JP4478129B2 - Rotation control device without spline - Google Patents

Description

  The present invention relates to a rotation control device, and more particularly, a spline adapted for use in selective control of transmission of rotational force between a first relative rotatable member and a second relative rotatable member. And in particular, in a preferred form, to a friction clutch device for driving a fan.

  When it is desired to intermittently transmit torque from one rotatable component to another, these components are interconnected with a clutch, and then this clutch is selected as required It is normal to actuate and deactivate automatically. Known clutch arrangements can be controlled using start-up systems based on electricity, mechanical, pneumatic, or hydraulic pressure. Each of these starting systems typically applies an axial load to the coupling element (typically comprised of any one of the rotatable components or separate components) to To driveably interconnect the rotatable components, it works by creating some relative axial shift between these coupling elements and one of the rotatable components.

  If a separate coupling element is utilized, this coupling element is typically drivingly connected to one of the rotatable components through a spline connection. With this arrangement, the coupling element can be easily shifted in the axial direction while still maintaining a driving connection with the respective rotatable component. The main drawback with this type of clutch is that the spline represents a highly wearable article and requires expensive machining. Obviously, when the spline connection deteriorates, the overall function of the clutch is adversely affected and maintenance is required. In addition, there is a need for lubricants (eg, grease).

  In a fluid start-up system, the coupling element is configured almost unchanged by an annular piston. Typically, at least one spring acts on the piston. The spring biases the piston to one of an operating position or a disengaged position. When the two rotatable components are interconnected, fluid pressure acts on the side of the piston that is opposite the spring, causing an axial shift of the piston. Since the axially shifting force produced by the fluid is equal to the product of the fluid pressure and the associated surface area of the piston, the surface area of the piston is directly related to the level of force that can be generated. However, this type of clutch piston typically has a small surface area, particularly in the case of an annular piston located around a hub or the like. Correspondingly, these clutches have a relatively low engagement and disengagement force associated therewith.

  Another problem recognized in the art considers the transmission of loads through bearings. In the field of rotational control devices, it is often found that fairly high loads (especially axial loads) are exerted on bearing units arranged between relative rotatable members. This high axial load often results in fatigue failure of the bearing, which requires that the bearing be replaced periodically.

  Based on these and other problems recognized in the art, the use of spline connections is avoided, relatively high engagement or disengagement forces can be generated, and the axial direction exerted on the internal bearings There is a need for a rotation control device that limits the degree of load.

(Summary of the Invention)
The present invention solves these and other problems, and deficiencies in the art, by providing a rotation control device having a fixed support shaft that rotatably installs a first member through a first bearing unit. To do. A first engagement surface is provided for rotation with the first member at a position axially spaced from the first bearing unit. The second member has a second engagement surface associated therewith that selectively frictionally engages the first engagement surface to interconnect the first and second members. Adapted to do.

  A piston is disposed axially between the first member and the second member to interconnect the engagement surfaces. In the most preferred form of the invention, the piston is annular or disk-shaped, as opposed to annular, extends radially across the outer annular portion of the first member and is sealingly engaged. With this arrangement, the piston has an enlarged surface area associated therewith which is preferably pressurized to allow the piston to be shifted relative to the first member. Adapted to be acted upon by a fluid. The cap member is sealed to the inner axial portion of the first member so that the cap member, the first member portion and the piston define a fluid action / de-action chamber for the rotation control device.

  The piston is rotatably supported by a second bearing unit, and this unit is interposed between the piston and the second member. Although relative rotation is possible between the piston and the second member, the piston and the second member are interconnected for simultaneous axial movement through the second bearing. Thus, the piston shift causes engagement and disengagement of the first and second engagement surfaces. At least one spring is provided to bias the piston into either the engaged or disengaged position, the spring extending radially with a reaction plate fixed for rotation with the first member; Acts between the piston. In one preferred form of the invention, the reaction plate defines a plurality of cavities spaced annularly and extending axially, which each spring acting to bias the piston into the engaged position. Accept. In another preferred form of the invention, an annular spring is interposed between the reaction plate and the piston to bias the piston to the disengaged position.

  In either form of the invention, the piston is not drivingly engaged directly with the first member, so that the need for splines in the rotation control device is avoided. Furthermore, the bearing unit is arranged such that a minimum axial load is exerted on the unit when the first and second members of the rotation control device are engaged. Further, as indicated above, the piston defines an enlarged surface area that can be acted upon by fluids or other axial forces that generate mechanisms that can cause large engagement / disengagement forces.

  Accordingly, an object of the present invention is to provide an improved rotation control device for use in selectively controlling the transmission of force between a first relative rotatable member and a second relative rotatable member. It is to be.

  Another object of the present invention is to provide a rotation control device of the type having a fixed support shaft that rotatably supports the first member through the first bearing member.

  Yet another object of the present invention is to provide a rotation control device that is started by the use of a piston with a large associated piston area that shifts in the axial direction, so that a considerably large engagement or disengagement force can be generated. Is to provide.

  Yet another object of the present invention is to introduce fluid pressure into a chamber defined by a piston, a portion of the first member, and a cap member sealed to the first member to shift the piston axially. It is to provide a rotation control device.

  It is a further object of the present invention to provide a rotation control device in which the piston is installed axially shiftable without using any spline connection.

  A still further object of the present invention is to provide a rotation control device in which a piston is interconnected through a second bearing for relative rotation with the second member and simultaneous axial movement.

  A still further object of the present invention is to provide a rotation control device that can be spring biased to either an engaged or disengaged position.

  A still further object of the present invention is to provide a rotation control device designed to provide a minimal load on the bearing unit in order to increase the service life.

  These and other objects, features and advantages of the present invention will become more readily apparent from the following detailed description of preferred embodiments of the invention when considered in conjunction with the drawings. In these drawings, like reference numerals indicate corresponding parts.

  Because it has a rotary joint that rotates the hub, the outer bearing ring of the bearing and the cap member together to selectively interconnect the first and second relative members with fluid pressure through the fluid passage in the shaft portion, A spline-free connection of the first and second relative members is achieved by the pressurized fluid.

  It should be noted that all figures are drawn only to simplify the explanation of the basic teachings of the invention; relating to the number, position, relationship and dimensions of the parts to form a preferred embodiment. Extensions to the figures are described or within the skill of the art. The following techniques of the present invention will be read and understood.

  Further, when the terms “first”, “second”, “internal”, “external”, “radial”, “axial”, and similar terms are used herein, these terms are It should be understood that, as will be apparent to the person viewing the drawing, only the structure shown in the drawing is referred to and is used only to facilitate the description herein. .

Detailed Description of Preferred Embodiments
Referring initially to FIG. 1, a rotation control device constructed in accordance with a first preferred embodiment in accordance with the teachings of the present invention is indicated generally at 10. In the most preferred form of the invention, the rotation control device 10 constitutes a friction clutch, which is particularly adapted for use in driving a fan, such as a cooling fan used in an automotive environment. The However, as will become more fully apparent from a reading and understanding of the present invention, as will be described in detail below, various aspects of the present invention are outside of this particular field (eg, in the field of baking devices). It can be used advantageously.

  As shown in this drawing, the rotation control device 10 comprises a substantially L-shaped journal bracket 14 formed integrally, which bracket defines the support mount for the entire device. The journal bracket 14 includes a flange portion 16 through which a plurality of bolts (not shown) extend to secure the journal bracket 14 to a support structure (not shown) (eg, engine block). Adapted to be screwed into place. The journal bracket 14 includes a shaft portion 22 that is adapted to support a sheave 26. In accordance with a preferred form in accordance with the preferred teachings of the present invention, the sheave 26 constitutes the first or input member of the rotation control device 10 and is rotatably supported on the shaft portion 22 by the first bearing unit 30. More specifically, the first bearing unit 30 includes inner and outer races, each of which is press fit onto the shaft portion 22 and pressed against the sheave 26. The inner race of the first bearing unit 30 causes the shaft portion 22 to abut the shaft portion 22 by contacting the shoulder 32 of the shaft portion 22 at one axial position and engaging the retainer element 34 with an axial position spaced apart. The retainer element is axially secured to 22 and is threadably attached to the reduced diameter inner axial end 36 of the shaft portion 22.

  The sheave 26 includes a shoulder 38 that places the sheave 26 axially with respect to the first bearing unit 30. In the preferred embodiment shown, the shoulder 38 represents an extension of the first or hub portion 42 of the sheave 26. The first portion 42 defines an outer radial grooved section 44 around which a belt (not shown) is adapted to extend for inputting rotational driving force into the sheave 26. The sheave 26 also includes a second portion 46 that is axially spaced from the first portion 42. With this arrangement, the sheave 26 is associated with a radially inner surface 48 and a radially outer surface 50, both of which are located within the limits of the sheave 26.

  In the most preferred form of the present invention, the rotation control device 10 constitutes a device controlled by fluid pressure. In this preferred form, the rotation control device 10 incorporates a cap member 54 that extends across the inner diameter surface 48. As clearly shown in FIG. 1, the cap member 54 also abuts the outer race of the first bearing unit 30 and is maintained axially by the snap ring 56. A seal 58 is interposed between the cap member 54 and the sheave 26. In the center of the cap member 54, a coupling 62 defining a fluid passage is fixed so as to be screwed. The passage of the coupling 62 is in fluid communication with the conduit 66 of the rotary joint 68. The rotary joint 68 is installed in a bore 70 formed in the shaft portion 22 of the bracket 14. In general, the rotary joint 68 takes the form of a cartridge known in the art and will therefore not be described in detail here. However, it should be noted that the conduit 66 is in further fluid communication with the passage 72 formed in the shaft portion 22. Thus, with this arrangement, the supply of pressurized fluid can be forced to flow selectively through cap member 54, through passage 72, through rotary joint 68 and coupling 62.

  During the initial assembly of the rotation control device 10, the first bearing unit 30 is initially placed against the shoulder 38 in the sheave 26. Thereafter, the sheave 26 and the first bearing unit 30 are slid over the shaft portion 22 of the journal bracket 14 until the first bearing 30 abuts against the shoulder 32. The retainer element 34 is then screwed onto the axial end 36 of the shaft portion 22, which presses the inner race of the first bearing unit 30 against the shoulder 32. The rotary joint 68 may actually be inserted before or after assembly of the sheave 26 and the first bearing unit 30 to the journal bracket 14. With the seal 58 and coupling 62 attached to the cap member 54, the cap member 54 is slid along the radial inner diameter surface 48 and pressed against the outer race of the first bearing unit 30. Thereafter, a snap ring 56 is installed in an annular groove formed in the diameter surface 48 to hold the cap member 54 in the axial direction. With this arrangement, the journal bracket 14 can be advantageously formed from one piece to enhance its structural features while still allowing the shaft 22 to extend fully into the sheave 26. In a preferred form, the fluid passage of the coupling 62 is threaded to accept bolts and the like to allow removal of the cap member 54 for disassembly (after removal of the snap ring 56).

  In the most preferred form of the invention, the retainer element 34 is formed with a drain hole 75 and the shaft portion 22 includes a drain passage 77 extending axially from the drain hole 75 through the journal bracket 14. With this preferred configuration, if any leakage occurs between the coupling 62 and the rotary joint 68, the fluid leaks through the drainage circuit rather than through the first bearing unit 30 and the bearing unit 30 Extend the service life.

  The rotation control device 10 further comprises a piston 76, in which a disc-shaped part is defined at least partly by a first axial surface 80, which flows through the coupling 62. Exposed to pressurized fluid. The piston 76 also includes a second axial surface 82 from which projecting outer and inner axially extending portions 86 and 88. The seal 90 is interposed between the outer axially extending portion 86 and the surface 50 of the second portion 46 of the sheave 26 so that a fluid chamber 92 is defined within the sheave 26 and this chamber Is preferably formed of a low porosity metal (eg, steel or iron) and more specifically between the cap member 54, the portion of the sheave 26, and the first axial surface 80 of the piston 76. is there. As will be described in further detail below, the piston 76 is adapted to selectively shift axially relative to the sheave 26 for engagement and disengagement of the rotation control device 10.

  In a preferred form of the invention, the seal 90 is secured to the sheave 26. More specifically, the axially extending annular protrusion 94 of the reaction plate 96 presses the seal 90 against the sheave 26. Of course, while adapting to some axial movement of the seal 90, it should be readily understood that the seal 90 can be supported by the piston 76 itself and the engagement surface 50. In any case, the piston 76 is slidable along the axial surface of the protrusion 94, the seal 90 and the second portion 46 of the sheave 26. The seal 90 preferably takes the form of a multi-cup seal and is disposed at the outermost portion of the fluid chamber 92 so that a viscous fluid (e.g., grease or other lubricant) is activated by the rotation controller 10. In between, there is a tendency to flow radially outward and immerse the seal 90. The reaction plate 96 includes an outermost peripheral flange portion 100 that is adapted to be axially bolted to the second portion 46 of the sheave 26. More particularly, the friction lining 102 defines a first friction engagement surface of the rotation control device 10 and receives a round head cap screw 104 that also extends through the flange portion 100 and of the sheave 26. The second part 46 is threadably received. Thus, tightening the screw 104 secures the friction lining 102 and reaction plate 96 to the sheave 26 and holds the annular seal 90 securely in the desired position.

  The reaction plate 96 includes an inner, axially extending annular portion 108 that includes a dust seal 110 and assists in defining a plurality of annularly spaced cavities 112. In a preferred embodiment, twelve such cavities 112 are equally spaced annularly in the reaction plate 96 and the walls of the cavities 112 define ribs, which structurally define the reaction plate 96. Reinforce. Each of the cavities 112 is adapted to receive a compression spring 116 that extends between the reaction plate 96 and the second axial surface 82 of the piston 76. Due to the presence of the spring 116, the piston 76 is biased towards the shaft portion 22 but through the passage 72, the rotary joint 68, and the coupling 62 defining the fluid path into the fluid chamber 92. The delivered fluid pressure may cause a shift of the piston 76 relative to the sheave 26 against the biasing force of the spring 116. During this axial shift, the piston 76 also slides relative to the reaction plate 96, where the axially extending portion 88 inside the piston 76 is the axially extending portion 108 inside the reaction plate 96. Guided along. In the most preferred form of the invention, this interface between piston 76 and reaction plate 96 comprises a friction reducing, TEFLON® infiltrated ceramic / metal coating applied by thermal spraying. Such an arrangement uses a lubricant (eg, grease, which tends to ooze out to the friction surface and can affect the engagement / disengagement forces for the rotation control device 10). It is considered more advantageous. This may be of particular relevance given to the intended field of use of the rotation control device 10 and the fact that dust can easily adhere to and enter any lubricant used. Also, adjacent radial surfaces of piston 76 and reaction plate 96 are not machined along a radial plane and have a spiral shape to provide stress relief.

  The rotation control device 10 also includes a second output member 120 that has a first outer radial section 124 that interconnects with a second inner radial section 128. The first radial section 124 is associated with a second friction lining 132 that is disposed in juxtaposition with the friction lining 102. In the most preferred form of the invention, the second friction lining 132 is comprised of a disk formed from steel or other hardened metal and is disposed within the insert mold when the second member 120 is formed. In this manner, the second friction lining 132 and the second member 120 are united. In the most preferred form of the invention, the second friction lining 132 is preferably in an inverted L shape as shown in FIG. 1, which assists in holding the lining 132 in place. The second friction lining 132 is also preferably formed with various radially concentric teeth 133 to enhance the heat transfer of the second friction lining 132 to the second member 120 and the two Increase the adhesion area between components. A disk-shaped lining 134 is also provided with various bores 134 that open to the sides of the second member 120 to allow the material of the second member 120 to flow into the bore during the molding / casting process. Can be possible. Accordingly, the bore 134 creates a peg and prevents relative rotation between the lining 132 and the second member 120. The friction lining 132 is preferably made of steel or iron, but the second member 120 is preferably made of aluminum, thereby making it lightweight and easy to make and machine, and inertial, overall Weight and reduced wear objectives are achieved. For similar reasons, the piston 76 and the reaction plate 96 are also preferably made of aluminum. However, it should be understood that the piston 76, reaction plate 96, and / or second member 120 may be formed as an integral one-piece casting of other materials such as cast iron.

  With this arrangement, the friction linings 102 and 132 define first and second friction engagement surfaces that are adapted to abut one another when the rotation control device 10 is engaged. The second member 120 is adapted to be installed using a threaded stub shaft 136 having a head portion 142. More particularly, the threaded stub shaft 136 is constituted by a jack bolt having a torque attachment and is adapted to be threadably received within an installation hub 144 defined in the center of the inner radial portion 128. The The installation hub 144 is preferably integrally formed with the cast-in steel insert 143, which is actually screwably attached to the stub shaft 136. An installation hub 144 is also provided with a shoulder 145 against which the inner race of the second bearing unit 146 is arranged. The second bearing unit 146 has an outer race that is press fit against the thermal expansion control insert 147, cast integrally with the piston 76, and in one axial direction the piston. This outer race is held in its desired position by a snap ring 148.

  During subsequent stages of assembly of the rotation control device 10, the piston 76 is inserted into the second portion 46 of the sheave 26, and then the reaction plate 96 (spring 116 is disposed in the cavity 112) is attached by screws 104. It is fixed to the sheave 26. With the stub shaft 136 extending through the second bearing unit 146, the second bearing unit 146 is press fit into the insert 147 and abuts against the piston 76. Thereafter, the snap ring 148 is inserted to maintain the outer race of the second bearing unit 146 in the axial direction. It should be realized that, due primarily to the configuration of the reaction plate 96, after the second bearing unit 146 is attached to the piston 76, the piston 76 can be inserted into the sheave 26 as well. Next, the second member 120 is inserted into the bearing unit 146. Thereafter, torque is applied to the stub shaft 136 to rotate the shaft and retract the second member 120 into the second bearing unit 146 until the shoulder 145 contacts the inner race of the second bearing unit 146. In tightening the threaded stub shaft 136 to the installation hub 144, the head portion 142 engages the inner race of the second bearing unit 146 so that the inner race is between the head portion 142 and the shoulder 145. Held in between. Due to this installation arrangement and the presence of the second bearing unit 146, the piston 76 and the second member 120 can rotate relative to each other. Further, since the second bearing unit 146 is in a radially inner position, contaminants and friction lining dust flow radially outward due to centrifugal forces generated during operation of the rotation control device 10, There is a tendency to move away from the second bearing unit 146. The second member 120 is also provided with a plurality of annularly spaced threaded shafts or studs 150 at the location of the second radial section 128, which are preferably within the second member 120. Combined. In the most preferred form of the invention, the rotation control device 10 builds a frictional fan clutch so that the threaded shaft 150 is adapted to install and receive a fan blade ring secured to the second member 120. Is done.

  With this configuration, the first portion of the sheave 26 is adapted to be driven in a manner that rotates relative to the journal bracket 14. Driving the sheave 26 also causes the reaction plate 96 and the first friction lining 102 to rotate. Further, although there is no spline connection between the piston 76 and the reaction plate 96 or sleeve 26, the piston 76 is generally rotated together with these components due to the placement and placement of the spring 116. . However, at least partial relative rotation is permitted between the piston 76 and both the sheave 26 and the reaction plate 96, and the second bearing unit 146 is between the piston 76 and the second member 120. It should be understood that it accommodates relative rotation.

  When used as a clutch (where rotation is enabled by both the sheave 26 and the second member), the spring 116 causes the piston 76 to engage the first frictional engagement surface defined by the frictional linings 102 and 132. And a position to be engaged between the second friction engagement surface and the second friction engagement surface. However, pressurized fluid may be introduced into the fluid chamber 92 to shift the piston 76 in the longitudinal direction of the device. Due to the internal engagement between the piston 76 and the second member 120 passing through the second bearing unit 146, the longitudinal shift of the device of the piston 76 relative to the sheave 26 causes the second member 120 to simultaneously move the longitudinal axis of the device. Shift in direction. The longitudinal shift of the device of the second member 120 disengages between the friction linings 102 and 132, thereby disengaging the clutch operation of the rotation control device 10.

  In this regard, the first axial side surface 80 of the piston 76 is flat (ie, non-annular) and substantially larger in radial dimension (ie, greater than the diameter of the first location 42 of the sheave 26). Note that it has dimensions). This structure establishes a large piston area that is actuated by pressurized fluid introduced into the fluid chamber 92. Thus, this large piston area allows a high disengagement force to be deployed in the rotation control device 10 at a given fluid pressure, while the large spring force quickly engages with less sliding and wear. Makes it possible to combine.

  In the most preferred form of the invention, air is utilized as the fluid pressurization source. However, it should be readily appreciated that other fluids (working fluids) can be utilized. In addition, other types of starting systems, including mechanical and spiral starting systems known in the art, can be readily incorporated without departing from the present invention. In the case of a vortex starter system, the magnet can simply be provided on a reaction plate 96 such as a compression spring 116 and is actuated by a drive ring on the second member 120. In any case, the spring 116 and fluid or other piston shifting system function to axially shift the piston 76 relative to the sheave 26, and in the form of the invention, between the sheave 26 and the second member 120. It is important to note that it is selectively disengaged. Therefore, when the pressure decreases, the rotation control device 10 enters a fail safe, that is, engagement mode.

  When the sheave 26 and the second member are engaged, a force transfer occurs at an outer radial position of the rotation control device 10. More specifically, these forces are transferred directly between the sheave 26 and the second member 120 through the friction linings 102 and 132. In this arrangement, the second bearing unit 146 is not overfilled during operation of the rotation control device 10, so that it is possible to extend the service life of the second bearing unit 146.

  In this respect, the rotation control device 10 of the present invention is used to ensure that the second member 120 is rotated again by using, for example, the thread shaft 150 or another structure of the same size. It can also function as a braking device. However, securing the second member 120 via the threaded shaft 150 is further necessary to match the shaft shaft in harmony with the piston 76. With such an arrangement, the engagement between the frictional linings 102 and 132 causes the rotating sheave 26 to break. The sheave 26 and the second member 120 can be selectively passed through other structures that bias the frictional rises 102 and 132 (eg, through the use of cam teeth, etc.) without departing from the spirit of the present invention. It should further be appreciated that they can be interconnected.

  In the embodiment of FIG. 1, the spring 116 biases the piston 76 into a position that engages between the frictional rises 102 and 132. FIG. 2 shows an alternative embodiment constructed in substantially the same way as the first example. However, here, the corresponding spring 116 is used to bias the rotation control device 10a to the disengaged position. According to this embodiment, the mounting ring 154 secures the sheave 26 corresponding to the reaction plate 96a therebetween. The mounting ring 154 is formed at a pair of axially spaced positions 158 and radially extending positions 159. Position 158 actually receives bolt 160 to interconnect the sheave 26, reaction plate 96a and mounting ring 154 together. On the other hand, the radially extending positions 159 of the mounting ring 154 actually define the first frictional engagement surface for the rotation control device 10a of this embodiment. A corresponding second member 120 a is provided on the radial flange 164 positioned in the undercut region generally defined by the position 159 of the mounting ring 154. The radial flange 164 holds a frictional rising 165 adapted to engage the position 159 of the mounting ring 154 to interconnect the sheave 26 and the second member 120a.

  Due to the positioning of the radial flange 164 between the sheave 26 and the position 159 of the mounting ring 154, the spring 116 biases the piston 76a in a direction that disengages the sheave 26 from the second member 120a. To provide a more precise arrangement, piston 76a is provided with a cavity 112a corresponding to each of springs 116 and a linear bearing surface 168 on which spring 116 acts on counteracting plate 96a.

  Except for the small differences described above, the embodiment of FIG. 2 is approximately the same size as the embodiment of FIG. However, due to the presence of the mounting ring 154 and the arrangement of the radial flange 164, the spring 116 actually moves the rotation control device 10a to the disengaged position by simultaneously shifting the piston 76a and the second member 120a in the axial direction. Be biased. By introducing pressurized fluid into the fluid chamber 92, the piston 76a and the second member 120a are simultaneously shifted, thereby interconnecting the sheave 26 with the second member 120a. For completeness, the mounting ring 154 is provided with a plurality of annularly spaced fins 170 for thermal radiation and intensity effects, and the corresponding fins (not labeled) are the cap members 54 and In the embodiment of FIG. 1, for example, it may be provided along the outer position of the second member inclined in the axial direction.

  Many extensions and modifications will now be apparent to those skilled in the art, as illustrated by the basic teachings of the present invention. For example, although the present invention is described with respect to a friction clutch as described above, it should be understood that these teachings may be applied to other types of torque transfer and / or rotation control devices (eg, brakes). It is. Furthermore, the rotation control device 10 and the most preferred form 10a have several unique features that are believed to produce synergistic results, such features being utilized separately or in other combinations. obtain.

  In general, the structural features of the present invention are provided to extend the useful life of the device. Due to the lack of shaft filling located on the bearing unit and the elimination of high wear materials such as splines, the rotation control device is substantially maintenance free. When used as a car fan clutch, the rotation control device is expected to last well beyond the full life of the car.

  Regardless of this particular use, the invention disclosed herein may be used in another specific form and described herein without departing from the spirit or its general characteristics. Each embodiment is considered in each example and is not limited. In particular, the scope of the present invention should be indicated not by the above description but by the appended claims, and the meaning equivalent to the claims and all changes in the central part within the scope are included in the claims. It is intended to be included in

  A rotation control device that does not require a spline is provided. This rotation control device can be applied to a friction clutch device or the like.

FIG. 1 is a cross-sectional view of a rotation control device constructed in accordance with a first preferred embodiment of the present invention. FIG. 2 is a cross-sectional view of a rotation control device constructed in accordance with a second preferred embodiment of the present invention.

Explanation of symbols

14 Journal bracket (support mount)
22 Shaft portion 26 Sheaves 30 and 146 Bearing unit 42 Hub portion 68 Rotary joint 76 Pistons 102 and 132 Friction lining 92 Fluid chamber 96 Reaction plate 120 Second member of rotation

Claims (7)

A rotation control device ,
First and second relative rotating members ;
A Lupi piston includes a radial portion and a portion extending in the axial direction of the inner, said first member includes a portion extending portions extending in the axial direction of the piston to slidably you support collar shaped axial and Lupi Ston,
And one spring even without least interposed between said first member and a radial portion of said piston,
And heart installed hub in that will be formed as part of said second member,
A first bearing unit you interposed between the installation hub portion and said second member extending in the axial direction of the piston, said first bearing unit, each of the said piston and said second member attached to, to permit relative rotation between said piston and said second member, while the for axial movement of the simultaneous relative said first member, to interconnect the piston and said second member and behenate a ring unit,
A first and second engagement surfaces Ru are provided respectively in said first and second members, when the piston is shifted in the axial direction, the said second engaging surface, said first engagement in contact with the engagement surface, the rotation controller having a combination of a selective engagement surface Ru is interconnected to said first and second relatively rotatable members. The rotation control device according to claim 1, wherein the radial portion of the piston is disk-shaped and non-annular. The rotation control device according to claim 2, further comprising a combination of jack bolts extending through the first bearing unit and threadably secured to an installation hub of the second member. 4. The rotation control device according to claim 3, in combination, further:
A journal having a shaft portion; and a second bearing unit, wherein the second bearing unit is configured to rotatably support the first member on the journal. A rotation control device comprising a second bearing unit interposed therebetween. The rotation control device according to claim 1, in combination, further:
A jack bolt extending through the first bearing unit, wherein the installation hub comprises a central threaded opening for threadably receiving the jack bolt, the first bearing unit A rotation control device comprising: a jack bolt that is sandwiched between the jack bolt and the installation hub. The rotation control device according to claim 1, wherein the spring moves the piston to cause engagement between the first engagement surface and the second engagement surface. The rotation control device according to claim 1, wherein the spring moves the piston to cause disengagement of the second engagement surface from the first engagement surface.

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