Clutch device for transmission

Abstract

The present invention provides a clutch device for a transmission, which may include: a first body and a second body, the second body being coaxially mounted to the first body; a friction element being mounted between the first body and the second body; a friction piston being configured to axially press the friction element by using hydraulic pressure; a retractable mechanism including a bite clutch, the bite clutch being configured to limit rotation between the first body and the second body, the retractable mechanism repeatedly engaging and disengaging the bite clutch by repeatedly applying pressure in its axial direction; and an operating piston being configured to provide pressure to the retractable mechanism in the axial direction of the retractable mechanism.

Description

Technical Field

[0001] The present invention relates to a structure of a power control device used in a transmission. Background Art

[0002] An automotive automatic transmission, for example, may use a number of power control devices that are hydraulically operated to engage a desired gear.

[0003] That is, various gear positions may be shifted into by engaging or disengaging the rotation elements of the planetary gear sets using a plurality of power control devices such as clutches or brakes.

[0004] A "clutch" is a device that connects or disconnects two rotating members that rotate separately, and a "brake" is a device that switches a state in which one rotating element is stopped and another state in which the other rotating element is rotating when one of the two rotating elements is a fixed part such as a transmission case.

[0005] That is, except for whether all target parts are rotating members, clutches and brakes are almost the same in actual configuration.

[0006] The following mechanism is used in a hydraulic automatic transmission of the related art: both the clutch and the brake include a plate pack constructed by alternately stacking a plurality of plates and discs between two parts, and the friction between the plates and the discs is changed by pressing the plate pack using hydraulic pressure, thereby engaging or disengaging the two parts.

[0007] As described above, the power control device including the concepts of clutch and brake herein is referred to as a "clutch device" in a combined component including a brake to distinguish it from a single clutch.

[0008] As described above, the clutch device used in the related art transmission requires a plurality of discs and plates for the disc pack, and the greater the torque that the disc pack must transmit or receive, the more discs and plates may be used.

[0009] However, as described above, when the number of plates and disks of the disk pack increases, resistance generated therebetween also increases, which becomes a major factor in consuming power even when the clutch device is not operated, resulting in reduced power transmission efficiency of the transmission.

[0010] The above description of the prior art of the present application is only used to help understand the background technology of the present invention and should not be understood as being included in the prior art known to those skilled in the art.

[0011] The information disclosed in the background section of the present invention is only intended to deepen the understanding of the general background technology of the present invention and should not be regarded as an admission or any form of suggestion that the information constitutes the prior art already known to those skilled in the art. Summary of the Invention

[0012] Various aspects of the present invention are directed to providing a clutch device configured for a transmission, which is configured to improve the power transmission efficiency of the transmission by transmitting or receiving sufficient torque and significantly reducing the resistance in the clutch device used in the transmission, thereby contributing to improving the fuel efficiency of the vehicle.

[0013] In order to achieve the above-mentioned objectives, the present invention is configured to be used in a clutch device for a transmission, including: a first body and a second body, the second body being coaxially mounted to the first body; a friction element being mounted between the first body and the second body; a friction piston being configured to axially press the friction element by using hydraulic pressure; a retractable mechanism including a bite clutch, the bite clutch being configured to limit the rotation between the first body and the second body, the retractable mechanism repeatedly engaging and disengaging the bite clutch by repeatedly applying pressure in its axial direction; and an operating piston being configured to provide pressure to the retractable mechanism in the axial direction of the retractable mechanism.

[0014] The retractable mechanism may include: a first bite gear formed on the outer surface of the first body; a bite shell whose rotation and axial movement are restricted by the second body; a bite ring which is slidably mounted in the bite shell and has the second bite gear on its inner surface to form the bite clutch by engaging with the first bite gear; a return spring which is mounted to apply an elastic force to the bite ring in a direction opposite to the direction of the pressure applied by the operating piston; and a switching ring which is slidably mounted in the bite shell and uses the pressure applied by the operating piston to move the bite ring so that when the bite ring moves out of the bite shell, the bite ring rotates in a direction relative to the bite shell.

[0015] The first snap-in gear of the first body and the second snap-in gear of the snap-in ring are formed so that surfaces axially facing each other are inclined surfaces parallel to each other.

[0016] A bite ring protrusion may be formed on the outer surface of the bite ring, and the bite ring protrusion is inserted into the bite ring shell and guided to slide axially; and a retaining groove and a release groove may be alternately formed on the inner surface of the bite shell along its circumference, the retaining groove accommodating the bite ring protrusion to keep the second bite gear of the bite ring engaged with the first bite gear of the first body, and the release groove guides the inserted bite ring protrusion to move freely axially.

[0017] The first partition wall between the retaining groove and the releasing groove of the snap-in housing and the snap-in ring protrusion may be formed such that surfaces axially facing each other are inclined surfaces parallel to each other.

[0018] The switching ring may have a switching portion having an inclined surface parallel to the inclined surface of the bite ring protrusion; and the inclined surface of the switching portion may extend from a position corresponding to a middle portion of the release groove to a position corresponding to a middle portion of the first partition wall.

[0019] A snap-in holding gear configured to mesh with the first snap-in gear when the second snap-in gear of the snap-in ring is separated from the first snap-in gear may be integrally formed on an inner surface of the switching ring.

[0020] A bite retaining ring having the bite retaining gear can be further installed between the switching ring and the operating piston. The bite retaining ring can be slidably inserted into the bite housing and is configured to engage with the first bite gear when the second bite gear of the bite ring is separated from the first bite gear.

[0021] The operating piston may be coaxially mounted on the outside of the friction piston, and the friction piston and the operating piston may be mounted to receive hydraulic pressure of the same pressure chamber together.

[0022] The operating piston may be coaxially installed outside the friction piston, and a second partition wall may be installed between the friction piston and the operating piston, so that hydraulic pressure supplied to the friction piston and hydraulic pressure supplied to the operating piston are configured to be independently controlled.

[0023] The friction element may be a disk pack formed by alternately arranging a predetermined number of disks and plates.

[0024] The friction element may be a conical friction clutch having a conical friction surface.

[0025] In addition, in order to achieve the purpose of the present invention, a clutch device configured for a transmission includes: a first body and a second body, the second body being coaxially mounted to the outside of the first body; a friction element, which is configured to generate friction between the first body and the second body; a friction piston, which is configured to increase the friction of the friction piston by applying pressure to the friction element; and a limiting retainer, which is configured to limit the relative rotation of the first body and the second body after the pressure applied to the friction element by the friction piston is removed.

[0026] The limiting retainer may include: a telescopic mechanism including a bite clutch, the bite clutch being configured to limit the relative rotation of the first body and the second body, the telescopic mechanism repeatedly engaging and disengaging the bite clutch by repeatedly applying pressure in its axial direction; and an operating piston being configured to provide pressure to the telescopic mechanism in the axial direction of the telescopic mechanism.

[0027] The retractable mechanism may include: a first engaging gear formed on the outer surface of the first body; a engaging ring configured to slide axially in the second body and having the second engaging gear on its inner surface to form the engaging clutch by engaging with the first engaging gear; a return spring installed to apply an elastic force to the engaging ring in a direction opposite to the direction of the pressure applied by the operating piston; and a switching mechanism configured to switch the following states: a state in which the second engaging gear of the engaging ring engages with the first engaging gear even if the pressure repeatedly applied by the operating piston is removed; and a state in which the second engaging gear is separated from the first engaging gear when the pressure from the operating piston is removed.

[0028] The switching mechanism may include: a snap ring protrusion that protrudes from the outer surface of the snap ring so that its axial sliding is guided by the second body; a release groove that is formed on the inner surface of the second body to guide the axial sliding of the snap ring protrusion; a retaining groove that is alternately formed on the second body with the release groove so that when the elasticity of the return spring is greater than the pressure of the operating piston, the second snap ring gear is kept in mesh with the first snap ring gear by accommodating the snap ring protrusion; an inclined surface that is formed to be inclined relative to the axial direction of the clutch device and is formed to be parallel to each other at a portion where an end of a first partition wall formed between the release groove and the retaining groove and the snap ring protrusion axially face each other; and a switching ring that is inserted into the release groove of the second body to slide axially, is capable of moving the snap ring toward the return spring by pushing the snap ring protrusion with the pressure provided by the operating piston, and has an inclined surface parallel to the inclined surface of the snap ring protrusion at a portion that contacts the snap ring protrusion.

[0029] A snap-in holding gear configured to mesh with the first snap-in gear when the second snap-in gear of the snap-in ring is separated from the first snap-in gear may be integrally formed on an inner surface of the switching ring.

[0030] A bite retaining ring having the bite retaining gear can be further installed between the switching ring and the operating piston. The bite retaining ring can be slidably inserted into the bite housing and is configured to engage with the first bite gear when the second bite gear of the bite ring is separated from the first bite gear.

[0031] The operating piston may be coaxially mounted on the outside of the friction piston, and the friction piston and the operating piston may be mounted to receive hydraulic pressure of the same pressure chamber together.

[0032] The operating piston may be coaxially mounted outside the friction piston, and a second partition wall may be provided between the friction piston and the operating piston, thereby configuring to independently control hydraulic pressure supplied to the friction piston and hydraulic pressure supplied to the operating piston.

[0033] According to various exemplary embodiments of the present invention, power transmission efficiency of a transmission is improved by transmitting or receiving sufficient torque and significantly reducing resistance in a clutch device used in the transmission, thereby contributing to improved fuel efficiency of a vehicle.

[0034] By incorporation into this document of the accompanying drawings and Figure 1 The detailed description is intended to illustrate certain principles of the present invention, and other features and advantages of the method and apparatus of the present invention will become more clearly apparent or elucidated. BRIEF DESCRIPTION OF THE DRAWINGS

[0035] Figure 1 are cross-sectional views illustrating various exemplary embodiments of a clutch device configured for a transmission according to various exemplary embodiments of the present invention;

[0036] Figure 2 yes Figure 1 An exploded perspective view of the main parts shown;

[0037] Figure 3 It shows Figure 2 A diagram of a first meshing gear and a second meshing gear shown;

[0038] Figure 4 It shows Figure 3 A diagram showing the meshing of the first and second splined gears;

[0039] Figure 5 It shows Figure 2 a diagram of the first body, snap-in ring, switching ring, and snap-in housing shown;

[0040] Figure 6 It is shown in detail Figure 5 an enlarged view of a portion of;

[0041] Figures 7 to 16 1. It is a diagram sequentially showing the engagement process of the bite clutch;

[0042] Figure 7 This is a diagram of separating the plate pack from the bite clutch;

[0043] Figure 8 is a diagram that moves the friction piston and engages the friction element;

[0044] Figure 9 A diagram showing a state in which the snap ring is moved by operating the piston and the second inclined surface of the second snap gear is brought into contact with the first inclined surface of the first snap gear;

[0045] Figure 10 is a diagram showing the snap-in ring being moved out of the snap-in housing and engaging with the switching ring;

[0046] Figure 11 It is shown in Figure 10 A diagram showing a state of the main part viewed along direction A in the state;

[0047] Figure 12 It is shown in three dimensions Figure 11 A diagram of the state of

[0048] Figure 13 is a diagram of engaging a snap-in ring into a snap-in housing;

[0049] Figure 14 is shown along direction A Figure 13 A diagram of the state of

[0050] Figure 15 is a diagram showing a three-dimensional view of an engaged state of a bite clutch; and

[0051] Figure 16 is shown along direction A Figure 15 A diagram of the state of

[0052] Figures 17 to 24 1. It is a diagram sequentially showing the disengagement process of the bite clutch;

[0053] Figure 17 This is a diagram showing the switching ring pressing the snap ring against the return spring;

[0054] Figure 18 is shown along direction A Figure 17 A diagram of the state of

[0055] Figure 19 This is a diagram showing the snap-in ring being removed from the snap-in shell;

[0056] Figure 20 is shown along direction A Figure 19 A diagram of the state of

[0057] Figure 21 is a diagram showing the snap-in ring being separated from the snap-in shell;

[0058] Figure 22 is shown along direction A Figure 21 A diagram of the state of

[0059] Figure 23 is a diagram showing a disengaged state of the bite clutch; and

[0060] Figure 24 is shown along direction A Figure 23 A diagram of the state of

[0061] Figure 25 are diagrams illustrating various exemplary embodiments of the present invention;

[0062] Figure 26 are diagrams illustrating various exemplary embodiments of the present invention; and

[0063] Figure 27 are drawings illustrating various exemplary embodiments of the present invention.

[0064] It should be understood that the accompanying drawings are not drawn to scale and show a somewhat simplified representation of various features illustrating the basic principles of the invention. The specific design features of the present invention disclosed herein (including, for example, specific dimensions, orientations, locations, and shapes) will be determined in part by the specific intended application and use environment.

[0065] In the figures, reference numbers refer to the same or equivalent parts of the present invention throughout the several figures of the drawing. DETAILED DESCRIPTION

[0066] Reference will now be made in detail to various embodiments of the present invention, examples of which are shown in the accompanying drawings and described below. Although the present invention will be described in conjunction with the exemplary embodiments, it should be appreciated that this description is not intended to limit the present invention to those exemplary embodiments. On the other hand, the present invention is intended to cover not only these exemplary embodiments, but also various alternative forms, modifications, equivalent forms, and other embodiments that may be included within the spirit and scope of the present invention as defined by the appended claims.

[0067] Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings. Throughout the drawings, the same reference numerals represent the same or similar parts.

[0068] Reference Figures 1 to 6A first exemplary embodiment of a clutch device for a transmission according to the present invention includes a first body BD1 and a second body BD2, a friction element FR, a friction piston 1, a telescopic mechanism, and an operating piston 3. The first body BD1 and the second body BD2 are coaxially mounted, the friction element FR is mounted between the first body BD1 and the second body BD2, the friction piston 1 is configured to axially press the friction element FR using hydraulic pressure, the telescopic mechanism includes a bite clutch DC that can restrict rotation between the first body BD1 and the second body BD2, and the telescopic mechanism repeatedly engages and disengages the bite clutch DC by repeatedly applying axial pressure, and the operating piston 3 is configured to provide pressure to the telescopic mechanism in the axial direction of the telescopic mechanism.

[0069] That is, in various aspects of the present invention, relative rotation is suppressed by generating friction between the first body BD1 and the second body BD2 via a hydraulically operated friction element FR, the relative rotation is kept suppressed by engaging the bite clutch DC, and the bite clutch DC is alternately engaged and disengaged by repeated axial pressure applied by a retractable mechanism.

[0070] Therefore, when the friction element FR is a disk pack comprising a plurality of disks and plates, the number of disks and plates is sufficient as long as they can overcome the relative rotation of the first and second bodies BD1 and BD2 during the early engagement phase of the clutch device. The bite clutch DC can instead function to stably maintain a continuously engaged state. Compared to the prior art, the number of disks and plates can be reduced, significantly reducing the resistance of the disk pack. Consequently, the power transmission efficiency of the transmission is improved, thereby potentially improving the fuel efficiency of the vehicle.

[0071] The first body BD1 and the second body BD2 are basically objects that can restrict relative rotation to each other and can enable relative rotation to each other. Figure 1 In the embodiment, the first body BD1 is a hub member, the second body BD2 is a transmission case, and basically, a clutch device located between the first body BD1 and the second body BD2 performs the function of an existing brake.

[0072] Obviously, when the second body BD2 is not a transmission case but a rotating member, the clutch device can be configured to perform the function of an existing clutch.

[0073] For reference, the term “axial direction” refers to a direction parallel to the rotation axes of the first and second bodies BD1 and BD2 .

[0074] In an exemplary embodiment, the retractable mechanism includes a first bite gear DG1, a bite housing DH, a bite ring DR, a return spring 5, and a switching ring SW, wherein the first bite gear DG1 is formed on the outer surface of the first body BD1, the rotation and axial movement of the bite housing DH are restricted by the second body BD2, the bite ring DR is slidably mounted on the bite housing DH, and has a second bite gear DG2 on the inner surface to form a bite clutch CD by engaging with the first bite gear DG1, the return spring 5 applies an elastic force to the bite ring DR in a direction opposite to the pressure applied by the operating piston 3, the switching ring SW is slidably mounted in the bite housing DH, and uses the pressure applied by the operating piston 3 to move the bite ring DR, so that when the bite ring DR moves out of the bite housing DH, the bite ring DR rotates in one direction relative to the bite housing DH.

[0075] That is, the snap clutch DC basically includes a first snap gear DG1 formed on the outer surface of the first body BD1 and a second snap gear DG2 formed on the snap ring DR.

[0076] For reference, as described below, the snap-in housing DH may be integrated with the second body BD2 rather than being separately provided.

[0077] The first snap gear DG1 of the first body BD1 and the second snap gear DG2 of the snap ring DR are formed so that the surfaces axially facing each other are inclined surfaces parallel to each other, as shown in FIG. Figure 3 and Figure 4 shown.

[0078] In order to distinguish the inclined surfaces, the inclined surface of the first meshing gear DG1 is referred to as a first inclined surface S1, and the inclined surface of the second meshing gear DG2 is referred to as a second inclined surface S2.

[0079] Therefore, when the second engaging gear DG2 of the engaging ring DR is pressed toward the first engaging gear DG1, the first inclined surface S1 and the second inclined surface S2 slide with each other, and they can be easily engaged by slight relative rotation without stopping, thereby always ensuring smooth and stable engagement of the engaging clutch DC.

[0080] The snap-in ring DR is configured to axially slide through the snap-in housing DH relative to the second body BD2, and the snap-in housing DH is fixed to the second body BD2 so as to be configured to guide the linear sliding of the snap-in ring DR.

[0081] Therefore, since the second body BD2 is the transmission case, the second meshing gear DG2 is Figure 1 The structure cannot rotate. Figure 4, whereby only the hub member as the first body BD1 is shown to be rotated by the first inclined surface S1 of the first meshing gear DG1 and the second inclined surface S2 of the second meshing gear DG2.

[0082] A snap-ring protrusion DR_P is formed on the outer surface of the snap-ring DR, and the snap-ring protrusion DR_P is inserted into the snap-ring housing DH and guided to slide axially.

[0083] Retaining grooves HG and release grooves RG are alternately formed along the circumferential direction on the inner surface of the bite shell DH. The retaining groove HG accommodates the bite ring protrusion DR_P to keep the second bite gear DG2 of the bite ring DR engaged with the first bite gear DG1 of the first body BD1, while the release groove RG guides the inserted bite ring protrusion DR_P to move freely axially.

[0084] That is, when the snap ring protrusion DR_P is removed from the release groove RG, the snap ring protrusion DR_P moves further toward the operating piston 3 than when it is inserted into the retaining groove HG, thereby separating the second snapping gear DG2 from the first snapping gear DG1. On the other hand, when the snap ring protrusion DR_P is inserted into the retaining groove HG, the second snapping gear DG2 meshes with the first snapping gear DG1.

[0085] The first partition wall W1 and the snap-in ring protrusion DR_P between the retaining groove HG and the releasing groove RG of the snap-in housing DH are formed so that surfaces axially facing each other are inclined surfaces parallel to each other.

[0086] For reference, in order to distinguish the inclined surfaces of the first partition wall W1 and the snap ring protrusion DR_P from other inclined surfaces, the inclined surface of the first partition wall W1 is referred to as a third inclined surface S3 and the inclined surface of the snap ring protrusion DR_P is referred to as a fourth inclined surface S4.

[0087] exist Figure 6 、 Figure 7 、 Figure 8 、 Figure 9 、 Figure 10 ,as well as Figure 11 The third inclined surface S3 and the fourth inclined surface S4 can be seen in FIG.

[0088] When the pressure provided by the operating piston 3 is greater than the elasticity of the return spring 5 , the snap ring DR moves toward the return spring 5 , and when the pressure provided by the operating piston 3 is less than the elasticity of the return spring 5 , the snap ring DR moves toward the operating piston 3 .

[0089] When the snap ring DR moves toward the operating piston 3 by the elasticity of the return spring 5, the fourth inclined surface S4 of the snap ring protrusion DR_P is guided by the third inclined surface S3 of the first partition wall W1 and rotates the snap ring DR, thereby the snap ring protrusion DR_P is alternately inserted into the retaining groove HG and the release groove RG.

[0090] That is, whenever the operating piston 3 presses the snap ring DR toward the return spring 5 and then releases the snap ring DR, the snap ring protrusion DR_P of the snap ring DR is repeatedly and alternately inserted into the retaining groove HG and the releasing groove RG of the snap housing DH.

[0091] This operation requires the help of a switching ring SW to be described below.

[0092] The switching ring SW has a switching portion having an inclined surface parallel to the fourth inclined surface S4 of the snap-ring protrusion DR_P.

[0093] The inclined surface of the switching portion is referred to as a fifth inclined surface to distinguish it from the other inclined surfaces.

[0094] In the exemplary embodiment, the fifth inclined surface S5 of the switching portion extends from a position corresponding to the middle portion of the relief groove RG to a position corresponding to the middle portion of the first partition wall W1. Figure 11 As shown, the switching portion may be formed by repeatedly connecting the fifth inclined surface S5 to the fifth inclined surface S5 via the sixth inclined surface S6 having an almost axially symmetrical shape.

[0095] When the operating piston 3 pushes the snap ring DR toward the return spring 5, the switching ring SW transmits the operating force to the snap ring DR, and when the snap ring protrusion DR_P of the snap ring DR is separated from the retaining groove HG or the release groove RG of the snap housing DH, the switching ring SW determines the rotation direction of the snap ring DR.

[0096] That is, when the snap-in ring protrusion DR_P is separated from the snap-in housing DH, the fifth inclined surface S5 of the switching ring SW is Figure 11 The snap-in ring protrusion DR_P is guided upward in the middle so that the front end of the fourth inclined surface S4 is accommodated in the groove formed at the junction of the fifth inclined surface S5 and the sixth inclined surface S6. In addition, when the pressure of the operating piston 3 is reduced and the snap-in ring protrusion DR_P moves toward the snap-in housing DH, the fourth inclined surface S4 of the snap-in ring protrusion DR_P is guided to surface-contact the third inclined surface S3 of the first partition wall W1.

[0097] In an exemplary embodiment of the present invention, when the second meshing gear DG2 of the meshing ring DR is separated from the first meshing gear DG1, the meshing holding gear 7 can engage with the first meshing gear DG1, and the meshing holding gear 7 is integrally formed on the inner surface of the switching ring SW, thereby continuously maintaining the structure of mechanically limiting the relative rotation of the first body BD1 and the second body BD2 through the meshing shell DH.

[0098] At the same time, as in Figure 25 In the second exemplary embodiment shown in , a bite retaining ring 9 having a bite retaining gear 7 can be further installed between the switching ring SW and the operating piston 3. The bite retaining ring 9 can be slidably inserted into the bite housing DH and can engage with the first bite gear DG1 when the second bite gear DG2 of the bite ring DR is separated from the first bite gear DG1.

[0099] That is, the switching ring SW uses the fifth and sixth inclined surfaces S5 and S6 to guide the movement of the snap-ring protrusions DR_P of the snap-ring DR, thereby continuously mechanically restricting relative rotation between the first and second main bodies BD1 and BD2, even though the snap-ring DR does not restrict relative rotation by having an integral snap-retaining gear 7 in the first exemplary embodiment. However, in the second exemplary embodiment, a snap-retaining ring 9 is separately provided to continuously restrict relative rotation between the first and second main bodies BD1 and BD2, even if the second snap-retaining gear DG2 is separated from the first snap-retaining gear DG1.

[0100] In the present case, the snap-in retaining ring 9 transmits the pressure of the actuating piston 3 to the switching ring SW, and the switching ring SW transmits the pressure to the snap-in ring DR.

[0101] exist Figure 1 In the illustrated first exemplary embodiment, the operating piston 3 is coaxially mounted outside the friction piston 1 , and the friction piston 1 and the operating piston 3 are mounted to receive hydraulic pressure from the same pressure chamber 11 together.

[0102] Therefore, when the hydraulic pressure of the pressure chamber 11 is operated, the friction piston 1 and the operating piston 3 are operated together.

[0103] At the same time, Figure 26 In the third exemplary embodiment shown in , the operating piston 3 is coaxially mounted on the outside of the friction piston 1, and a second partition wall W2 is installed between the friction piston 1 and the operating piston 3, so that the hydraulic pressure provided to the friction piston 1 and the hydraulic pressure provided to the operating piston 3 can be independently controlled.

[0104] Therefore, the third exemplary embodiment may have an advantage in that the clutch device can be controlled more smoothly and accurately by independently controlling the hydraulic pressure supplied to the friction piston 1 and the hydraulic pressure supplied to the operating piston 3 , respectively.

[0105] In addition, despite Figure 1 In the first exemplary embodiment shown, the friction element FR is a disk pack formed by alternately arranging a plurality of disks and plates, but as shown in FIG. Figure 27 As shown in the fourth exemplary embodiment, unlike the first exemplary embodiment, the friction element FR may be a conical friction clutch 13 having a conical friction surface.

[0106] Obviously, various mechanisms that can continuously change the friction between the first body BD1 and the second body BD2 by applying axial pressure can be used as the friction element FR.

[0107] Hereinafter, based on the first exemplary embodiment, referring to Figures 7 to 16 To describe the engagement process of the clutch device of the present invention, and with reference to Figures 17 to 24 To describe the disengagement process of the clutch device of the present invention.

[0108] Figure 7 This is a diagram showing that the plate pack serving as the friction element FR and the bite clutch DC are disengaged.

[0109] In the present state, the snap-in ring protrusion DR_P of the snap-in ring DR can slide axially in the relief groove RG of the snap-in housing DH.

[0110] When hydraulic pressure is supplied to the friction piston 1 and the operating piston 3 in the current state, as shown in FIG. Figure 8 As shown, the friction piston 1 generates friction by engaging the friction element FR while moving leftward in the figure, thereby suppressing relative rotation between the first body BD1 and the second body BD2.

[0111] The operating piston 3 moves the snap ring DR toward the return spring 5 to the left in the figure through the switching ring SW, so that the second inclined surface S2 of the second snap gear DG2 of the snap ring DR is as shown in FIG. Figure 9 The first inclined surface S1 of the first engaging gear DG1 of the first body BD1 is shown in contact with the first inclined surface S1 of the first engaging gear DG1 of the first body BD1 (refer to Figure 4 ).

[0112] When the snap ring DR moves further to the left, the second snap gear DG2 is fully engaged with the first snap gear DG1 and then completely moves out of the first snap gear DG1 of the first body BD1, and the snap ring DR also moves out of the snap housing DH. Figure 10 shown.

[0113] In the present state, just after being moved out of the release groove RG of the snap-in housing DH, the snap-in ring protrusion DR_P contacts the fifth inclined surface S5 on the fourth inclined surface S4 and rotates by the elastic force of the return spring 5, so that Figure 11 As shown, the front end portion of the fourth inclined surface S4 is accommodated in a groove formed between the fifth inclined surface S5 and the sixth inclined surface S6 of the switching ring SW.

[0114] In the present state, as described above, the relative rotation between the first body BD1 and the second body BD2 is restricted by the engagement holding gear 7 of the switching ring SW.

[0115] That is, when hydraulic pressure is applied to the friction piston 1 and the operating piston 3, first, the relative rotation of the first body BD1 and the second body BD2 is restricted by the friction element FR. Then, the second meshing gear DG2 meshes with the first meshing gear DG1, and the meshing clutch DC is temporarily engaged, thereby achieving secondary restriction. Even if the meshing clutch is disengaged again, this restricted state is maintained by the meshing holding gear 7 of the switching ring SW, thereby achieving a third restricted state, as shown in FIG. Figure 11 shown.

[0116] In the present state, when the hydraulic pressure applied to the operating piston 3 is removed, the fourth inclined surface S4 of the snap-in ring protrusion DR_P moves on the third inclined surface S3 of the first partition wall W1 of the snap-in housing DH, as shown in FIG. Figure 14 As shown, and inserted into the retaining groove HG of the snap-in housing DH, as shown Figure 16 As shown, in the immediate state, the second meshing gear DG2 is gear-meshed with the first meshing gear DG1 , so that the meshing clutch DC is actually engaged.

[0117] In the current state, even if hydraulic pressure is not applied to the operating piston 3 and the friction piston 1, the engagement of the first body BD1 and the second body BD2 is continuously and stably maintained, thereby reducing the energy generated by the hydraulic pressure normally used to continuously press the friction element RF, thereby helping to improve the fuel efficiency of the vehicle.

[0118] Reference Figures 17 to 27 The operation of disengaging the clutch device that has been engaged as described above will be described.

[0119] In order to disengage the clutch device, hydraulic pressure is applied to the operating piston 3, so that the switching ring SW presses the snap ring protrusion DR_P of the snap ring DR toward the return spring 5. Figure 17 and Figure 18 shown.

[0120] The fifth inclined surface S5 of the switching ring SW continuously pushes the snap ring protrusion DR_P, so that the snap ring protrusion DR_P moves out of the retaining groove HG of the snap housing DH, and then guides the snap ring protrusion DR_P to rotate toward the release groove RG, as shown in FIG. Figure 20 shown.

[0121] When the snap ring protrusion DR_P of the snap ring DR is inserted into the release groove RG, the hydraulic pressure applied to the operating piston 3 is removed. Therefore, the snap ring protrusion DR_P slides along the release groove RG toward the operating piston 3 by the elasticity of the return spring 5. Figure 22 and Figure 24 As shown, the second splined gear DG2 of the splined ring DR is separated from the first splined gear DG1 of the first body BD1, so that the clutch device is disengaged.

[0122] Obviously, the pressure applied to the friction element FR is also removed, so that the first body BD1 and the second body BD2 become relatively rotatable.

[0123] When the clutch device is engaged and disengaged, the above-mentioned operation is performed alternately and repeatedly each time pressure is applied to and removed from the friction piston 1 and the operating piston 3, wherein the engaged state of the bite clutch DC is maintained and then the disengaged state of the bite clutch DC is maintained.

[0124] On the other hand, the present invention can be expressed as follows.

[0125] That is, the clutch device of the present invention configured for a transmission may include a first body BD1 and a second body BD2, a friction element FR, a friction piston 1, and a limit retainer, wherein the first body BD1 and the second body BD2 are coaxially installed on the inside and the outside, the friction element FR is configured to generate friction between the first body BD1 and the second body BD2, the friction piston 1 is configured to increase the friction of the friction piston 1 by applying pressure to the friction element FR, and the limit retainer is configured to limit the relative rotation of the first body BD1 and the second body BD2 even if the pressure applied to the friction element FR by the friction piston 1 is removed.

[0126] The limiting retainer may include a telescopic mechanism and an operating piston 3, wherein the telescopic mechanism forms a bite clutch DC that can limit the relative rotation of the first body BD1 and the second body BD2, and repeatedly engages and disengages the bite clutch DC by repeatedly applying axial pressure, and the operating piston 3 is configured to provide pressure to the telescopic mechanism in the axial direction of the telescopic mechanism.

[0127] The retractable mechanism may include: a first meshing gear DG1, a meshing ring DR, a return spring 5, and a switching mechanism, wherein the first meshing gear DG1 is formed on the outer surface of the first body BD1, the meshing ring DR is configured to slide axially in the second body BD2, and has a second meshing gear DG2 on the inner surface to form a meshing clutch CD by engaging with the first meshing gear DG1, the return spring 5 is installed to apply an elastic force to the meshing ring DR in a direction opposite to the pressure applied by the operating piston 3, and the switching mechanism is configured to switch the following states: a state in which the second meshing gear DG2 of the meshing ring DR is meshed with the first meshing gear DG1 even if the pressure repeatedly applied by the operating piston 3 is removed; and a state in which the second meshing gear DG2 is separated from the first meshing gear DG1 when the pressure from the operating piston 3 is removed.

[0128] That is, the second body BD2 can perform the function of the snap-in housing DH without a separate snap-in housing DH, and the number of parts can be reduced by forming the release groove RF, the holding groove HG and the first partition wall W1 on the second body BD2, and the first partition wall W1 will be described below.

[0129] This means that, depending on the shape or structure of the second body BD2 , the above-mentioned separate snap-in housing DH may be provided, and a configuration for performing the functions of the present invention may be integrated with the second body BD2 .

[0130] The switching mechanism may include: a snap ring protrusion DR_P, a release groove RG, a holding groove HG, an inclined surface, and a switching ring SW. The snap ring protrusion DR_P protrudes from the outer surface of the snap ring DR so that its axial sliding is guided by the second body BD2. The release groove RG is formed on the inner surface of the second body BD2 to guide the axial sliding of the snap ring protrusion DR_P. The holding groove HG and the release groove RG are alternately formed on the second body BD2 so that when the elasticity of the return spring 5 is greater than the pressure of the operating piston 3, the second snap ring gear DG2 is engaged with the second snap ring gear DG2 by accommodating the snap ring protrusion DR_P. The first bite gear DG1 remains engaged, the inclined surface is inclined relative to the axial direction, and is parallel to each other at the end of the first partition wall W1 formed between the release groove RG and the retaining groove HG and the portion where the bite ring protrusion DR_P faces each other axially, the switching ring SW is inserted into the release groove RG of the second body BD2 to slide axially, and is capable of moving the bite ring DR toward the return spring 5 by pushing the bite ring protrusion DR_P with the pressure provided by the operating piston 3, and has an inclined surface parallel to the inclined surface of the bite ring protrusion DR_P at the portion in contact with the bite ring protrusion DR_P.

[0131] A snap-holding gear 7 may be integrally formed on the inner surface of the switching ring SW, and the snap-holding gear 7 may be engaged with the first snap-holding gear DG1 when the second snap-holding gear DG2 of the snap-holding ring DR is separated from the first snap-holding gear DG1.

[0132] A bite retaining ring 9 can be further installed between the switching ring SW and the operating piston 3. The bite retaining ring 9 has a bite retaining gear 7 and can be slidably inserted into the bite housing DH, and can engage with the first bite gear DG1 when the second bite gear DG2 of the bite ring DR is separated from the first bite gear DG1.

[0133] The operating piston 3 is installed outside the friction piston 1 , and the friction piston 1 and the operating piston 3 may be installed to receive hydraulic pressure of the same pressure chamber 11 together.

[0134] The operating piston 3 is coaxially mounted outside the friction piston 1 , and a second partition wall W2 may be provided between the friction piston 1 and the operating piston 3 , so that the hydraulic pressure supplied to the friction piston 1 and the operating piston 3 may be independently controlled.

[0135] For ease of explanation and precise definition in the appended claims, the terms "above," "below," "inside," "outside," "up," "down," "upward," "downward," "front," "back," "inside," "outside," "inwardly," "outwardly," "interior," "exterior," "inner," "exterior," "inner," "outward," "forward," and "rearward" are used to describe features of the exemplary embodiments with reference to the positions of such features as shown in the drawings. It will be further understood that the term "connect" or its derivatives refers to both direct and indirect connections.

[0136] The foregoing descriptions of specific exemplary embodiments of the present invention have been presented for purposes of illustration and description. The foregoing descriptions are not intended to be exhaustive, nor are they intended to limit the invention to the precise forms disclosed, and it is apparent that many variations and modifications are possible in light of the foregoing teachings. The exemplary embodiments have been selected and described in order to explain the specific principles of the invention and its practical application, thereby enabling others skilled in the art to realize and utilize the various exemplary embodiments of the invention and their various alternative forms and modifications. The scope of the invention is intended to be defined by the appended claims and their equivalents.

Claims

1. A clutch device for a transmission, the clutch device comprising: a first body and a second body, the second body being coaxially mounted to the first body; a friction element installed between the first body and the second body; a friction piston configured to axially press the friction element by using hydraulic pressure; a retractable mechanism including a bite clutch configured to restrict rotation between the first body and the second body, the retractable mechanism repeatedly engaging and disengaging the bite clutch by repeatedly applying pressure in an axial direction thereof; as well as an operating piston configured to provide pressure to the telescopic mechanism in an axial direction of the telescopic mechanism, Wherein, the bite clutch of the retractable mechanism comprises: a first engaging gear formed on an outer surface of the first body; and The second engaging gear, Wherein, the retractable mechanism further comprises: a snap-in housing, which is restricted in rotation and axial movement by the second body; a snap ring slidably mounted in the snap housing and having the second snap gear on an inner surface thereof to form the snap clutch by meshing with the first snap gear; a return spring installed to apply an elastic force to the snap ring in a direction opposite to the direction of the pressure applied by the operating piston; and A switching ring is slidably mounted in the snap-in housing and is moved by pressure applied by the operating piston so that when the snap-in ring is moved out of the snap-in housing, the snap-in ring rotates in a direction relative to the snap-in housing.

2. The clutch device for a transmission according to claim 1, wherein: Surfaces axially facing each other in the first snap-in gear of the first body and the second snap-in gear of the snap-in ring are inclined surfaces parallel to each other.

3. The clutch device for a transmission according to claim 2, in, A snap-in ring protrusion is formed on an outer surface of the snap-in ring, the snap-in ring protrusion being inserted into the snap-in housing and guided to slide axially; Wherein, retaining grooves and release grooves are alternately formed on the inner surface of the snap-in shell along its circumference, the retaining groove accommodates the snap-in ring protrusion to keep the second snap-in gear of the snap-in ring engaged with the first snap-in gear of the first body, and the release groove guides the inserted snap-in ring protrusion to move freely axially.

4. The clutch device for a transmission according to claim 3, wherein: Surfaces of the snap-in ring protrusion and the first partition wall between the retaining groove and the releasing groove of the snap-in housing and facing each other axially are inclined surfaces parallel to each other.

5. The clutch device for a transmission according to claim 4, in, The switching ring has a switching portion having an inclined surface parallel to the inclined surface of the snap ring protrusion; The inclined surface of the switching portion is formed to extend from a position corresponding to a middle portion of the relief groove to a position corresponding to a middle portion of the first partition wall.

6. The clutch device for a transmission according to claim 5, wherein: A snap-in holding gear is configured to mesh with the first snap-in gear when the second snap-in gear of the snap-in ring is separated from the first snap-in gear, and the snap-in holding gear is integrally formed on an inner surface of the switching ring.

7. The clutch device for a transmission according to claim 5, wherein: A bite retaining ring having a bite retaining gear is further installed between the switching ring and the operating piston. The bite retaining ring can be slidably inserted into the bite housing and is configured to engage with the first bite gear when the second bite gear of the bite ring is separated from the first bite gear.

8. The clutch device for a transmission according to claim 1, wherein: The operating piston is coaxially mounted on the outside of the friction piston, and the friction piston and the operating piston are configured to receive hydraulic pressure from the same pressure chamber together.

9. The clutch device for a transmission according to claim 1, wherein: The operating piston is coaxially installed outside the friction piston, and a second partition wall is installed between the friction piston and the operating piston, thereby configuring to independently control the hydraulic pressure supplied to the friction piston and the hydraulic pressure supplied to the operating piston.

10. The clutch device for a transmission according to claim 1, wherein The friction element is a disk pack formed by alternately arranging a predetermined number of disks and plates.

11. The clutch device for a transmission according to claim 1, wherein: The friction element is a conical friction clutch having a conical friction surface.

12. A clutch device configured for use in a transmission, the clutch device comprising: a first body and a second body, wherein the second body is coaxially mounted to an outer side of the first body; a friction element configured to generate friction between the first body and the second body; a friction piston configured to increase friction of the friction piston by applying pressure to the friction element; as well as a limit retainer configured to limit relative rotation of the first body and the second body after the pressure applied to the friction element by the friction piston is removed, Wherein, the limiting retainer comprises: a retractable mechanism including a bite clutch configured to restrict relative rotation of the first body and the second body, the retractable mechanism repeatedly engaging and disengaging the bite clutch by repeatedly applying pressure in an axial direction thereof; and an operating piston configured to provide pressure to the telescopic mechanism in an axial direction of the telescopic mechanism, Wherein, the bite clutch of the retractable mechanism comprises: a first engaging gear formed on an outer surface of the first body; and The second engaging gear, Wherein, the retractable mechanism further comprises: a snap ring configured to slide axially in the second body and having the second snap gear on an inner surface thereof to form the snap clutch by meshing with the first snap gear; a return spring installed to apply an elastic force to the snap ring in a direction opposite to the direction of the pressure applied by the operating piston; and A switching mechanism configured to switch between a state in which the second meshing gear of the meshing ring is engaged with the first meshing gear even if the pressure repeatedly applied by the operating piston is removed, and a state in which the second meshing gear is separated from the first meshing gear when the pressure from the operating piston is removed.

13. The clutch device for a transmission according to claim 12, wherein: The switching mechanism includes: a snap-in ring protrusion protruding from an outer surface of the snap-in ring so that its axial sliding is guided by the second body; a relief groove formed on an inner surface of the second body to guide axial sliding of the snap-in ring protrusion; Retaining grooves are formed alternately with the releasing grooves on the second body so that when the elasticity of the return spring is greater than the pressure of the operating piston, the second snap-in gear is kept in mesh with the first snap-in gear by accommodating the snap-in ring protrusion; an inclined surface formed to be inclined with respect to the axial direction of the clutch device and formed to be parallel to each other at a portion where an end portion of a first partition wall formed between the release groove and the retaining groove and the snap-ring protrusion axially face each other; and A switching ring, which is inserted into the release groove of the second body to slide axially, is configured to push the bite ring protrusion by utilizing the pressure provided by the operating piston, thereby moving the bite ring toward the return spring, and has an inclined surface parallel to the inclined surface of the bite ring protrusion at a portion in contact with the bite ring protrusion.

14. The clutch device for a transmission according to claim 13, wherein: A snap-in holding gear is configured to mesh with the first snap-in gear when the second snap-in gear of the snap-in ring is separated from the first snap-in gear, and the snap-in holding gear is integrally formed on an inner surface of the switching ring.

15. The clutch device for a transmission according to claim 13, wherein: A bite retaining ring having a bite retaining gear is further installed between the switching ring and the operating piston. The bite retaining ring can be slidably inserted into the bite housing and is configured to engage with the first bite gear when the second bite gear of the bite ring is separated from the first bite gear.

16. The clutch device for a transmission according to claim 12, wherein: The operating piston is coaxially mounted on the outside of the friction piston, and the friction piston and the operating piston are configured to receive hydraulic pressure from the same pressure chamber together.

17. The clutch device for a transmission according to claim 12, wherein: The operating piston is coaxially mounted outside the friction piston, and a second partition wall is provided between the friction piston and the operating piston, thereby configuring to independently control the hydraulic pressure supplied to the friction piston and the hydraulic pressure supplied to the operating piston.

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