KR102270686B1 - One-Way Clutch and Torque Converter Using the Same - Google Patents

Abstract

The present invention relates to a one-way clutch that restricts rotation of a reactor of a torque converter in one direction and allows rotation in the other direction, and a torque converter to which the same is applied. The one-way clutch 50 includes an outer race 51 and an inner race 53 that are mutually rotationally constrained in one direction and mutually rotate in the other direction, and the outer race 51 and the inner race 53 A support member 55 for supporting the in the axial direction is provided. The inner race 53 includes an axial extension 5332 connected to a fixed end to be rotationally constrained and to allow axial sliding movement, and a radial extension extending radially outward from the axial extension portion ( 535). The radial extension 535 is integral with the axial extension 532 . The axial extension 532 faces the outer race 51 . A surface of the outer race 51, the axial extension portion 532, and the outer race 51 facing each other is provided with a ratchet inclined surface 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 rotation of a reactor of a torque converter in one direction and allows rotation in the other direction, and a torque converter to which the same is applied.

A torque converter for a vehicle is a mechanical element that transmits a driving force (torque) transmitted from an engine to a transmission side. The torque converter is provided between the engine and the transmission. In the starting stage, the torque converter multiplies the driving force of the engine through fluid 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, a torque converter includes a front cover, an impeller, a turbine, a reactor, a lock-up clutch, and a torsional damper. The front cover is made of a disk-shaped member, is connected to the crankshaft of the engine, and rotates by receiving driving force from the engine. The impeller is coupled to the front cover and rotates together in response to the rotation of the front cover. The turbine is disposed at a position facing the impeller and receives a fluid flowing by rotation of the impeller to receive rotational force. A reactor is positioned between the impeller and the turbine to selectively divert the flow of oil from the turbine back to the impeller. The lock-up clutch directly connects or disconnects the front cover and the turbine by the piston. The piston is actuated by moving axially by the fluid. The torsional damper absorbs shock and vibration acting in the direction of rotation of the shaft in the path directly connected between the front cover and the turbine.

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

However, the above-mentioned type of one-way clutch not only takes up a lot of space in the axial direction, but also the weight cannot be neglected. This inevitably causes an increase in the axial length of the torque converter for a vehicle, and deteriorates fuel efficiency.

In order to solve the above-mentioned problems, as in Patent Documents 1 and 2, at least one of the outer race and the inner race, a one-way clutch in which a serrated ratchet having an inclined surface and a jaw is formed has been proposed. Since the one-way clutch having such a structure has a simpler structure than a one-way clutch such as a sprag type, it does not occupy a lot of space in the axial direction and is advantageous for cost reduction and weight reduction.

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

In addition, 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, , 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 devised to solve the above problems, and an object of the present invention is to provide a ratchet-type one-way clutch capable of suppressing and minimizing noise generation 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 costs, and a torque converter to which the same is applied.

One-way clutch 50 of the present invention for solving the above-described problems, an outer race 51 and an inner race 53 that are mutually rotationally constrained in one direction and mutually 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, so that rotation of the reactor 40 with respect to the fixed end in one direction is not allowed and rotation in the other direction is allowed. .

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 to be rotationally constrained.

The inner race 53 is installed at the fixed end to be movable in the axial direction 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 in which the distance from the outer race 51 to the rear increases in one circumferential direction. That is, the inclined surface of the first locking part 511 may be closer to the inner race 53 in one circumferential direction.

The second locking part 538 may have a ratchet structure having an inclined surface in which the distance from the inner race 53 to the front becomes smaller as it goes in one circumferential direction. That is, the inclined surface of the second locking part 538 may move away from the outer race 51 in one 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 capable of acting like a rigid body.

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

The support portion 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 a force that rotates in one direction. At this time, due to 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 that rotates 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 to the rear, and the direction of the force transmitted to the outer arm 5511 is switched to the front by the support part 5514 . and is 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 be in 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 vicinity, the reactor 40 is driven by the fluid returning from the turbine 30 to the impeller 20 direction of rotational force.

In other words, until the speed ratio of the turbine 30 to the impeller 20 reaches the coupling point from zero, the outer race 51 may be forced backward by the reactor 40 . And when the coupling point is exceeded, 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 can move backwards. Accordingly, the inner race 53 may be allowed to move backward.

In the initial stage of driving, the fluid returning from the turbine 30 to the impeller 20 changes direction in the reactor 40 and applies a force to push the reactor 40 rearward, and the outer race 51 provides a force pushing backward. receive That is, when the reactor 40 receives a force to rotate in one direction by the fluid flowing from the turbine 30 toward the impeller 20 , the outer race 51 is moved 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 smaller than the force pushing the reactor 40 backward by the fluid of the torus, so the first locking part of the outer race 51 The engagement between the 511 and the second locking part 538 of the inner race 53 is not prevented.

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

In this case, when the outer race 51 and the inner race 53 are immediately separated from each other, noise due to friction or impact does not occur. That is, in the transition region, when 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, the outer race can be reliably 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, a ratio (a:b) of the lengths 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 lengths of the first radial length (a) and the second radial length (b) may be 1:9 to 2:8.

A plurality of levers 551 may be provided at predetermined intervals in the circumferential direction, and the plurality of levers 551 may be interconnected to the connecting ring 553 in the circumferential direction.

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

The lever 551 may be provided with ribs 5513 in the radial direction to reinforce bending rigidity of the lever 551 in the radial direction.

The front angle j between the outer arm 5511 and the inner arm 5512 extending forward from the support part 5514 may form an obtuse angle. Accordingly, the axial length of the one-way clutch 50 can be reduced.

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

The spline hub 533 may be slidably movable in the axial direction with respect to the fixed end and may be connected to be rotationally constrained.

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

The second locking part 538 may be provided on the front surface of the radial extension part 535 , and the radial extension part 535 may be supported by the inner arm 5512 . The inner arm 5512 may support the rear surface of the radial extension part 535 in a forward direction.

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 It is possible to provide 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.

The turbine 30 may be rotatably supported with respect to the outer race 51 through the 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 may be installed on the 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 the 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 portion 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, the fixing force of the one-way clutch is further secured in the torque multiplication region of the torque converter, and the one-way clutch is reliably free of rotation 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 removed.

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, the specific effects of the present invention will be described together while describing specific details for carrying out the invention below.

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.
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 between 0 and the coupling point, and FIG. 6 is a cross-sectional view VI-VI of FIG. 5 .
7 is a side view showing the state of the reactor and the one-way clutch after the coupling point, and FIG. 8 is a cross-sectional view VIII-VIII of FIG. 7 .
9 is a view showing the axial load 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, and various changes may be made and may be implemented in various different forms. Only the present embodiment is provided to complete the disclosure of the present invention and to fully inform those 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 the configuration of any one embodiment and the configuration of other embodiments to each other or substitutes.

The accompanying drawings are only for easy understanding of the embodiments disclosed in the present specification, and the technical spirit 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, in consideration of the convenience of understanding, the size or thickness may be exaggeratedly large or small, but the protection scope of the present invention should not be construed as being limited thereto.

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

Terms including an ordinal number such as 1st, 2nd, etc. 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.

When a component is referred to as being “connected” or “connected” to another component, it is understood that the other component may be directly connected or connected to the other component, but other components may exist in between. it should be On the other hand, when it is mentioned that a certain element is "directly connected" or "directly connected" to another element, it should be understood that the other element does not exist in the middle.

When an element is referred to as being "on" or "below" another element, it should be understood that other elements may be present in the middle as well as disposed directly on the other element. .

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

For convenience of description, 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 any one direction (first axial direction). ), for example, means a direction toward the engine, which is a power source, and the rear (rear) means another direction (second axial direction), for example, a direction toward the transmission. Therefore, the front (front) means the surface on which the surface faces the front, and the rear (rear) means the surface on which the surface faces the rear.

The radial or radial direction means a direction approaching 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 referred to as a centrifugal direction, and a direction closer to the center is referred to as a centripetal direction.

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

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

[Torque Converter]

Referring to FIG. 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 the 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 into the turbine 30 while receiving a radially outward force by centrifugal force.

The turbine 30 is installed to face the impeller 20 in front of the impeller 20 , and receives the force of the fluid flowing from the impeller 20 to rotate about a predetermined axis. The center of rotation of the impeller 20 and the turbine 30 is 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 at 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 via the reactor 40 . The reactor 40 includes an annular reactor body 41 and a plurality of reactor blades 411 extending radially outwardly from the reactor body 41 . The radially 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 periphery of the reactor body 41, and the one-way clutch 50 is supported by a fixed end. The one-way clutch 50 prevents rotation of the reactor 40 with respect to the fixed end in one direction, and allows rotation of the reactor 40 with respect to the fixed end in the other direction.

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

When the speed ratio (SR) of the impeller 20 and the turbine 30 reaches 1:1 by rotating the turbine 30 following the impeller 20 , the front cover 12 is connected to the lock-up clutch 60 . It is directly connected to the output side (O) by 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 the 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-fitted with the inner circumferential surface of the reactor body 41 , so that the outer race 51 can move 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, while mutual rotation is constrained, 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 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 forward from the rear surface of the outer race 51 . A plurality of first locking parts 511 may be formed to extend in a circular arc shape along the circumferential direction on the bottom surface of the seating groove 513 . In the embodiment, a structure in which three first locking parts 511 are formed at intervals of 120 degrees is exemplified.

The first locking part 511 may be in the 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 the depression from the rear surface gradually decreases in one direction in the circumferential direction.

A slit 512 may be formed in the outer race 51 . The slit 512 may be disposed in the center of the width direction of the first locking part 511 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 constrained with respect to the fixed end. The inner race 53 may be allowed to slide in an 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 532 may be in the form of a pipe extending in the axial direction. A spline hub 533 having a tooth shape fixed so as not to be rotated with respect to the fixed end is provided on the inner periphery of the axial extension portion 532 . The spline hub 533 is rotationally constrained with respect to the fixed end, but allows sliding movement in the axial direction. A first outer peripheral surface 5321 having a predetermined diameter and a second outer peripheral surface 5322 having a larger diameter than the first outer peripheral surface 5321 are provided on the outer periphery 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 step 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 portion 532 is in contact with the radially inner end of the inner arm 5512 of the lever 551 of the support member 55, which will be described later, to attach the support member 55 to the shaft. sort about The first outer peripheral surface 5321 of the axial extension portion 532 contacts the inner peripheral 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 . Steps of the first outer circumferential surface 5321 and the second outer circumferential surface 5322 function as a stopper for limiting the slide movement so that the bearing supporter 57 does not move further forward than the step.

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

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

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

A second locking part 538 having a shape complementary to that of the first locking part 511 of the outer race 51 is provided on the front surface of the radially extending part 535 . If the first locking part 511 is a ratchet inclined surface groove, the second locking part 538 may be a ratchet inclined surface protrusion having a complementary shape. The inclined surface of the second locking part 538 has a shape in which the protrusion height gradually decreases toward the other direction in the circumferential direction. Therefore, when the first locking part 511 wants to rotate in the other direction with respect to the second locking part 538, the inclined surface of the first locking part 511 climbs up the inclined surface of the second locking part 538. 1 Rotation of the locking unit 511 is allowed (see FIG. 8).

On the other hand, the other ends of the first locking part 511 and the second locking part 538 in the circumferential direction form a stepped shape that engages 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 (refer to FIG. 6).

5 and 6, in the initial driving period (SR 0.00 ~ coupling point), the fluid returning from the turbine 30 to the impeller 20 is converted by the reactor 40 and transferred to the impeller 20 , in this process, the reactor 40 receives a force T1 that rotates in one direction. And, due to the shape of the reactor blade 411, the reactor 40 also receives a force backward in the axial direction. However, the step of the first locking part 511 of the one-way clutch 50 is caught by the step of the second locking part 538 , and the reactor 40 does not rotate.

See Figures 7 and 8. When driving proceeds to reach the coupling point, the fluid returning from the turbine 30 to the impeller 20 applies a force T2 that rotates 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 rides up the inclined surface of the second locking part 538 . Accordingly, 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. As such, when the reactor 40 rotates in the other direction, the outer race 51 and the inner race 53 of the one-way clutch 50 move in a direction away from each other, so that the first locking part 511 and the second It is preferable not to engage the two locking parts 538 with each other.

When the coupling point is reached, the reactor 40 begins to receive a force also forward in the axial direction due to the shape of the reactor blade 411 . However, in the 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 coupling point is reached and the transition proceeds, the outer race 51 is not 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 in the forward direction. There may be operating areas that do not move reliably forward in the axial direction. In such a 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 for supporting the outer race 51 and the inner race 53 in the front from the rear of the outer race 51 and the inner race 53 .

The support member 55 includes a lever 551 including an outer arm 5511 and an inner arm 5512 . The lever 551 includes a support part 5514 , an outer arm 5511 extending radially outward from the support part 5514 , and an inner arm 5512 extending radially inward from the support part 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 forward from the support part 5514 . The front angle j between the outer arm 5511 and the inner arm 5512 may be an obtuse angle. Accordingly, the one-way clutch 50 can be configured in a compact manner by reducing the volume occupied by the lever 551 in the front-rear direction while smoothly operating the lever 551 .

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 radially extending part 535 of the inner race 53 . A rib 5513 is formed on the lever 551 so that the outer arm 5511 and the inner arm 5512 can maintain a predetermined front angle j. Accordingly, the bending rigidity of the outer arm 5511 and the inner arm 5512 is greatly reinforced.

When the bending rigidity of the outer arm 5511 and the inner arm 5512 is greatly reinforced, the force that the outer race 51 pushes the outer arm 5511 rearward is the inner arm 5512 through the lever 551. The force that pushes the radial extension 535 of the inner race 53 forward is transmitted reliably. Similarly, the force that the radial extension portion 535 of the inner race 53 pushes the inner arm 5512 backward is the force that the outer arm 5511 pushes the outer race 51 forward through the lever 551. definitely conveyed. Also, when the force that the outer race 51 pushes the outer arm 5511 backward is released, the force that the inner arm 5512 pushes the inner race 53 forward through the lever 551 is also definitely released. And when the force that the inner race 53 pushes the inner arm 5512 backward is released, the force that the outer arm 5511 pushes the outer race 51 forward through the lever 551 is also definitely released.

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

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

5 and 6, in the initial driving period (SR 0.00 ~ coupling point), the fluid returning from the turbine 30 to the impeller 20 is converted 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 that rotates in one direction, and also receives a force Fouter in the axial direction rearward. This force (Fouter) is transmitted as a force (Finner) that pushes 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 are in close contact with each other.

See Figures 7 and 8. When the driving progresses and the coupling point is reached, the reactor 40 and the outer race 51 start to receive a force T2 that rotates in the other direction by the fluid returning from the turbine 30 to the impeller 20, Although the force (Fouter) is also received in the forward axial direction, the force that the reactor 40 receives in the axial direction in the transition region is insignificant.

On the other hand, the fluid in the inner space of the cover 10 causes a flow, and the fluid flow also occurs in the radially inner region of the reactor body 41 in which the outer race 51 and the inner race 53 are disposed. Since the force (Fouter) that the reactor 40 receives axially forward by the fluid returning from the turbine 30 to the impeller 20 in the transition region is insignificant compared to the flow of this fluid, 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. A portion of the flow of the fluid 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 pushing force. If the area of the radial extension portion 535 of the outer race 51 and the inner race 53 is adjusted, 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 more forward than the inner race 53 can be strengthened by the flow of the fluid. Reactor 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 pushing 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 rearward, respectively.

According to the embodiment, as shown in FIG. 4 , the first radial length (a) of the outer arm 5511 extending outward in the radial direction from the support part 5514 is radially inward from the support part 5514 . The second radial length (b) of the inner arm 5512 that extends to ? may be greater (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 with respect to the support part 5514 is the outer race 51 and the outer arm. It is greater than the moment caused by the force pushing (5511) backwards. 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, by adjusting the area of the radial extension portion 535 of the outer race 51 and the inner race 53 together with or independently of the adjustment of the lengths a and b of the lever 551, the fluid 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 noise from the one-way clutch 50, the outer race 51 and the inner after the coupling point It is desirable to ensure that the laces 53 are axially far apart from each other.

[Leverby a:b]

_{The force (F blade} ) received by the reactor 40 by the fluid _{and the force (F shell} ) received by the one-way clutch 50 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). _{The axial load} (F axial ) gradually decreases as the speed ratio increases as shown in FIG. 9 , and then slightly recovers after reaching the lowest state near the speed ratio 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 an _{axial load} (F axial ). And the _{axial load (F axial) is supported by the reaction force (F x} ) in the support portion 5514 of the lever 551 through the lever 551 , and their relationship is as follows.

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

On the other hand, when the radial distances between the outer arm 5511 and the inner arm 5512 are a and b, respectively, the axial load is the outer arm 5511 and the inner arm 5512 by the lever ratio (a:b). are distributed appropriately.

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

_{At this time, 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 and analysis values of the force of the outer arm and the inner arm according to the lever ratio are as follows.

speed ratio
SR celebrating
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 celebrating
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 celebrating
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 celebrating
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 celebrating
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 larger the value of Fo-Fi, the greater the lever 551 and the outer race 51 The tendency to spread the inner race 53 away from each other in the axial direction becomes greater. Referring to the above tables, the Fo-Fi value has a lever ratio of 2:8 as a peak, and the lever ratio becomes larger or smaller, and the 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 in the transition region can be sufficiently secured.

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 . ) is definitely received a force backward toward the support end, supported by the support portion 5514, and does not flow. If it is before reaching the transition region, the reactor 40 is surely forced backward by the fluid of the torus, so despite the results of the above numerical analysis, the lever 551 is expected to stably maintain its position. However, in the transition region, since it is not guaranteed that the reactor 40 receives a force backward by the torus fluid, the result of the above numerical analysis may be important for 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 may 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 relatively rotatably supported with respect to the outer race 51 through a first bearing B1.

The first outer peripheral 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. And 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. 1 shows a structure in which the bearing supporter 57 is installed in the axial extension portion 532 of the inner race 53 and is 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 directly contact the support part 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, the present invention has been described with reference to the illustrated drawings, but the present invention is not limited by the embodiments and drawings disclosed in the present specification. It is obvious that variations can be made. In addition, although the effects of the configuration of the present invention are not explicitly described and described while describing the embodiments of the present invention, it is natural that the effects predictable by 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 part (ratchet inclined surface groove)
512: slit
513: seating groove
514: through hole
53: inner race
532: axial extension
5321: first outer peripheral surface
5322: second outer circumferential surface
533: spline hub
535: radial extension
538: second locking part (ratchet inclined surface protrusion)
55: support member
551: lever
5511: outer arm
a: the length of the outer arm in the first radial direction
5512: inner arm
b: the second radial length of the inner arm
j: Anterior angle between the outer arm and the inner arm
5513: rib
5514: support
553: connecting ring
57: bearing supporter
60: lock-up clutch
B1: 1st bearing
B2: 2nd bearing

Claims (14)

As a one-way clutch (50) disposed between the reactor (40) and the fixed end of the torque converter (1), the one-way rotation of the reactor (40) with respect to the fixed end is not allowed and rotation in the other direction is allowed,
The one-way clutch 50 includes:
an outer race 51 connected to the reactor 40 and rotating integrally with the reactor 40;
An inner race 53 that is movable in an axial direction with respect to the fixed end and connected to be rotationally constrained;
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 the front surface of the inner race 53 facing the outer race 51 and provided in an area corresponding to the area where the first locking part 511 is provided; and
A support part 5514 supported rearward 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 ( A one-way clutch comprising; a support member (55) extending radially inward from 5514 and including a lever (551) having an inner arm (5512) for forwardly supporting the inner race (53).
The method according to claim 1,
The inner race 53 includes a spline hub 533 connected to the fixed end, and a radial extension portion 535 extending radially from the spline hub 533,
The spline hub (533) is axially movably connected with respect to the fixed end, the one-way clutch.
3. The method according to claim 2,
and the radial extension (535) is integral with the spline hub (533).
3. The method according to claim 2,
The first locking portion (511) is provided on the front surface of the radially extending portion (535), one-way clutch.
3. The method according to claim 2,
The inner arm 5512 supports the rear surface of the radial extension 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.
7. The method of claim 6,
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 ribs (5513) in the radial direction to reinforce the bending rigidity of the lever (551) in the radial direction.
The method according to claim 1,
The one-way clutch, wherein the front angle j between the outer arm 5511 and the inner arm 5512 extending forward from the support part 5514 forms an obtuse angle.
Cover 10 receiving the rotational force of the engine;
an impeller 20 which rotates 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
A torque converter comprising a; one-way clutch (50) of any one of claims 1 to 9, disposed between the reactor (40) and the fixed end.
11. The method of claim 10,
When the reactor 40 receives a force to rotate in one direction by the fluid flowing from the turbine 30 toward the impeller 20, the outer race 51 receives a force to move backward by the fluid. under,
When the reactor 40 receives a force to rotate in the other direction by the fluid flowing from the turbine 30 toward the impeller 20 , the outer race 51 is forced to move forward by the fluid Received, torque converter.
11. The method of claim 10,
The turbine (30) is rotatably supported with respect to the outer race (51) via a first bearing (B1), the torque converter.
11. The method of claim 10,
The impeller (20) is rotatably supported with respect to the support member (55) through a second bearing (B2), the torque converter.
11. The method of claim 10,
A bearing supporter 57 extending in a 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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