KR20210044413A - One-Way Clutch and Torque Converter Using the Same - Google Patents

Abstract

The present invention relates to a one-way clutch, which limits one-directional rotation of a reactor of a torque converter and allows a rotation in the other direction, and a torque converter applying the same. The one-way clutch (50) comprises: an outer race (51) and inner race (53), which are mutually rotated and bound in one direction and which are allowed to mutually rotate in the other direction; and a support member (55), which supports the outer race (51) and the inner race (53) in an axial direction. The inner race (53) includes: an axial-directional extension unit (5332) connected to a fixing end to rotate and to be bound and to be allowed to slide and move in an axial direction; and a radial-directional extension unit (535), which is outwardly extended in a radial direction from the axial-directional extension unit. The radial-directional extension unit (535) is integrated with the axial-directional extension unit (532). The axial-directional extension unit (532) faces the outer race (51). On the outer race (51) and on a surface where the axial-directional extension unit (532) and the outer race face each other, ratchet inclined surfaces are placed to be engaged with each other.

Description

One-Way Clutch and Torque Converter Using the Same}

The present invention relates to a one-way clutch, and more particularly, to a one-way clutch that restricts one-way rotation of a reactor of a torque converter and allows rotation in the other direction, and a torque converter to which the same.

The vehicle torque converter is a mechanical element that transmits the driving force (torque) transmitted from the engine to the transmission side. The torque converter is provided between the engine and the transmission. The torque converter multiplies the driving force of the engine through a fluid in the starting stage and transmits it to the transmission, and in the lock-up stage transmits the driving force of the engine to the transmission through direct mechanical connection.

In general, the torque converter includes a front cover, an impeller, a turbine, a reactor, a lock-up clutch, and a torsion damper. The front cover is made of a disk-shaped member, and is connected to the crankshaft of the engine and rotates by receiving driving force from the engine. The impeller is combined with the front cover and rotates together in response to the rotation of the front cover. The turbine is disposed at a position opposite to the impeller and receives the fluid flowing by the rotation of the impeller to receive the rotational force. The reactor is located between the impeller and the turbine and selectively diverts the flow of oil from the turbine and returns it to the impeller. The lock-up clutch directly connects or disconnects the front cover and the turbine by means of a piston. The piston operates by moving in the axial direction by the fluid. The torsion damper absorbs shock and vibration acting in the direction of rotation of the shaft in the direct connection path between the front cover and the turbine.

The reactor is allowed to rotate in only one direction by means of a one-way clutch. The one-way clutch is provided between the fixed end and the radially inner edge of the reactor. Conventionally, as such a one-way clutch, a sprag type or a roller type has been mainly applied.

However, the one-way clutch of the above-described type not only occupies a lot of space in the axial direction, but also the weight cannot be ignored. This inevitably caused an increase in the axial length of the vehicle torque converter and deteriorated fuel economy.

In order to solve the above-described problem, a one-way clutch having a toothed ratchet having an inclined surface and a jaw on at least one of the outer race and the inner race as in Patent Documents 1 and 2 has been proposed. The one-way clutch having such a structure is simpler than that of a one-way clutch such as a sprag type, so it does not take up much space in the axial direction, and is advantageous in cost reduction and weight reduction.

However, in the above-described one-way clutch structure, the axial position of the outer race in the transition region where the outer race starts to rotate relatively to the inner race cannot be controlled as desired. Accordingly, noise was frequently generated when the outer race collided with the inner race and the like.

And the one-way clutch of the ratchet structure described above can reduce the space occupied by the one-way clutch in the axial direction compared to the conventional sprag type or roller type structure, but due to the structure for axial movement of the outer race and the inner race However, there was a limit to reducing the space occupied by the one-way clutch in the axial direction.

KR 10-0216105 B1 JP, H05-045306, U

The present invention has been conceived to solve the above-described problems, and an object of the present invention is to provide a ratchet type one-way clutch capable of suppressing and minimizing the generation of noise in a transition region, and a torque converter to which the same is applied.

An object of the present invention is to provide a one-way clutch capable of minimizing the axial length of a torque converter by minimizing the axial length, and a torque converter to which the same is applied.

An object of the present invention is to provide a one-way clutch that has a simple structure and is easy to manufacture, which can reduce weight and reduce manufacturing cost, and a torque converter to which the same is applied.

The one-way clutch 50 of the present invention for solving the above-described problem is an outer race 51 and an inner race 53 that are mutually restricted in rotation in one direction and allowed to rotate in the other direction, and the outer race (51) and a support member (55) for supporting the inner race (53) in the axial direction.

The one-way clutch 50 is disposed between the reactor 40 and the fixed end of the torque converter 1, and does not allow one-way rotation of the reactor 40 with respect to the fixed end, but allows the other direction. .

The outer race 51 is connected to the reactor 40 and rotates integrally with the reactor 40.

The inner race 53 is connected to the fixed end so as to be rotationally restricted.

The inner race 53 is installed at the fixed end so as to be axially movable with respect to the fixed end.

A first locking part 511 is provided on the rear surface of the outer race 51 facing the inner race 53.

A second locking part 538 is provided on the front surface of the inner race 53 facing the outer race 51. The second locking part 538 is provided in an area corresponding to the area in which the first locking part 511 is provided.

The first locking part 511 may have a ratchet structure having an inclined surface that gradually increases a distance from the outer race 51 to the rear toward one direction in the circumferential direction. That is, the inclined surface of the first locking part 511 may be closer to the inner race 53 as it goes in one direction in the circumferential direction.

The second locking part 538 may have a ratchet structure having an inclined surface in which a distance from the inner race 53 toward the front direction gradually decreases as one direction in the circumferential direction increases. That is, the inclined surface of the second locking part 538 may be further away from the outer race 51 as it goes in one direction in the circumferential direction.

The inclined surface of the first locking part 511 and the inclined surface of the second locking part 538 may be parallel to each other.

The support member 55 includes a lever 551. The lever 551 may be made of metal so as to have rigidity that can behave like a rigid body.

The lever 551 includes a support portion 5514, an outer arm 5511 extending radially outward from the support portion 5514, and an inner arm extending radially inward from the support portion 5514 ( 5512).

The support part 5514 is supported by a support end. The outer arm 5511 supports the outer race 51 forward, and the inner arm 5512 supports the inner race 53 forward.

When the speed ratio (SR) of the turbine 30 to the impeller 20 is low, that is, in the initial stage of driving, the reactor 40 by the fluid returning from the turbine 30 to the impeller 20 ) Receives the force to rotate in one direction. At this time, by the shape of the reactor blade 411 of the reactor 40, the reactor 40 may be pressed backward in the axial direction. Accordingly, the outer race 51 rotating integrally with the reactor 40 may also be pressed backward.

The outer arm 5511 of the lever 551 receives the force that the outer race 51 is pressed backward, and the direction of the force received by the outer arm 5511 is switched to the front by the support part 5514 And transmitted to the inner arm 5512. Accordingly, the inner arm 5512 may press the inner race 53 forward. The action of the lever 551 causes the first locking part 511 of the outer race 51 and the second locking part 538 of the inner race 53 to come into close contact with each other.

When driving continues and the speed ratio of the turbine 30 to the impeller 20 increases and reaches the coupling point, the reactor 40 is driven by the fluid returning from the turbine 30 to the impeller 20. It receives the force to rotate in the direction.

In other words, the outer race 51 may receive a force backward by the reactor 40 until the speed ratio of the turbine 30 to the impeller 20 reaches the coupling point from 0. And, beyond the coupling point, the outer race 51 may receive a force forward by the reactor 40.

When a force is applied to the outer race 51 forward, the outer race 51 moves forward, and accordingly, the outer arm 5511 of the lever 551 also moves forward, and the inner arm 5512 is You can move backwards. Accordingly, the inner race 53 may be allowed to move backward.

At the beginning of driving, the fluid returning from the turbine 30 to the impeller 20 changes direction in the reactor 40 and exerts a force pushing the reactor 40 backward, and the outer race 51 exerts a force pushing backward. Receive. That is, when the reactor 40 receives a force to rotate in one direction by a fluid flowing from the turbine 30 toward the impeller 20, the outer race 51 is a force to move backward by the fluid. Receive. Therefore, even if the reaction force that the lever 551 pushes the outer race 51 forward is large, the reaction force is less than the force that the reactor 40 pushes backward by the fluid of the torus, so that the first locking portion of the outer race 51 It does not interfere with the engagement of 511 and the second locking portion 538 of the inner race 53.

As the speed ratio of the turbine 30 to the impeller 20 increases, the force of the torus fluid pushing the reactor 40 backward decreases. When the coupling point is reached, the fluid in the torus starts to rotate and does not push the reactor 40 backward. When the reactor 40 receives a force to rotate in the other direction by a fluid flowing from the turbine 30 toward the impeller 20, the outer race 51 is a force to move forward by the fluid Receive.

In this case, the outer race 51 and the inner race 53 must be immediately separated from each other so that noise due to friction or impact does not occur. That is, in the transition region, the reaction force of the lever 551 against the inner race 53 is small, and the reaction force of the lever 551 against the outer race 51 is large, so that the outer race can be surely separated from the inner race.

To this end, the first radial length (a) between the support part 5514 and the support point of the outer arm 5511 is a second radial length between the support part 5514 and the support point of the inner arm 5512 It may be equal to or less than (b).

Preferably, the ratio (a:b) of the first radial length (a) and the second radial length (b) may be 0.5:9.5 to 3:7.

More preferably, a ratio (a:b) of the first radial length (a) and the second radial length (b) may be in the range of 1:9 to 2:8.

The lever 551 may be provided with a plurality of predetermined intervals in the circumferential direction, and the plurality of levers 551 may be interconnected to the connection ring 553 in the circumferential direction.

The connection ring 553 may interconnect the support portions 5514 of the plurality of levers 551.

The lever 551 is provided with a rib 5513 in a radial direction, and bending stiffness of the lever 551 in the radial direction may be reinforced.

An obtuse angle j between the outer arm 5511 and the inner arm 5512 extending forward from the support portion 5514 may form an obtuse angle. Accordingly, it is possible to reduce the length of the one-way clutch 50 in the axial direction.

The inner race 53 may include a spline hub 533 connected to the fixed end and a radial extension 535 extending radially from the spline hub 533.

The spline hub 533 may slide in the axial direction with respect to the fixed end and may be connected to be rotationally restricted.

The radial extension 535 may be integrally formed with the spline hub 533.

The second locking part 538 may be provided on the front surface of the radially extending part 535, and the radially extending part 535 may be supported by the inner arm 5512. The inner arm 5512 may support the rear surface of the radially extending part 535 forward.

In addition, the present invention, the cover 10 receiving the rotational force of the engine, the impeller 20 rotating integrally with the cover 10, the turbine 30 facing the impeller 20, the impeller 20 and A torque converter 1 including a reactor 40 disposed between the turbines 30 and the one-way clutch 50 disposed between the reactor 40 and a fixed end may be provided.

The turbine 30 may be rotatably supported with respect to the outer race 51 through a first bearing B1. The first bearing B1 may be supported by the front surface of the outer race 51.

The impeller 20 may be rotatably supported with respect to the inner race 53 through a second bearing B2. A bearing supporter 57 is installed on an outer periphery of the spline hub 533 of the inner race 53, and the second bearing B2 may be supported by the bearing supporter 57. The support member 55 may be supported in the axial direction by the bearing supporter 57. The bearing supporter 57 may be disposed between the support member 55 and the second bearing B2 in an axial direction.

Alternatively, the impeller 20 may be rotatably supported with respect to the support member 55 through the second bearing B2. The second bearing B2 and the support member 55 may be supported in an axial direction. The second bearing B2 may be supported by the support part 5514 of the lever 551 of the support member 55.

According to the present invention, by adding a lever structure to the ratchet type one-way clutch, while further securing the fixing force of the one-way clutch in the torque multiplication region of the torque converter, the one-way clutch can be surely rotated freely in the coupling point and transition region. can do.

According to the present invention, by adding a lever structure to the ratchet type one-way clutch, noise generated from the one-way clutch in the transition region can be eliminated.

In addition, according to the present invention, compared to the sprag-type or roller-type one-way clutch, the volume occupied by the one-way clutch can be greatly reduced, and the weight and manufacturing cost can be reduced.

In addition to the above-described effects, specific effects of the present invention will be described together with explanation of specific matters for carrying out the present invention.

1 is a cross-sectional view of a torque converter to which a one-way clutch according to the present invention is applied.
FIG. 2 is a side cross-sectional view illustrating a reactor and a one-way clutch of the torque converter of FIG. 1.
3 and 4 are exploded perspective views of the reactor and the one-way clutch of FIG. 2 viewed from different directions.
FIG. 5 is a side view showing the state of the reactor and the one-way clutch when the speed ratio of the turbine to the impeller is 0 to between the coupling point, and FIG. 6 is a cross-sectional view of FIG. 5.
7 is a side view showing a state of a reactor and a one-way clutch after a coupling point, and FIG. 8 is a VIII-VIII cross-sectional view of FIG. 7.
9 is a diagram showing the celebratory weight according to the speed ratio.

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

The present invention is not limited to the embodiments disclosed below, but various modifications may be made and may be implemented in various different forms. However, this embodiment is provided to complete the disclosure of the present invention and to fully inform a person of ordinary skill in the scope of the invention. Therefore, the present invention is not limited to the embodiments disclosed below, and all changes and equivalents included in the technical spirit and scope of the present invention as well as substituting or adding to each other the constitution of one embodiment and the constitution of another embodiment. To include substitutes.

The accompanying drawings are only for making it easier to understand the embodiments disclosed in the present specification, and the technical idea disclosed in the present specification is not limited by the accompanying drawings, and all changes and equivalents included in the spirit and scope of the present invention It should be understood to include water or substitutes. In the drawings, components may be expressed exaggeratedly large or small in size or thickness in consideration of convenience of understanding, etc., but this will not limit the scope of the present invention to be interpreted.

The terms used in this specification are only used to describe specific embodiments or examples, and are not intended to limit the present invention. And expressions in the singular include plural expressions, unless the context clearly indicates otherwise. In the specification, terms such as to include or consist of are intended to designate the existence of features, numbers, steps, actions, components, parts, or combinations thereof described in the specification. In other words, in the specification, terms such as to include, to consist of. It is to be understood that it does not preclude the possibility of the presence or addition of one or more other features or numbers, steps, actions, components, parts, or combinations thereof.

Terms including ordinal numbers such as first and second may be used to describe various elements, but the elements are not limited by the terms. The above terms are used only for the purpose of distinguishing one component from another component.

When a component is referred to as being "connected" or "connected" to another component, it is understood that it may be directly connected or connected to the other component, but other components may exist in the middle. It should be. On the other hand, when a component is referred to as being "directly connected" or "directly connected" to another component, it should be understood that there is no other component in the middle.

When an element is referred to as being “above” or “being below” another element, it should be understood that not only is disposed directly above the other element, but also other elements may exist in the middle. .

Unless otherwise defined, all terms used herein including technical or scientific terms have the same meaning as commonly understood by one of ordinary skill in the art to which the present invention belongs. Terms as defined in a commonly used dictionary should be interpreted as having a meaning consistent with the meaning in the context of the related technology, and should not be interpreted as an ideal or excessively formal meaning unless explicitly defined in the present application. Does not.

For convenience of explanation, the direction along the longitudinal direction of the axis forming the center of rotation of the torque converter is referred to as the axial direction. The front-rear direction or the axial direction is a direction parallel to the rotation axis, and the front (front) is in any one direction (the first axis direction). ), for example, refers to the direction toward the engine, which is the power source, and the rear (rear) refers to the other direction (the second axis direction), such as the direction toward the transmission. Therefore, the front (front) means the surface that the surface faces forward, and the rear (rear surface) means the surface that the surface faces rearward.

The radial or radial direction means a direction closer to the center or a direction away from the center along a straight line passing through the center of the rotation axis on a plane perpendicular to the rotation axis. A direction away from the center in a radial direction is called a centrifugal direction, and a direction closer to the center is called a centripetal direction.

The circumferential direction or the circumferential direction means a direction surrounding the rotation axis. The outer circumference means the outer circumference, and the inner circumference means the inner circumference. Accordingly, the outer circumferential surface is a surface facing the rotation axis, and the inner circumferential surface is a surface facing the rotation axis.

The circumferential side means a surface whose normal line faces the circumferential direction.

[Torque Converter]

1, the torque converter 1 has an input side (I) and an output side (O). For example, the rotational driving force of the engine is input to the cover 10 from the front of the cover 10. The cover 10 includes a front cover 12 and a rear cover 15 defining a hollow space in which an internal fluid can be filled. The front cover 12 and the rear cover 15 are coupled to each other and rotate integrally.

The input of the torque converter 1 is transmitted to the impeller 20 through the front cover 12 and the rear cover 15. The impeller 20 is fixed to the inner surface of the rear cover 15, and the cover 10 and the impeller 20 rotate together about a predetermined axis. As the impeller 20 rotates, the fluid inside the impeller 20 has rotational kinetic energy of the impeller 20 and flows to the turbine 30 while receiving a force radially outward by the centrifugal force.

The turbine 30 is installed to face the impeller 20 in front of the impeller 20 and rotates around a predetermined axis by receiving the force of the fluid flowing from the impeller 20. The rotation centers of the impeller 20 and the turbine 30 are coaxial, and the impeller 20 and the turbine 30 face each other to form a torus. The turbine 30 is connected to the output side (O) from the inside in the radial direction to output a rotational force.

A reactor 40 is provided in a radially inner portion where the impeller 20 and the turbine 30 face each other. The fluid introduced into the turbine 30 flows radially inward and returns to the impeller 20 through the reactor 40. The reactor 40 includes an annular reactor body 41 and a plurality of reactor blades 411 extending radially outward from the reactor body 41. Radial outer ends of the plurality of reactor blades 411 may be interconnected in a ring shape.

A one-way clutch 50 is installed on the inner circumference of the reactor body 41, and the one-way clutch 50 is supported by a fixed end. The one-way clutch 50 prevents the reactor 40 from rotating in one direction with respect to the fixed end, and allows the reactor 40 to rotate in the other direction with respect to the fixed end.

The impeller 20 rotates in the other direction, and following this, the turbine 30 also rotates in the other direction.

When the turbine 30 follows and rotates the impeller 20 so that the speed ratio (SR) of the impeller 20 and the turbine 30 reaches 1:1, the front cover 12 moves to the lock-up clutch 60. It is directly connected to the output side (O). Then, the rotational force of the input side (I) is directly transmitted to the output side (O) through the lock-up clutch 60.

[One-way clutch]

The one-way clutch 50 includes an outer race 51 fixed to an inner circumferential surface of the reactor body 41 so as to rotate together with the reactor 40, and an inner race 53 that does not rotate with respect to the fixed end.

The outer race 51 may be installed on the inner circumference of the reactor body 41. According to the embodiment, the outer circumferential surface of the outer race 51 is press fit with the inner circumferential surface of the reactor body 41, so that the outer race 51 can behave integrally with the reactor body 41. have. However, the outer race 51 does not necessarily behave integrally with the reactor 40. For example, the outer race 51 and the reactor 40 are mutually restricted in rotation, but mutual axial movement may be allowed.

The outer race 51 has a disk shape in which a through hole 514 is formed in the center. A circular seating groove 513 that is larger than the through hole 514 is provided on the rear surface of the outer race 51. The seating groove 513 has a shape recessed from the rear of the outer race 51 to the front. A plurality of first locking portions 511 may be formed to extend in an arc shape along a circumferential direction on the bottom surface of the seating groove 513. In the embodiment, a structure in which the three first locking portions 511 are formed at 120 degree intervals is illustrated.

The first locking part 511 may have a shape of an inclined surface recessed from the rear surface of the outer race 51, more specifically, the bottom surface of the seating groove 513. The inclined surface of the first locking part 511 may have a shape in which the depth of depression from the rear surface gradually decreases as it goes in one direction in the circumferential direction.

A slit 512 may be formed in the outer race 51. The slit 512 may be disposed at the center of the first locking part 511 in the width direction and may have an arc-shaped opening extending along the circumferential direction. The slit 512 allows the flow of fluid generated in the inner space of the cover 10.

The inner race 53 is installed at the fixed end so as to be rotationally restricted with respect to the fixed end. The inner race 53 may be allowed to slide in the axial direction with respect to the fixed end.

The inner race 53 includes an axial extension portion 532 extending in the axial direction and a radial extension portion 535 extending radially outward from the axial extension portion 532.

The axial extension part 532 may be in the form of a pipe extending in the axial direction. In the inner periphery of the axial extension part 532, a spline hub 533 having a tooth shape fixed so as not to rotate with respect to the fixed end is provided. The spline hub 533 is rotationally constrained with respect to a fixed end, but allows a slide movement in the axial direction. A first outer circumferential surface 5321 having a predetermined diameter and a second outer circumferential surface 5322 having a larger diameter than the first outer circumferential surface 5321 are provided on the outer circumference of the axial extension portion 532. The second outer circumferential surface 5322 may be disposed in front of the first outer circumferential surface 5321, and a stepped due to a difference in diameter may be provided at a boundary between the first outer circumferential surface 5321 and the second outer circumferential surface 5322.

The second outer circumferential surface 5322 of the axial extension part 532 contacts the radially inner end of the inner arm 5512 of the lever 551 of the support member 55 to be described later, so that the support member 55 is attached to the shaft. Sort about. The first outer circumferential surface 5321 of the axial extension part 532 is in contact with the inner circumferential surface of the bearing supporter 57 to be described later to align the center of the bearing supporter 57 and support the bearing supporter 57. The stepped portions of the first outer circumferential surface 5321 and the second outer circumferential surface 5322 function as a stopper to limit the slide movement so that the bearing supporter 57 does not move further forward than the stepped step.

The radially extending portion 535 may have an annular flat plate shape extending radially outward from the front portion of the axially extending portion 532. The radial extension 535 may be integral with the axial extension 532. These may be integrally molded or may be individually assembled and then integrally assembled.

The front surface of the radial extension 535 faces the rear surface of the outer race 51. The radial extension 535 may regulate a range in which the outer race 51 moves backward. Similarly, the outer race 51 may regulate a range in which the inner race 53 moves forward.

The radial extension 535 faces the outer race 51 behind the outer race 51. At least a portion of the radially extending portion 535 may be accommodated in the seating groove 513 of the outer race 51. The outer circumferential surface of the radially extending part 535 and the inner circumferential surface of the seating groove 513 may face each other and support relative rotation therebetween. Accordingly, the center of the axis of the outer race 51 may be aligned.

On the front surface of the radially extending part 535, a second locking part 538 having a shape complementary to the first locking part 511 of the outer race 51 is provided. If the first locking part 511 is a ratchet inclined groove, the second locking part 538 may be a ratchet inclined protrusion having a shape complementary thereto. The inclined surface of the second locking part 538 has a shape in which the protruding height gradually decreases toward the other direction in the circumferential direction. Therefore, when the first locking part 511 is to rotate in the other direction with respect to the second locking part 538, the inclined surface of the first locking part 511 rises up the inclined surface of the second locking part 538. One locking portion 511 is allowed to rotate (see Fig. 8).

On the other hand, the other end portions of the first locking portion 511 and the second locking portion 538 in the circumferential direction form a stepped shape that meshes with each other. Therefore, when the first locking part 511 is to rotate in one direction with respect to the second locking part 538, the stepped shapes engage with each other to limit the rotation of the first locking part 511 (see FIG. 6).

5 and 6, the fluid returning from the turbine 30 to the impeller 20 at the initial driving stage (SR 0.00 ~ coupling point) is changed by the reactor 40 and transferred to the impeller 20. , In this process, the reactor 40 receives a force T1 to rotate in one direction. In addition, by the shape of the reactor blade 411, the reactor 40 receives force even in the axial direction rearward. However, since the stepped step of the first locking part 511 of the one-way clutch 50 is caught by the stepped step of the second locking part 538, the reactor 40 does not rotate.

See Figs. 7 and 8. When the driving proceeds to reach the coupling point, the fluid returning from the turbine 30 to the impeller 20 applies a force T2 to rotate the reactor 40 in the other direction. Accordingly, when the first locking part 511 rotates in the other direction, the inclined surface of the first locking part 511 rises along the inclined surface of the second locking part 538. Therefore, the outer race 51 and the inner race 53 move in the axial direction in a direction away from each other. By this principle, the reactor 40 is allowed to rotate in the other direction. In this way, when the reactor 40 rotates in the other direction, the outer race 51 and the inner race 53 of the one-way clutch 50 surely move in a direction away from each other, It is preferable that the two locking portions 538 do not mesh with each other.

When the coupling point is reached, the reactor 40 starts to receive force in the axial direction by the shape of the reactor blade 411. However, in a transition region where the reactor 40 starts to rotate in the other direction, the force that the reactor 40 receives in the axial direction may be small. Therefore, when the transition proceeds to reach the coupling point, the outer race 51 is unstable until the reactor blade 411 receives a positive force in the axial direction by the fluid returning from the turbine 30 to the impeller 20. There may be operating areas that do not reliably move forward in the axial direction. In this driving area, a phenomenon in which the outer race 51 collides with the inner race 53 may occur, which may cause noise.

[Support member]

The one-way clutch 50 further includes a support member 55 supporting the outer race 51 and the inner race 53 forward from the rear of the outer race 51 and the inner race 53.

The support member 55 includes a lever 551 having an outer arm 5511 and an inner arm 5512. The lever 551 includes a support portion 5514, an outer arm 5511 extending radially outward from the support portion 5514, and an inner arm 5512 extending radially inward from the support portion 5514 Includes. The support portion 5514 is supported from the rear by a predetermined support end. The support end may be the bearing supporter 57 shown in FIGS. 1 and 4 or the second bearing B2 shown in FIGS. 5 and 7.

The outer arm 5511 and the inner arm 5512 extend obliquely in front of the support part 5514. The front angle j of the outer arm 5511 and the inner arm 5512 may be an obtuse angle. Accordingly, while the operation of the lever 551 is smoothly performed, the volume occupied by the lever 551 in the front-rear direction can be reduced, thereby making the one-way clutch 50 compact as a whole.

The front end of the outer arm 5511 is in contact with the rear surface of the outer race 51, and the front end of the inner arm 5512 is in contact with the rear surface of the radial extension 535 of the inner race 53. A rib 5513 is formed in the lever 551 so that the outer arm 5511 and the inner arm 5512 can maintain a predetermined front angle j. Accordingly, the bending stiffness of the outer arm 5511 and the inner arm 5512 is greatly reinforced.

When the bending stiffness of the outer arm 5511 and the inner arm 5512 is greatly reinforced, the force of the outer race 51 pushing the outer arm 5511 backward is the inner arm 5512 through the lever 551. It is surely transmitted by pushing the radially extending portion 535 of the inner race 53 forward. Similarly, the force that the radial extension 535 of the inner race 53 pushes the inner arm 5512 backward is a force that the outer arm 5511 pushes the outer race 51 forward through the lever 551. Definitely delivered. In addition, when the force of the outer race 51 pushing the outer arm 5511 to the rear is released, the force that the inner arm 5512 pushed the inner race 53 forward through the lever 551 is also reliably released. And when the force of the inner race 53 pushing the inner arm 5512 to the rear is released, the force that the outer arm 5511 pushed the outer race 51 forward through the lever 551 is also reliably released.

A plurality of the levers 551 are provided at equal intervals along the circumferential direction. And the levers are interconnected by an annular connection ring 553. The connecting ring 553 connects the support portions 5514 of the lever 551, and accordingly, the plurality of levers 551 form one component, that is, a support member 55.

The operation of the one-way clutch 50 including the support member 55 will be described again.

5 and 6, the fluid returning from the turbine 30 to the impeller 20 at the initial driving stage (SR 0.00 ~ coupling point) is changed by the reactor 40 and transferred to the impeller 20. , In this process, the reactor 40 and the outer race 51 receive a force T1 to rotate in one direction, and also receive a force rearward in the axial direction. This force (Fouter) is transmitted as a force (Finner) pushing the inner race 53 forward through the lever 551. This acts in a direction in which the outer race 51 and the inner race 53 come into close contact with each other.

See Figs. 7 and 8. When the driving progresses and reaches the coupling point, the reactor 40 and the outer race 51 start to receive the force T2 to rotate in the other direction by the fluid returning from the turbine 30 to the impeller 20, It starts to receive a force forward in the axial direction as well, but the force received by the reactor 40 forward in the axial direction in the transition region is negligible.

Meanwhile, the fluid in the inner space of the cover 10 causes flow, and the fluid flows also in the radially inner region of the reactor body 41 in which the outer race 51 and the inner race 53 are disposed. In the transition region, the force received by the reactor 40 in the axial direction forward by the fluid returning from the turbine 30 to the impeller 20 is insignificant compared to the flow of this fluid, so the radial direction of the reactor body 41 The flow of fluid occurring in the inner region pushes the outer race 51 and the inner race 53 forward or backward. Part of the fluid flow may pass through the slit 512 of the outer race 51.

If the fluid flows forward in the radially inner region of the reactor body 41, both the outer race 51 and the inner race 53 receive a force pushed forward. By adjusting the areas of the radially extending portions 535 of the outer race 51 and the inner race 53, it is possible to adjust the force received by the outer race 51 and the inner race 53 by the fluid. That is, the area of the outer race 51 controls the area of the inner race 53, so that the tendency of the outer race 51 to move further forward than the inner race 53 may be strengthened by the flow of fluid. When the fluid flows backward in the radially inner region of the body 41, both the outer race 51 and the inner race 53 receive a force that is pushed backward. Then, both the outer race 51 and the inner race 53 push the outer arm 5511 and the inner arm 5512 of the lever 551 to the rear.

According to an embodiment, as shown in FIG. 4, the outer arm 5511 extending radially outward from the support portion 5514 is more radially inward from the support portion 5514 than the first radial length (a). The length (b) of the inner arm (5512) extending in the second radial direction may be larger (a<b). Then, according to the principle of the lever 551, the moment generated by the force that the inner race 53 pushes the inner arm 5512 backward based on the support part 5514 is, the outer race 51 is the outer arm. It is greater than the moment caused by the force pushing the (5511) back. Accordingly, the outer race 51 receives a force forward by the inner race 53 and the lever 551. That is, although both the outer race 51 and the inner race 53 are in contact with the lever 551, the inner race 53 moves backward while the outer race 51 moves forward. Accordingly, the first locking part 511 and the second locking part 538 may be separated from each other.

Of course, with the adjustment of the lengths (a, b) of the lever 551, or independently, by adjusting the area of the radial extension 535 of the outer race 51 and the inner race 53, It is also possible to adjust the force received by the outer race 51 and the inner race 53.

In the transition region of the reactor 40 starting from the coupling point of the impeller 20 and the turbine 30, in order to prevent the one-way clutch 50 from making noise, the outer race 51 and the inner It is desirable to ensure that the races 53 are separated from each other in the axial direction.

[Leverby a:b]

The force received by the reactor 40 by the fluid (F _blade ) and the force received by the one-way clutch 50 (F _shell ) are as follows.

F _blade = 0.5πρ(w _imp ² -w _tur ² )(r _c ⁴ -r _s ⁴ )×0.5 ... (Equation 1)

F _shell = 0.5πρ(w _imp ² -w _tur ² )(r _s ⁴ -r _o ⁴ ) ... (Equation 2)

Here, ρ is the density of the fluid, w _imp is the angular velocity of the impeller 20, w _tur is the angular velocity of the turbine 30, r _c is the outer radius _{of the reactor 40, r s} is the inner radius of the reactor 40, And r _o is the inner radius of the inner race 53. As shown in FIG. 9, the F _axial gradually decreases as the speed ratio increases, and then slightly recovers after reaching the lowest state near the speed ratio of 0.85.

_{The force (F blade} ) received by the reactor 40 by the fluid _{and the force (F shell} ) received by the one-way clutch 50 become _{F axial} . And the _{axial weight (F axial) is supported by the reaction force (F x} ) in the support portion 5514 of the lever 551 through the lever 551, the relationship between these is as follows.

F _blade + F _shell = F _axial = F _x ... (Equation 3)

On the other hand, when the radial distance between the outer arm 5511 and the inner arm 5512 is a and b, respectively, the axial weight is the outer arm 5511 and the inner arm 5512 by lever ratio (a:b). Each is properly distributed.

F _x = F _outer + F _inner ... (Equation 4)

_{In this case, the force F outer acting on the outer arm 5511 and the force F inner} acting on the inner arm 5512 according to the lever ratio a:b are as follows.

F _outer = (F _x ×b) / (a+b) ... (Equation 5)

F _inner = (F _x ×a) / (a+b) ... (Equation 6)

Using this relationship, the simulation analysis of the force of the outer arm and the inner arm according to the lever ratio is as follows.

Speed ratio
SR Congratulation
Fx(N) a: b = 1: 9 Outer arm Fo(N) Inner arm Fi(N) Fx-Fo(N) Fo-Fi(N) 0 203.1 193.1 21.5 10 171.6 0.1 201.4 191.1 21.2 10.3 169.9 0.2 196.2 187.5 20.8 8.7 166.7 0.3 186.3 177.7 19.7 8.6 158 0.4 174.7 163.2 18.1 11.5 145.1 0.5 157.3 147 18.6 10.3 128.4 0.6 144 134 17.1 10 116.9 0.7 128.4 119 15.4 9.4 103.6 0.75 117.4 107 14.3 10.4 92.7 0.8 104.3 98 12.8 6.3 85.2 0.85 87.1 77.2 10.8 9.9 66.4 0.9 103.5 93.3 12.7 10.2 80.6 0.92 109.1 99.2 13.2 9.9 86

Speed ratio
SR Congratulation
Fx(N) a: b = 2: 8 Outer arm Fo(N) Inner arm Fi(N) Fx-Fo(N) Fo-Fi(N) 0 203.1 173 30.3 30.1 142.7 0.1 201.4 171.1 30 30.3 141.1 0.2 196.2 168 29.1 28.2 138.9 0.3 186.3 159 28 27.3 131 0.4 174.7 150 23.5 24.7 126.5 0.5 157.3 136 21.1 21.3 114.9 0.6 144 126.1 19 17.9 107.1 0.7 128.4 113 16.1 15.4 96.9 0.75 117.4 105 13.3 12.4 91.7 0.8 104.3 94.1 10.5 10.2 83.6 0.85 87.1 80.2 8.3 6.9 71.9 0.9 103.5 93.5 10.3 10 83.2 0.92 109.1 98.1 11.5 11 86.6

Speed ratio
SR Congratulation
Fx(N) a: b = 3: 7 Outer arm Fo(N) Inner arm Fi(N) Fx-Fo(N) Fo-Fi(N) 0 203.1 156.8 35.1 46.3 121.7 0.1 201.4 156.1 34.9 45.3 121.2 0.2 196.2 151.2 33.4 45 117.8 0.3 186.3 151 30.9 35.3 120.1 0.4 174.7 142.3 28.2 32.4 114.1 0.5 157.3 132.3 24.6 25 107.7 0.6 144 108 22.2 36 85.8 0.7 128.4 96.6 19.2 31.8 77.4 0.75 117.4 88.7 17.4 28.7 71.3 0.8 104.3 79.3 15.2 25 64.1 0.85 87.1 68.8 12.9 18.3 55.9 0.9 103.5 77.5 14.4 26 63.1 0.92 109.1 81 15 28.1 66

Speed ratio
SR Congratulation
Fx(N) a: b = 4: 6 Outer arm Fo(N) Inner arm Fi(N) Fx-Fo(N) Fo-Fi(N) 0 203.1 132.1 55.2 71 76.9 0.1 201.4 130.5 54 70.9 76.5 0.2 196.2 128.9 52.1 67.3 76.8 0.3 186.3 122 50.4 64.3 71.6 0.4 174.7 115.1 49.5 59.6 65.6 0.5 157.3 105.3 47.7 52 57.6 0.6 144 96.6 38.5 47.4 58.1 0.7 128.4 88.1 30.3 40.3 57.8 0.75 117.4 80.6 28.8 36.8 51.8 0.8 104.3 73.5 22.6 30.8 50.9 0.85 87.1 63.1 19.8 24 43.3 0.9 103.5 72.2 21.1 31.3 51.1 0.92 109.1 75.6 23.3 33.5 52.3

Speed ratio
SR Congratulation
Fx(N) a: b = 5: 5 Outer arm Fo(N) Inner arm Fi(N) Fx-Fo(N) Fo-Fi(N) 0 203.1 111.2 80.4 91.9 30.8 0.1 201.4 110.5 80.2 90.9 30.3 0.2 196.2 107.9 79.2 88.3 28.7 0.3 186.3 103.2 75.4 83.1 27.8 0.4 174.7 97.3 70.3 77.4 27 0.5 157.3 88.1 61.2 69.2 26.9 0.6 144 83 57.6 61 25.4 0.7 128.4 75.3 51.1 53.1 24.2 0.75 117.4 69.1 49.3 48.3 19.8 0.8 104.3 63.3 45.3 41 18 0.85 87.1 54.2 41 32.9 13.2 0.9 103.5 61.3 44.2 42.2 17.1 0.92 109.1 65.5 46.6 43.6 18.9

In the transition region (SR 0.85 or more), the greater the force (Fo) acting on the outer arm compared to the force (Fi) acting on the inner arm, that is, the greater the value of Fo-Fi, the greater the lever 551 and the outer race 51 There is a greater tendency to spread the inner race 53 in a direction away from each other in the axial direction. Referring to the previous tables, the value of Fo-Fi peaks at a lever ratio of 2:8, so that the lever ratio becomes larger or smaller, and that tendency decreases. And the degree to which such a tendency decreases becomes smaller toward the side where the lever ratio becomes larger (1:9). Therefore, if the lever ratio is within the range of about 0.5:9.5 to 3:7, the tendency of the lever 551 to spread the outer race 51 and the inner race 53 can be sufficiently secured in the transition region.

On the other hand, the magnitude of the force Fi acting on the inner arm 5512 must be greater than the difference between the reaction force Fx acting on the lever 551 and the force Fo acting on the outer arm 5511, the lever 551 ) Surely receives the force backwards toward the support end, is supported by the support part 5514, and does not flow. If it is before reaching the transition region, the reactor 40 is surely received backward force by the fluid of the torus, and therefore, despite the result of the above numerical analysis, the lever 551 is expected to stably maintain its position. However, in the transition region, since the reactor 40 is not guaranteed to receive a force backward by the fluid of the torus, the result of the above numerical analysis may be important in predicting the behavior of the lever 551. From this point of view, when the lever ratio among the results of the numerical analysis is 1:9 and 2:8, the lever 551 can stably maintain its position. That is, if the lever ratio is within the range of 1:9 to 2:8, the lever 551 can stably maintain its position.

[Rotation support structure]

Referring to FIG. 1, the turbine 30 and the output side O may face the front surface of the outer race 51 with the first bearing B1 interposed therebetween. The turbine 30 is supported to be relatively rotatable with respect to the outer race 51 through a first bearing B1.

The first outer circumferential surface 5321 of the axial extension portion 532 of the inner race 53 may be inserted into the annular bearing supporter 57. The front surface of the bearing supporter 57 supports the support part 5514 of the support member 55 forward. In addition, the rear surface of the bearing supporter 57 supports the second bearing B2. The rear cover 15 and the impeller 20 are rotationally supported by the second bearing B2. In FIG. 1, a structure in which a bearing supporter 57 is installed on an axial extension portion 532 of an inner race 53 and interposed between the support member 55 and the rear cover 15 is disclosed. However, as shown in FIGS. 5 and 7, the second bearing B2 may be directly in contact with the support portion 5514 of the support member 55 while the bearing supporter 57 is omitted. If the bearing supporter 57 is omitted, the axial dimension of the torque converter 1 can be further reduced.

As described above with reference to the drawings illustrated for the present invention, the present invention is not limited by the embodiments and drawings disclosed in the present specification, and various It is obvious that transformations can be made. In addition, even if not explicitly described and described the effects of the configuration of the present invention while describing the embodiments of the present invention, it is natural that the predictable effects of the configuration should also be recognized.

1: torque converter
I: input side
O: output side
10: cover
12: front cover
15: rear cover
20: impeller
30: turbine
40: reactor
41: reactor body
411: Reactor Blade
50: one-way clutch
51: outer race
511: first locking portion (ratchet inclined surface groove)
512: slit
513: seating groove
514: through hole
53: inner race
532: axial extension
5321: 1st outer peripheral surface
5322: second outer peripheral surface
533: spline hub
535: radial extension
538: second locking portion (ratchet inclined surface protrusion)
55: support member
551: lever
5511: outer arm
a: length in the first radial direction of the outer arm
5512: inner arm
b: the length of the inner arm in the second radial direction
j: front angle of outer arm and inner arm
5513: rib
5514: base
553: connecting ring
57: bearing support
60: lock-up clutch
B1: first bearing
B2: second bearing

Claims (14)

As a one-way clutch 50 that is disposed between the reactor 40 and the fixed end of the torque converter 1, it does not allow one-way rotation of the reactor 40 with respect to the fixed end and allows the other direction of rotation,
The one-way clutch 50 is:
An outer race 51 connected to the reactor 40 and integrally rotating with the reactor 40;
An inner race 53 connected to be axially movable and rotationally constrained with respect to the fixed end;
A first locking part 511 provided on a rear surface of the outer race 51 facing the inner race 53;
A second locking part 538 provided on a front surface of the inner race 53 facing the outer race 51 and provided in an area corresponding to an area in which the first locking part 511 is provided; And
A support part 5514 supported by a support end, an outer arm 5511 extending radially outward from the support part 5514 and supporting the outer race 51 forward, and the support part 5514 A support member (55) including a lever (551) extending radially inward from and having an inner arm (5512) for supporting the inner race (53) forwardly (55); including, a one-way clutch.
The method according to claim 1,
The inner race 53 includes a spline hub 533 connected to the fixed end, and a radial extension part 535 extending radially from the spline hub 533,
The spline hub 533 is connected to be movable in the axial direction with respect to the fixed end,
The radial extension 535 is integrally formed with the spline hub 533, a one-way clutch.
The method according to claim 2,
The first locking portion 511 is provided on the front surface of the radially extending portion 535, a one-way clutch.
The method according to claim 2,
The inner arm (5512) is a one-way clutch for supporting the rear surface of the radially extending portion (535) forward.
The method according to claim 1,
The lever 551 is provided with a plurality of predetermined intervals in the circumferential direction,
A plurality of the levers (551) are interconnected to the connecting ring (553) in the circumferential direction, one-way clutch.
The method of claim 5,
The connecting ring 553 interconnects the support portions 5514 of the plurality of levers 551, one-way clutch.
The method according to claim 1,
The lever 551 is provided with a rib 5513 in the radial direction, and reinforces the bending rigidity of the lever 551 in the radial direction.
The method according to claim 1,
A one-way clutch, wherein a front angle j of the outer arm 5511 and the inner arm 5512 extending forward from the support portion 5514 forms an obtuse angle.
A cover 10 receiving the rotational force of the engine;
An impeller 20 rotating integrally with the cover 10;
A turbine 30 facing the impeller 20;
A reactor 40 disposed between the impeller 20 and the turbine 30; And
Torque converter comprising; the one-way clutch (50) of any one of claims 1 to 8, disposed between the reactor (40) and the fixed end.
The method of claim 9,
When the reactor 40 receives a force to rotate in one direction by a fluid flowing from the turbine 30 toward the impeller 20, the outer race 51 is forced to move backward by the fluid. under,
When the reactor 40 receives a force to rotate in the other direction by a fluid flowing from the turbine 30 toward the impeller 20, the outer race 51 is a force to move forward by the fluid Receiving, torque converter.
The method of claim 9,
The turbine 30 is rotatably supported with respect to the outer race 51 through a first bearing (B1),
Torque converter.
The method of claim 11,
The turbine (30) is rotatably supported with respect to the outer race (51) through a first bearing (B1), a torque converter.
The method of claim 11,
The impeller 20 is rotatably supported with respect to the support member 55 through a second bearing (B2).
The method of claim 11,
A bearing supporter 57 extending in the radial direction is installed on the outer periphery of the inner race 53,
The impeller 20 is rotatably supported with respect to the bearing supporter 57 through a second bearing B2,
The bearing supporter 57 is provided between the support member 55 and the second bearing B2.

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