KR20200083129A - Torque converter - Google Patents

Abstract

The present invention relates to a torque converter having an antiresonance damper, which can minimize a size in a radial direction and a size in an axial direction of the antiresonance damper to decrease the entire size of the torque converter, and can be compact. To this end, the torque converter comprises the antiresonance damper, wherein the antiresonance damper includes a pair of mass plates, a plurality of fastening means, and a plurality of damper springs.

Description

Torque converter {TORQUE CONVERTER}

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

As a fluid power transmission device that transmits 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 used.

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

Generally, the lock-up device has a piston and a damper mechanism.

The piston is disposed to be movable along the direction of the rotation axis, and when pressed to the front cover, engages with the front cover and rotates by receiving torque from the front cover through a friction force.

The damper mechanism serves to absorb and attenuate the torsion vibration transmitted to the front cover and transmit it to the output member, and an elastic body, preferably a coil spring, which elastically connects between the input member and the output member that rotates integrally with the piston. Includes.

The anti-resonance damper is a technique for reducing the resonance frequency to a practical rotational speed or lower to improve the vibration damping performance. The inertial body is installed on the torque transmission path of the lockup device, and is composed of an inertial mass and a coil spring.

In this regard, Korean Patent Publication No. 10-2017-0078607 discloses a semi-resonant damper in which an inertial mass is formed by connecting a coil spring to an outer end of an output member.

However, the anti-resonance damper disclosed in the above-mentioned prior art is disposed on the anti-resonance damper on the radially outer side with respect to the outer coil spring corresponding to the first damper mechanism as a torsion damper, thereby increasing the radial size of the torque converter, and the anti-resonance damper It is difficult to secure a sufficient size for the inertial mass due to the constraint on the space occupied by the inertial force of the inertial mass, and thus, the damping performance of the anti-resonant damper is insufficient.

Korean Patent Publication No. 10-2017-0078607

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

In order to solve the above-mentioned problems, the torque converter according to the present invention includes a first mass plate and a second mass plate in which a semi-resonant damper is disposed to face each other with a rotating plate provided on a power transmission path of the torque converter between them. A pair of mass plates, including mass plates; A plurality of fastening means extending through the rotating 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 plates and the rotating plate with respect to the rotational direction, and arranged in an arc shape, wherein the plurality of fastening means are respectively provided in the rotational direction of the rotating plate. Characterized in that disposed between the damper springs.

In addition, the plurality of damper springs have the same shape with each other, and each includes a plurality of coil springs arranged at equal intervals along the rotational direction, and the plurality of fastening means have the same shape with each other, and each of the plurality of coils It includes a plurality of rivets arranged at equal intervals between the springs.

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

Also, the radius of the first concentric circle becomes larger 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 rotating plate is greater than or equal to the outer diameters of the plurality of coil springs.

Further, 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 can reduce the overall size of the torque converter by minimizing the radial size and the axial size of the semi-resonant damper while having sufficient anti-resonance damping performance, and has a compactable effect.

1 is a cross-sectional view illustrating a rotation axis of a torque converter having a semi-resonant damper according to an embodiment of the present invention.
2 is a cross-sectional view in a direction perpendicular to the rotation axis of the torque converter shown in FIG. 1.
3 is a perspective view of an anti-resonance damper assembly according to an embodiment of the present invention.
4 is an exploded perspective view of FIG. 3.
5 is a front view of the driven plate shown in FIG. 4.
6A and 6B are cross-sectional views of FIG. 2 cut along different 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 a semi-resonant 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.

The present invention can be applied to various changes and can have various embodiments, and specific embodiments will be illustrated in the drawings and 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 and second may be used to describe various components, but the components may not be limited by the terms. The terms are only for the purpose of distinguishing one component from other components. For example, the first component may be referred to as a second component without departing from the scope of the present invention, and similarly, the second component may be referred to as a first component.

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

When a component is said to be "connected" to or "connected" to another component, it may be directly connected to or connected to the other component, but other components may exist in the middle. Can be understood. On the other hand, when a component is said to be "directly connected" or "directly connected" to another component, it can be understood that no other component exists in the middle.

The terms used in this application are only used to describe specific embodiments, and are not intended to limit the present invention. Singular expressions may include plural expressions unless the context clearly indicates otherwise.

In this application, terms such as “include” or “have” are intended to indicate that a feature, number, step, operation, component, part, or combination thereof described in the specification exists, and that one or more other features are present. It can be understood that the existence or addition possibilities of fields or numbers, steps, actions, components, parts or combinations thereof are not excluded in advance.

Unless otherwise defined, all terms used herein, including technical or scientific terms, may have the same meaning as commonly understood by a person skilled in the art to which the present invention pertains. Terms, such as those defined in a commonly used dictionary, may be interpreted as having meanings that are consistent with meanings in the context of related technologies, and are interpreted as ideal or excessively formal meanings unless explicitly defined in the present application. It may not be.

In addition, the following embodiments are provided to more fully explain to those having average knowledge in the art, and the shapes and sizes of elements in the drawings may be exaggerated for more clear explanation.

<Overall configuration of torque converter>

1 is a cross-sectional view of the torque converter 1 in the direction of the rotation axis (X-X), and FIG. 2 is a cross-sectional view in the direction perpendicular to the rotation axis (X-X) of the torque converter 1 shown in FIG. 1. An overall configuration of a torque converter 1 having a semi-resonant 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 the crankshaft of an engine not shown to the input shaft of a transmission not shown, the front cover 2 to which the rotational force of the crankshaft is input, and the front cover 2 The impeller 3 connected to the turbine 4 connected to the output hub 43, the stator 5 disposed between the impeller 3 and the turbine 4, the front cover 2 and the turbine 4 It comprises a lock-up device (6) disposed between.

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

The turbine 4 is arranged 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 rivets R2. Includes.

The output hub 43 is connected to an input shaft of a transmission (not shown) so as to transmit 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 as needed, and as shown in FIG. 1, between the front cover 2 and the turbine 4 Is placed in space.

The lockup device 6 is provided with a piston 61 and a drive plate 62 as input members, a drive plate 63 as an output member, and a drive plate 62 and a drive plate 63 as a damper mechanism. It has a first damper (D1) and a second damper (D2) for resiliently connecting to each, and is provided directly on the driven plate (63) is provided with a semi-resonant damper (DD) for improving the vibration damping performance.

piston

The piston 61 functions 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, and the inner surface of the front cover 2 When in close contact with the friction force is installed to directly receive the torque of the front cover (2).

To this end, the radially inner end of the piston 61 is movably supported by the output hub 43 in the direction of the rotation axis X-X, and is also supported relative to the output hub 43 to be rotatable. In addition, the friction member (61a) as a means for increasing the frictional force on one side of the piston 61 facing the inner surface of the front cover (2) and the torque of the front cover (2) can 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. The function of supporting the spring 65 is performed.

To act as an input member together with the piston 61, the drive plate 62 is securely fixed to the piston 61 in a plurality of places through rivets R1.

First elastic body -First coil spring (64)

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

Second elastic body -Second coil spring (65)

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

However, since the second coil spring 65 corresponds to a member that serves as an auxiliary damper for the first coil spring 64, it corresponds to a member that can be omitted, and the second coil spring 65 as the second damper D2 It will be understood that the configuration in which) is omitted is also included in the scope of the present invention.

For convenience, hereinafter, description will be made 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 the first coil spring 64 and the second coil spring from the piston 61 and the drive plate 62 as input members It acts as an output member provided to be able to rotate relative to the piston 61 and the drive plate 62 so that the torque transmitted through (65) can finally be output to the output hub (43). (DD) is installed to serve to support the anti-resonance damper (DD).

That is, in Figures 1 and 2, there is shown an embodiment in which the anti-resonant damper (DD) of the present invention is a driven plate 63 as a rotating plate is installed and supported. However, the present invention is not limited to this, and it will be considered that the configuration in which the semi-resonant damper DD is installed on another rotating element, for example, an intermediate member provided between the input member and the output member, falls 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 has 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) 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).

The outer body portion (63a), the first receiving the third coil spring (68) of the outer locking portion (63b), the torque is transmitted through the first coil spring 64, and a semi-resonant damper (DD) to be described later The spring hole 63g and the stopper hole 63h which limits 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 circumference of the ring-shaped outer body portion 63a in the direction of the rotation axis XX, and is formed in plural over the outer circumference of the body portion 63a. The ends of the first coil spring 64 are arranged between the ends, and the ends of the first coil spring 64 are supported in the rotational direction.

The first spring hole 63g corresponds to the number of the plurality of third coil springs 68 in the circumferential direction so as to accommodate the third coil spring 68 constituting the anti-resonance damper DD. It is formed in an arc shape, and both end surfaces of the first spring hole 63g are maintained in contact with the third coil spring 68, so that the intermediate locking portion 63d acting as an elastic force of the third coil spring 68 is applied. Acts as

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

The connecting portion 63f is a portion that integrally connects the outer body portion 63a and the inner body portion 63e in a bridge shape. Preferably, the plate-shaped plate-shaped member is press-worked to form an outer body portion of the plate-shaped member. It may be manufactured by partially removing the intermediate portion between 63a and the inner body portion 63e to form a plurality of windows 63w. Both sides of the connecting portion 63f formed through the window 63w, that is, the left and right inner surfaces in the rotational direction of the window 63w contact the second coil spring 65 described above in the torque transmission process to turn the second coil spring 65 on. It acts as an inner locking portion 63c to compress.

<Anti-resonant damper>

Inertial mass

As an inertial mass constituting the anti-resonant damper (DD), both sides of the outer body portion (63a) of the driven plate (63) to enable rotation relative to the driven plate (63) with the output member driven plate (63) therebetween And a first mass plate 66 and a second mass plate 67 disposed in close contact with each other.

4, the first mass plate 66 and the second mass plate 67 are formed of plate-like ring members similar to the shape of the outer body portion 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.

At this time, the first mass plate 66 and the second mass plate 67 are interlocked with each other through the plurality of rivets R3 described above to have the same effect as the single mass body, and operate integrally.

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

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

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

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, respectively, the second spring hole 66b and the third spring hole 67b With, 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 when damping. Acts as spring locking portions 66d and 67d.

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

6(a), the second spring hole 66b and the third spring hole 67b of the first mass plate 66 and the second mass plate 67 are driven plates 63, respectively. ), the radial width (L1) of the inner surface facing the) is formed larger than the radial width (L2) of the outer surface, the radial width (L2) of the outer surface is the outer diameter (L3) of the third coil spring 68 It can be formed smaller than.

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 processing of the first mass plate 66 and the second mass plate 67 by setting a separate additional member. Preventive structures can be implemented.

Third elastic body

The first mass body plate 66 and the second mass plate 67 and the output member as a damper spring resiliently connected to the rotational direction of the driven plate 63, the plurality of third coil springs 68, the driven plate 63 ) Is inserted into the first spring hole (63g), both ends of the first spring hole (63g) of the intermediate engaging portion (63d), the first mass plate 66 and the second mass plate 67 spring jam It is elastically deformable in the rotational direction by the portions 66d and 67d and is arranged at equal intervals a2 along the first concentric circles C1 as arc shapes.

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

Compact means

As described above, the present invention aims to provide a semi-resonant damper (DD) having a minimized radial size and an axial size.

First, as a means for minimizing the radial size of the semi-resonant damper DD, as shown in FIG. 5, disposed at equal intervals a1 between the 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.

More specifically, the radius (ds) of the first concentric circle where the radius (dr) of the second concentric circle (C2) connecting the centers of the plurality of rivets (R3) connects the central axis of the plurality of third coil springs (68) ).

That is, the radius (dr) of the second concentric circle (C2) connecting the center of the plurality of rivets (R3) is greater than the radius (ds) of the first concentric circle connecting the central axis of the plurality of third coil springs (68) It is possible to suppress the increase in the outer diameter of the driven plate 63 by setting it to be less or the like, and further, 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 illustrated in the same embodiment, but this is only exemplary, and the radius of the second concentric circle (C2) ( It will be appreciated that the embodiment in which dr) is set smaller than the radius (ds) of the first concentric circle falls within the scope of the present invention.

On the other hand, as a means for minimizing the axial size of the anti-resonant damper DD, as shown in FIG. 6, the minimum axial thickness t1 of the driven plate and the minimum axial thickness t2 of the first mass plate 66 ) And the total thickness (ta) of the semi-resonant damper assembly summing the axial minimum thickness (t3) of the second mass plate (67) is set not less than the outer diameter (L3) of the third coil spring (68).

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

Furthermore, the length (tr) of the plurality of rivets (R3) connecting them so that the first mass plate (66) and the second mass plate (67) rotate integrally is greater than the overall thickness (ta) of the anti-resonant damper assembly described above. It is set not to be large.

Similarly, the length of the plurality of rivets R3 (so that the plurality of rivets R3) do not protrude from the outer surfaces of the first mass plate 66 and the second mass plate 67 in the state where the anti-resonance damper DD is assembled By limiting tr), the axial size of the anti-resonant damper DD including a 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 torque converter>

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

With the front cover 2 and the impeller 3 rotating, power 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 through the output hub 43 to the input shaft of a transmission not shown.

When the rotational speed of the input shaft remains approximately constant, power transmission through the lock-up device 6 is started. In more detail, the piston 61 moves to the engine side according to a 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 is secondary As the second coil spring 65 is compressed in the rotational direction between the drive plate 62 and the inner locking portion 63c of the driven plate 63, the power attenuated by the torsion vibration is transmitted to the driven plate 63.

On the other hand, when power is transmitted to the driven plate 63, the middle engaging portion 63d of the driven plate 63 and the spring engaging portions 66d, 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 vibration having a phase opposite 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, finally, the vibration dampened power is transmitted to the turbine 4 and the output hub 43 via the driven plate 63.

As described above, it will be understood that the above-described technical configuration of the present invention can be implemented in other specific forms by those skilled in the art to which the present invention pertains without changing the technical spirit or essential features of the present invention.

Therefore, the embodiments described above are illustrative in all respects and should be understood as non-limiting, and the scope of the present invention is indicated by the following claims rather than the above detailed description, and the meaning and scope of the claims And it should be construed that all modifications or variations derived from the equivalent concept are 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 having an anti-resonant damper,
The anti-resonance damper,
A pair of mass plates including a first mass plate and a second mass plate disposed opposite to each other with a rotating plate provided on the power transmission path of the torque converter interposed therebetween;
A plurality of fastening means extending through the rotating plate and connecting the first mass plate and the second mass plate to rotate integrally; And
The pair of mass plate and the rotating plate is resiliently connected to the rotational direction, and includes a plurality of damper springs arranged in an arc shape,
Each of the fastening means is a torque converter, characterized in that disposed between the plurality of damper springs in the rotational direction of the rotating plate.
In claim 1,
The plurality of damper springs have the same shape with each other, and each includes a plurality of coil springs arranged at equal intervals along the rotational direction,
The plurality of fastening means has a same shape with each other, each of which comprises a plurality of rivets arranged at equal intervals between the plurality of coil springs Torque converter.
In claim 2,
The plurality of coil springs are arranged in an arc shape along a first concentric circle,
The plurality of rivets are torque converters, characterized in that arranged at equal intervals along the second concentric circle.
In claim 3,
The radius of the first concentric circle is larger than the radius of the second concentric circle Torque converter.
In claim 3,
The radius of the first concentric circle and the radius of the second concentric circle are the same, characterized in that the torque converter.
In claim 2,
The thickness of the assembly of the first mass plate, the second mass plate and the rotating plate is greater than or equal to the outer diameter of the plurality of coil springs Torque converter.
In claim 6,
Torque converter, characterized in that the length of the plurality of rivets is less than or equal to the thickness of the assembly.

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