WO2020189808A1

WO2020189808A1 - Double-layer one-way clutch bearing

Info

Publication number: WO2020189808A1
Application number: PCT/KR2019/003074
Authority: WO
Inventors: 유병수
Original assignee: 유병수
Priority date: 2019-03-15
Filing date: 2019-03-15
Publication date: 2020-09-24

Abstract

The present invention relates to a double-layer one-way clutch bearing, and the purpose of the present invention is to provide a double-layer one-way clutch bearing which includes a clutch part and a bearing part formed in a double-layer structure and thus can easily be implemented with a narrow width. To this end, the present invention provides a double-layer one-way clutch bearing comprising: an inner wheel which is shaped like a circular ring such that a shaft can be fitted through the center portion thereof, includes a first coupling part formed on the outer circumference thereof, and includes a first groove extending in the circumferential direction on the rear surface thereof; an outer wheel which is shaped like a circular ring surrounding the outer circumference of the inner wheel, includes a second coupling part formed on the inner circumference thereof to be inserted to the first groove and coupled to the inner wheel, and includes a second groove extending in the circumferential direction on the front surface thereof such that the first coupling part is inserted to the second groove; a bearing part configured in the first groove to support the rotation of the inner wheel and the outer wheel; and a clutch part configured in the second groove and operated such that the inner wheel and the outer wheel rotate together in a first direction, and only the inner wheel or the outer wheel rotates in a second direction opposite to the first direction.

Description

Double layer one-way clutch bearing

The present invention relates to a one-way clutch bearing that transmits power in only one direction, and more particularly, a one-way clutch bearing having a narrow width can be easily configured by comprising a clutch part and a bearing part in a multilayer structure, and the clutch part It relates to a double-layer one-way clutch bearing made to transmit a large torque including a double friction force induction structure.

In general, Wenway clutch bearings are bearings made to transmit power in only one direction, and are used for various purposes, such as transmissions of vehicles and driving devices of various industrial machines.

1 is a cross-sectional view of a conventional one-way clutch bearing.

Conventional one-way clutch bearing is configured between the inner ring 10, the outer ring 20 arranged in a concentric structure on the outer side of the inner ring 10, and the inner ring 10 and the outer ring 20, the inner ring 10 ) And a bearing unit 30 connecting the outer ring 20 in a rotatable structure, and the inner ring 10 and the outer ring 20 are configured between the inner ring 10 and the outer ring 20 for rotation in one direction. ) Is rotated together, and for rotation in the other direction, only one of the inner ring 10 or the outer ring 20 is rotated, and thus the clutch part 40 is configured to transmit power only in a predetermined direction.

Such a conventional one-way clutch bearing has a wide width W as the bearing units 30 are configured on both left and right sides of the clutch unit 40.

Accordingly, when a plurality of one-way clutch bearings are installed on one shaft, a large amount of installation space is required due to the wide width of the one-way clutch bearing, and there is a problem that a device configured using the one-way clutch bearing becomes large.

In addition, in the conventional one-way clutch bearing, when a torque greater than the frictional force formed between the roller and the inner ring or the roller and the outer ring acts in the process of transmitting torque while the roller constituted in the clutch part is sandwiched between the inner and outer rings, the inner ring and There is a problem in that the outer ring does not rotate together and the phenomenon that it spins is generated.

In addition, when a drag phenomenon occurs between the roller and the inner ring or the roller and the outer ring in the process of transmitting torque while the inner ring and the outer ring are interposed between the roller, there is a problem in that vibration or noise is generated.

(Prior technical literature)

(Patent Document)

(Patent Document 1) Unexamined Patent Publication No. 10-2004-0007698 (published on January 24, 2004)

The present invention has been made in consideration of the above problems, and an object of the present invention is to provide a multilayer one-way clutch bearing that can easily implement a one-way clutch bearing having a narrow width by forming a clutch part and a bearing part in a multilayer structure.

Another object of the present invention is to provide a double-layer one-way clutch bearing capable of transmitting a large torque by using a double friction force induction structure configured in a clutch unit.

Another object of the present invention is to provide a multilayer one-way clutch bearing capable of reducing the generation of vibration and noise.

Another object of the present invention is to provide a multilayer one-way clutch bearing with increased service life by reducing the amount of wear generated during clutch operation.

The present invention, which achieves the above object and performs the task to eliminate the conventional defect, is made in a circular ring shape so that the shaft can be fitted in the central part, but the first coupling part is formed around the outer circumference, and An inner ring formed with a first groove extending in the circumferential direction; Consisting of a circular ring shape surrounding the outer circumference of the inner ring, a second coupling portion inserted into the first groove and coupled to the inner ring is formed around the inner circumference, and the first coupling portion is formed to extend in a circumferential direction on the front surface. An outer ring formed with a second groove to be inserted; A bearing unit configured in the first groove to support rotation of the inner and outer rings; And a clutch unit configured in the second groove to rotate the inner ring and the outer ring together when rotating in the first direction, and to rotate only the inner ring or the outer ring when rotating in the second direction opposite to the first direction. It provides a double-layer one-way clutch bearing characterized by.

Meanwhile, in the multilayer one-way clutch bearing, the clutch portion is formed on the inner or outer ring so as to rotate together with the inner or outer ring in the second groove, protruding into the second groove, and the circumference or outer ring of the inner ring A ring-shaped protrusion extending along the circumference of the circumference and formed to have a trapezoidal cross section; A plurality of inserted double wedge friction force induction clutch stoppers formed in a block shape having a binding groove including two corresponding inclined surfaces inclined to generate frictional force while being in close contact with the two slopes formed on the ring-shaped protrusions; The second groove is formed on the other of the inner ring and the outer ring so as to face the ring-shaped protrusion, but when rotating in the first direction, the inserted double wedge friction force induction clutch stopper is pressed to come into close contact with the ring-shaped protrusion. A plurality of cam-shaped protrusions formed to be distributed along the circumference of the inner ring or the outer ring, and including an inclined surface for releasing the pressure of the inserted double wedge friction force induction clutch stopper when rotating in the second direction; And a plurality of elastic members disposed between the inserted double wedge friction force inducing clutch stopper and the cam-shaped protrusion to elastically support the inserted double wedge friction force inducing clutch stopper.

Meanwhile, in the double-layer one-way clutch bearing, two corresponding inclined surfaces formed on the inserted double wedge friction force inducing clutch stopper may be configured to be in line with the slope of the ring-shaped protrusion formed of a curved surface.

Meanwhile, in the multilayer one-way clutch bearing, the clutch portion is formed on the inner or outer ring so as to rotate together with the inner or outer ring in the second groove, and has a predetermined depth, and extends along the circumference of the inner ring or the outer ring. A ring-shaped groove formed to have a trapezoidal cross section; Consisting of a block having a trapezoidal cross section including two corresponding inclined surfaces inclined to generate friction while being in close contact with the two slopes formed in the ring-shaped groove, a plurality of insertion-type double wedge friction forces that are partially inserted and coupled to the ring-shaped groove Induction clutch stopper; The second groove is formed in the remaining one of the inner and outer rings in which the ring-shaped groove is not formed so as to face the ring-shaped groove. When rotating in the first direction, the insert-type double wedge friction force induction clutch stopper is pressed to come into close contact with the ring-shaped groove. A plurality of cam-shaped protrusions formed to be distributed along the circumference of the inner ring or the outer ring, and including an inclined surface for releasing the pressure of the inserted double wedge friction force induction clutch stopper when rotating in two directions; And a plurality of elastic members disposed between the insert-type double wedge friction force inducing clutch stopper and the cam-type protrusion to elastically support the insert-type double wedge friction force inducing clutch stopper.

In addition, the present invention is made in the shape of a circular ring so that the shaft can be fitted in the central portion, the inner ring consisting of a first coupling portion is formed around the outer circumference, and a first groove extending in the circumferential direction is formed on the rear; Consisting of a circular ring shape surrounding the outer circumference of the inner ring, a second coupling portion inserted into the first groove and coupled to the inner ring is formed around the inner circumference, and the first coupling portion is formed to extend in a circumferential direction on the front surface. An outer ring formed with a second groove to be inserted; A bearing unit configured in the second groove to support rotation of the inner and outer rings; And a clutch unit configured in the first groove to rotate the inner ring and the outer ring together when rotating in the first direction, and to rotate only the inner ring or the outer ring when rotating in the second direction opposite to the first direction. One-way clutch bearings are provided.

At this time, the clutch part is formed on the inner ring or the outer ring so as to rotate with the inner ring or the outer ring in the inside of the first groove, protrudes into the inside of the first groove, and extends along the circumference of the inner ring or the outer ring, and trapezoidal A ring-shaped protrusion formed to have a cross section of the shape; A plurality of inserted double wedge friction force induction clutch stoppers formed in a block shape having a binding groove including two corresponding inclined surfaces inclined to generate frictional force while being in close contact with the two slopes formed on the ring-shaped protrusions; The inner ring and the outer ring are formed on the other of the inner ring and the outer ring so as to face the ring-shaped protrusion inside the first groove, and when rotating in the first direction, the inserted double wedge friction force induction clutch stopper is pressed to come into close contact with the ring-shaped protrusion. A plurality of cam-shaped protrusions formed to be distributed along the circumference of the inner ring or the outer ring, and including an inclined surface for releasing the pressure of the inserted double wedge friction force induction clutch stopper when rotating in the second direction; And a plurality of elastic members disposed between the inserted double wedge friction force inducing clutch stopper and the cam-shaped protrusion to elastically support the inserted double wedge friction force inducing clutch stopper.

In addition, the clutch part is formed on the inner ring or the outer ring so as to rotate together with the inner ring or the outer ring inside the first groove, has a predetermined depth, extends along the circumference of the inner ring or the outer ring, and has a trapezoidal cross section. Formed ring-shaped grooves; Consisting of a block having a trapezoidal cross section including two corresponding inclined surfaces inclined to generate friction while being in close contact with the two slopes formed in the ring-shaped groove, a plurality of insertion-type double wedge friction forces that are partially inserted and coupled to the ring-shaped groove Induction clutch stopper; The inner ring and the outer ring are formed in the other of the inner ring and the outer ring so as to face the ring-shaped groove in the inside of the first groove, but when rotating in the first direction, the insert-type double wedge friction force induction clutch stopper is pressed to closely contact the ring-shaped groove, A plurality of cam-shaped protrusions formed to be distributed along the circumference of the inner ring or the outer ring, and including an inclined surface for releasing the pressure of the inserted double wedge friction force induction clutch stopper when rotating in two directions; And a plurality of elastic members disposed between the insert-type double wedge friction force inducing clutch stopper and the cam-type protrusion to elastically support the insert-type double wedge friction force inducing clutch stopper.

According to the present invention having the above characteristics, since the bearing portion and the clutch portion are configured in a multilayer structure, it is possible to provide a one-way clutch bearing having a narrow width.

In addition, when multiple one-way clutch bearings are installed on one shaft, the area of the space required to install multiple one-way clutch bearings can be reduced due to the narrow width of the one-way clutch bearings. It can help in miniaturization of equipment to which clutch bearings are applied.

In addition, since the two slopes of the ring-shaped protrusion and the two corresponding slopes of the double wedge friction force inducing clutch stopper are in close contact with each other, a large frictional force can be generated, so that a large torque can be transmitted.

In addition, even if the force of the elastic member that elastically supports the double wedge friction force induction clutch stopper is decreased, a large friction force can be obtained, and the amount of wear generated during clutch operation can be reduced, thereby extending the service life of the one-way clutch bearing.

In addition, the double wedge friction force induction clutch stopper located between the ring-shaped protrusion and the cam-shaped protrusion is composed of a block and maintains a stable close contact with the ring-shaped protrusion and the cam-shaped protrusion, so vibration or noise is generated in the process of transmitting torque. Can be prevented.

1 is a cross-sectional view of a conventional one-way clutch bearing,

2 is a cross-sectional view of a double-layer one-way clutch bearing according to a first embodiment of the present invention,

3 is a front view of a double-layer one-way clutch bearing according to a first embodiment of the present invention,

4 is a detailed view of a clutch part according to a first embodiment of the present invention,

5 is a perspective view of a clutch part according to a first embodiment of the present invention,

6 is a cross-sectional view showing a coupling structure of a ring-shaped protrusion and an inserted double wedge friction force induction clutch stopper according to a first embodiment of the present invention;

7 is a cross-sectional view of a double-layer one-way clutch bearing in which the clutch portion is inverted up and down according to the first embodiment;

8 is a detailed view of a clutch part of another structure according to the first embodiment of the present invention,

9 is a cross-sectional view of the clutch part shown in FIG. 8;

10 is an exemplary view showing the relationship between the force generated between the cam-shaped protrusion and the inserted double wedge friction force induction clutch stopper;

11 is an exemplary view showing the relationship between the force formed between the inserted double wedge friction force induction clutch stopper and the ring-shaped protrusion;

12 is a cross-sectional view of a double-layer one-way clutch bearing according to a second embodiment of the present invention,

13 is a cross-sectional view of a double-layer one-way clutch bearing in which a clutch portion is vertically inverted according to a second embodiment;

14 is a cross-sectional view of a clutch part of another structure according to the second embodiment.

(Explanation of code)

(Explanation of symbols for major parts of the drawing)

110: inner ring 111: first coupling portion

112: first groove 120: outer ring

121: second coupling portion 122: second groove

130: bearing part 140: clutch part

141: ring-shaped protrusion 141a: slope

141`: ring-shaped groove

142: Insertion type double wedge friction force induction clutch stopper

142b: corresponding slope

142`: Insertion type double wedge friction induction clutch stopper

1421: coupling groove 143: cam-type protrusion

143a: inclined surface 144: elastic member

210: inner ring 211: first coupling portion

212: first groove 220: outer ring

221: second coupling portion 222: second groove

230: bearing part 240: clutch part

241: ring-shaped protrusion 241a: slope

241`: ring-shaped groove

242: Insertion type double wedge friction force induction clutch stopper

242b: corresponding slope

242`: insert type double wedge friction induction clutch stopper

2421: coupling groove 243: cam-type protrusion

243a: inclined surface 244: elastic member

Hereinafter, preferred embodiments of the present invention will be described in detail in conjunction with the accompanying drawings. In describing the present invention, when it is determined that a detailed description of a related known function or configuration may unnecessarily obscure the subject matter of the present invention, a detailed description thereof will be omitted.

In the multilayer one-way clutch bearing according to the present invention, the bearing unit 130 and the clutch unit 140 configured between the inner ring 110 and the outer ring 120 are formed in a two-layer structure, that is, a double layer, so that the width is relatively narrow. A one-way clutch bearing can be easily configured, and a relatively large torque can be transmitted by a double frictional force inducing structure configured in the clutch unit 140, and these features are described in the first embodiment and the first described below. Both examples are the same.

2 is a cross-sectional view of a multilayer one-way clutch bearing according to a first embodiment of the present invention, FIG. 3 is a front view of a multilayer one-way clutch bearing according to a first embodiment of the present invention, and FIG. 4 is a first embodiment of the present invention. A detailed view of the clutch unit according to the embodiment, Fig. 5 is a perspective view of the clutch unit according to the first embodiment of the present invention, and Fig. 6 is a ring-shaped protrusion according to the first embodiment of the present invention and an inserted double wedge friction force induction clutch stopper 7 is a cross-sectional view of a double-layer one-way clutch bearing in which the clutch portion according to the first embodiment is vertically inverted.

The multilayer one-way clutch bearing according to the first embodiment of the present invention includes an inner ring 110, an outer ring 120, a bearing unit 130, and a clutch unit 140.

The inner ring 110 is a portion coupled to the shaft so as to behave together with the shaft, and is formed in a circular ring shape so that the shaft can be coupled through the central portion, and a first for coupling with the outer ring 120 around the outer circumference The coupling part 111 is formed, and a first groove 112 for coupling with the outer ring 120 and installation of the bearing part 130 is formed on the rear surface.

On the other hand, the first coupling portion 111 is formed in a circular belt shape, and is inserted into the second groove 122 formed on the front surface of the outer ring 120 when the inner ring 110 and the outer ring 120 are coupled.

In addition, the first groove 112 is a groove formed to have a certain depth from the rear surface of the inner ring 110, is made in a ring shape extending along the circumference of the inner ring 110, the second coupling portion 121 to be described later And it is formed wide enough to provide a space for installation of the bearing unit 130.

The inner ring 110 including the first coupling part 111 and the first groove 112 has a'C'-shaped cross-section with an open rear surface.

On the other hand, at the inlet side of the first groove 112, the bearing unit 130 and the second coupling unit 121 are provided with the first groove ( A first fixing plate 151 is installed to prevent separation from 112, and the first fixing plate 151 is formed in a circular ring shape, and fixed by a snap ring 152 fastened to the first groove 112. do.

On the other hand,

reference numerals

155 and 156 shown in FIG. 2 are disc bushes that are installed at a contact portion between the inner ring 110 and the outer ring 120 to reduce frictional resistance.

The outer ring 120 is a part constituting the outer region of the one-way clutch bearing, and is formed in a circular ring shape surrounding the outer circumference of the inner ring 110, and the inner circumference is a first for coupling with the inner ring 110. A second coupling portion 121 is formed, and a second groove 122 for coupling with the inner ring 110 and installation of the clutch 140 is formed on the front surface.

On the other hand, the second coupling portion 121 is made in a circular belt shape, and is inserted into the first groove 112 formed on the rear surface of the inner ring 110 when the inner ring 110 and the outer ring 120 are coupled.

In addition, the second groove 122 is a groove formed to have a predetermined depth from the front surface of the outer ring 120, is made in a ring shape extending along the circumference of the outer ring 120, the first coupling portion 111 and It is formed wide enough to provide a space for the installation of the clutch unit 140.

The outer ring 120 including the second coupling portion 121 and the second groove 122 has a'C'-shaped cross-section with an open front.

On the other hand, at the entrance side of the second groove 122, while protecting the clutch unit 140 configured in the second groove 122 from the external environment, the clutch unit 140 and the first coupling unit 111 are provided with the second groove ( A second fixing plate 153 is installed to prevent separation from 122, and the second fixing plate 153 is formed in a circular ring shape, and fixed by a snap ring 154 fastened to the second groove 122. do.

The bearing unit 130 supports rotation of the inner ring 110 and the outer ring 120 so that the inner ring 110 and the outer ring 120 can rotate smoothly, and is configured in the first groove 112.

The bearing unit 130 may be configured by installing a known bearing including a plurality of balls or rollers in the first groove 112.

In addition, as shown in FIG. 2, the bearing unit 130 may be configured in a manner in which a plurality of balls are directly installed between the inner ring 110 and the second coupling unit 121.

Meanwhile, in FIG. 2, a structure of the bearing unit 130 is shown in which balls are installed in a two-row structure, but the balls may be installed in a single-row structure.

The clutch unit 140 is to allow the inner ring 110 and the outer ring 120 to rotate together or only the inner ring 110 or the outer ring 120 to rotate independently according to the rotation direction, and the ring-shaped protrusion 141, the inserted double It consists of a wedge friction force induction clutch stopper 142, a cam-shaped protrusion 143, and an elastic member 144.

The clutch unit 140 may be configured to transmit the movement of the outer ring 120 to the inner ring 110, or may be configured to transmit the movement of the inner ring 110 to the outer ring 120, and FIGS. 2 to 6 show the outer ring 120 The structure of the clutch unit configured to transmit the movement of) to the inner ring 110 is shown, and FIG. 7 shows the structure of the clutch unit configured to transmit the movement of the inner ring 110 to the outer ring 120.

First, the clutch unit 140 configured to transmit the movement of the outer ring 120 to the inner ring 110 will be described with reference to FIGS. 2 to 6.

In this case, the ring-shaped protrusion 141 is formed integrally with the inner ring 110 to behave together with the inner ring 110, and extends along the circumference of the inner ring 110 on the outer circumferential surface of the inner ring 110 and in an outward direction. It protrudes and is formed to have a trapezoidal cross section.

The ring-shaped protrusion 141 formed as described above is formed on the outside of the first coupling portion 121 and is located inside the second groove 122 formed in the outer ring 120 when the inner ring 110 and the outer ring 120 are coupled. Is done.

The inserted double wedge friction force induction clutch stopper 142 is made of a block having a shape of a hexahedron, and the ring-shaped protrusion 141 is inserted and a binding groove 1421 coupled with the ring-shaped protrusion 141 is formed on the bottom surface. , The upper surface 142a which faces the cam-shaped protrusion 143 and is in close contact is formed to be inclined.

Meanwhile, the binding groove 1421 includes two corresponding inclined surfaces 142b that are in close contact with the two slopes 141a formed on the ring-shaped protrusion 141, and face the upper surface of the ring-shaped protrusion 141. The surface 142c is spaced apart from the ring-shaped protrusion 141.

Therefore, when the cam-shaped protrusion 143 presses the upper surface 142a of the inserted double wedge friction force induction clutch stopper 142 by the rotation of the outer ring 120, the two corresponding inclined surfaces 142b are ring-shaped protrusions 141 ), the friction force is generated while being in close contact with the two slopes 141a of), and since the two corresponding inclined surfaces 142b and the slope 141a are in close contact with each other to generate friction, it is possible to stably transmit a large torque.

On the other hand, as the ring-shaped protrusion 141 is formed to extend along the outer circumference of the inner ring 110, the two slopes 141a are made of a curved surface, and two corresponding slopes 142b that are in close contact with these two slopes 141a ) Is preferably configured to be in line contact with the slope (141a) made of a flat surface.

According to this structure, when the outer ring 120 and the inserted double wedge friction force induction clutch stopper 142 move in the second direction D2 while the outer ring 120 rotates in the second direction D2, the ring-shaped protrusion The lubricant applied to the surface of 141 flows smoothly between the inserted double wedge friction force induction clutch stopper 142 and the ring-shaped protrusion 141, and in particular, the line contact between the slope 141a and the corresponding inclined surface 142b is a lubricant. Since the role of the lubricant increases while dragging and moving, it is possible to reduce the wear of the ring-shaped protrusion 141 and the inserted double wedge friction force induction clutch stopper 142.

The inserted double wedge friction force induction clutch stopper 142 configured as described above is composed of a plurality, and is disposed to be distributed along the circumference of the inner ring 110 and the outer ring 120.

The cam-shaped protrusion 143 is formed integrally with the outer ring 120 so as to behave together with the outer ring 120 and face the ring-shaped protrusion 141 inserted into the second groove 122. It protrudes from the inside of the groove 122, and, like the inserted double wedge friction force induction clutch stopper 142, is formed in a structure distributed along the circumference of the outer ring 120.

On the other hand, each cam-shaped protrusion 143 presses the inserted double wedge friction force induction clutch stopper 142 when the outer ring 120 rotates in the first direction (D1) to closely contact the ring-shaped protrusion 141, and the outer ring ( When 120) rotates in the second direction D2, it includes an inclined surface 143a for releasing the pressure of the inserted double wedge friction force induction clutch stopper 142.

At this time, the inclined surface 143a is formed to be inclined to form a structure in which the cam-shaped protrusion 143 gradually protrudes from the second direction D2.

The elastic member 144 is disposed between the inserted double wedge friction force inducing clutch stopper 142 and the cam-shaped protrusion 143 to push the inserted double wedge friction force inducing clutch stopper 142 in the second direction D2. .

Such an elastic member 144 may be composed of a coil spring or a circular plate spring, and a plurality of inserted-type double wedge frictional force inducing clutch stoppers 142 and cam-shaped protrusions 143 are each disposed between.

When the outer ring 120 rotates in the first direction (D1), the clutch stopper 142 is inserted into the double wedge friction force induction clutch stopper 142 by the cam-shaped protrusion 143, and the ring-shaped protrusion 141 ), and thus the inner ring 110 and the outer ring 120 are bound and rotated together.

On the other hand, when the outer ring 120 rotates in the second direction (D2), the cam-shaped protrusion 143 moves in a direction away from the inserted double wedge friction force induction clutch stopper 142, while the inserted double wedge friction induction clutch Since the pressurization of the stopper 142 is released, the inner ring 110 and the outer ring 120 cannot rotate together, and only the outer ring 120 rotates.

Next, a description will be given of the clasp processing unit 140 configured to transmit the movement of the inner ring 120 to the outer ring 120 with reference to FIG. 7.

In this case, the ring-shaped protrusion 141 behaves together with the outer ring 110 formed integrally with the outer ring 120, and extends along the circumference of the outer ring 120 from the inside of the second groove 122 and the second groove It protrudes in the inward direction of 122 and is formed to have a trapezoidal cross section.

The inserted double wedge friction force induction clutch stopper 142 differs only in that it is arranged in a vertically inverted posture inside the second groove 122, and the practical configuration is described with reference to FIGS. 2 to 6 Since it is the same as the inserted double wedge friction force induction clutch stopper 142, a detailed description will be omitted.

The cam-shaped protrusion 143 is formed integrally with the inner ring 110 and moves together with the inner ring 110, and the inner ring 110 faces the ring-shaped protrusion 141 protruding from the inside of the second groove 122. It is formed to protrude outward.

A plurality of these cam-shaped protrusions 143 are formed to be distributed along the circumference of the inner ring 110, and each cam-shaped protrusion 143 is an inserted double wedge friction force induction clutch when the inner ring 110 rotates in the first direction (D1). It is configured to include an inclined surface 143a for pressing the stopper 142 and releasing the pressurization of the inserted double wedge friction force induction clutch stopper 142 when the inner ring 110 rotates in the second direction D2.

The elastic members 144 are disposed between the inserted double wedge friction force inducing clutch stopper 142 and the cam-shaped protrusion 143, respectively.

According to the clutch unit 140 configured as described above, when the inner ring 110 rotates in the first direction (D1), the cam-shaped protrusion 143 presses the inserted double wedge friction force induction clutch stopper 142 to move the inner ring 110 When the inner ring 110 rotates in the second direction (D2), the cam-shaped protrusion 143 is separated by the inserted double wedge friction force induction clutch stopper 142, so the movement of the inner ring 110 is It is not transmitted to the outer ring 120.

FIG. 8 is a detailed view of a clutch part having another structure according to the first embodiment of the present invention, and FIG. 9 is a cross-sectional view of the clutch part shown in FIG. 8.

The clutch part 140 may include a ring-shaped groove part 141 ′, an insert-type double wedge friction force inducing clutch stopper 142 ′, a cam-shaped protrusion 143, and an elastic member 144.

The ring-shaped groove portion 141 ′ is formed on the inner ring 110 or the outer ring 120 so as to rotate together with the inner ring 110 or the outer ring 120 in the second groove 122, and has a predetermined depth, and the inner ring ( It extends along the circumference of 110) or the circumference of the outer ring 120 and is formed to have a trapezoidal cross section.

Meanwhile, in FIGS. 8 and 9, a structure of a ring-shaped groove portion 141 ′ formed to extend along the circumference of the inner ring 110 from the outside of the inner ring 110 is shown.

The insert-type double wedge friction force induction clutch stopper (142 ′) has a trapezoidal cross section including two corresponding inclined surfaces (1421 ′) inclined to generate frictional force while being in close contact with the two slopes formed in the ring-shaped groove part (141 ′). It is made of a block, and is formed to be coupled by being partially inserted into the ring-shaped groove 141 ′.

Meanwhile, the two corresponding inclined surfaces 1421 ′ are preferably configured to be in line contact with the slopes 1411 ′ of the ring-shaped grooves 141 ′ made of a flat surface.

The cam-shaped protrusion 143 is formed in the remaining one of the inner ring 110 and the outer ring 120 in which the ring-shaped groove 141 ′ is not formed so as to face the ring-shaped groove 141 ′ inside the second groove 122. , When rotating in the first direction, the insert-type double wedge friction force inducing clutch stopper (142`) is pressed to come into close contact with the ring-shaped groove part (141`), and when rotating in the second direction, the insert-type double wedge friction force inducing clutch stopper (142`) is pressed. It consists of including the inclined surface (143a) to be released, is formed to be distributed along the circumference of the inner ring 110 or the outer ring 120.

Meanwhile, in FIGS. 8 and 9, the structure of the cam-shaped protrusion 143 which is formed integrally with the outer ring 120 and moves together with the outer ring 120 is shown.

The plurality of elastic members 144 are disposed between the insertion-type double wedge friction force induction clutch stopper 142 ′ and the cam-type protrusion 143 to elastically support the insertion-type double wedge friction force induction clutch stopper 142 ′.

When the outer ring 120 rotates, the inserted double wedge friction force inducing clutch stopper 142 ′ is pressed by the cam-shaped protrusion 143 when the outer ring 120 is rotated, and thus the insert type double wedge friction force inducing clutch stopper 142 ′ ) Is in close contact with the ring-shaped groove portion 141 ′, and the inner ring 110 and the outer ring 120 are bound and rotated together.

Hereinafter, while the clutch unit 140 of the double-layer one-way clutch bearing described with reference to FIGS. 2 to 6 functions, the movement of the outer ring 120 is transmitted to the inner ring 110 so that the inner ring 110 and the outer ring 120 It will be described a process in which only the outer ring 120 rotates together or because the movement of the outer ring 120 is not transmitted to the inner ring 110.

When the outer ring 120 is rotated in the first direction (D1) by an external force, a plurality of cam-shaped protrusions 143 formed in the outer ring 120 move in the first direction (D1) and the inserted double wedge friction force induction clutch The stopper 142 is pressed, whereby the two corresponding inclined surfaces 142b of the inserted double wedge friction force induction clutch stopper 142 are in close contact with the two slopes 141a of the ring-shaped protrusion 141.

Therefore, a friction force is formed between the two corresponding inclined surfaces 142b and the two inclined surfaces 141a, and due to this frictional force, the inner ring 110 and the outer ring 120 rotate in the first direction D1, so that the inner ring 110 ) And the associated shaft rotates.

As described above, in the process of rotating the outer ring 120 and the inner ring 110, the friction force generated between the inserted double wedge friction force induction clutch stopper 142 and the ring-shaped protrusion 141 can be interpreted as follows.

FIG. 10 is an exemplary view showing the relationship between the force generated between the cam-shaped protrusion and the inserted double wedge friction force inducing clutch stopper, and FIG. 11 is a relationship between the force formed between the inserted double wedge friction force inducing clutch stopper and the ring-shaped protrusion. The illustrated exemplary diagram is shown.

The frictional force T formed between the inserted double wedge friction force induction clutch stopper 142 and the cam-shaped protrusion 143 may be calculated by the following [Equation 1].

T = μP ---------- [Equation 1]

Here, μ is the coefficient of friction, and P is the force applied to the contact surface.

On the other hand, in [Equation 1], the size of P acts as a variable that determines the torque capacity.

On the other hand, the force that the elastic member 144 pushes the inserted double wedge friction force inducing clutch stopper 142 is Ps, and the inserted double wedge friction force inducing clutch stopper induced by the elastic member 144 to the inner ring 110 When the frictional force of 142 is called Ph, and the inclination angle of the cam-shaped protrusion 143 is θ, Ph can be calculated by the following [Equation 2].

Ph = Ps / 2sin(θ/2) ---------- [Equation 2]

On the other hand, if the force formed between the inserted double wedge friction force induction clutch stopper 142 and the ring-shaped protrusion 141 is Pc, and the angle of the slope 141a is β, Pc is expressed in [Equation 3] below. Can be calculated by

Pc = Ph / [2 sin(θ/2) × 2 sin(β/2)] ---------- [Equation 3]

The Pc causes reversal prevention of the clutch bearing, and the larger Pc, the greater the torque can be transmitted.

On the other hand, according to [Equation 3], when θ and β are each 6°, a large force of 91Ph can be obtained between the inserted double wedge friction force induction clutch stopper 142 and the ring-shaped protrusion 141 , It is possible to transmit large torque even with a small size one-way clutch bearing. And at this time, if the angles θ and β are increased, it is advantageous to reduce the amount of wear and increase the lifespan.

On the other hand, when the outer ring 120 rotates in the second direction (D2) by an external force, the cam-shaped protrusion 143 formed on the outer ring 120 moves in a direction away from the inserted double wedge friction force induction clutch stopper 142 Therefore, the pressurization of the inserted double wedge friction force induction clutch stopper 142 is released, and accordingly, rotational force is not transmitted to the inner ring 110 so that only the outer ring 120 rotates.

As described above, in the multilayer one-way clutch bearing according to the present invention, the bearing unit 130 and the clutch unit 140 configured between the inner ring 110 and the outer ring 120 are formed in a multilayer structure, so that the width is narrow. In addition to being able to easily implement a one-way clutch bearing, the inner ring 110 and the outer ring 120 are more improved by the double friction force induction structure implemented by the inserted double wedge friction force induction clutch stopper 142 and the ring-shaped protrusion 141. Since it is tightly bound, it is possible to transmit a large torque, and the clutch angles θ and β can be increased, which helps to extend the life.

Particularly, when a multilayer one-way clutch bearing having a narrow width according to the present invention is applied to the continuously variable transmission disclosed in Korean Patent Publication No. 10-1828249, the continuously variable transmission can be further downsized.

12 is a cross-sectional view of a double-layer one-way clutch bearing according to a second embodiment of the present invention.

The double-layer one-way clutch bearing according to the second embodiment of the present invention includes an inner ring 210, an outer ring 220, a bearing unit 230, and a clutch unit 240.

Meanwhile, the inner ring 210 is configured to include a first groove 212 and a first coupling portion 211, and the outer ring 220 includes a second groove 222 and a second coupling portion 221 The inner ring 210 and the outer ring 220 are configured in the same manner as the inner ring 110 and the outer ring 120 according to the first embodiment.

On the other hand, the bearing unit 230 according to the second embodiment is configured in the second groove 222, the clutch unit 240 is configured in the first groove 212, such a bearing unit 230 and the clutch unit ( 240) is different from that of the first embodiment.

That is, the bearing unit 230 according to the second embodiment may be configured by installing a known bearing or a plurality of balls in the second groove 222 formed in the outer ring 220.

The clutch part 240 is composed of a ring-shaped protrusion 241, an inserted double wedge friction force induction clutch stopper 242, a cam-shaped protrusion 243, and an elastic member 244.

The ring-shaped protrusion 241 is formed inside the first groove 212 so as to face the second coupling part 221 inserted into the first groove 212, and extends along the circumference of the inner ring 110, 1 protrudes in the inward direction of the groove 212 and is formed to have a trapezoidal cross section.

The inserted double wedge friction force induction clutch stopper 242 faces the two slopes 241a formed on the ring-shaped protrusion 241 and comes in close contact with the binding groove including two corresponding slopes 242b inclined to generate frictional force ( 2421 is formed in the form of a block formed on the bottom surface, and a plurality of the first grooves 212 are arranged to be distributed and coupled to the ring-shaped protrusion 241.

The cam-shaped protrusion 243 is formed on the outside of the second coupling part 221 so as to face the ring-shaped protrusion 241 located inside the first groove 212, the first direction (D1) of the outer ring 220 During rotation, the inserted double wedge friction force induction clutch stopper 242 is pressed to come in close contact with the ring-shaped protrusion 241, and when the outer ring 220 rotates in the second direction (D2), the inserted double wedge friction force induction clutch stopper 242 It consists of including the inclined surface (243a) for releasing the pressure, and is formed to be spaced apart from each other along the circumference of the outer ring 220.

The elastic member 244 is disposed between the inserted double wedge friction force inducing clutch stopper 242 and the cam-shaped protrusion 243 to elastically support the inserted double wedge friction force inducing clutch stopper 242.

The two-layer one-way clutch bearing according to the second embodiment configured as described above differs from the first embodiment in that the positions of the bearing unit 230 and the clutch unit 240 are reversed from each other, but the practical effect is the same. , A more detailed description will be omitted.

13 is a cross-sectional view of a double-layer one-way clutch bearing in which the clutch portion is vertically inverted according to the second embodiment.

As already described, the clutch unit 240 according to the second embodiment includes a ring-shaped protrusion 241, an inserted double wedge friction force induction clutch stopper 242, a cam-shaped protrusion 243, and an elastic member 244. .

Meanwhile, in the case of the clutch part 240 shown in FIG. 13, the ring-shaped protrusion 241 is formed on the outer ring 220 and is configured to behave together with the outer ring 220, and the cam-shaped protrusion 243 is the inner ring 210 ) Is formed in the inner ring 210 and is configured to behave with the inner ring 210, and is installed in the first groove 212 with the posture of the inserted double wedge friction force inducing clutch stopper 242 inverted up and down to prevent the movement of the inner ring 210 It is configured to transmit to the outer ring 220.

The configuration of the clutch unit 240 is different only from the clutch unit 140 described with reference to FIG. 7 and the installation position, and the detailed configuration may be the same, and thus a more detailed description thereof will be omitted.

14 is a cross-sectional view of a clutch portion having another structure according to the second embodiment.

The clutch part 240 according to the second embodiment may include a ring-shaped groove part 241 ′, an insert-type double wedge friction force inducing clutch stopper 242 ′, a cam-shaped protrusion 243, and an elastic member 244.

On the other hand, the ring-shaped groove portion 241 ′ is formed on the inner ring 210 or the outer ring 220 so as to rotate together with the inner ring 210 or the outer ring 220 inside the first groove 212, and has a predetermined depth. , It extends along the circumference of the inner ring 210 or the outer ring 220, and is formed to have a trapezoidal cross-section.

Meanwhile, in FIG. 14, a structure of a ring-shaped groove portion 241 ′ formed to extend along the circumference of the inner ring 210 is shown.

The inserted double wedge friction force induction clutch stopper 242 ′ includes two corresponding inclined surfaces 2421 ′ inclined to generate frictional force while being in close contact with the two slopes 2411 ′ formed in the ring-shaped groove 241 ′. It is made of a block having a trapezoidal cross section, and is formed to be coupled by being partially inserted into the ring-shaped groove 241 ′.

On the other hand, the two corresponding inclined surfaces 2421 ′ are preferably configured to be in line contact with the slopes 2411 ′ of the ring-shaped grooves 241 ′ made of a flat surface.

The cam-shaped protrusion 243 is formed in the remaining one of the inner ring 210 and the outer ring 220 in which the ring-shaped groove 241 ′ is not formed so as to face the ring-shaped groove 241 ′ inside the first groove 212. , When rotating in the first direction, the insert-type double wedge friction force inducing clutch stopper (242`) is pressed to come into close contact with the ring-shaped groove part 241`. It consists of including the inclined surface (243a) to be released, is formed to be distributed along the circumference of the inner ring 210 or the outer ring 220.

Meanwhile, FIG. 14 shows a structure of a cam-shaped protrusion 243 formed integrally with the outer ring 220 and moving together with the outer ring 220.

The plurality of elastic members 244 are disposed between the inserted double wedge friction force inducing clutch stopper 242 ′ and the cam-shaped protrusion 243 to elastically support the inserted double wedge friction force inducing clutch stopper 242 ′.

When the outer ring 220 is rotated, the inserted double wedge friction force inducing clutch stopper 242 ′ is pressed by the cam-shaped protrusion 243 when the outer ring 220 is rotated, and as a result, the inserted double wedge friction force inducing clutch stopper 242 ′ ) Is in close contact with the ring-shaped groove portion 241 ′ and the inner ring 210 and the outer ring 220 are bound and rotated together.

The present invention is not limited to the specific preferred embodiments described above, and any person having ordinary knowledge in the technical field to which the present invention pertains without departing from the gist of the present invention claimed in the claims can implement various modifications Of course, such changes are within the scope of the claims.

Claims

An inner ring formed in a circular ring shape so that the shaft can be fitted in the central portion, the first coupling portion formed around the outer circumference, and a first groove extending in the circumferential direction formed on the rear surface;

Consisting of a circular ring shape surrounding the outer circumference of the inner ring, a second coupling portion inserted into the first groove and coupled to the inner ring is formed around the inner circumference, and the first coupling portion is formed to extend in a circumferential direction on the front surface. An outer ring formed with a second groove to be inserted;

A bearing unit configured in the first groove to support rotation of the inner and outer rings; And

It is configured in the second groove, the inner ring and the outer ring rotate together when rotating in the first direction, and when rotating in the second direction opposite to the first direction, the clutch unit operates to rotate only the inner ring or the outer ring; Double-layer one-way clutch bearing made of.
The method according to claim 1,

The clutch part,

It is formed on the inner ring or outer ring so as to rotate with the inner ring or the outer ring in the inside of the second groove, protruding into the inside of the second groove, extending along the circumference of the inner ring or the outer ring, and formed to have a trapezoidal cross section. Ring-shaped protrusions;

A plurality of inserted double wedge friction force induction clutch stoppers formed in a block shape having a binding groove including two corresponding inclined surfaces inclined to generate frictional force while being in close contact with the two slopes formed on the ring-shaped protrusions;

The second groove is formed on the other of the inner ring and the outer ring so as to face the ring-shaped protrusion, but when rotating in the first direction, the inserted double wedge friction force induction clutch stopper is pressed to come into close contact with the ring-shaped protrusion. A plurality of cam-shaped protrusions formed to be distributed along the circumference of the inner ring or the outer ring, and including an inclined surface for releasing the pressure of the inserted double wedge friction force induction clutch stopper when rotating in the second direction; And

A double-layer one-way clutch bearing comprising: a plurality of elastic members disposed between the inserted double wedge friction force inducing clutch stopper and the cam-shaped protrusion to elastically support the inserted double wedge friction force inducing clutch stopper.
The method according to claim 2,

Two corresponding inclined surfaces formed on the inserted double wedge friction force induction clutch stopper are formed in a flat surface, and are configured to contact the slopes of the ring-shaped protrusion formed of a curved surface.
The method according to claim 1,

The clutch part,

A ring-shaped groove formed in the inner ring or the outer ring so as to rotate together with the inner ring or the outer ring in the second groove, having a predetermined depth, extending along the circumference of the inner ring or the outer ring, and having a trapezoidal cross section;

Consisting of a block having a trapezoidal cross section including two corresponding inclined surfaces inclined to generate friction while being in close contact with the two slopes formed in the ring-shaped groove, a plurality of insertion-type double wedge friction forces that are partially inserted and coupled to the ring-shaped groove Induction clutch stopper;

The second groove is formed in the remaining one of the inner and outer rings in which the ring-shaped groove is not formed so as to face the ring-shaped groove. When rotating in the first direction, the insert-type double wedge friction force induction clutch stopper is pressed to come into close contact with the ring-shaped groove. A plurality of cam-shaped protrusions formed to be distributed along the circumference of the inner ring or the outer ring, and including an inclined surface for releasing the pressure of the inserted double wedge friction force induction clutch stopper when rotating in two directions; And

A multilayer one-way clutch bearing comprising: a plurality of elastic members disposed between the insert-type double wedge friction force inducing clutch stopper and the cam-shaped protrusion to elastically support the insert-type double wedge friction force inducing clutch stopper.
An inner ring formed in a circular ring shape so that the shaft can be fitted in the central portion, the first coupling portion formed around the outer circumference, and a first groove extending in the circumferential direction formed on the rear surface;

Consisting of a circular ring shape surrounding the outer circumference of the inner ring, a second coupling portion inserted into the first groove and coupled to the inner ring is formed around the inner circumference, and the first coupling portion is formed to extend in a circumferential direction on the front surface. An outer ring formed with a second groove to be inserted;

A bearing unit configured in the second groove to support rotation of the inner and outer rings; And

It is configured in the first groove, the inner ring and the outer ring rotate together when rotating in the first direction, and when rotating in the second direction opposite to the first direction, the clutch unit operates to rotate only the inner ring or the outer ring; Double-layer one-way clutch bearing made of.
The method of claim 5,

The clutch part,

It is formed in the inner ring or outer ring so as to rotate with the inner ring or outer ring in the inside of the first groove, protruding into the inside of the first groove, extending along the circumference of the inner ring or the outer ring, and formed to have a trapezoidal cross section Ring-shaped protrusions;

A plurality of inserted double wedge friction force induction clutch stoppers formed in a block shape having a binding groove including two corresponding inclined surfaces inclined to generate frictional force while being in close contact with the two slopes formed on the ring-shaped protrusions;

The inner ring and the outer ring are formed on the other of the inner ring and the outer ring so as to face the ring-shaped protrusion inside the first groove, and when rotating in the first direction, the inserted double wedge friction force induction clutch stopper is pressed to come into close contact with the ring-shaped protrusion. A plurality of cam-shaped protrusions formed to be distributed along the circumference of the inner ring or the outer ring, and including an inclined surface for releasing the pressure of the inserted double wedge friction force induction clutch stopper when rotating in the second direction; And

A double-layer one-way clutch bearing comprising: a plurality of elastic members disposed between the inserted double wedge friction force inducing clutch stopper and the cam-shaped protrusion to elastically support the inserted double wedge friction force inducing clutch stopper.
The method of claim 6,

Two corresponding inclined surfaces formed on the inserted double wedge friction force inducing clutch stopper are formed in a flat surface, and are configured to be in line contact with the slopes of the ring-shaped protrusion formed of a curved surface.
The method of claim 5,

The clutch part

A ring-shaped groove formed in the inner ring or the outer ring so as to rotate together with the inner ring or the outer ring in the first groove, having a predetermined depth, extending along the circumference of the inner ring or the outer ring, and having a trapezoidal cross section;

Consisting of a block having a trapezoidal cross section including two corresponding inclined surfaces inclined to generate friction while being in close contact with the two slopes formed in the ring-shaped groove, a plurality of insertion-type double wedge friction forces that are partially inserted and coupled to the ring-shaped groove Induction clutch stopper;

The inner ring and the outer ring are formed in the other of the inner ring and the outer ring so as to face the ring-shaped groove in the inside of the first groove, but when rotating in the first direction, the insert-type double wedge friction force induction clutch stopper is pressed to closely contact the ring-shaped groove, A plurality of cam-shaped protrusions formed to be distributed along the circumference of the inner ring or the outer ring, and including an inclined surface for releasing the pressure of the inserted double wedge friction force induction clutch stopper when rotating in two directions; And

A multilayer one-way clutch bearing comprising: a plurality of elastic members disposed between the insert-type double wedge friction force inducing clutch stopper and the cam-shaped protrusion to elastically support the insert-type double wedge friction force inducing clutch stopper.