WO2013058278A1

WO2013058278A1 - Roller clutch device

Info

Publication number: WO2013058278A1
Application number: PCT/JP2012/076835
Authority: WO
Inventors: 澤　司郎
Original assignee: 株式会社ユニバンス
Priority date: 2011-10-21
Filing date: 2012-10-17
Publication date: 2013-04-25
Also published as: JP5877404B2; JPWO2013058278A1

Abstract

Provided is a roller clutch device which enables easier manufacturing. A roller clutch device is provided with a first inner ring (11) (first member) and a second inner ring (12) (second member) which are provided side by side in an axial direction, and is provided with a plurality of first rollers (31) and second rollers (32) which are provided to face the first member and the second member, respectively, and an outer ring (20) is laid across the plurality of first rollers (31) and second rollers (32). When rotational power is inputted from the second inner ring (12) (second member), the first rollers (31) and the second rollers (32) engage with outer peripheral raceway surfaces (11a, 12a) and inner peripheral raceway surfaces (21a, 22a), and the rotational power is transmitted to the outer ring (20) and outputted to the first inner ring (11) (first member). The structure can be simplified, thereby enabling easier manufacturing.

Description

Roller clutch device

The present invention relates to a roller clutch device, and more particularly to a roller clutch device that can be easily manufactured.

The clutch means for interrupting the driving force of the mechanical device includes a viscous joint (also known as a viscous coupling), a fluid joint, and a friction plate clutch. The inventor has filed a patent application regarding this type of clutch means (Patent Document 1). In Patent Document 1, an intermediate raceway is arranged between an inner ring raceway surface and an outer ring raceway surface, and a plurality of rollers are inclined between the intermediate raceway ring and the inner ring raceway surface. A technique is disclosed in which a plurality of rollers are arranged to be inclined with respect to the raceway surface. In the technique disclosed in Patent Document 1, when rotational power is applied to the inner ring or the outer ring, each roller bites into the raceway surface in a wedge shape, and the rotational power is transmitted between the inner ring and the outer ring via the roller and the intermediate raceway. Communicated.

Japanese Patent No. 4614167

However, in the above conventional technique, the raceway surfaces must be formed on the inner circumferential surface and the outer circumferential surface (both sides of the intermediate raceway) of the intermediate raceway facing the inner ring raceway surface and the outer ring raceway surface. That is, in order to transmit the rotational power between the inner ring and the outer ring through the roller and the intermediate raceway, when the rotational power is loaded, between the inner peripheral surface of the intermediate raceway and the inner ring raceway, This is because it is necessary to engage the rollers between the outer peripheral surface of the intermediate raceway and the outer raceway surface. As described above, since the raceway surfaces have to be formed on both surfaces of the intermediate raceway, it is difficult to manufacture and there is a risk of lack of mass productivity.

The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a roller clutch device that can be easily manufactured.

Means for Solving the Problems and Effects of the Invention

In order to achieve this object, according to the roller clutch device of the first aspect, the outer ring is disposed on the radially outer side of the inner ring configured to be rotatable about the central axis, and the outer ring is in contact with the inner ring. It is configured to be capable of relative rotation and relative movement in the axial direction. An inner circumferential raceway surface is formed on the inner circumferential surface of the outer ring, and an outer circumferential raceway surface facing the inner circumferential raceway surface is formed on the outer circumferential surface of the inner ring. A plurality of rollers are interposed between the outer peripheral raceway surface and the inner peripheral raceway surface, and the rollers are held at intervals from each other in the circumferential direction while being inclined at a predetermined angle from the plane including the central axis by a cage. . Therefore, when rotational power is input to the inner ring or the outer ring and rotated in a predetermined direction, the roller revolves around the central axis while rotating by being guided by the outer circumferential track surface and the inner circumferential track surface. Guided by the rotation of the roller, the inner ring and the outer ring move relative to each other in the direction in which the distance between the outer raceway surface and the inner raceway surface is reduced while being elastically deformed in the radial direction. As a result, the rollers engage with the outer raceway surface and the inner circumference raceway surface to transmit the rotational power.

One of the inner ring and the outer ring includes a first member and a second member that are arranged in parallel in the axial direction, and the roller includes a plurality of first rollers and second rollers that are respectively opposed to the first member and the second member. It is prepared for. Since the other of the inner ring or the outer ring is laid across the plurality of first rollers and the second roller, the rotational power input from one of the first member or the second member is transmitted to the other of the inner ring or the outer ring, and the first Output to the other of the one member or the second member.

According to this roller clutch device, the raceway surface with which the first roller and the second roller engage is formed on each of the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring. Therefore, it is possible to omit an intermediate track ring that has to form track surfaces on the outer peripheral surface and the inner peripheral surface (both surfaces), and the structure can be simplified. Therefore, there exists an effect which can make manufacture easy.

According to the roller clutch device of claim 2, the plurality of first rollers are held at intervals in the circumferential direction by the first retainer disposed on the radially outer side or the radially inner side of the first member, The plurality of second rollers are held at intervals in the circumferential direction by the second cage arranged in parallel to the outside in the axial direction of the first cage. When the roller engages with the inner raceway surface and the outer raceway surface by the elastic member disposed at one axial end of the first cage or the second cage, the first cage and the second cage are engaged with the inner raceway surface and the outer raceway surface. The roller is biased in the same direction as the moving direction in the axial direction. Since the first cage and the second cage biased by the elastic member are regulated in the axial direction by the position regulating member arranged at the other axial end of the second cage or the first cage. The first cage and the second cage can be prevented from separating from between the inner circumferential raceway surface and the outer circumferential raceway surface.

Here, when the first cage and the second cage roller (the first roller and the second roller) urged by the elastic member are engaged (engaged) with the inner circumferential track surface and the outer circumferential track surface, the roller is a shaft. Rolls on the inner and outer raceway surfaces while moving in one direction. Along with this, the first holder and the second holder that hold the first roller and the second roller also move to one side in the axial direction. Since the elastic member is deformed and follows as the first cage and the second cage move to one side in the axial direction, the first cage and the second cage are in contact with each other when the roller is engaged. Interference between the roller and the second roller can be suppressed.

In addition, the first roller and the second roller have small contact points with the outer raceway surface and the inner raceway surface, the thickness of the contact oil film fluctuates, a difference in surface pressure due to centrifugal force, The rolling friction coefficient varies for each contact location due to the variation of the contact area depending on the accuracy of assembly. In addition, the first roller and the second roller are affected by gravitational acceleration, vibration, etc. of the usage environment, so when engaged, disengaged or overrunning, one of the outer raceway surface and the inner raceway surface in the axial direction. It tends to be unevenly distributed.

On the other hand, by urging one of the first cage or the second cage with an elastic member and providing a position restricting member on the other of the first cage or the second cage, the first cage or the second cage The other of the first cage and the second cage can be clamped by one of the cages and the position regulating member. As a result, the first cage and the second cage can be displaced to the optimum positions in the axial direction. Thereby, there exists an effect which can hold | maintain a 1st roller and a 2nd roller in the optimal position of an outer peripheral track surface and an inner peripheral track surface with a 1st holder | retainer or a 2nd holder | retainer.

Also, when the input torque disappears or overruns, the roller moves to the other side in the axial direction (the direction opposite to the moving direction when the roller is engaged). Since the elastic member receives the displacement of the first cage and the second cage due to the movement of the roller, the rollers (first roller and second roller) that move to the other side in the axial direction when the engagement of the rollers is released. It can suppress that a roller) interferes with a 1st holder | retainer and a 2nd holder | retainer.

Further, since the cage is divided into the first cage and the second cage, the first cage and the second cage can be relatively moved in the axial direction and the rotational direction. Thereby, the freedom degree of the 1st roller and 2nd roller hold | maintained at a 1st holder | retainer and a 2nd holder | retainer can be improved. As a result, it is possible to prevent the first retainer and the second retainer from interfering with the first roller and the second roller when the first roller and the second roller are engaged or disengaged.

Therefore, according to the roller clutch device of the second aspect, in addition to the effect of the first aspect, the first roller and the second roller can be held at the optimum positions of the outer peripheral raceway surface and the inner peripheral raceway surface, and the roller (first When the roller and the second roller) are engaged and when the roller is disengaged, the roller can be prevented from interfering with the first holder and the second holder. As a result, the first cage and the second cage are rubbed by the rollers to reduce durability, or the disengaged roller collides with the first cage and the second cage to generate noise. Can be suppressed.

According to the roller clutch device of the third aspect, the inner circumferential raceway surface or the outer circumferential raceway surface of the second member is formed in the same shape as the inner circumferential raceway surface or the outer circumferential raceway surface of the first member. Since the second roller is formed in the same shape as the first roller, the first roller and the second roller can be made the same part, and in addition to the effect of

claim

1 or 2, the parts can be shared. There is an effect that can be achieved.

It is an axial sectional view of the roller clutch device in the first embodiment. It is an expanded sectional view of the part which a roller and an outer ring contact. It is an axial sectional view of a roller clutch device in a second embodiment.

1,101 Roller clutch device 10,110 Inner ring 11 First inner ring (first member)
12 Second inner ring (second member)
11a, 12a, 111, 112

Outer raceway surface

20, 120 Outer ring 21 First outer ring 22 Second outer ring 121 First outer ring (first member)
122 Second outer ring (second member)
21a, 22a, 121a, 122a Inner circumferential raceway surface 30 Roller 31 First roller 32 Second roller 40 Retainer 41 First retainer 42 Second retainer 53 Disc spring (elastic member)
54,154 Position restriction member O Center axis

Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings. FIG. 1 is a sectional view in the axial direction of a roller clutch device 1 according to a first embodiment of the present invention. FIG. 2 shows a portion where a roller 30 (first roller 31) and an outer ring 20 (first outer ring 21) are in contact with each other. It is an expanded sectional view. In FIG. 1, illustration of the lever 51 in the longitudinal direction is omitted.

As shown in FIG. 1, the roller clutch device 1 includes a rod 2 serving as a rotation center, an inner ring 10 disposed on the outer periphery of the rod 2, an outer ring 20 disposed on the radially outer side of the inner ring 10, A plurality of rollers 30 interposed between the outer ring 20 and the inner ring 10 and a retainer 40 that holds the plurality of rollers 30 between the outer ring 20 and the inner ring 10 are mainly configured.

The inner ring 10 is an annular member having a function for transmitting the rotational power of the input shaft 3, and the first inner ring 11 and the second inner ring 12 constituting the inner ring 10 are arranged in the axial direction of the outer periphery of the rod 2. It is installed. The input shaft 3 is a flange-like member through which the rod 2 penetrates. The input shaft 3 is configured to be rotatable with respect to the rod 2 and is disposed on one end side (right side in FIG. 1) of the rod 2 in the axial direction. A stopper 4 is formed in a hook shape at one axial end of the rod 2, and a disc spring 5 is inserted between the stopper 4 and the input shaft 3. As a result, the input shaft 3 is biased toward the other axial end side (left side in FIG. 1).

The input shaft 3 is connected to other members (not shown) that transmit rotational power so as to be immovable in the axial direction by bolts or the like inserted through holes 3a that are formed through the axial direction. Further, since the input shaft 3 is fixed to the axial end surface of the second inner ring 12 and the fastening member 6 such as a bolt, when the rotational power is input to the input shaft 3, the second inner ring 12 is connected to the input shaft 3. Rotates together.

The first inner ring 11 and the second inner ring 12 have outer raceway surfaces 11a and 12a that form a single-plane rotation hyperboloid around the central axis O of the rod 2, respectively. In the present embodiment, the outer peripheral raceway surfaces 11a and 12a have the same shape and the same outer diameter, and the outer peripheral raceway surfaces 11a and 12a have one end in the axial direction on the other axial end side (left side in FIG. 1). It is formed to have a smaller diameter than the side (right side in FIG. 1).

The output shaft 7 is a flange-like member through which the rod 2 penetrates, is configured to be rotatable with respect to the rod 2, and is disposed on the other axial end side of the rod 2. Since the output shaft 7 is fixed to the axial end surface of the first inner ring 11 and the fastening member 8 such as a bolt, the output shaft 7 rotates integrally with the first inner ring 11. Since the hook-shaped stopper 9 is fixed to the other axial end of the rod 2, the stopper 9 restricts the movement of the output shaft 7 toward the other axial end (the left side in FIG. 1). The output shaft 7 cannot be moved in the axial direction with other members (not shown) for transmitting rotational power by bolts or the like inserted through holes 7a formed through the output shaft 7 in the axial direction. Connected.

The outer ring 20 is an annular member having a function of transmitting the rotational power of the input shaft 3 together with the inner ring 10. The outer ring 20 is spaced apart from the first inner ring 11 and the second inner ring 12 by a predetermined distance. 2 The first outer ring 21 and the second outer ring 22 are respectively provided on the radially outer side of the inner ring 12.

The first outer ring 21 and the second outer ring 22 have axial end surfaces in contact with each other and are connected by a fastening member 23 such as a bolt. Thus, the first outer ring 21 can be rotated relative to the first inner ring 11 and the second inner ring 12 integrally with the second outer ring 22, and can be integrated with the second outer ring 22 and the first inner ring 11 and The second inner ring 12 can be moved relative to the axial direction. Further, the first outer ring 21 and the second outer ring 22 are formed with inner

circumferential raceways

21a and 22a that form a single lobe rotating hyperboloid around the central axis O on the respective inner circumferential surfaces. In the present embodiment, the inner circumferential raceway surfaces 21a and 22a have the same shape and the same inner diameter, and the inner circumferential raceway surfaces 21a and 22a have a radius centered on the central axis O and other axial directions. The end side (left side in FIG. 1) is formed to have a smaller diameter than the one axial end side (right side in FIG. 1).

The second outer ring 22 (outer ring 20) has a pair of flanges 24 projecting in an annular shape on the outer peripheral surface, and a concave groove 24a is formed on the outer peripheral surface of the flange 24. The groove 24a is a portion into which the tip of the lever 51 is inserted. The first outer ring 21 and the second outer ring 22 (outer ring 20) are axially moved by swinging the lever 51 supported by the fulcrum 51a in the axial direction. Can be moved to.

The first outer ring 21 and the second outer ring 22 (outer ring 20) are arranged at one end side in the axial direction by a disc spring 52 disposed between the end face in the axial direction of the output shaft 7 and the end face on the other end side in the axial direction of the first outer ring 21. (Right side of FIG. 1). That is, the disc spring 52 urges the outer ring 20 toward one end in the axial direction in a direction in which the interval between the inner circumferential raceway surfaces 21a and 22a and the outer circumferential raceway surfaces 11a and 12a is reduced in the axial direction. The axial positions of the first outer ring 21 and the second outer ring 22 (outer ring 20) urged toward the one axial end side by the disc spring 52 are regulated by the position of the lever 51.

The roller 30 is a cylindrical member for engaging with the inner ring 10 and the outer ring 20 to transmit rotational power, and a first roller 31 interposed between the first inner ring 11 and the first outer ring 21; And a second roller 32 interposed between the second inner ring 12 and the second outer ring 22. The first roller 31 and the second roller 32 are provided between the first inner ring 11 and the first outer ring 21 and between the second inner ring 12 and the second outer ring 22, respectively. 42 (retainer 40).

The first retainer 41 and the second retainer 42 are spaced apart from each other in the circumferential direction so that the first roller 31 and the second roller 32 rotate smoothly without interfering with each other. This is a member for holding the two rollers 32. The second cage 42 is juxtaposed on the outside in the axial direction of the first cage 41 so that the axial end surface can be slidably contacted with the axial end surface of the first cage 41. The first cage 41 and the second cage 42 have a radius around the central axis O such that the other end in the axial direction (left side in FIG. 1) has a smaller diameter than the one end side in the axial direction (right side in FIG. 1). It is formed in a substantially truncated cone shape. The first roller 31 and the second roller 32 are accommodated in a plurality of pocket holes 41 a and 42 a formed so as to penetrate in the thickness direction of the peripheral surfaces of the first holder 41 and the second holder 42.

The first roller 31 is disposed between the first inner ring 11 and the first outer ring 21 at a predetermined angle α (for example, 8 to 15 °) with respect to the plane including the central axis O by the first cage 41. As a result, the outer peripheral surface can come into linear contact with the outer peripheral raceway surface 11a and the inner peripheral raceway surface 21a. Further, the second roller 32 is inclined by a predetermined angle α (for example, 8 to 15 °) from the surface including the central axis O in the opposite direction to the first roller 31 by the second cage 42 and the second inner ring 12 and the second roller 32. By being arranged between the two outer rings 22, the outer peripheral surface can come into linear contact with the outer peripheral raceway surface 12a and the inner peripheral raceway surface 22a.

When the first roller 31 and the second roller 32 rotate around the central axis O at a high speed (for example, 10000 rpm or more), the first roller 31 and the second roller 32 receive a centrifugal force and receive the inner circumferential track of the outer ring 20. Since it revolves while skewing with the

surfaces

21a and 22a, heat is generated by sliding friction. Therefore, as shown in FIG. 2, the outer peripheral shape of the 1st roller 31 is set so that the contact part C of the 1st roller 31 and the internal peripheral track surface 21a may be a point contact. For example, a convex full crown is formed in the center of 0.003 mm from both ends of the first roller 31 so as to be in line contact at the time of torque load (engagement) that generates a high surface pressure. The same applies to the second roller 32.

Referring back to FIG. The first retainer 41 and the second retainer 42 are arranged on one end side in the axial direction by a disc spring 53 disposed between the end face in the axial direction of the output shaft 7 and the end face on the other end side in the axial direction of the first retainer 41 ( The right side of FIG. Specifically, the axial end surface on the small diameter side of the first cage 41 is pushed in the axial direction by the disc spring 53, and the axial end surface on the large diameter side of the first cage 41 is on the small diameter side of the second cage 42. The second retainer 42 is urged to one axial end side (right side in FIG. 1) together with the first retainer.

The position restricting member 54 is a disk-shaped member for restricting the axial position of the first retainer 41 and the second retainer 42 urged toward the one axial end side by the disc spring 53, and the second retainer 42 is provided so as to be able to come into contact with the axial end face on the large diameter side of 42. In the present embodiment, one end of the position regulating member 54 is fixed to the axial end surface of the second outer ring 22 on the input shaft 3 side, and the other end is on the input shaft 3 side (large diameter side) of the second cage 42. Pressed against the axial end face. Accordingly, the axial positions of the first retainer 41 and the second retainer 42 can be restricted by the axial position of the outer ring 20.

A thrust bearing (not shown) is disposed on the axial end surfaces of the first cage 41 and the second cage 42. This is to smoothly rotate the first cage 41 and the second cage 42 around the central axis O while receiving a load acting in the axial direction.

Also, the first inner ring 11, the second inner ring 12, the first outer ring 21 and the second outer ring 22 are hardened and hardened to a hardness HRC 62 to 63 with bearing steel SUJ-2 material. The cone angles of the first inner ring 11 and the second inner ring 12, the first outer ring 21 and the second outer ring 22 are appropriately selected in accordance with the use conditions within a range of approximately 10 ± 2 degrees. The skew angles of the first roller 31 and the second roller 32 are appropriately selected in the range of 8 to 15 degrees according to the use conditions. The first roller 31 and the second roller 32 are made of bearing steel SUJ-2 and having a hardness of about HRC65. Moreover, the 1st holder | retainer 41 and the 2nd holder | retainer 42 are formed with metal, such as iron, and the product made from a synthetic resin reinforced with fiber.

The axial direction end surface (the receiving surface of the thrust bearing) of the second retainer 42 that contacts the position restricting member 54, and the first retainer 41 and the second retainer where the first retainer 41 and the second retainer 42 contact each other. The axial end surface of the vessel 42 (the receiving surface of the thrust bearing) serves as a smooth surface to reduce frictional resistance so that an oil film is easily formed. It is desirable to form an oil groove (not shown) on the receiving surface. This is to prevent seizure by spreading the lubricant.

Next, the operation of the roller clutch device 1 will be described with reference to FIG. When the lever 51 is in a free state where no external force is applied, the outer ring 20 is pushed to the input shaft 3 side by the disc spring 52, and the inner circumferential raceway surfaces 21 a and 22 a are forced on the outer circumferential surfaces of the first roller 31 and the second roller 32. The outer peripheral raceway surface 11 a contacts the outer peripheral surface of the first roller 31.

When rotational power in a predetermined direction (arrow direction in FIG. 1) is input to the input shaft 3, the second roller 32 rolls on the outer raceway surface 12a of the second inner ring 12 (the rotation direction of the second roller 32 is the counter arrow in FIG. 1). Direction), the traction bites into the inner circumferential raceway surface 22a of the second outer ring 22, locks (engages) with the wedge action, and rotates integrally with the second inner ring 12 and the second outer ring 22 (outer ring 20). When the second outer ring 22 and the first outer ring 21 rotate together, the first roller 31 rolls on the inner raceway surface 21a of the first outer ring 21 and bites into the outer raceway surface 11a of the first inner ring 11 by its traction. The first outer ring 21 (outer ring 20) and the first inner ring 11 rotate integrally with each other by being locked (engaged) by the wedge action. That is, the input torque is output from the second inner ring 12 to the first inner ring 11 (the rotation direction is the arrow direction in FIG. 1). The first inner ring 11, the second inner ring 12, the first outer ring 21, and the second outer ring 22 do not necessarily have the same dimensions as long as the elastic displacement amount is set to be the same.

When the first roller 31 is engaged with the first inner ring 11 and the first outer ring 21 and the second roller 32 is engaged with the second inner ring 12 and the second outer ring 22, the first roller 31 and the second roller 32 (roller 30) rolls slightly by the amount of elastic displacement and is displaced toward the input shaft 3 in the axial direction. At the same time, the first outer ring 21 and the second outer ring 22 (outer ring 20) are also displaced toward the input shaft 3 in the axial direction. The amount of axial displacement of the outer ring 20 is approximately twice the amount of axial displacement of the roller 30.

When the transmission of the rotational power is interrupted, an axial external force is applied to the lever 51 slidably contacting the groove 24a provided on the outer peripheral surface of the second outer ring 22, and the first outer ring 21 and the second outer ring 22 (outer ring 20) are moved. It is displaced to the output shaft 7 side in the axial direction. Thereby, since the inner

peripheral raceway surfaces

21a and 22a of the outer ring 20 are separated from the first roller 31 and the second roller 32, transmission of rotational power can be turned off. As described above, the roller clutch device 1 can switch the state of transmitting the rotational power or the state of interrupting the transmission of the rotational power by operating the lever 51.

When the roller clutch device 1 is in a state of transmitting rotational power, the first roller 31 and the second roller 32 are the inner ring 10 (first inner ring 11 and second inner ring 12) and the outer ring 20 (first outer ring 21 and second roller 32). It is located at an intermediate point where the outer ring 22) is relatively displaced. Accordingly, the first retainer 41 and the second retainer 42 are displaced from the output shaft 7 side in the axial direction to the input shaft 3 side. The position restricting member 54 is displaced integrally with the outer ring 20 toward the input shaft 3, and the axial displacement is approximately twice the displacement of the second cage 42. The outer ring 20 is composed of the second cage. Since it displaces to the side which produces a clearance gap with 42, interference with the 2nd holder | retainer 42 can be prevented.

Thereby, when the 1st roller 31 and the 2nd roller 32 engage, the displacement of the axial direction of the 1st retainer 41 and the 2nd retainer 42 is not prevented, but the 1st retainer 41 and the 2nd retainer It can suppress that the 1st roller 31 and the 2nd roller 32 interfere with 42 (inner wall surface of the pocket holes 41a and 42a). As a result, the first holder 41 and the second holder 42 can be prevented from being rubbed by the first roller 31 and the second roller 32 and the durability of the first holder 41 and the second holder 42 being lowered.

On the contrary, when rotational power in a predetermined direction (arrow direction in FIG. 1) is input to the output shaft 7 with respect to the input shaft 3 by relative rotation with the input shaft 3, the first roller 31 is moved to the first inner ring. 11, the outer peripheral raceway surface 11a and the inner peripheral raceway surface 21a of the first outer ring 21 are moved out in the direction of overrunning. Further, centrifugal force is applied to the first roller 31, and the first roller 31 moves along the inner circumferential raceway surface 21a of the first outer ring 21, and is detached from the outer circumferential raceway surface 11a and the inner circumferential raceway surface 21a.

When transmission of power from the first inner ring 11 to the first outer ring 21 via the first roller 31 is interrupted, the second roller 32 is also rotated by the relative rotation between the second outer ring 22 and the second inner ring 12 so that the outer raceway surface 12a. And the inner circumferential raceway surface 22a. Since the output shaft 7 side in the axial direction of the first retainer 41 and the second retainer 42 is elastically supported by the disc spring 53, the first roller 31 and the second roller 32 have the outer peripheral track surfaces 11a, 12a and the inner periphery. When separated from the raceway surfaces 21a and 22a, the first retainer 41 and the second retainer 42 can be displaced toward the output shaft 7 in the axial direction.

As a result, when the engagement of the first roller 31 and the second roller 32 is released, the first roller 31 and the second roller 32 that move to the output shaft 7 side in the axial direction are replaced with the first holder 41 and the first roller 41. 2 Interference with the cage 42 (inner wall surfaces of the

pocket holes

41a, 42a) can be suppressed. As a result, it can be suppressed that the first roller 31 and the second roller 32 that have been disengaged collide with the first retainer 41 and the second retainer 42 to generate noise (abnormal noise).

Moreover, since the cage 40 is divided into the first cage 41 and the second cage 42, the first cage 41 and the second cage 42 can be relatively moved in the axial direction and the rotational direction. Thereby, the freedom degree of the 1st roller 31 and the 2nd roller 32 hold | maintained at the 1st holder | retainer 41 and the 2nd holder | retainer 42 can be improved. As a result, the first retainer 41 and the second retainer 42 are prevented from interfering with the first roller 31 and the second roller 32 when the first roller 31 and the second roller 32 are engaged or disengaged. it can. The first holder 41 and the second holder 42 displaced toward the input shaft 3 in the axial direction are restricted from moving in the axial direction by contacting the position restricting member 54 (thrust bearing).

As described above, according to the roller clutch device 1 described with reference to FIG. 1, the rotational power input to the second inner ring 12 is output to the first inner ring 11 via the outer ring 20. The dimension in the radial direction can be reduced as compared with a roller clutch device (see FIG. 2 of Patent Document 1) that omits and outputs rotational power from the outer ring 20 radially outward.

Further, when the first roller 31 and the second roller 32 are engaged with the inner ring 10 and the outer ring 20, the outer raceway surfaces 11 a and 12 a of the inner ring 10 are elastically displaced radially inward, and the inner raceway surfaces 21 a and 22a is elastically displaced radially outward. The elastic displacement of the inner ring 10 and the outer ring 20 can absorb impact, vibration, and the like. The roller clutch device 1 includes the inner race 10 (the first roller 11 and the second roller 12) arranged in parallel in the axial direction, so that the outer raceway surfaces 11a and 12a and the inner circumference raceway surfaces 21a and 22a, the first roller 31 and the first roller 31 are arranged. The two rollers 32 come into contact with and engage with each other. Therefore, the roller clutch device 1 has a structure in which the first roller 31 and the second roller 32 are arranged in series between the input shaft 3 and the output shaft 7.

By arranging the first roller 31 and the second roller 32 and the like that contribute to elasticity in series between the input shaft 3 and the output shaft 7, compared to a roller clutch device in which the inner ring 10 is not juxtaposed in the axial direction, The spring constant between the input shaft 3 and the output shaft 7 can be reduced. Therefore, it is possible to improve absorption performance such as shock and vibration. As a result, it is possible to make it difficult to transmit the input noise, vibration, and the like to the output side, and it is possible to prevent the output side from being quickly worn out due to the influence of vibration or the like.

Further, the positions (load points) at which the outer peripheral raceway surfaces 11a and 12a and the inner

peripheral raceway surfaces

21a and 22a are engaged with the roller 30 are changed every time they are engaged, so that it is difficult for repeated loads to be generated at the same position. Therefore, the design considering the fatigue life can be eliminated.

On the other hand, since the first roller 31 and the second roller 32 roll in overrunning, the load is small and wear can be suppressed. Further, since the first roller 31 and the second roller 32 are provided, the overrunning speed can be bisected by the first roller 31 and the second roller 32. In addition, since the first roller 31 and the second roller 32 are pressed against the outer raceway surfaces 11a and 12a and the

inner raceway surfaces

21a and 22a by the pressure of the disc spring 53, the first roller 31 and the second roller 32 are fast-running. Even if a strong centrifugal force acts on the two rollers 32, the first roller 31 and the second roller 32 can be prevented from separating from the outer raceway surfaces 11a and 12a and the

inner raceway surfaces

21a and 22a.

Therefore, the first roller 31 and the second roller 32 can be quickly and reliably switched from the overrunning state to the locked state. Further, the first roller 31 and the second roller 32 divide the overrunning speed into two, so that the over-running speed is compared with the roller clutch device that does not have the double row rollers 30 (the first roller 31 and the second roller 32). The allowable rotational speed of running can be doubled.

Since the inner ring 10 is engaged with the outer peripheral raceway surfaces 11a and 12a and the outer ring 20 is the inner

peripheral raceway surfaces

21a and 22a, the inner ring 10 is engaged with the roller 30 and the outer ring 20 is engaged with the inner ring. What is necessary is just to process a surrounding surface. Since it is not necessary to process both sides like a conventional intermediate race, manufacture can be facilitated.

Further, when the outer peripheral raceway surfaces 11a and 12a are machined into a conical shape, the shape can be made almost the same as that of an ISO standard tapered roller bearing, so that the productivity is excellent and the manufacturing cost can be reduced. Furthermore, since the first outer ring 21 and the second outer ring 22, the first inner ring 11 and the second inner ring 12 arranged in parallel in the axial direction can be formed in substantially the same shape, the outer raceway surfaces 11a and 12a and the inner circumference raceway surfaces 21a and 22a. It is easy to adjust the elastic curve in the axial direction, and it is possible to improve productivity and reduce manufacturing costs.

The outer ring 20 (the first outer ring 21 and the second outer ring 22) is configured to be rotatable with respect to the central axis O and movable in the axial direction. The first retainer 41 and the second retainer 42 are The first roller 31 and the second roller 32 are held independently of each other. The outer ring 20, the first retainer 41, and the second retainer 42 are urged by the disc springs 52, 53, so that the first roller 31 and the second roller 32 have the outer peripheral track surfaces 11a, 12a and the inner peripheral track surface 21a. , 22a. Therefore, even if the first roller 31, the second roller 32, the outer peripheral raceway surfaces 11a and 12a and the inner

peripheral raceway surfaces

21a and 22a are worn, the first roller 31 and the second roller 32 are moved to the respective raceway surfaces by the wear amount. Can be corrected by pressing Therefore, it is not necessary to consider the wear of the first roller 31, the second roller 32, and each raceway surface.

In addition, since the second roller 32 is formed in the same shape as the first roller 31, the parts can be shared. In addition, since the outer raceway surface 12a of the second inner ring 12 is formed in the same shape as the outer raceway surface 11a of the first inner ring 11, the processing of the outer raceway surfaces 11a and 12a can be facilitated. . Moreover, since the inner peripheral raceway surface 22a of the second outer ring 22 is formed in the same shape as the inner peripheral raceway surface 21a of the first outer ring 21, the inner

peripheral raceway surfaces

21a and 22a can be easily processed. Can do. Thereby, the productivity of the inner ring 10 (first inner ring 11 and second inner ring 12) and the outer ring 20 (first outer ring 21 and second outer ring 22) can be improved.

Furthermore, since the outer diameters of the outer raceway surfaces 11a and 12a are formed to the same dimension, the outer circumference raceway surfaces 11a and 12a can be machined using a common gauge, machining tool, etc., and the machining cost can be reduced. Since the inner

peripheral raceway surfaces

21a and 22a have the same inner diameter, the same effect can be realized. Further, the elastic curves in the axial direction of the outer peripheral raceway surfaces 11a and 12a and the elastic curves in the axial direction of the inner

peripheral raceway surfaces

21a and 22a can be made the same. Thereby, between the 1st roller 31 and the 2nd roller 32, when the inner

periphery track surface

21a, 22a and the outer periphery track surface 11a, 12a and the 1st roller 31 and the 2nd roller 32 engage or disengage, It is possible to prevent the behavior from being disturbed and improve the reliability of the clutch operation.

Next, a second embodiment will be described with reference to FIG. 1st Embodiment demonstrated the case where the inner ring | wheel 10 was comprised by the 1st inner ring | wheel 11 and the 2nd inner ring | wheel 12 which can be rotated relatively. On the other hand, in the second embodiment, a case will be described in which the outer ring is composed of a first outer ring and a second outer ring that can rotate relative to each other. In addition, about the part same as 1st Embodiment, the same code | symbol is attached | subjected and the following description is abbreviate | omitted. FIG. 3 is an axial sectional view of the roller clutch device 101 according to the second embodiment.

As shown in FIG. 3, the roller clutch device 101 includes a rod 102 serving as a rotation center, an inner ring 110 disposed on the outer periphery of the rod 102, an outer ring 120 disposed on the radially outer side of the inner ring 110, A plurality of rollers 30 interposed between the outer ring 120 and the inner ring 110 and a retainer 40 that holds the plurality of rollers 30 between the outer ring 120 and the inner ring 110 are mainly configured.

The inner ring 110 is a cylindrical member that functions to transmit the rotational power of the input shaft 103 to the output shaft 107, and is disposed on the radially outer side of the rod 102 and is movable in the axial direction with respect to the rod 102. And it is comprised so that rotation around the central axis O is possible.

The input shaft 103 is a flange-like member through which the rod 102 penetrates. The input shaft 103 is configured to be rotatable with respect to the rod 102 and movable in the axial direction, and is arranged on one end side (right side in FIG. 3) of the rod 102. Has been. The output shaft 107 is a flange-like member through which the rod 102 penetrates. The output shaft 107 is configured to be rotatable with respect to the rod 102 and is disposed on the other axial end side (left side in FIG. 3) of the rod 102. The input shaft 103 and the output shaft 107 have through

holes

103a and 107a formed so as to penetrate in the axial direction. The input shaft 103 and the output shaft 107 are connected to other members (not shown) that transmit rotational power so as not to move in the axial direction by bolts or the like inserted through the through

holes

103 and 107a.

On the outer peripheral surface of the inner ring 110, outer peripheral raceway surfaces 111 and 112 that form a single-lobed hyperboloid around the central axis O of the rod 102 are formed and arranged in parallel in the axial direction. In the present embodiment, the outer peripheral raceway surfaces 111 and 112 are formed in the same shape, and the outer peripheral raceway surfaces 111 and 112 have the other end side in the axial direction (left side in FIG. 3) and one end side in the axial direction (right side in FIG. 3). It is formed to have a smaller diameter.

The outer ring 120 is an annular member having a function of transmitting the rotational power of the input shaft 103 to the output shaft 107 together with the inner ring 110, and includes a first outer ring 121 and a second outer ring 122 arranged in parallel in the axial direction. ing. The first outer ring 121 and the second outer ring 122 are respectively arranged on the outer sides in the radial direction of the outer raceway surfaces 111 and 112 with a predetermined distance from the inner ring 110, can be rotated relative to each other around the central axis O, and can be relative to the inner ring 110. It is configured to be rotatable.

On the inner peripheral surfaces of the first outer ring 121 and the second outer ring 122, inner

peripheral raceway surfaces

121a and 122a forming a single lobe rotating hyperboloid around the central axis O are formed. In the present embodiment, the inner

peripheral raceway surfaces

121a and 122a are formed in the same shape, and the inner

peripheral raceway surfaces

121a and 122a have a radius centered on the central axis O and the other end side in the axial direction (FIG. 3). The left side) is formed to have a smaller diameter than the one axial end side (the right side in FIG. 3).

In the first outer ring 121, a through hole 121 b continuous with the through hole 107 a is formed in the axial direction, and a shaft-like member (not shown) such as a bolt is inserted into the through

holes

107 a and 121 b to connect the output shaft 107. It is connected. In the second outer ring 122, a through hole 122b that is continuous with the through hole 103a is formed in the axial direction, and a shaft-like member (not shown) such as a bolt is inserted into the through

holes

103a and 122b to connect with the input shaft 103. It is connected. As a result, the first outer ring 121 and the second outer ring 122 can rotate integrally with the output shaft 107 and the input shaft 103, respectively.

An annular seal 130 is interposed between the opposed axial end faces of the first outer ring 121 and the second outer ring 122. The seal 130 is a member for closing a gap existing between the axial end surfaces of the first outer ring 121 and the second outer ring 122 that rotate relative to each other, and radially outward from between the first outer ring 121 and the second outer ring 122. Prevents lubricating oil from leaking. The seal 130 includes an insertion member 131 that is inserted between the first outer ring 121 and the second outer ring 122, and a cover portion 132 that is disposed on the radially outer side of the insertion member 131.

The insertion member 131 is disposed at the tip of the elastic body and an annular elastic body (not shown) made of rubber or the like extending in the axial direction from the axial end surfaces of the first outer ring 121 and the second outer ring 122. And an annular sliding contact portion (not shown). The sliding contact portion is formed of a fluororesin, carbon graphite, ceramics, or the like having excellent wear resistance. The sliding contact portions are brought into contact with each other and are in sliding contact with each other by the relative rotation of the first outer ring 121 and the second outer ring 122 to be sealed. Further, since the insertion member 131 includes an elastic body (not shown), it can be elastically deformed in the axial direction. The second outer ring 122 can be displaced in the axial direction as much as the insertion member 131 is elastically deformed. Moreover, since the cover part 132 is arrange | positioned at the radial direction outer side of the insertion member 131, even if lubricating oil leaks from the insertion member 131, scattering can be prevented.

In the roller clutch device 101, a stopper 104 is formed in a hook shape at one axial end of the rod 102, and a disc spring 105 is inserted between the stopper 104 and the input shaft 103. As a result, the input shaft 103 is biased toward the other end in the axial direction (left side in FIG. 3) with respect to the stopper 104. A disc spring 132 is interposed between the axial end surface of the input shaft 103 and the axial end surface of the inner ring 110. As a result, the inner ring 110 is biased toward the other axial end side (left side in FIG. 3) with respect to the input shaft 103.

The position restricting member 154 (thrust bearing) is a disk-shaped member for restricting the axial position of the first retainer 41 and the second retainer 42 urged toward the one axial end side by the disc spring 53, The second cage 42 is provided so as to be in contact with the axial end surface on the large diameter side. In the present embodiment, one end of the position regulating member 154 is fixed to the axial end surface inside the input shaft 103, and the other end is connected to the axial end surface of the second cage 42 on the input shaft 103 side (large diameter side). Pressed. Accordingly, the axial positions of the first retainer 41 and the second retainer 42 can be restricted by the axial position of the input shaft 103.

In addition, the elastic force in the axial direction of the insertion member 131 (seal 130) is set to a value smaller than the elastic force in the axial direction of the disc springs 105 and 132. Thereby, when the rotational power is not input to the input shaft 103 or the output shaft 107, the first outer ring 121 (inner circumferential track surface 121a) and the inner ring 110 (outer circumferential track surface 111) are in contact with the first roller 31. It can be prevented from becoming insufficient.

Further, the elastic force in the axial direction of the disc spring 105 is set to a value smaller than the elastic force in the axial direction of the disc spring 132. Thereby, when the rotational power is not input to the input shaft 103 or the output shaft 107, the second outer ring 122 (inner circumferential raceway surface 122a) and the inner ring 110 (outer circumferential raceway surface 112) are in contact with the second roller 32. It can be prevented from becoming insufficient.

According to the roller clutch device 101 configured as described above, when rotational power in a predetermined direction (the arrow direction in FIG. 3) is input to the input shaft 103 and the second outer ring 122, the second roller 32 moves the inner circumferential raceway surface 122a. The second roller 32 rotates (the direction of rotation of the second roller 32 is the direction opposite to the arrow in FIG. 3), bites into the outer raceway surface 112 of the inner ring 110 by its traction, and locks (engages) with the wedge action. Rotates together. When the second outer ring 122, the inner ring 110, and the second roller 32 rotate together, the first roller 31 rolls on the outer raceway surface 111 and bites into the inner circumference raceway surface 121a of the first outer ring 121 by the traction. It is locked (engaged) by the action and rotates together with the first outer ring 121 and the inner ring 110. That is, the input torque is output from the second outer ring 122 to the first outer ring 121 (the rotation direction is the arrow direction in FIG. 3).

On the other hand, when rotational power in a predetermined direction (the arrow direction in FIG. 3) is input to the output shaft 107 due to relative rotation with the input shaft 103, the first roller 31 causes the inner circumferential raceway surface 121 a of the first outer ring 121 and the inner ring 110 to move. The outer raceway surface 111 moves out in the direction of overrunning. Further, centrifugal force is applied to the first roller 31, and the first roller 31 moves along the inner circumferential raceway surface 121 a of the first outer ring 121 and is detached from the inner circumferential raceway surface 121 a and the outer circumferential raceway surface 111.

When transmission of power from the first outer ring 121 to the inner ring 110 via the first roller 31 is interrupted, the second roller 32 is also rotated by the relative rotation between the second outer ring 122 and the inner ring 110 so that the second roller 32 also has the inner raceway surface 122a and the outer circumference raceway. Detach from surface 112. When the first roller 31 and the second roller 32 are separated from the outer peripheral raceway surfaces 111 and 112 and the inner

peripheral raceway surfaces

121a and 122a, the first retainer 41 and the second retainer that hold the first roller 31 and the second roller 32. 42 is displaced to the output shaft 107 side in the axial direction when the disc spring 53 is compressed, and is positioned on the input shaft 103 side by the bias of the disc spring 53.

As described above, according to the roller clutch device 101, the rotational power input to the second outer ring 122 is output to the first outer ring 121 via the inner ring 110. The inner ring 110 that functions as a kind of flywheel can have a smaller mass and radius than the outer ring 20 (which functions as a flywheel) of the roller clutch device 1 according to the first embodiment. Therefore, according to the roller clutch device 101, in addition to the effect produced by the roller clutch device 1 described in the first embodiment, the moment of inertia of the inner ring 110 can be reduced, and the response of the clutch can be improved.

The present invention has been described above based on the embodiments. However, the present invention is not limited to the above embodiments, and various improvements and modifications can be made without departing from the spirit of the present invention. It can be easily guessed. For example, the numerical values (for example, the number and size of each component) given in the above embodiment are merely examples, and other numerical values can naturally be adopted.

In each of the above embodiments, the outer

peripheral raceway surfaces

11a, 12a, 111, 112 and the inner

peripheral raceway surfaces

21a, 22a, 121a, 122a are formed as a single-leaf rotating hyperboloid, and the first roller 31 and the second roller 32 are cylindrical. However, the present invention is not necessarily limited to this, and it is naturally possible to employ the outer peripheral raceway surface, the inner peripheral raceway surface, the first roller, and the second roller in other forms. As other forms, for example, the outer peripheral raceway surface and the inner peripheral raceway surface are formed of a single leaf rotating hyperboloid and the first roller and the second roller are conical, or the outer peripheral raceway surface or the inner peripheral raceway surface is cylindrical. Examples of the first roller and the second roller are drums, drums, and cylinders.

In the first embodiment, the case where the outer ring 20 is moved in the axial direction using the lever 51 in order to make the inner ring 10 and the outer ring 20 and the roller 30 unengageable has been described. However, the present invention is not limited to this. Of course, by adopting a means for moving the inner ring 10 (particularly, the second inner ring 12) in the axial direction, the inner ring 10, the outer ring 20, and the roller 30 can be made non-engageable.

In the first embodiment, the case where the lever 51 is used as the means for moving the outer ring 20 in the axial direction has been described. However, the present invention is not necessarily limited to this, and other moving means may naturally be adopted. Is possible. Examples of other moving means include known means such as a cylinder using fluid pressure and an electromagnet using magnetic force.

In the second embodiment described above, the lever 51 described in the first embodiment is not provided with a means for releasing the engagement of the roller 30, but the present invention is not necessarily limited thereto. Naturally, it is possible to provide an engagement releasing means for forcibly releasing the engagement of the roller 30 by moving the outer ring 120 (particularly the second outer ring 122) or the inner ring 110 in the axial direction. The engagement / disengagement of the clutch can be switched by operating the disengaging means. In the roller clutch device 1 according to the first embodiment, the lever 51 may be omitted.

In the second embodiment, it is possible to provide gear teeth and pulley grooves on the outer periphery of the first outer ring 121 and the second outer ring 122. By providing gear teeth or pulley grooves on the outer circumferences of the first outer ring 121 and the second outer ring 122, the rotational power is supplied to the roller clutch device 101 by the gears meshing with the teeth or the belt stretched on the pulley grooves. Can input and output. The roller clutch device is formed by integrally forming a gear on the outer periphery of the first outer ring 121 or the second outer ring 122, as compared with the case where the first outer ring 121 or the second outer ring 122 is fitted on the inner peripheral surface of the gear. The diameter of 101 can be reduced.

Moreover, although the said 1st Embodiment demonstrated the case where the 1st inner ring | wheel 11 was provided rotatably with respect to the rod 2, it is not necessarily restricted to this, The rod 2 is provided rotatably and 1st is provided. Of course, it is possible to provide the inner ring 11 so as to rotate integrally with the rod 2. Also in this case, the first inner ring 11 rotates around the central axis O.

In each of the embodiments described above, the case where the

inner rings

10, 110, the outer rings 20, 120, and the cage 40 are urged in the axial direction by the disc springs 5, 52, 53, 105, 132 has been described. Of course, it is possible to employ other elastic members. Examples of other elastic members include a compression coil spring and a rubber-like elastic body.
Although a description is omitted in each of the above embodiments, a stopper that prevents the

inner ring

10, 110 or the

outer ring

20, 120 from moving in the axial direction when the

inner ring

10, 110 and the

outer ring

20, 120 are engaged with the roller 30 ( Of course, it is possible to provide the same. The axial end face of the

inner ring

10, 110 or the

outer ring

20, 120 that moves in the axial direction is brought into contact with the stopper, and further axial displacement can be restricted. Thereby, the function of a torque limiter can be provided. As a result, even if the roller 30 bites into the

inner rings

10 and 110 and the

outer rings

20 and 120 to the limit with excessively input torque, problems such as pop-out can be prevented. Further, if the displacement amount of the stopper is measured in a non-contact manner, it has a torque sensor function for detecting the drive torque with high accuracy even during high-speed rotation, and a simple horsepower meter can be configured by using the tachometer together.

Claims

An inner ring configured to be rotatable about a central axis;
An outer ring disposed on the radially outer side of the inner ring and configured to be rotatable relative to the inner ring and movable relative to the axial direction;
An inner circumferential raceway surface formed on the inner circumferential surface of the outer ring,
An outer peripheral raceway surface facing the inner peripheral raceway surface and formed on the outer peripheral surface of the inner ring;
A plurality of rollers that are interposed between the outer circumferential raceway surface and the inner circumferential raceway surface and engage the inner circumferential raceway surface and the outer circumferential raceway surface to transmit rotational power;
In a roller clutch device comprising a retainer that holds the plurality of rollers spaced apart from each other in the circumferential direction while being inclined at a predetermined angle from a surface including the central axis,
One of the inner ring and the outer ring is configured to include a first member and a second member arranged in parallel in the axial direction,
The roller includes a plurality of first rollers and second rollers provided to face the first member and the second member, respectively.
The other of the inner ring or the outer ring is straddled across the plurality of first rollers and second rollers, and rotational power input from one of the first member or the second member is applied to the first member. Or it outputs to the other of the said 2nd member, The roller clutch apparatus characterized by the above-mentioned.
The retainer is disposed on the radially outer side or the radially inner side of the first member, and holds the plurality of first rollers spaced apart from each other in the circumferential direction;
The second cage is arranged in parallel to the outside of the first cage in the axial direction, and holds the plurality of second rollers spaced apart from each other in the circumferential direction.
A movement direction in the axial direction of the roller when the roller engages with the inner circumferential raceway surface and the outer circumferential raceway surface, disposed at one axial end of the second cage or the first cage; An elastic member for urging the first cage and the second cage in the same direction;
Position restriction that restricts the axial position of the first and second cages arranged at the other axial end of the second cage or the first cage and biased by the elastic member The roller clutch device according to claim 1, further comprising a member.
In the second member, the inner raceway surface or the outer circumference raceway surface is formed in the same shape as the inner circumference raceway surface or the outer circumference raceway surface of the first member,
The roller clutch device according to claim 1, wherein the second roller is formed in the same shape as the first roller.