member 23, so that the expansion can be reliably suppressed with a simple structure.

[Second Embodiment] A coupling 201 (a second embodiment of the present invention) will be described with reference to FIG.

This coupling 201 is characterized in that
It has the features 3 and 5, and is used in place of the coupling 1 in a four-wheel drive vehicle using the coupling 1 of the first embodiment. Hereinafter, differences will be described while giving the same reference numerals to members having the same functions as those of the coupling 1. The left side of FIG. 2 is in front of the vehicle (engine side).
, And members without reference numerals are not shown.

In this embodiment, a crank portion 31b is formed on a lock nut 31 as an expansion suppressing means. The lock nut 31 is fixed integrally with the rotor 25 by being screwed into the screw portion 29 of the rotor 25, and the crank portion 31 b is located at the end of the cylindrical member 23.

At the rear end of the cylindrical member 23 of the rotating case 3, a stepped lower insertion piece 23 b is formed.
When the lock nut 31 is screwed onto the rotor 25, the insertion piece 2
3b is adapted to be inserted into the crank portion 31b. By this insertion, the crank portion 31b of the lock nut 31 presses the insertion piece 23b from the outside in the radial direction.

Also in this embodiment, the lock nut 3
Reference numeral 1 denotes a material having a smaller thermal expansion coefficient than that of the cylindrical member 23 of the rotating case 3 and a thermal expansion coefficient equivalent to that of the rotor 25. Accordingly, the lock nut 31 is formed of the same iron-based alloy as the rotor 25, and has a smaller degree of expansion than the cylindrical member 23 even when the cylindrical member 23 expands. For this reason, the crank portion 31b
Presses the insertion piece 23b from the outside, so that the expansion of the cylindrical member 23 to the outside in the radial direction can be favorably suppressed.

As described above, also in this embodiment, since the radial expansion of the rotating case 3 (the cylindrical member 23) can be suppressed, oil leakage does not occur, and the main clutch 7, the ball cam 9, the pilot clutch 15 The lubrication and cooling of the spline portions 71, 75, 87, the thrust bearing 77, the washer 79, the cam ring 13, the pressure plate 11, and the X rings 41, 43 can be sufficiently performed, and the durability is improved. In addition, since it is not necessary to increase the length of the threaded portion 29 of the rotor 25 to prevent oil leakage, the rotor 25 is compact, and the on-board performance is improved.

Since the expansion of the rotating case 3 is within a certain range, the operation of the main clutch 7, the ball cam 9, the cam ring 13, the pressure plate 11, the pilot clutch 15 and the like is not affected, and the intermittent power supply is ensured. Can be done.

Further, since the expansion of the rotating case 3 is suppressed, the cylindrical member 23 can be formed of a lightweight metal such as aluminum, so that the weight of the entire coupling can be reduced.

[0086]

According to the first aspect of the present invention, the expansion suppressing means suppresses the expansion of the outer rotating member, so that oil leakage can be prevented and the connection between the cover member and the outer rotating member is loosened. Disappears. Further, since there is no oil leakage, lubrication and cooling efficiency of the main clutch, the pilot clutch, and the like with oil can be improved, and durability can be improved.

Further, since it is not necessary to prevent the oil leakage by increasing the length of the screw portion, it becomes compact,
The on-board performance is improved. In addition, since the expansion of the outer rotating member is within a certain range, the main clutch disposed inside,
There is no effect on the operation of the pilot clutch and the like, so that the power can be intermittently connected. In addition, since the expansion of the outer rotating member is suppressed, the outer rotating member can be formed of a lightweight metal, and the weight of the entire coupling can be reduced.

According to the second aspect of the present invention, the same effects as those of the first aspect can be obtained. In addition, since the lock nut is used as the expansion suppressing means, the coupling is easy, and the assembling property is improved. In addition, the expansion of the outer rotating member can be suppressed with a simple structure.

The coupling according to claim 3 is based on claims 1 and 2
In addition to providing the same effect as the configuration described above, the expansion suppressing means is integrated with the cover member, so that the expansion of the outer rotating member can be reliably suppressed, and the expansion suppressing means itself It is not necessary to increase the strength of the material more than necessary, and an inexpensive material can be used.

The coupling according to the fourth aspect is the first to third aspects.
In addition to obtaining the same effect as the above configuration, the expansion of the outer rotating member is suppressed by the tapered surface, so that a simple structure can be obtained.

The coupling according to the fifth aspect of the invention can provide the same effects as those of the first to third aspects, and also has a simple structure because the expansion of the outer rotating member is suppressed by the crank portion. Becomes

[Brief description of the drawings]

FIG. 1 is a sectional view showing a first embodiment of the present invention.

FIG. 2 is a sectional view showing a second embodiment of the present invention.

FIG. 3 is a sectional view showing a conventional coupling.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Coupling 3 Rotation case (outside rotation member) 5 Inner shaft (inside rotation member) 31 Lock nut (expansion suppression means) 31a Tapered surface 31b Crank part

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3D043 AB17 EA18 EB12 EC00 EC01 3J056 AA34 AA60 AA63 BC02 BE06 BE07 CD01 EA05 GA02 GA12

Claims (5)

[Claims] An outer rotating member and an inner rotating member,
In a hermetic type coupling for interrupting power from one of the outer rotating member or the inner rotating member to the other, a cover member for closing an opening side of the outer rotating member is inserted and fixed to the outer rotating member, and Expansion suppression means for suppressing radial expansion is provided, and the expansion suppression means is formed of a material having a smaller thermal expansion coefficient than the outer rotating member and having a thermal expansion coefficient equivalent to that of the cover member. A coupling characterized by: 2. The coupling according to claim 1, wherein the expansion suppressing means is a lock nut having a double nut structure. 3. The coupling according to claim 1, wherein the expansion suppressing means is integrated with the cover member. 4. The coupling according to claim 1, wherein the expansion suppressing means has a tapered surface that covers an outer peripheral surface of the outer rotating member. 5. The coupling according to claim 1, wherein the expansion suppressing means has a crank portion that covers an outer peripheral surface of the outer rotating member.