KR102290314B1 - Torque converter - Google Patents

Abstract

The present invention relates to a torque converter having an anti-resonant damper that can reduce the overall size of the torque converter by minimizing the radial size and the axial size of the anti-resonance damper, and can be made compact.

Description

Torque converter {TORQUE CONVERTER}

The present invention relates to a torque converter that is a fluid type power transmission device, and more particularly, to a torque converter having an anti-resonance damper capable of reducing the overall size of the torque converter by minimizing the size of the anti-resonance damper.

As a fluid power transmission device for transmitting power generated from an engine of a vehicle to a transmission, a torque converter having an anti-resonance damper and a lock-up device is widely applied.

The lockup device is a device for transmitting torque by mechanically connecting the front cover of the torque converter and the turbine, and is disposed in a space between the turbine and the front cover. Torque is transmitted directly from the front cover to the turbine without passing through the impeller by this lock-up device.

In general, a lock-up device has a piston and a damper mechanism.

The piston is arranged to be movable along the rotational axis direction, and when the front cover is pressed, the piston engages the front cover and receives torque from the front cover through frictional force to rotate.

The damper mechanism absorbs and attenuates the torsion vibration transmitted to the front cover and transmits it to the output member, and includes an elastic body, preferably a coil spring, that elastically connects the input member and the output member rotating integrally with the piston. include

The anti-resonance damper is a technology for improving vibration damping performance by lowering the resonant frequency to below the practical rotation speed, and is installed on the torque transmission path of the lock-up device with an inertial mass body, and is composed of an inertial mass and a coil spring.

In this regard, as a prior document, Korean Patent Laid-Open Publication No. 10-2017-0078607 discloses an anti-resonant damper in which an inertial mass is connected to an outer end of an output member by a coil spring.

However, the anti-resonance damper disclosed in the preceding document is a torsion damper disposed in the anti-resonance damper radially outward with respect to the outer coil spring corresponding to the first damper mechanism, so that the radial size of the torque converter is increased, and the anti-resonance damper There is a problem in that it is difficult to secure a sufficient size for the inertial mass due to the constraint on the space occupied by the inertial mass, and thus the inertial force of the inertial mass is insufficient, and accordingly, the damping performance of the anti-resonance damper is insufficient.

Korean Patent Publication No. 10-2017-0078607

The present invention has been devised to solve the above problems, and while having sufficient anti-resonance damping performance, it is possible to reduce the overall size of the torque converter by minimizing the radial size and axial size of the anti-resonance damper, and The object is to provide a torque converter with a possible anti-resonant damper.

In order to solve the above problems, a torque converter according to the present invention includes a lock-up device selectively connectable to rotate integrally with an engine output side, a damper connected to the lock-up device, an output hub connected to rotate integrally with a transmission input side, and an anti-resonance damper.
Here, the anti-resonance damper may include: a rotation plate connected to the damper at an outer peripheral end and connected to rotate integrally with the output hub at an inner peripheral end; a pair of mass plate including a first mass plate and a second mass plate disposed to face each other with the rotation plate interposed therebetween; a plurality of fastening means extending through the rotation plate and connecting the first mass plate and the second mass plate to rotate integrally; and a plurality of damper springs elastically connecting the pair of mass plate and the rotation plate with respect to a rotation direction and disposed in an arc shape, wherein the plurality of fastening means includes the plurality of damper springs in the rotation direction of the rotation plate, respectively. It is characterized in that it is disposed between the damper springs of the.

In addition, the plurality of damper springs have the same shape and include a plurality of coil springs disposed at equal intervals along the rotation direction, respectively, and the plurality of fastening means have the same shape as each other, and each of the plurality of coils has the same shape. A plurality of rivets are equally spaced between the springs.

In addition, the plurality of coil springs are arranged in an arc shape along a first concentric circle, and the plurality of rivets are arranged at equal intervals along a second concentric circle.

Also, the radius of the first concentric circle is greater than the radius of the second concentric circle.

In addition, the radius of the first concentric circle and the radius of the second concentric circle are the same.

In addition, the thickness of the assembly of the first mass plate, the second mass plate, and the rotation plate is greater than or equal to the outer diameter of the plurality of coil springs.

In addition, the length of the plurality of rivets is less than or equal to the thickness of the assembly.

The torque converter according to the present invention has the effect of reducing the overall size of the torque converter by minimizing the radial size and the axial size of the anti-resonance damper while having sufficient anti-resonance damping performance, and enables compactness.

1 is a cross-sectional view in the direction of rotation axis of a torque converter having an anti-resonance damper according to an embodiment of the present invention.
FIG. 2 is a cross-sectional view in a direction perpendicular to a rotation axis of the torque converter shown in FIG. 1 .
3 is a perspective view of an anti-resonant damper assembly according to an embodiment of the present invention.
4 is an exploded perspective view of FIG. 3 .
FIG. 5 is a front view of the driven plate shown in FIG. 4 .
6A and 6B are cross-sectional views of FIG. 2 taken at different positions along lines La and Lb perpendicular to the rotation axis XX.
7 is a schematic diagram for explaining a torque transmission process of a torque converter having an anti-resonance damper according to an embodiment of the present invention.

Hereinafter, a torque converter according to the present invention will be described in detail with reference to the accompanying drawings.

Since the present invention can have various changes and can have various embodiments, specific embodiments are illustrated in the drawings and will be described in detail in the detailed description. This is not intended to limit the present invention to specific embodiments, and should be construed to include all modifications, equivalents, and substitutes included in the spirit and scope of the present invention.

In describing the present invention, terms such as first, second, etc. may be used to describe various components, but the components may not be limited by the terms. The above terms are only for the purpose of distinguishing one component from another. For example, without departing from the scope of the present invention, a first component may be referred to as a second component, and similarly, a second component may also be referred to as a first component.

The term “and/or” may include a combination of a plurality of related listed items or any of a plurality of related listed items.

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

The terms used in the present application are only used to describe specific embodiments, and are not intended to limit the present invention. The singular expression may include the plural expression unless the context clearly dictates otherwise.

In the present application, terms such as "comprise" or "have" are intended to designate that a feature, number, step, operation, component, part, or combination thereof described in the specification exists, and one or more other features It may be understood that the presence or addition of numbers, steps, operations, components, parts, or combinations thereof is not precluded in advance.

Unless defined otherwise, all terms used herein, including technical or scientific terms, may 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 a commonly used dictionary may be interpreted as having a meaning consistent with the meaning in the context of the related art, and unless explicitly defined in the present application, it is interpreted in an ideal or excessively formal meaning. it may not be

In addition, the following embodiments are provided to more completely explain to those with average knowledge in the art, and the shapes and sizes of elements in the drawings may be exaggerated for clearer description.

<Overall composition of torque converter>

1 is a cross-sectional view in the direction of rotation axis (X-X) of the torque converter 1, and FIG. 2 is a cross-sectional view in a direction perpendicular to the axis of rotation (X-X) of the torque converter 1 shown in FIG. 1 . An overall configuration of the torque converter 1 having the anti-resonance damper DD according to an embodiment of the present invention will be described with reference to FIGS. 1 and 2 .

The torque converter 1 is a device for transmitting power from a crankshaft of an engine (not shown) to an input shaft of a transmission (not shown). an impeller 3 connected to, a turbine 4 connected to an output hub 43, a stator 5 disposed between the impeller 3 and the turbine 4, a front cover 2 and a turbine 4 and a lock-up device 6 disposed therebetween.

An impeller 3 is fixed to the front cover 2 , and a fluid chamber is formed therein by the front cover 2 and the impeller 3 .

The turbine 4 is disposed so as to face the impeller 3 inside the fluid chamber. The turbine 4 includes a turbine shell 41 , a plurality of turbine blades 42 fixed to the turbine shell 41 , and an output hub 43 fixed to the turbine shell 41 by a rivet R2 . include

The output hub 43 is connected to an input shaft of a transmission (not shown) so as to transmit the rotational force to the outside.

The stator 5 is a mechanism for regulating the flow of hydraulic oil from the turbine 4 to the impeller 3 , and is disposed between the impeller 3 and the turbine 4 .

<Configuration of lock-up device>

The lock-up device 6 serves to mechanically connect the front cover 2 and the turbine 4 if necessary, and as shown in FIG. 1 , is provided between the front cover 2 and the turbine 4 . placed in space.

The lock-up device 6 has a piston 61 and a drive plate 62 as input members, a driven plate 63 as an output member, and a drive plate 62 and a driven plate 63 as a damper mechanism. and a first damper (D1) and a second damper (D2) for elastically connecting to each other, and an anti-resonance damper (DD) installed directly on the driven plate 63 to improve vibration damping performance.

piston

The piston 61 serves to switch the torque transmission path between the front cover 2 and the turbine 4 , and is pressed toward the front cover 2 by the action of hydraulic pressure to the inner surface of the front cover 2 . It is installed so that the torque of the front cover 2 is directly transmitted through frictional force when in close contact with it.

To this end, the radially inner end of the piston 61 is movably supported by the output hub 43 in the rotational axis X-X direction, and is supported rotatably relative to the output hub 43 . In addition, a friction member 61a is provided on one side of the piston 61 facing the inner surface of the front cover 2 as a means for increasing friction and allowing the torque of the front cover 2 to be effectively transmitted to the piston 61 . is installed

drive plate

The drive plate 62 is fixed to the aforementioned piston 61 and functions as an input member together with the piston 61, and at the same time, the first coil spring 64 and the second coil corresponding to the damper mechanisms D1 and D2. It functions to support the spring (65).

In order to act as an input member together with the piston 61, the drive plate 62 is firmly fixed to the piston 61 at a plurality of places via a rivet R1.

first elastic body - first coil spring (64)

The first coil spring 64 as a first elastic body constituting the first damper D1 has a function of absorbing torsion vibration by elastically connecting the drive plate 62 and a driven plate 63 to be described later in the rotational direction. It is arranged in an arc shape to perform

second elastic body - second coil spring (65)

The second coil spring 65 as a second elastic body constituting the second damper D2 elastically connects the drive plate 62 and the driven plate 63 to be described later in the rotational direction to absorb the torsion vibration and torque. It is arranged in an arc shape to perform the function of transmitting the above-mentioned first coil spring 64, rather than the inner surface of the piston 61 from the inner side in the radial direction, and the inner holding protrusion 62e of the drive plate 62. It is supported in the rotational axis (XX) direction and the radial direction by this.

However, the second coil spring 65 corresponds to a member that can be omitted because it corresponds to a member serving as an auxiliary damper with respect to the first coil spring 64, and the second coil spring 65 as the second damper D2. ) will be considered to be naturally included in the scope of the present invention.

For convenience, the following description will be based on an embodiment in which the second coil spring 65 as the second damper D2 is included.

driven plate

The driven plate 63 is connected to the turbine 4 to rotate integrally with the turbine 4 , and a first coil spring 64 and a second coil spring from a piston 61 as an input member and a drive plate 62 . Acts as an output member rotatably provided with respect to the piston 61 and the drive plate 62 so as to finally output the torque transmitted through 65 to the output hub 43, an anti-resonance damper to be described later (DD) is installed and serves to support the anti-resonance damper (DD).

That is, in FIGS. 1 and 2 , an embodiment in which the anti-resonance damper DD of the present invention is installed and supported as a rotating plate is shown as a driven plate 63 . However, the present invention is not limited thereto, and a configuration in which the anti-resonant damper DD is installed on another rotating element, for example, an intermediate member provided between the input member and the output member, will naturally fall within the scope of the present invention. For convenience, the following description will be made based on an embodiment in which the anti-resonance damper DD is installed on the driven plate 63 corresponding to the output member.

The detailed configuration of the driven plate 63 is shown in FIGS. 3 to 5 .

3 to 5 , the driven plate 63 includes a ring-shaped outer body portion 63a, a ring-shaped inner body portion 63e, and an outer body portion 63a and an inner body portion 63e. It has a connecting portion 63f for connecting in the form of a bridge, and the inner body portion 63e is simultaneously fixed to the output hub 43 and the turbine shell 41 through a plurality of rivets R2.

In the outer body portion 63a, an outer locking portion 63b to which torque is transmitted through the first coil spring 64, and a third coil spring 68 of an anti-resonance damper DD, which will be described later, are accommodated in the first A spring hole 63g and a stopper hole 63h limiting the rotation range of the mass of the anti-resonance damper DD are formed.

The outer locking portion 63b is a portion extending by bending a portion of the outer periphery of the ring-shaped outer body portion 63a in the direction of the rotation axis XX, and is formed in plurality over the outer periphery of the body portion 63a. It is disposed between the ends of the first coil springs 64 and supports the ends of the first coil springs 64 in the rotational direction.

The first spring hole 63g has a plurality of pieces corresponding to the number of the plurality of third coil springs 68 in the circumferential direction to accommodate the third coil spring 68 constituting the anti-resonance damper DD. Formed in an arc shape, both end surfaces of the first spring hole (63g) are maintained in contact with the third coil spring (68), the intermediate engaging portion (63d) to which the elastic force of the third coil spring (68) acts. acts as

The stopper hole 63h is a portion through which the rivet R3 integrally connecting the first mass plate 66 and the second mass plate 67 of the anti-resonance damper DD, which will be described later, extends through. It is formed between the first spring holes 63g and extends to a predetermined length in the rotational direction. The relative rotation amount of the driven plate 63 with respect to the first mass plate 66 and the second mass plate 67, which will be described later, is limited by the length of the stopper hole 63h in the rotation direction.

The connecting portion 63f is a part that integrally connects the outer body portion 63a and the inner body portion 63e in a bridge shape, and preferably, the outer body portion of the plate-shaped member by pressing the disk-shaped plate-shaped member or the like. A plurality of windows 63w may be formed by partially removing an intermediate portion between the 63a and the inner body portion 63e. Both side surfaces of the connection portion 63f formed through the window 63w, that is, the left and right inner surfaces of the window 63w in the rotational direction, contact the second coil spring 65 described above during the torque transmission process to obtain the second coil spring 65. It acts as an inner locking part 63c for compression.

<Anti-resonance damper>

inertial mass

As an inertial mass constituting the anti-resonance damper DD, both sides of the outer body portion 63a of the driven plate 63 are rotatable relative to the driven plate 63 with the driven plate 63 interposed therebetween. and a first mass plate 66 and a second mass plate 67 disposed to face each other in close contact with each other.

As shown in FIG. 4 , the first mass plate 66 and the second mass plate 67 are formed as a plate-shaped ring member similar to the shape of the outer body part 63a of the driven plate 63 , respectively. It is disposed in close contact with both sides of the outer body portion 63a of the driven plate 63 .

In this case, the first mass plate 66 and the second mass plate 67 are coupled to each other through the above-described plurality of rivets R3 so as to have the same effect as a single mass, and thus operate as one body.

To this end, the body portion 66a of the first mass plate 66 and the body portion 67a of the second mass plate 67 have rivet holes 66c and 67c through which the plurality of rivets R3 respectively extend. It is formed at equal intervals (a1) along the rotational direction.

As described above, since the plurality of rivets R3 each extend through the stopper hole 63h of the driven plate 63, the first mass plate 66 due to the interaction between the rivet R3 and the stopper hole 63h. ) and the relative rotation amount of the driven plate 63 with respect to the second mass plate 67 is limited by the length of the stopper hole 63h in the rotation direction.

In addition, the first mass plate 66 and the second mass plate 67 are configured to be directly connected to the third coil spring 68 which is a damper spring without an intermediate connecting member, unlike in the related art.

To this end, the first mass plate 66 and the second mass plate 67 cooperate with each other to receive the third coil spring 68 by a second spring hole 66b and a third spring hole 67b, respectively. and both end surfaces of each of the second spring hole 66b and the third spring hole 67b contact both ends of the third coil spring 68 to press both ends of the third coil spring 68 during a damping action. to act as spring engaging portions 66d and 67d.

The second spring hole 66b and the third spring hole 67b are formed to have substantially the same rotational length as the first spring hole 63g of the driven plate 63 described above.

In addition, as shown in FIG. 6A , the second spring hole 66b and the third spring hole 67b of the first mass plate 66 and the second mass plate 67 are respectively connected to the driven plate 63 . ), the radial width L1 of the inner surface is formed to be larger than the radial width L2 of the outer surface, and the radial width L2 of the outer surface is the outer diameter L3 of the third coil spring 68 It can be formed smaller.

In this way, the radial width L1 of the inner surface of the second spring hole 66b and the third spring hole 67b of the first mass plate 66 and the second mass plate 67 and the radial direction of the outer surface By setting the relationship of the width L2, the axial support and release of the third coil spring 68 is provided without additional members or without additional processing for the first mass plate 66 and the second mass plate 67. A preventive structure may be implemented.

third elastic body

A plurality of third coil springs 68 as damper springs elastically connecting the first and second mass plate 66 and the second mass plate 67 with respect to the rotation direction of the driven plate 63 serving as the output member, the driven plate 63 ), both ends of which are inserted into the first spring hole 63g, the intermediate engaging portion 63d of the first spring hole 63g, and the spring engaging portion of the first mass plate 66 and the second mass plate 67 It is supported so as to be elastically deformable in the rotational direction by the portions 66d and 67d, and is arranged in an arc shape along the first concentric circles C1 at equal intervals a2, respectively.

Accordingly, when the driven plate 63, the first mass plate 66, and the second mass plate 67 rotate relative to each other, the third coil spring 68 is compressed in the rotational direction, and thus the driven plate 63 is A vibration having a phase opposite to that of the input vibration is applied to the driven plate 63 , so that the torque in a state in which the vibration is attenuated is finally transmitted to the output hub 43 .

means of compaction

As described above, it is an object of the present invention to provide an anti-resonant damper DD having a minimized radial size and an axial size.

First, as a means for minimizing the radial size of the anti-resonance damper DD, as shown in FIG. 5 , it is disposed at equal intervals a1 between a plurality of third coil springs 68 arranged in an arc shape. The radial position of the plurality of rivets R3 is limited so as not to deviate from the radial position of the third coil springs 68 .

In more detail, the radius dr of the second concentric circle C2 connecting the centers of the plurality of rivets R3 is the radius ds of the first concentric circle connecting the central axes of the plurality of third coil springs 68 . ) is set not greater than

That is, the radius dr of the second concentric circle C2 connecting the centers of the plurality of rivets R3 is greater than the radius ds of the first concentric circle connecting the central axes of the plurality of third coil springs 68 . It is possible to suppress an increase in the outer diameter of the driven plate 63 by setting it to be less than or equal to this, and furthermore, the outer diameter size of the anti-resonance damper DD can be kept to a minimum.

In FIG. 5 , the radius dr of the second concentric circle C2 and the radius ds of the first concentric circle are shown in an embodiment in which the same is set, but this is merely exemplary, and the radius of the second concentric circle C2 ( An embodiment in which dr) is set smaller than the radius ds of the first concentric circle will naturally fall within the scope of the present invention.

Meanwhile, as a means for minimizing the axial size of the anti-resonance damper DD, as shown in FIG. 6 , the axial minimum thickness t1 of the driven plate and the axial minimum thickness t2 of the first mass plate 66 are shown. ) and the total thickness ta of the anti-resonance damper assembly including the minimum thickness t3 in the axial direction of the second mass plate 67 is set not to be smaller than the outer diameter L3 of the third coil spring 68 .

That is, by configuring the third coil spring 68 not to protrude from the outer surfaces of the first mass plate 66 and the second mass plate 67 in the state in which the anti-resonance damper DD is assembled, the third coil spring ( 68), the axial size of the anti-resonance damper DD can be kept to a minimum.

Furthermore, the length tr of the plurality of rivets R3 connecting the first mass plate 66 and the second mass plate 67 to rotate integrally is greater than the overall thickness ta of the aforementioned anti-resonance damper assembly. set not to be large.

Similarly, in the state where the anti-resonance damper DD is assembled, the length of the plurality of rivets R3 ( tr), the axial size of the anti-resonance damper DD including the plurality of rivets R3 is kept to a minimum, and interference with other components constituting the torque converter 1 can also be easily avoided. there will be

<Operation of the torque converter>

Hereinafter, an operation of the torque converter 1 having the anti-resonance damper DD according to an embodiment of the present invention will be described with reference to FIG. 7 .

In a state where the front cover 2 and the impeller 3 are rotating, hydraulic oil flows from the impeller 3 to the turbine 4 and power is transmitted from the impeller 3 to the turbine 4 through the hydraulic oil. The power transmitted to the turbine 4 is transmitted to an input shaft of a transmission, not shown, through an output hub 43 .

When the rotational speed of the input shaft remains approximately constant, power transmission through the lock-up device 6 is initiated. In more detail, the piston 61 moves toward the engine according to the change in hydraulic pressure, and the friction member 61a of the piston 61 is pressed toward the inner surface of the front cover 2 .

As a result, the piston 61 rotates integrally with the front cover 2 , and power is transmitted from the front cover 2 to the drive plate 62 through the piston 61 .

When power is transmitted to the drive plate 62, the first coil spring 64 is primarily compressed in the rotational direction between the drive plate 62 and the outer engaging portion 63b of the driven plate 63, and secondary As the second coil spring 65 is compressed in the rotational direction between the drive plate 62 and the inner locking part 63c of the driven plate 63 , the torsion vibration is attenuated power is transmitted to the driven plate 63 .

Meanwhile, when power is transmitted to the driven plate 63 , the intermediate engaging portion 63d of the driven plate 63 and the spring engaging portions 66d and 67d of the first mass plate 66 and the second mass plate 67 . ), the third coil spring 68 is compressed in the rotational direction, and the vibration having the opposite phase to the vibration input to the driven plate 63 is transmitted to the driven plate 63 through the third coil spring 68 . .

As a result, the finally vibration-damped power is transmitted to the turbine 4 and the output hub 43 via the driven plate 63 .

As such, those skilled in the art to which the present invention pertains will understand that the above-described technical configuration of the present invention may be implemented in other specific forms without changing the technical spirit or essential characteristics of the present invention.

Therefore, the embodiments described above are to be understood as illustrative and not restrictive in all respects, and the scope of the present invention is indicated by the following claims rather than the foregoing detailed description, and the meaning and scope of the claims And all changes or modifications derived from the equivalent concept should be construed as being included in the scope of the present invention.

Torque Converter(1) Front Cover(2)
Impeller(3) Turbine(4)
Stator(5) Lockup Device(6)
Piston(61) Drive Plate(62)
Driven Plate (63) First Coil Spring (64)
second coil spring 65 first mass plate 66
second mass plate 67 third coil spring 68

Claims (7)

A torque converter comprising: a lock-up device selectively connectable to rotate integrally with an engine output side; a damper connected to the lock-up device; an output hub connected to rotate integrally with a transmission input side to transmit rotational force; and an anti-resonance damper,
The anti-resonance damper is
a rotating plate connected to the damper at an outer circumferential end and connected to rotate integrally with the output hub at an inner circumferential end;
a pair of mass plate including a first mass plate and a second mass plate disposed to face each other so as to be rotatable relative to the rotation plate with the rotation plate interposed therebetween;
a plurality of fastening means extending through the rotation plate and connecting the first mass plate and the second mass plate to rotate integrally; and
a plurality of damper springs elastically connecting the pair of mass plate and the rotation plate in a rotation direction and arranged in an arc shape;
including,
The plurality of fastening means are respectively disposed between the plurality of damper springs in the rotational direction of the rotation plate.
In claim 1,
The plurality of damper springs have the same shape as each other, and each includes a plurality of coil springs disposed at equal intervals along the rotation direction,
The plurality of fastening means has the same shape as each other, and each of the plurality of coil springs comprises a plurality of rivets arranged at equal intervals between the coil springs.
In claim 2,
The plurality of coil springs are arranged in an arc shape along a first concentric circle,
The plurality of rivets are arranged at equal intervals along a second concentric circle.
In claim 3,
The torque converter, characterized in that the radius of the first concentric circle is larger than the radius of the second concentric circle.
In claim 3,
A torque converter, characterized in that the radius of the first concentric circle and the radius of the second concentric circle are the same.
In claim 2,
The thickness of the assembly of the first mass plate, the second mass plate, and the rotation plate is greater than or equal to an outer diameter of the plurality of coil springs.
In claim 6,
The length of the plurality of rivets is less than or equal to the thickness of the assembly torque converter.

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