KR20070101945A - Reverse input clutch bearing assembly - Google Patents

Abstract

The present invention relates to an anti-backlash clutch bearing assembly, the configuration of which can be slid between an inner ring and an outer ring arranged to have concentric raceway surfaces of different radii, and an outer ring surface facing the inner ring and the outer ring. A plurality of rolling elements arranged in a circumferential manner, a retainer for supporting them so that the arrangement of the rolling elements can be maintained, and coupled to each other in contact with one of the inner and outer rings to maintain a clearance in the rotational direction thereof. A pair of control wheels, each of which is controlled in the axial direction and the rotation direction so as to maintain a relative difference in rotational speed between the inner wheel, the outer ring and the control wheel, and transmits or blocks torque between the two members selected therefrom. According to the clutch bearing assembly of the present invention, characterized in that it comprises a wedge ring assembly In this case, the rotational force input from the input shaft can be smoothly transmitted to the output shaft, and the rotational force inputted from the output shaft can be operated without any external control by itself and can be transmitted to the input shaft by locking or separating the output shaft. There is an effect that can perform all the functions as a bearing.

Description

Reverse input blocking clutch bearing assembly

1 is a front side perspective view showing the combined appearance of the inner ring control reverse input prevention clutch bearing assembly according to a preferred embodiment of the present invention.

Figure 2 is a rear side perspective view showing the combined appearance of the inner ring control reverse input prevention clutch bearing assembly according to a preferred embodiment of the present invention.

Figure 3 is an exploded perspective view of the disassembled and arranged the elements of the respective parts of the inner ring control reverse input prevention clutch bearing assembly according to a preferred embodiment of the present invention.

Figure 4 is a front view showing the combined appearance of the inner ring control reverse input prevention clutch bearing assembly according to a preferred embodiment of the present invention.

FIG. 5 is a partially enlarged view of the cross-sectional view of the V-V line and the main part of FIG. 4.

FIG. 6 is a cross-sectional view taken along the line VI-VI of FIG. 5.

FIG. 7 is a cross-sectional view taken along line VII-VII of FIG. 5.

8 is an exploded perspective view showing the structure of a rotational direction locking cam applied to the inner ring control type reverse input prevention clutch bearing assembly.

FIG. 9 illustrates that power is transmitted during positive input from the input side control wheel side to the output side inner wheel side by the configuration of an example in which the inner wheel control type reverse input prevention clutch bearing assembly is applied, and vice versa. Schematic longitudinal section showing the principle of operation being locked.

10 is a conceptual view for explaining the principle of operation of restoring the axial wedge ring to the forward or neutral position by the interlocking of the inner ring and the control wheel and the axial drive cam included in the configuration of the inner ring control type reverse input clutch bearing assembly; to be.

11 and 12 are locked or separated as the rotating direction wedge ring is rotated forward and reverse by interlocking the inner ring and the rotating direction wedge ring and the rotating direction locking cam included in the inner ring control type reverse input prevention clutch bearing assembly. This is a conceptual diagram to explain the principle that works in the form of.

FIG. 13 illustrates that power is transmitted during positive input from the input side inner ring side to the output side outer ring side by the configuration of another example in which the inner wheel control type reverse input prevention clutch bearing assembly is applied; Schematic longitudinal section showing the principle of operation that is separated.

FIG. 14 is an exploded perspective view illustrating disassembled and arranged elements of each part of the outer ring controlled reverse input prevention clutch bearing assembly according to the preferred embodiment of the present invention.

15 is a front view showing the combined appearance of the outer ring controlled reverse input prevention clutch bearing assembly according to a preferred embodiment of the present invention.

FIG. 16 is a cross-sectional view taken along the line XVI-XVI of FIG. 15.

17 is a cross-sectional view taken along the line X'-X 'of FIG.

FIG. 18 is a cross-sectional view taken along line XVIII-XV in FIG. 16. FIG.

19 is a rear perspective view showing the structure of a control wheel applied to the outer ring control type reverse input prevention clutch bearing assembly.

FIG. 20 illustrates that power is transmitted during positive input from the input side control wheel side to the output side outer ring side by the configuration of an example in which the outer ring control type reverse input prevention clutch bearing assembly is applied, and vice versa. Schematic longitudinal section showing the principle of operation being locked.

Figure 21 is a lock type while the rotation direction wedge ring or axial wedge ring is rotated forward and reverse by interlocking the control wheel and the outer ring and the rotational locking cam and retainer included in the configuration of the outer ring control type reverse input prevention clutch bearing assembly Or conceptual diagram for explaining the principle of operation in the form of a detachable.

22 is a principle that the wedge ring is rotated in a forward or reverse direction by a relative rotational movement of the outer ring, the rolling element, and the retainer included in the outer ring control type reverse input prevention clutch bearing assembly. A conceptual diagram for explaining.

FIG. 23 illustrates that power is transmitted during positive input from the input side outer ring side to the output side inner ring side by the configuration of another example in which the outer ring control type reverse input prevention clutch bearing assembly is applied, and vice versa. Schematic longitudinal section showing the principle of operation that is separated.

24 is a perspective view of each shape illustrating the rolling elements of various shapes applied to the reverse input prevention clutch bearing assembly of the present invention.

25 is a front view illustrating the configuration of a rotational resistor that can be applied to the outer ring control type reverse input prevention clutch bearing assembly of the detachable structure according to the present invention.

FIG. 26 is a sectional view taken along the line XXVI-XXVI in FIG. 24.

27 is a front sectional view illustrating a configuration in which a manual operation lever for selectively setting the rotational direction of the inner ring is mounted on the control wheel side of the outer ring control type reverse input prevention clutch bearing assembly according to the present invention.

28 is a sectional view taken along the line XX'-XX 'of FIG. 27.

<Description of Symbols for Major Parts of Drawings>

d1; Clearance of the neutral position between the axial wedge ring and the rolling element

d2; Clearance of neutral position between axial wedge ring and inner ring

d3; Unidirectional gap between axial wedge ring and inner ring

d4; Normal gap between the inner circumferential surface of the rotational locking cam contact and the rotational locking cam

d5; Neutral gap between control wheel and outer ring locking cam seat

d6; Unidirectional gap between control wheel and outer ring locking cam seat

w; Rotational wedge width 1; Input shaft

2 ; Output shaft 2a; Output rotating body

3; Fixed shafts 10a, 10b, 110; Inner ring

11a, 11b, 21, 110a, 121a, 121b; Rolling element track surface

12, 122; Axial wedge ring contact surface 12a; Axial drive cam seating work

13; Coupling grooves 13a, 133; Rotation Cam Locking Groove

14; Rotational Neutral Restoration Springs

14a; Direction of rotation neutral return spring 15; Spline

15a; Rocking camshaft seating hole 15b; Snap ring seating groove

20, 120a, 120b; Outer ring 30, 130; Control wheel

31; Axial coupling hole 31a; Keyway

32, 131; Spline 32a; Axial guide groove

33, 111; Spline grooves 40, 140; Rolling elements

45, 145; Retainer 46, 146; Rolling element receiving hole

47, 83, 147, 183; Through holes 50 and 150; Rolling resistor

51; Fixing bracket 52; Manual Lever

60, 160; Fixture 70, 170; Axial wedge ring

71, 172; Inclined plane 72; Wonju Prize Home

73; Axial drive cam 74; Body part

75, 76; Eccentric shaft 80, 180; Rotary Wedge Ring

81, 181; Rotational direction locking cam contacts 82, 182; Rotary Wedge

84, 184; Rotational locking cam 85; Rocking camshaft

85a; Cam working surface 86; Cam spring

87, 187; Rotary Direction Wedge Neutral Restoration Spring

120c; Outer ring cover 123; Pushpin Seater

124; Outer ring locking cam seat 125a, 125b; Fastener

126; Fastener 132; Axial Wedge Ring Support

134; Pressurized protrusion 171; Ring flange

173; Axial Wedge Neutral Restoration Spring

174a; Pushpin 174b; Lubricating Ball

The present invention relates to a clutch bearing assembly for preventing reverse input, in particular, the present invention allows the rotational force input from the input shaft to be smoothly transmitted to the output shaft while operating itself without the need for external control against the rotational force input from the output shaft. The present invention relates to a reverse input preventing clutch bearing assembly which is prevented from being transmitted to an input shaft by being locked or separated.

In general, a traditional clutch means a device in which two or more wide friction surfaces are combined to transmit and block power, or to be separated or combined to allow or prevent rotation.

However, such a conventional clutch should be provided with a large friction surface for smooth power transmission, and should be provided with a power source such as hydraulic pressure required for operation along with a control element for controlling its operation. In addition, when unexpected rotational force in an arbitrary direction is transmitted from the output side (referred to as reverse input), there is a fear that the equipment installed on the input side may deviate or be damaged.

In order to solve this problem, the proposed mechanical elements include a one-way clutch that self-controls the transmission or slipping of power according to the rotational direction of the input shaft. There is this.

However, these one-way clutches do not require a control element such as hydraulic pressure for operation, can be used to drive each part in one direction, and have the advantage of preventing reverse rotation of each part, while the one-way clutch engages. According to the configuration, when the rotational force is transmitted from the output shaft (reverse input) in the power transmission direction, there is a problem that the equipment installed on the input shaft may leave the set position or be damaged.

A device proposed to improve such a reverse input problem is a Sprag type reverse locking clutch of the US Formsprag. The reverse input prevention clutch is configured so that the sprag does not contact the housing (fixed body) by the rotation of the input shaft, thereby transmitting power to the output shaft, and the rotational force of the output shaft operates to lock the output shaft to the contact shaft. It is to cut off power transmission to the input shaft. The reverse input prevention clutch has a structure in which a configuration is divided into a bearing portion and a clutch portion, a ball is provided in the bearing portion, and a sprag is provided in the clutch portion, respectively, and a control element necessary for operation is not necessary.

In addition, another apparatus for improving the reverse input problem is a reverse input prevention clutch (TORQUE DIODE ™) proposed by US Pat. No. 6,695,118 and NT Publication No. 2003/0000796 of NTN Japan. . The reverse input prevention clutch is configured to prevent the reverse input by locking the output shaft or blocking the power transmission by using a roller, a pocket is installed between the input shaft and the output shaft, the roller is fitted in the pocket However, this structure has a problem in that the clutch is separated and the input shaft and the output shaft cannot support the load at the moment of relative rotation.

Therefore, in applying the conventional anti-backlash clutches proposed to date, since the bearing and the clutch to support the load can only be installed, the rollers must be configured in the form of a double row such as 2 to 3 rows, As a result, the number of parts required for the production of the product increases significantly, leading to an increase in the manufacturing cost, and the productivity decrease due to the increase in the number of assembly processes, as well as the size of the product has to be enlarged.

The present invention has been made to solve the above-mentioned problems, the object of the invention, while the rotational force input from the input shaft to be smoothly transmitted to the output shaft while operating in itself without additional external control for the rotational force input from the output shaft To prevent the input shaft from being transmitted to the input shaft by locking or disconnecting the output shaft, and to provide a high mechanical reliability while achieving a lightweight and compact structure, thereby providing a reverse input prevention clutch bearing assembly as a basic mechanical element. .

Another object of the present invention is to provide a reverse input preventing clutch bearing assembly operable as a one-way clutch capable of selecting a locking direction.

Still another object of the present invention is to implement a selected one of the functions as the reverse input locking device, the reverse input separating device or the one-way clutch device capable of locking direction control, and at the same time to operate as a bearing. To provide a reverse input prevention clutch bearing assembly.

In order to achieve the above object, the reverse input prevention clutch bearing assembly according to the present invention includes an inner circumferential surface and an outer ring arranged to have concentric raceway surfaces of different radii, and an outer circumferential surface of the inner and outer race surfaces is slid. A plurality of rolling elements arranged in a circumferential manner so as to be circumferential, a retainer supporting them so that the arrangement of the rolling elements can be maintained, and contacting any one of the inner and outer rings to maintain a clearance in the rotational direction thereof, and to be interoperable with each other. As long as the rotation is controlled in the axial direction and the rotational direction so as to maintain the relative control speed between the combined control wheel and the inner and outer wheels and the control wheel, the torque is transmitted or interrupted between the two selected members. It characterized in that it comprises a pair of wedge ring assembly.

In addition, it is preferable that the fixing body for fixing the rotation to any one of the inner ring and the outer ring is combined.

In addition, the fixing body is preferably made of a housing.

In addition, the fixed body is preferably a fixed shaft that is fitted with the inner ring and the outer ring.

In addition, the rolling element is preferably made of a cylindrical roller in contact with the raceway surface of the inner ring and outer ring.

In addition, the control wheel, which is installed in contact with the inner ring side, the power transmission body which can be combined in a pair with a multi-faceted corresponding power transmission body formed on the circumference of the inner ring is formed on the circumference of the control wheel It is preferable that the power transmission is made while forming a rotational direction gap when the two power transmission dies are coupled to each other and delayed by the gap.

In addition, the control wheel, which is installed in contact with the outer ring side, a power transmission body that can be combined in a pair with a multi-faceted corresponding power transmission body formed on the circumference of the outer ring is formed on the circumference of the control wheel, It is preferable that the transmission in the rotational direction is formed at the time of coupling between the two power transmission dies so that power transmission is achieved while delaying by the clearance.

In addition, the power transmission body is preferably made of a spline and a spline groove.

In addition, the control wheel, when combined with any one of the inner ring and the outer ring in the absence of external power, the rotation direction neutral restoring to be automatically centered (centering) at the same clearance so that both side wall surfaces do not contact each other It is preferable that the spring is further provided.

In addition, the rotational direction neutral restoring spring is preferably made of a coil spring.

In addition, the control wheel is drawn together with the rotation of the input shaft with rotational resistance, such as physical frictional force with the surface of the stationary body on which the control wheel is separately supported when either the inner or outer ring is engaged with the input shaft. It is preferable that the rotation resistor is made to be further provided to enable the rotation.

In addition, the rotational resistor, it is preferable that both ends are clamped by a fixing body provided on one side to surround the outer periphery of the control wheel and have a structure of a ring clamp to induce frictional resistance between the contact surface.

In addition, it is preferable that one side of the circumference of the control wheel is further provided with a manual operation lever capable of setting the rotational direction of the inner ring in either direction by manual operation.

In addition, the wedge ring assembly has an inclined surface in the axial direction that corresponds to an inclined surface formed on one of the inner and outer rings of the inner ring and the inner ring by an axial movement stroke that moves forward and returns to its original position along an axial direction. And an axial wedge ring in which the degree of close contact with one of the inclined surfaces of the outer ring is changed, and return means for returning the axial wedge ring to its original position without applying external power, and concentrically adjacent the retainer. A rotational wedge formed to face a circumferential surface of the rolling element and capable of interlocking with the axial wedge ring, the rotational wedge being disposed to receive a portion of the rolling element and limit the rotation of the rolling element. Rotational wedge ring, and the retainer and the rotational direction wedge ring rotates when a greater rotation force than a predetermined elasticity Rotational wedge ring neutral restoring spring that provides elastic coupling force so that the retainer and the rotational wedge ring rotate together at different rotational speeds, and rotational locking cam that elastically links the rotational wedge ring and the control wheel. It is preferred that made, including.

In addition, the return means for the axial wedge ring, the cylindrical central body portion is accommodated in the seating hole formed in a plurality of through holes at equal intervals along the circumferential predetermined line of the inner ring, the central body portion is unevenly distributed on both sides of the cylindrical end portion And an eccentric shaft protruding from each other is inserted between the circumferential guide groove formed along the circumference of the axial wedge ring and the axial guide groove formed on the circumference of the control wheel, so as to eccentrically rotate the seat hole of the inner ring as the center of rotation. It is preferable that the axial drive cam is formed.

In addition, the return means of the axial wedge ring is disposed adjacent to one side of the axial wedge ring, the axial wedge ring neutral in the form of a ring-shaped leaf spring that directly presses the axial wedge ring in the axial direction by contact. It is preferable that the restoration spring is made.

Further, the axial wedge ring neutral restoring spring is disposed on an opposite side thereof with the axial wedge ring interposed therebetween to push the axial wedge ring in the direction in which the axial wedge ring neutral restoring spring is compressed. It is preferable that the push pin forms a pair with the pin, and the push pin is coupled to move forward and backward along the seating hole formed through the outer ring in the axial direction when the control wheel rotates.

In addition, the rotation direction locking cam, the locking cam shaft formed by the cam action surface is unevenly distributed on one side, and the locking cam shaft is coupled to the circumference of the control wheel to return the locking cam shaft to the left and right sides to rotate or return to the original state It is desirable to include a cam spring that provides elasticity so that it can be.

In addition, the rotation direction locking cam is preferably made of a spring bent in the 'W' shape.

Hereinafter, the reverse input prevention clutch bearing assembly according to the preferred embodiment of the present invention will be described in detail with reference to the accompanying drawings.

1 to 28 are shown in detail in various forms the apparatus configuration, operation principle and application examples of the reverse input prevention clutch bearing assembly according to various embodiments of the present invention, Figures 1 and 2 Front and rear perspective views showing the combined shape of the inner ring control reverse input prevention clutch bearing assembly according to the embodiment, FIG. 3 is an exploded arrangement of the respective elements of the inner ring control reverse input prevention clutch bearing assembly according to the embodiment. 4 is an exploded front view showing a combined appearance of an inner ring control reverse input prevention clutch bearing assembly according to the embodiment, FIG. 5 is a sectional view taken along line V-V of FIG. 6 is a sectional view taken along the line VI-VI of FIG. 5, FIG. 7 is a sectional view taken along the line VII-VII of FIG. 5, and FIG. 8 is a rotating room applied to the inner ring control type reverse input preventing clutch bearing assembly according to the embodiment. 9 is an exploded perspective view showing the structure of the directional locking cam 84. FIG. 9 shows the inner ring 10a from the output side control wheel 30 by the configuration of an example in which the inner ring control reverse input prevention clutch bearing assembly according to the embodiment is applied. Fig. 10 is a schematic longitudinal sectional view showing the principle of operation in which power is transmitted at positive input to the reverse direction and vice versa at reverse input, in which the driving is stopped and locked. FIG. 10 is a configuration of the inner-wheel control type reverse input prevention clutch bearing assembly. Concept diagram for explaining the operation principle of restoring the axial wedge ring 70 to the forward or neutral position by the interlocking of the inner ring 10a, 10b, the control wheel 30, and the axial drive cam 73 included. 11 and 12 are rotated by the interlocking of the inner ring (10a) (10b) and the rotational direction wedge ring 80 and the rotational direction locking cam 84, etc. included in the configuration of the inner ring-controlled reverse input clutch bearing assembly Directional wedge ring 80 Concept diagram for explaining the principle of operating in the form of locking or detaching type while being rotated reversely, FIG. 13 shows the inner ring-controlled reverse input prevention clutch bearing assembly according to another example configuration from the input side inner ring (10a) (10b) side. Fig. 14 is a schematic longitudinal sectional view showing the principle of operation in which power is transmitted at the positive input to the output side outer ring 20 and vice versa, at the reverse input, the drive is cut off and separated. An exploded perspective view of disassembled and arranged the elements of the outer ring control type reverse input prevention clutch bearing assembly according to the embodiment, Figure 15 is a front view showing the combined appearance of the outer ring control type reverse input prevention clutch bearing assembly according to the embodiment; 16 is a cross-sectional view taken along the line XVI-XVI of FIG. 15, FIG. 17 is a cross-sectional view taken along the line X′-X ′ of FIG. 16, FIG. 18 is a cross-sectional view taken along the line X′-X ′ of FIG. 16, and FIG. Back perspective view showing the structure of a control wheel 130 applied to a controlled reverse input prevention clutch bearing assembly, and FIG. 20 shows an example configuration in which the outer ring controlled reverse input prevention clutch bearing assembly is applied. Fig. 21 is a schematic longitudinal cross-sectional view showing the operation principle in which power is transmitted at the positive input to the output side outer rings 120a and 120b, and vice versa. Rotational direction wedge ring 180 or axial direction by interlocking control wheel 130 and outer ring 120a, 120b, rotational direction locking cam 184, retainer 145, etc. included in the configuration of the prevention clutch bearing assembly Conceptual diagram for explaining the principle that the wedge ring 170 is operated in the form of a lock type or a detachable type while being rotated forward and reverse, FIG. 22 is a configuration of the outer ring control type reverse input prevention clutch bearing assembly. The rotational direction of the wedge ring 180 is rotated forward and backward by the relative rotational movement of the outer ring (120a) (120b) and the rolling element 140 and the retainer 145, such as a lock type or a detachable type 23 is a conceptual diagram for explaining the power is transmitted from the input side outer ring 120a, 120b side to the output side inner ring 110 by the configuration of another example in which the outer ring control type reverse input prevention clutch bearing assembly is applied. On the contrary, the reverse input is a schematic longitudinal cross-sectional view showing the operating principle in which the driving is blocked and separated, respectively, and FIG. 24 shows a rolling element 40 having various shapes applied to the reverse input preventing clutch bearing assembly of the present invention. 25 is a perspective view of each form illustrating the 140, Figure 25 is a configuration of a rotational resistor 50 that can be applied to the outer ring control type reverse input prevention clutch bearing assembly of the separable structure according to the present invention 26 is a cross sectional view taken along the line XXVI-XXVI of FIG. 24, and FIG. 27 is a rotational direction of the inner ring 10 selectively on the control wheel 30 side of the outer ring control type reverse input prevention clutch bearing assembly according to the present invention. 28 is a sectional view taken along line XX'-XX 'of FIG. 27, illustrating a configuration in which the manual operation lever 52 for setting is mounted.

Prior to explaining the structure of the present invention, for convenience, the position of the control wheel 30 is in contact with the rolling element 40 together with the inner ring (10a) (10b) for the purpose of distinguishing the embodiments of the present invention. This is referred to as an 'inner ring controlled clutch bearing assembly (see FIG. 3)', and the outer ring controlled clutch bearing assembly forms a structure in which the position of the control wheel 130 is in contact with the rolling element 140 together with the outer rings 120a and 120b. (See FIG. 14).

In addition, the material of each component provided in the embodiment of the present invention may be applied by selecting or combining plastic, ceramic, steel or alloy steel.

First, the configuration illustrated in FIGS. 1 to 13 implements a preferred embodiment of the inner ring control type reverse input prevention clutch bearing assembly, and the control wheel 30 has a clearance in the rotational direction with the inner rings 10a and 10b. It has a gap between the interlocking splines 15, 32, and is coupled to allow power transmission (see mainly the exploded perspective view of FIG. 3 and the coupling cross-sectional view of FIG. 5).

Inner ring control reverse input prevention clutch bearing assembly according to the present invention, as shown in Figures 1 to 4, the inner ring (10a) (11a, 11b, 21) arranged to have concentric circular raceway surfaces (11a, 11b) of different radius ( 10b) and a plurality of circumferentially arranged so that the outer circumferential surface is slidable between the outer ring 20 and the opposite raceway surfaces 11a, 11b, 21 of the inner ring 10a, 10b and outer ring 20. The rolling element 40, the retainer 45 for supporting them so that the arrangement of the rolling element 40 can be maintained, and the inner ring (10a) 10b in contact with the inner ring 10a (10b) to maintain the clearance in the rotational direction and to be mutually interoperable The rotation is controlled with respect to the axial direction and the rotation direction, respectively, so as to maintain a relative speed difference between the combined control wheel 30 and the inner ring 10a, 10b, the outer ring 20 and the control wheel 30. Includes a pair of wedge ring assemblies that transmit or block torque between two selected members It achieves the configuration.

In this configuration of the inner ring control type reverse input prevention clutch bearing assembly of the present invention, the inner ring (10a, 10b), as shown in Figure 3, the other in the engaging groove 13 of one inner ring (10a) The spline 15 of the inner ring 10b is fitted to form a single body. Inside the coupling groove 13 of the inner ring (10a) of the rotation direction locking cam exposure groove 13a through which the cam action surface 85a of the rotation direction locking cam 84 can be exposed to the outside, On the inner side surface of the one inner ring (10a) is formed a rotational direction neutral restoring spring receiving groove (14). On the inner circumferential surface of the other inner ring 10b, a spline 15 is formed as a multi-faceted corresponding power transmission die, and the spline 15 is provided with a locking cam shaft seating hole 15a and a snap ring seating groove 15b.

In addition, the outer ring 20 forms an outer casing capable of accommodating each component, and an inner circumferential surface of the outer ring 20 forms a rolling element raceway 21 as shown in FIG. 3.

One of the inner ring (10a) (10b) and the outer ring (20) may be coupled to the fixture 60 for fixing the rotation does not occur, for example, the housing shown in Figs. will be.

In addition, the rolling element 40 generally applies a cylindrical roller (b in FIG. 24) in contact with the raceways 11a, 11b and 21 of the inner ring 10a, 10b and the outer ring 20. In some cases, however, as shown in Fig. 24, a spherical cylindrical shape (a), a long-angle shape or a two-step inclined shape (c) (e), a spherical shape (d), and a (two step) stepped cylindrical shape ( f) It is possible to apply rollers such as (g). In addition, it is possible to apply rollers of various shapes such as cones and needles, and to design a track surface of a suitable shape according to the shape of the applied rollers. Of course, changes must be made. This is the same also in the embodiment of the outer ring controlled reverse input prevention clutch bearing assembly which will be described later.

In addition, the retainer 45, as shown in Figure 3, a plurality of rolling elements receiving hole 46 that can accommodate the rolling elements 40, and the rotation direction wedge ring neutral restoring spring for each position therebetween A plurality of through holes 47 that can accommodate 87 are formed.

In addition, the control wheel 30, which is installed in contact with the one side inner ring (10b) side, as shown in Figure 3, a multi-faceted corresponding power transmission formed on the circumference of the inner ring (10a) (10b) A power transmission mold that can be coupled to the mold (spline 15) in a pair is formed on the circumference of the control wheel 30, and when the coupling between the two power transmission bodies forms a rotational direction of play and is delayed by the play. It is formed to transmit power. That is, in the above embodiment, the corresponding power transmission bodies of the inner ring 10b are splines 32 and spline grooves 33, and the power transmission bodies of the control wheels 30 engaged with and coupled to the spline grooves and splines It is a structure consisting of (15). Although not shown in detail in the drawings, as the other power transmission member, a serration, a polygon rod, or one or more key grooves and keys may be applied.

On the spline 32 of the control wheel 30, an axial guide groove 32a capable of receiving one eccentric shaft 76 of the axial drive cam 73 is formed along the axial direction, and the control wheel ( On the inner circumferential surface side of 30, a shaft coupling hole 31 into which the input shaft 1 and the like can be inserted, and a key groove 31a for fixing the input shaft 1 are formed.

And, as shown in Figures 3, 5 and 7, the rotation direction neutral restoring spring receiving groove 14a is formed in one side of the control wheel 30 and the inner ring 10a. It is inserted into 14 to support the control wheel 30 and the inner ring 10a, 10b elastically at the same time. That is, in the rotational direction neutral restoring spring 14a in the form of a coil, both side wall surfaces of the splines 32 and 15 of the control wheel 30 and the inner ring 10b do not contact each other without applying external power. The control wheel 30 can be automatically centered at the same clearance within the inner ring 10b.

In some cases, when one of the inner ring 10a, 10b and outer ring 20 is coupled to the input shaft 1, as shown in Figure 13, one side of the control wheel 30 is supported separately Rotating resistor 50 may be installed to be rotated by the rotation of the input shaft 1 with the rotational resistance, such as physical frictional force with the surface of the fixed body (60). That is, the rotational resistor 50 may have a frictional resistance in contact with the fixed body 60 in the form of a brake shoe as shown in FIG. 13, or the outer ring control type application shown in FIGS. 25 and 26. As shown in the example structure, both ends are clamped by the fixing bracket 51 installed on one side to enclose the outer circumference of the control wheel 30, and a ring-type clamp or the like may be used to induce frictional resistance between the contact surfaces.

Alternatively, as shown in the structure of the outer ring control type application example shown in Figs. 27 and 28, on one side of the circumference of the control wheel 30, the rotational direction of the inner ring 10 is set in either direction by manual operation. Manual operation lever 52 may be further installed.

In addition, the wedge ring assembly, as shown in Figures 3 and 5, the return to move the axial wedge ring 70 and the axial wedge ring 70 to the original position when no external power is applied Means for axial drive cam 73, rotational wedge ring 80, rotational wedge ring neutral restoring spring 87 as a return means of the rotational wedge ring 80, and the rotational wedge ring ( 80) to achieve a structure including a rotation direction locking cam 84 for elastically interlocking between the control wheel 30.

In the wedge ring assembly, the axial wedge ring 70 corresponds to the axial wedge ring contact surface 12, which is an inclined surface formed on the circumference of the one inner ring 10a, as shown in FIG. A part having an inclined surface 71 in contact with the axial direction and having a close contact with the axial wedge ring contact surface 12 of the inner ring 10a by an axial movement stroke that moves forward and returns to its original position along the axial direction. to be. Inside the axial wedge ring 70 is formed a circumferential guide groove 72 along its circumference.

The inclined surface 71 of the axial wedge ring 70 has a large frictional resistance surface for contacting the axial wedge ring contact surface 12 of the inner ring 10a to generate a sufficient rotational force (torque). Innumerable fine irregularities can be formed to have.

The axial drive cam 73 has a cylindrical central body portion 74 is accommodated in the axial drive cam seating hole (12a) formed through a plurality of at regular intervals along the circumferential predetermined line of the inner ring (10a) The eccentric shafts 75 and 76 are formed to be unilaterally protruded on both sides of the cylindrical end portion of the central body portion 74, and the circumferential guide grooves 72 and the control wheels of the axial wedge ring 70 are formed. It is inserted between the axial guide grooves 32a formed on the circumference of 30 to form an eccentric rotation structure with the axial drive cam seating hole 12a of the inner ring 10a as the center of rotation, and such an axial drive cam ( 73 are provided radially in number.

The operating principle of the axial wedge ring 70 is a partial enlarged view of FIG. 5 and as shown in FIG. 10, in which the control wheel 30 is spaced in a rotational direction with the spline 15 toward one inner ring 10b. When rotating in one direction (for example, clockwise), the axial drive cam 73 is a central body portion 74 accommodated in the axial drive cam seating hole 12a of the other inner ring 10a as the center of rotation. Circumferential guide of the axial wedge ring 70 while one side of the eccentric shaft 76 is pulled by the axial guide groove 32a of the control wheel 30 to rotate together in one direction (counterclockwise direction). The other eccentric shaft 75 accommodated in the groove 72 also rotates at the same time, and the axial wedge ring 70 moves forward by the rotation of the eccentric shaft 75 so that the axial wedge of the inner ring 10a is rotated. The control wheel 30 is maintained by maintaining a close state between the ring contact surface 12 and the inclined surface 71 of the axial wedge ring 70. An inner ring (10a) (10b) is to be rotated in an environment with. On the contrary, when the control wheel 30 is stopped rotating, between the spline 32 of the control wheel 30 and the spline 15 of the inner ring 10b by the restoring action of the rotational direction neutral restoring spring 14a. Maintain a normal gap. In the figure, reference numeral d1 denotes a gap between the axial wedge ring 70 in a stationary state and the rolling element 40 in a neutral position, and d2 denotes an axial wedge ring 70 and an inner ring 10a and 10b in a stationary state. The gap in the neutral position of the liver, and d3 denotes the ubiquitous gap between the axial wedge ring 70 and the inner ring 10b after the minute rotation.

As shown in FIGS. 3 and 6, the rotational wedge ring 80 is disposed concentrically adjacent to the retainer 45 to accommodate a portion of the rolling element 40 and the rolling element ( Rotational direction wedges 82 capable of limiting the rotation of 40 are formed toward the circumferential surface of the rolling element 40 and disposed adjacent thereto so as to be interlockable with the axial wedge ring 70. One side of the circumference is formed with a ring-shaped rotational locking cam contact portion 81 which is in contact with the rotational locking cam 84, and between the rolling elements 40, the rotational wedge ring neutral restoring spring ( A plurality of through-holes 83 for installing 87 are formed. For reference, the rotational wedge 82 is arranged at that position in the rotational wedge width w shown in the partial enlarged view of FIG. 5.

The rotational wedge ring neutral restoring spring 87, as shown in Figure 3 and 7, when the retainer 45 and the rotational wedge ring 80 is rotated but a greater rotational force than a predetermined elasticity is applied to the The retainer 45 and the rotational direction wedge ring 80 are components that provide an elastic coupling force to be rotated together at different rotational speeds.

As shown in FIGS. 3, 6, and 8, the rotation direction locking cam 84 includes a locking cam shaft 85 formed with a cam working surface 85a on one side, and the locking cam shaft 85. Wrapping is coupled to the circumference of the control wheel 30 is composed of a structure comprising a cam spring 86 for providing elasticity to return the locking cam shaft 85 to the left and right sides or to the original rotation. The rotational direction locking cam 84 has a small width between the inner circumferential surface of the rotational direction locking cam contact portion 81 and the rotational direction locking cam 84, as shown in the left view of FIG. The normal gap d4 of is maintained.

In the inner ring control type reverse input prevention clutch bearing assembly having the structure as described above, the operation principle when the clutch bearing assembly acts as a reverse input locking type will be described in detail with reference to FIGS. same.

First, the input shaft (1) is coupled to the control wheel 30 side, the output shaft (2) is coupled to the inner ring (10a) (10b) side, and the fixed body 60 such as the housing is coupled to the outer ring 20 in Figure 9 In the device configuration as shown, the positive input power (rotational force) transmitted from the input shaft (1) to the output shaft (2) is a smooth power transmission function by operating the inner ring-controlled reverse input prevention clutch bearing assembly of the present invention in a bearing state. Will be performed. In other words, when the rotational speed by the rotational force of the output shaft 2 exceeds the rotational speed of the input shaft 1, the clutch bearing assembly is locked, and the rotational speed by the rotational force of the output shaft 2 becomes If the rotation speed is less than the rotational drive together with the input shaft (1).

That is, as shown in FIG. 10 (refer to FIG. 5), the control wheel 30 is formed by the clearance between the spline 15 of the inner ring 10b meshed with each other and the spline 32 of the control wheel 30. When rotating in one direction (clockwise), the center body portion 74 of the axial drive cam 73 that can freely rotate in the axial drive cam seating groove 12a of the inner ring 10a is rotated. The eccentric shaft 76 on one side thereof is caught by the axial guide groove 32a of the control wheel 30 to move together with the control wheel 30 and the circumferential guide groove 72 of the axial wedge ring 70. While rotating the eccentric shaft 75 on the other side in the opposite direction (counterclockwise) with respect to the rotation direction of the control wheel 30, the axial wedge ring 70 moves forward in the axial direction to the inner ring 10a. Tightly fitting on the axial wedge ring contact surface 12 of the control wheel 30 and the inner ring (10a) 10b can rotate together during the continuous rotation of the control wheel 30 Maintain state.

At the same time, as shown in FIG. 11, the cam spring 86 accommodated in the spline groove 33 of the control wheel 30 also moves together by the play between the splines 15, 32, and the rotational direction locking cam 84. ) By pressing one side and rotating the locking cam shaft 85 inserted on the inner ring 10a in the same direction (clockwise) at the center of rotation so that the cam action surface 85a on one side of the wedge ring 80 rotates. It is in contact with the inner circumferential surface of the rotating cam contacting portion 81 in the rotational direction. At this time, the retainer 45 rotating together with the rolling element 40 rotates slower than the inner ring 10a by the same principle as the carrier of the sun gear and the planetary gear, and with the wedge ring neutral restoring spring 87 in the rotational direction. The rotational direction wedge ring 80, which is elastically coupled to the retainer 45, rotates slower than the inner ring 10a, and eventually rotates in the rotational direction in which the rotational direction locking cam 84 rotates in a counterclockwise direction. In contact with the cam contact 81, the rotational locking cam 84 is not fitted. Therefore, even when the control wheel 30 and the inner ring 10a and the rolling element 40 continue to rotate, the rotational wedge 82 of the rotating wedge ring 80 does not restrain the rolling element 40. The clutch bearing assembly performs a power transmission function to the output shaft 2 toward the inner ring 10a, 10b while operating in a bearing state. This driving mechanism can be similarly applied to the case where the control wheel 30 rotates in the opposite direction.

In addition, the reverse input drive in which the torque of the input shaft 1 or more is loaded on the output shaft 2 and the power (rotation force) is to be transmitted from the output shaft 2 to the input shaft 1 is the inner-wheel control type reverse input prevention clutch of the present invention. As the bearing assembly is locked in the clutch state and coupled to the outer ring 20, the bearing assembly blocks the reverse driving to the input shaft 1.

That is, as shown in FIG. 12, when more rotational force is loaded on the output shaft 2 than the rotational force of the input shaft 1, the output-side inner rings 10a and 10b are in one direction (clockwise direction) for convenience. It can be explained on the assumption that the control wheel 30 is rotated and the control wheel 30 is relatively stopped. When the inner wheels 10a and 10b rotate by the play between the splines 15 and 32, the inner ring 10b is splined. The locking cam shaft 85 accommodated in the locking cam shaft seating hole 15a of 15 also moves together, but one side of the cam working surface 85a of the rotation direction locking cam 84 is supported by the control wheel 30 so that the movement is performed. The cam working surface 85a on the one side is rotated in the direction of rotation of the wedge ring 80 by maintaining a state inclined to one side as rotated in the opposite direction (counterclockwise direction) of the moving direction by the elastic force of the cam spring 86 which is not present. It is in contact with the inner circumferential surface of the locking cam contacting portion 81 of the rotation direction. At this time, the retainer 45 that rotates like the rolling element 40 rotates slower than the inner ring 10a, and is elastically coupled to the retainer 45 by the rotational direction wedge ring neutral restoring spring 87. The rotational direction wedge ring 80 rotates slower than the inner ring 10a, and eventually comes into contact with the rotational direction locking cam contact portion 81 in which the rotational direction locking cam 84 rotates in a counterclockwise direction. The cam 84 is press fit, and the rotation direction wedge ring 80 rotates at the same speed as the inner ring 10a. The rotation direction wedge ring 80 that rotates faster than the rolling element 40 rotates the rotation direction wedge 82 between the rolling element 40 and the inner ring 10a while compressing the rotation direction wedge ring neutral restoring spring 87. The rolling element 40 is provided to ride the rotation direction wedge 82 so that the rotation direction wedge 82 is locked in a more firmly fitted state between the rolling element 40 and the inner ring 10a. do.

Thus, the present clutch bearing assembly is firmly in contact with the inner ring (10a) (10b) and the outer ring (20) coupled to the fixed body 60, the inner ring (10a) (10b) is no longer able to rotate. While operating in a state in which the clutch is stopped so that it is impossible to lock, it serves to block the reverse drive to the control wheel 30. This driving mechanism is also applicable to the case where the inner rings 10a and 10b rotate in opposite directions.

In addition, in the inner-wheel control type reverse input prevention clutch bearing assembly having the structure as described above, an operation principle when the clutch bearing assembly acts as a reverse input shutoff type will be described with reference to FIGS. 13 and 10 to 12. It will be described in detail as follows.

First, the input shaft 1 supported to be rotatable to the fixed body 60 is coupled to the inner ring 10a, 10b side, and the output shaft 2 is coupled to the outer ring 20 side, and the rotation resistor 50 on the control wheel 30 side. ) Is coupled to the rotational resistor 50 in contact with the fixture 60 in a state capable of inducing frictional resistance. Positive input power (rotational power) transmitted to the) is to perform a smooth power transmission function by operating the inner ring-controlled reverse input prevention clutch bearing assembly of the present invention in a clutch state. In other words, when the rotational speed by the rotational force of the output shaft 2 exceeds the rotational speed of the input shaft 1, the clutch bearing assembly is locked, and the rotational speed by the rotational force of the output shaft 2 becomes If the rotation speed is less than the rotational drive together with the input shaft (1).

That is, when the inner ring 10a, 10b is rotated in one direction (clockwise) by the clearance between the spline 15 of the inner ring 10b which is meshed with each other and the spline 32 of the control wheel 30, Although the directional drive cam 73 also has to move along with its clearance width, one eccentric shaft 76 of the axial drive cam 73 has an axial guide groove of the spline 32 on the control wheel 30 side at a stationary state ( The axial drive cam 73 is forced to rotate in any direction (clockwise) in the axial drive cam seating groove 12a of the inner ring 10a because it is kept in a state that it cannot be caught by 32a). In addition, while the other eccentric shaft 75 of the axial drive cam 73 also rotates in the same direction (clockwise), the axial wedge ring 70 is moved forward in the axial direction to axially wedge the inner ring 10a. Close fitting on the ring contact surface 12 stops by frictional resistance during the continuous rotation of the inner rings 10a, 10b. Dunn control wheel 30 and the inner ring (10a), (10b) maintains a state in which the rotatable together.

At the same time, as shown in Figure 12, the locking cam shaft seat hole of the inner ring (10b) spline 15 when the inner ring (10a) (10b) is rotated clockwise by the play between the splines (15, 32) The locking cam shaft 85 accommodated in the 15a moves together, but the cam working surface 85a side of the rotational locking cam 84 is supported by the control wheel 30 so that the elastic force of the cam spring 86 is not moved. By maintaining the inclined state to one side as rotated in the opposite direction (counterclockwise direction) of the movement direction by means of the cam working surface 85a on one side of the rotation direction locking cam contact portion of the rotation direction wedge ring ( 81) It comes into contact with the inner circumferential surface. At this time, the retainer 45 that rotates like the rolling element 40 rotates slower than the inner ring 10a, and is elastically coupled to the retainer 45 by the rotational direction wedge ring neutral restoring spring 87. The rotational direction wedge ring 80 rotates slower than the inner ring 10a, and eventually comes into contact with the rotational direction locking cam contact portion 81 in which the rotational direction locking cam 84 rotates in a counterclockwise direction. The cam 84 is press fit, and the rotation direction wedge ring 80 rotates at the same speed as the inner ring 10a. The rotation direction wedge ring 80 that rotates faster than the rolling element 40 rotates the rotation direction wedge 82 between the rolling element 40 and the inner ring 10a while compressing the rotation direction wedge ring neutral restoring spring 87. The rolling element 40 is provided to ride the rotation direction wedge 82 so that the rotation direction wedge 82 is locked in a more firmly fitted state between the rolling element 40 and the inner ring 10a. do.

Therefore, when the input shaft 1 continues to rotate, the control wheel 30, which is tightly coupled to the inner rings 10a and 10b by the rotational direction locking cam 84, causes frictional resistance with the fixing body 60. While being dragged and delayed rotation, the inner ring 10a, 10b and the outer ring 20 are kept in a fitted state by using the non-rotating rolling element 40 as a medium, compared to the control wheel 30. It is possible to transmit power toward the output shaft (2) coupled to the outer ring 20 while simultaneously rotating relatively fast.

In addition, the reverse input drive in which the torque of the input shaft 1 or more is loaded on the output shaft 2 and the power (rotation force) is to be transmitted from the output shaft 2 to the input shaft 1 is the inner-wheel control type reverse input prevention clutch of the present invention. The bearing assembly is separated into a bearing state and coupled to the outer ring 20 to block the reverse driving to the input shaft 1.

That is, when more rotational force than that of the input shaft 1 is loaded on the output shaft 2, the output side outer ring 20 rotates faster than the input side inner ring 10a, 10b, or the output side outer ring 20 ) May be considered to be reversed by the outer ring 20 after stopping the rotation of the input inner ring (10a) (10b). First, in the case where the outer ring 20 rotates faster in one direction (clockwise) than the inner rings 10a and 10b, the rolling element 40 is rotated by the rotational wedge 82 as shown in FIG. As the outer ring 20 is rotated faster than the inner ring 10a or 10b while the rotating ring is stopped, the rolling element 40 is rotated in a loosening direction (clockwise) by rubbing the rolling element 40 which is in physical contact with the outer ring 20. As a result, the engagement state with the rotational wedge 82 is released, and the retainer 45 also rotates relatively quickly compared to the inner ring 10a, 10b while the cam working surface of the rotational locking cam 84 is rotated. By rubbing the 85a to rotate in the release direction (clockwise), the outer ring 20 and the inner ring 10a and 10b are operated in a bearing state without mutual interference.

Next, when the torque of the outer ring 20 is greater than the torque of the inner rings 10a and 10b to attempt to reverse the rotation of the inner ring 10a and 10b after the rotation stops, as shown in FIG. As described above, the engagement position between the outer ring 20 and the control wheel 30 is changed, so that the axial wedge ring 70 moves backward in the axial direction by the axial drive cam 73 and the inner ring 10a. Separate rotation is possible, respectively, and at the same time, the rolling element 40 is also restored by restoring the rotational wedge 82 to a neutral position while releasing the fitting engagement state of the rotational locking cam 84. The inner ring 10a, 10b and the outer ring 20 are separated and operated in a bearing state without mutual interference.

On the other hand, the configuration shown in Figures 14 to 23 implements a preferred embodiment of the outer ring control type clutch bearing assembly, the control wheel 130 is the outer ring (120a, 120b) and play in the rotational direction (axial wedges) It has a gap between the ring support piece 132 and the outer ring side locking cam seat 124, and is coupled to enable power transmission (refer to an exploded perspective view of FIG. 14 and a coupling cross-sectional view of FIG. 16).

Outer ring control type reverse input prevention clutch bearing assembly according to the present invention, as shown in Figs. 14 to 18, the inner ring 110 arranged to have concentric circular raceway raceway surface (110a) (121a, 121b) of different radii. ) And the outer circumferential surface may be slid between the outer ring (120a) (120b) (120c) and the opposing raceway (110a) (121a, 121b) of the inner ring 110 and outer ring (120a) (120b) (120c). A plurality of rolling elements 140 arranged in a circumferential manner, retainers 145 supporting them so that the arrangement of the rolling elements 140 can be maintained, and the inner ring 110 and outer ring 120a and 120b. A control wheel 130 which is in contact with one of the sides 120c and maintains a clearance in the rotational direction thereof, and is coupled to be interlocked with each other, and the inner ring 110 and the outer ring 120a, 120b, 120c and the control wheel 130 To control the rotation in the axial direction and the direction of rotation so as to maintain the relative rotational speed difference between the two Between it forms a structure including a pair of wedge ring assembly, which to pass or block a torque.

In the configuration of the outer ring control type reverse input prevention clutch bearing assembly of the present invention, the inner ring 110, as shown in Figure 14, coupled with the corresponding power transmission body formed in the output shaft (2) or fixed shaft (3), etc. A spline groove 111 or the like as a multi-sided power transmission die is formed on the inner circumferential surface thereof, and the rolling element raceway surface 110a is formed on the outer circumferential surface of the inner ring 110.

In addition, the outer ring (120a) (120b) (120c), the outer raceway surface 121a (121b) of the rolling element 140 and at the same time forming an outer casing that can accommodate each component, Figure 14 16, the outer outer ring 120b and the outer ring cover 120c constituting a pair of outer casings integrally coupled by a plurality of fasteners 126, and the outer outer ring 120b and the outer ring. The inner outer ring 120a interposed between the cover 120c and organically assembled with the cover 120c and in contact with the control wheel 130 is interlocked with each other.

The inner and outer outer ring (120a) (120b) has a structure in which the rolling elements raceway surface (121a) (121b) in contact with the rolling element 130 is divided into portions each formed, respectively, of the inner outer ring (120a) The inner circumferential surface forms an inclined axial wedge ring contact surface 122 whose inner diameter linearly increases along one axial direction, so that the outer circumferential surface of the axial wedge ring 170 is connected to the axial wedge ring contact surface 122. The outer ring-side locking cam sheet 124 is formed so as to be in close contact with the outer outer ring (120a) surrounding the front circumference of the plurality of rotational locking cam 184 seated so as to be arranged at a predetermined interval And a plurality of axial wedge ring support pieces 132 protruding on the circumference of the control wheel 130, and the control wheel between the intervals between the outer ring side locking cam seat 124. The axial wedge ring 170 in accordance with the rotation of the A plurality of push pin seating holes 123 for inserting a plurality of push pins 174a which can be moved forward and backward in the axial direction are formed therethrough. In addition, the outer outer ring 120b and the outer ring cover 120c are formed at positions corresponding to a plurality of fastening holes 125a and 125b for fastening them with the fastener 126 to be integrally coupled. .

Any one of the inner ring 110 and outer ring (120a) (120b) (120c), may be coupled to the fixture 160 for fixing the rotation does not occur, for example, as shown in Figures 20 and 23 Likewise, the fixed shaft 3 to be fitted with the inner ring 110, the housing for supporting the outer ring (120a) (120b, 120c) rotatably.

In addition, the rolling element 140 applies a cylindrical roller (b in FIG. 24) contacting the raceways 110a (121a, 121b) of the inner ring 110 and outer ring (120a) (120b) (120c). In general, but in some cases, as shown in Fig. 24, a spherical cylindrical shape (a), an oblong shape or a two-stage inclined shape (c) (e), a spherical shape (d), and (two steps) Rollers such as stepped cylinders (f) (g) may be applied. In addition, rollers of various shapes, such as cones and needles, may be applied. Of course, a slight design change should be made to have.

In addition, the retainer 145, as shown in Figure 14, a plurality of rolling elements receiving hole 146 that can accommodate the rolling elements 140, and the rotation direction wedge ring neutral restoring spring for each position therebetween A plurality of through holes 147, each of which can accommodate 187, is formed.

In addition, the control wheel 130, which is installed in contact with the inner outer ring (120a), as shown in Figure 14, 16 and 19, if formed protruding on the front circumference of the outer ring (120a) An axial wedge ring support piece 132 is formed on the outer circumference of the control wheel 130 as a power transmission mold that can be coupled in a pair with the outer ring side locking cam seat 124 which is a corresponding power transmission type of the die. On the contact surface of the axial wedge ring support piece 132, a pressing protrusion 134 is formed to advance and retract the push pin 174a when the control wheel 130 rotates, and one side circumference of the ring-shaped body is formed. On the rotational locking cam exposure groove 133 is formed so that the rotational locking cam 184 can be exposed to the outside, and in some cases, on the inner peripheral surface of the ring-shaped body, it can play a key role in the shaft coupling Spline 133 as a power transmission body can be formed.

The gap between the two power transmission bodies, i.e., the outer ring side locking cam seat 124 and the axial wedge ring support piece 132, forms a rotational direction gap d5 (see FIG. 21) at the time of its engagement. Delayed by d5), power transmission takes place. In addition, when the control wheel 130 is engaged with the outer ring 120a without applying external power, both side wall surfaces of the outer ring side locking cam seat 124 and the axial wedge ring support piece 132 contact each other. The rotational direction wedge ring neutral restoring spring 187 is provided so that it can be automatically centered at the same clearance. As will be described later, the rotational wedge ring neutral restoring spring 187 serves to elastically connect the retainer 145 concentrically arranged with the rotational wedge ring 180.

In some cases, when the outer ring (120a) (120b) is coupled to the input shaft 1, as shown in Figure 23, one side of the control wheel 130, the surface of the fixed body 160 is supported separately Rotational resistor 150 may be installed to be driven and rotated along with the rotation of the input shaft 1 with the rotational resistance such as physical frictional force. That is, the rotary resistor 150, as shown in Figure 23 can be fixed to the fixed body 160 and its inner circumferential surface in contact with the outer circumferential surface of the control wheel 130 may have a frictional resistance.

In addition, the wedge ring assembly, as shown in Figures 14 and 16 to 18, the axial wedge ring 170 and the axial wedge ring 170 is moved to its original position when no external power is applied. An axial wedge ring neutral restoring spring 173, which is a returning means, a rotational wedge ring 180, a rotational wedge ring neutral restoring spring 187 which is a return means of the rotational wedge ring 180, It forms a structure including a rotation direction locking cam 184 for elastically interlocking between the rotation direction wedge ring 180 and the control wheel 130.

In the above wedge ring assembly, the axial wedge ring 170 is in contact with the axial wedge ring contact surface 122 formed on the inner circumferential surface of the inner outer ring 120a, as shown in FIG. The inclined surface 172 in the direction is formed, the ring flange 171 is formed on one side circumference of the inclined surface 172, the outer ring by the axial movement stroke to move forward and return to the original position along the axial direction It is a component that changes the degree of close contact with the axial wedge ring contact surface 122 of (120a).

The inclined surface 172 of the axial wedge ring 170 has a surface with a large frictional resistance for contacting the axial wedge ring contact surface 122 of the outer ring 120a to generate sufficient rotational force (torque). Innumerable fine irregularities can be formed.

The axial wedge ring neutral restoring spring 173 is a component for returning the axial wedge ring to its original position without external force applied thereto, and is disposed adjacent to one side of the axial wedge ring 170. A ring-shaped leaf spring structure that presses the axial wedge ring 170 directly in the axial direction by contact is applied.

The axial wedge ring neutral restoring spring 173 is disposed on an opposite side of the axial wedge ring with the axial wedge ring 170 interposed therebetween so that the axial wedge ring 170 has the axial wedge ring neutral restoring spring. A pair of push pins (174a) for pressing in the compression direction of the (173), the push pins (174a), the rotation of the control wheel 130 through the outer ring (120a) in the axial direction Along the plurality of push pin seating holes 123 formed so as to be forward and backward in the axial direction at the same time, respectively, one end of the push pin 174a and the axial wedge ring support piece of the control wheel 130 ( The lubricating ball 174b may be interposed between the working surfaces of the 132 to minimize frictional resistance when the control wheel 130 rotates.

Referring to the operation principle of the axial wedge ring 170, first, when the control wheel 130 and the inner outer ring (120a) is rotated or stopped at the same speed, the front surface of the outer ring (120a) and The pressure protrusion 134 formed on the working surface of the axial wedge ring support piece 132 of the control wheel 130 is in contact with the lubrication ball 174b and the push pin 174a and the ring of the axial wedge ring 170. Since the flange 171 is placed in a neutral position capable of sequentially pressing, the flange 171 is spaced apart from the axial wedge ring contact surface 122 of the inner outer ring 120a and the inclined surface 172 of the axial wedge ring 170. The axial wedge ring 170 remains rotatable freely, at which time the axial wedge ring neutral restoring spring 173 is compressed. On the contrary, as shown in the coupling cross-sectional view shown in FIG. 16, when the control wheel 130 rotates in one direction by the rotational direction clearance d5 with the locking cam seat 124 toward the inner outer ring 120a. When the pressure protrusion 134 moves in position, a portion of the lubricating ball 174b is received into a groove lower than that of the pressure protrusion 134, so that the axial wedge ring neutral restoring spring 173 The push pin 174a and the ring flange 171 of the axial wedge ring 170 can be sequentially pressed by the elastic action, such that the axial wedge ring contact surface 122 of the inner outer ring 120a and the axial direction are provided. By contacting the inclined surface 172 of the wedge ring 170 to maintain the state in which the axial wedge ring 170 is in close contact with the inner outer ring (120a).

As shown in FIGS. 14 and 18, the rotational wedge ring 180 is disposed concentrically adjacent to the retainer 145 to accommodate a portion of the rolling element 140 and the rolling element ( Rotational direction wedge 182 capable of limiting the rotation of the 140 is formed toward the circumferential surface of the rolling element 140 and disposed adjacent thereto so as to be interlocked with the axial wedge ring 170. One side of the circumference is provided with a rotation direction locking cam contact portion 181 that can contact the rotation direction locking cam 184, and the rotation direction wedge ring neutral restoring spring 187 is installed between the rolling elements 140. A plurality of through holes 183 may be formed.

The rotational wedge ring neutral restoring spring 187, as shown in Figs. 14 and 18, when the retainer 145 and the rotational wedge ring 180 is rotated but a greater rotational force than a predetermined elasticity is applied. The retainer 145 and the rotational direction wedge ring 180 are components that provide an elastic coupling force to be rotated together at different rotational speeds.

The rotation direction locking cam 184 is a component for elastically interlocking the rotation direction between the wedge ring 180 and the control wheel 130, 'W' shaped as shown in Figs. The spring is bent.

In the outer ring control type reverse input prevention clutch bearing assembly having the structure as described above, the operation principle when the clutch bearing assembly acts as a reverse input locking type will be described in detail with reference to FIGS. 20 to 22 as follows. same. However, although the structure of the clutch bearing assembly for the reverse input locking and detaching type applied to FIGS. 20 and 23 is described somewhat differently from the above-described embodiment, the operation principle is the same, and thus it is necessary to be absolutely free from this. Note that there is no.

First, the input shaft 1 is coupled to the control wheel 130 side, the fixed shaft 3 is coupled to the inner ring 110 side, and the output rotating body 2a such as a disk is coupled to the outer ring 120 shown in FIG. In the device configuration as described above, the positive input power (rotational force) transmitted from the input shaft 1 to the output rotating body 2a is smoothly transmitted by the outer ring controlled reverse input preventing clutch bearing assembly of the present invention operated in a bearing state. It will perform the function. In other words, when the rotational speed due to the rotational force of the output rotating body 2a exceeds the rotational speed of the input shaft 1, the clutch bearing assembly is locked, and the rotational speed due to the rotational force of the output rotating body 2a becomes the input shaft. If the rotational speed of (1) is less than the rotational drive together with the input shaft (1).

That is, as shown in Fig. 21, in the neutral position where the left and right clearance d5 between the power transmission bodies is maintained in a normal state, the tip of the rotation direction locking cam 184 is the outer circumferential surface of the rotation direction wedge ring (rotation direction). If the control wheel 130 is rotated by the play d5 in one direction (for example, clockwise) in this state, the play d5 is kept in a light contact with the locking cam contact portion 181). As the ubiquitous (gap d6) to one side, the other surfaces between the power transmission bodies are in close contact with each other. At this time, the axial wedge ring 170 is firmly in close contact with the outer ring 120a by the axial wedge ring neutral restoring spring 173, and at the same time the rotational locking cam 184 is pressed clockwise to press One side tip of the rotational direction locking cam 184 lies in the rotational direction and is spaced apart from the outer circumferential surface of the rotational direction wedge ring 180, and the other side tip of the rotational direction locking cam 184 that is not pressurized continues in the rotational direction wedge ring ( Contact with the outer circumferential surface of 180). In this state, when the control wheel 130 continues to rotate and rotates together with the outer ring 120a (corresponding to reference numerals 120c and 124 in the drawing), the retainer 145 rotates relatively slower than the outer ring 120a. At the same time, the rotational wedge ring 180 also rotates slowly with the retainer 145 to operate in the same state as they rotate counterclockwise, wherein the rotational wedge ring 180 is the rotational locking cam. The contacted tip of 184 is pressed down and continues to rotate counterclockwise without mutual interference. Therefore, as shown in FIG. 22, the rotational wedge 182 of the rotational wedge ring 180 restrains the rolling element 140 that is delayed and rotates while sliding clockwise together with the outer ring 120a. The outer ring 120a, 120b, 120c and the control wheel 130 continue to rotate together, so that the clutch bearing assembly operates in a bearing state while the control wheel 130 is operated in a bearing state. It is to be able to smoothly transmit the power of the outer ring (120a, 120b, 120c) toward the output rotor (2a). This driving mechanism may be similarly applied to the case where the control wheel 30 rotates in the opposite direction.

The reverse input drive in which the torque of the input shaft 1 or more is loaded on the output rotor 2a and the power (rotational force) is to be transmitted from the output rotor 2a to the input shaft 1 is the outer ring control type of the present invention. The reverse input preventing clutch bearing assembly is locked to the clutch state and coupled to the outer ring 120 to block the reverse driving to the input shaft 1.

That is, when more rotational force than the rotational force of the input shaft 1 is loaded on the output rotor 2a, the outer ring 120a rotates in one direction (clockwise) for convenience and the control wheel 130 is relatively stopped. It can be described assuming a state that the outer ring (120a) is rotated clockwise as much as the clearance between the power transmission die (d5) when the rotation direction locking cam 184 also rotates together, the rotation direction locking One side tip of the cam 184 is pressed counterclockwise while being pressed by the control wheel 130 and spaced apart from the outer circumferential surface of the rotational wedge ring 180, the other side tip of the non-pressing rotational locking cam 184 Is in contact with the outer circumferential surface of the rotational wedge ring 180. In this state, when the outer ring 120a continues to rotate and rotates together with the control wheel 130, the retainer 145 rotates relatively slower than the outer ring 120a and at the same time the rotation direction wedge ring 180. ) Also rotates slowly with the retainer 145 so that they operate in the same state as they rotate counterclockwise, wherein the rotational direction locking cam 184 is supported by the outer ring side locking cam sheet 124 and is in contact therewith. The tip is in close contact with the outer circumferential surface of the rotational wedge ring 180. Accordingly, the rotational wedge ring 180 is rotated clockwise together with the outer ring 120a and the rotational wedge 182 is rotated while being delayed while sliding clockwise together with the outer ring 120a. The rolling element 140 is restrained, and thus, the rolling element 140 is firm between the inner ring 110 which is stopped by the fixed shaft 3 and the outer ring 120a, 120b and 120c which are still rotating. In close contact with the outer ring, a clutch state in which the outer ring can no longer rotate is performed, thereby preventing a reverse driving of the control wheel 130 toward the input shaft 1. This driving mechanism may also be applied to the case in which the outer ring 120a, 120b, 120c rotates in the opposite direction.

In addition, in the outer ring control type reverse input prevention clutch bearing assembly having the above structure, the operation principle when the clutch bearing assembly acts as a reverse input shutoff type will be described in detail with reference to FIGS. 21 to 22. As follows.

First, the input shaft 1 supported to be rotatable to the fixture 160 is coupled to the outer ring 120 side, the output shaft 2 is coupled to the inner ring 110 side, and the rotation resistor 150 is coupled to the fixture 160 side. In the device configuration as shown in FIG. 23, which is coupled and brought into contact with the control wheel 130 in a state capable of inducing frictional resistance, it is transmitted from the input shaft 1 to the output shaft 2. Positive input power (rotational power) is the outer ring-controlled reverse input prevention clutch bearing assembly of the present invention is operated in a clutch state to perform a smooth power transmission function. In other words, when the rotational speed by the rotational force of the output shaft 2 exceeds the rotational speed of the input shaft 1, the clutch bearing assembly is locked, and the rotational speed by the rotational force of the output shaft 2 becomes If it is below the rotation speed, it is driven to rotate together with the input shaft (1).

That is, in the neutral position where the left and right clearances d5 between the power transmission bodies are maintained in the normal state, the tip of the rotational direction locking cam 184 extends to the outer circumferential surface of the rotational direction wedge ring 180 (rotational direction locking cam contact portion 181). Keep a little touch. In this state, when the outer ring 120a rotates in one direction (for example, clockwise) by the clearance d5, the rotation direction locking cam 184 also rotates together, and at this time, the rotation direction locking cam 184 One side tip is pressed counterclockwise while being pressed by the control wheel 130 is spaced apart from the outer circumferential surface of the rotation direction wedge ring 180, the other tip of the non-pressing rotation direction locking cam 184 continues to the rotation direction In contact with the outer circumferential surface of the wedge ring (180). In this state, when the outer ring 120a continues to rotate and rotates together with the control wheel 130, the retainer 145 rotates relatively slower than the outer ring 120a and at the same time the rotation direction wedge ring 180. ) Also rotates slowly with the retainer 145 so that they operate in the same state as they rotate counterclockwise, wherein the rotational direction locking cam 184 is supported by the outer ring side locking cam sheet 124 and is in contact therewith. The tip is in close contact with the outer circumferential surface of the rotational wedge ring 180, the rotational wedge ring 180 is rotated in the clockwise direction with the outer ring (120a) and the rotational wedge 182, the With the outer ring 120a, the rolling element 140 restrains the rolling element 140, which is delayed and rotates in a clockwise direction. As a result, the rolling element 140 continuously rotates the outer ring 120a, 120b, 120c and the inner ring. Dogs between 110 Be in close contact with and support a clutch condition that can be rotated integrally.

Therefore, when the input shaft 1 continues to rotate, the control wheel 130, which is tightly coupled to the outer ring 120a by the rotation direction locking cam 184, is attracted while causing frictional resistance with the fixed body 160. The inner ring 110 and the outer ring (120a) (120b) (120c) is a delayed rotation is maintained relative to the control wheel 130 by maintaining the interference fit state using the rolling element 140 as a medium It is possible to transmit power toward the output shaft (2) coupled to the inner ring 110 while simultaneously rotating rapidly. This driving mechanism may also be applied to the case in which the outer ring 120a, 120b, 120c rotates in the opposite direction.

In addition, the reverse input drive in which the torque of the input shaft 1 or more is loaded on the output shaft 2 and the power (rotation force) is to be transmitted from the output shaft 2 to the input shaft 1 is the outer ring control type reverse input prevention clutch of the present invention. The bearing assembly is separated into a bearing state and coupled to the outer ring 120a to block the reverse driving to the input shaft 1.

That is, when more rotational force than the rotational force of the input shaft 1 is loaded on the output shaft 2, the output side inner ring 110 rotates faster than the input side outer ring 120a, or the torque of the output side inner ring 110 It may be considered that the reverse rotation by the inner ring 110 after stopping the rotation of the input outer ring (120a). First, when the inner ring 110 rotates faster than the outer ring 120a, the inner ring 110 is rotated by the rotational direction wedge 182 in the state where the inner ring 110 rotates. As it rotates faster than 120a, the engagement of the wedge 182 in the rotational direction is released by rubbing the rolling element 140 physically contacted with the rotational body in the unwinding direction, and together with the retainer 145, While rotating relatively fast compared to the outer ring (120a), the contact tip of the rotation direction locking cam 184 is spaced apart to rotate in the release direction to operate in a bearing state without mutual interference between the inner ring (110) and outer ring (120a). .

Subsequently, when the torque of the inner ring 110 is large and offset by the torque of the outer ring 120a and the rotation of the outer ring 120a is to be reversed after the rotation stops, the inner ring 110 and the control wheel 130 are rotated. By changing the coupling position between the axial wedge ring 170 by the push pin 174a is moved backward in the axial direction is separated from the outer ring (120a) and each independent rotation is possible at the same time, the rotation direction As the fitting engagement of the locking cam 184 is released, the rolling element 140 is also rotatable by restoring the rotational wedge 182 to a neutral position, and thus the inner ring 110 and the outer ring 120a. ) Are separated and operated in a bearing state without mutual interference.

As described above, the reverse input prevention clutch bearing assembly according to the embodiment of the present invention includes a folding device having a rotational displacement, such as a vehicle side mirror, a bed, a chair or a robot joint; A lifting device of a rotary movement type such as an elevator, a screw jack or a vehicle power window; Linear moving switchgear such as vehicle sunroof, shutter or electric door; Electric steering device, bicycle sprocket, electric wheel chair, electric car, ball screw applied rear wheel, washing machine, center differential clutch of vehicle, limit slip differential (LSD) device, copier It can be widely applied to a wide variety of fields, such as rotating devices in device elements such as paper feeders or transmissions.

Hereinafter, various application examples to which the reverse input preventing clutch bearing assembly according to the embodiment of the present invention is specifically listed will be described in detail.

[Application Example 1]

25 and 26 show an example of an impact protection device that can be applied in an electric side rearview mirror (side mirror) of a vehicle.

This application example is applied to the outer ring control clutch bearing assembly of the present invention, the side mirror head is mounted on the output shaft (2) on the output side inner ring 10 side, the gear connected to the motor is mounted on the input outer ring (20) side The outer circumference of the control wheel 30 is coupled to the rotary resistor 50 made of a ring-shaped clamp that induces frictional resistance, and both ends of the ring-shaped clamp are fixed to the fixed bracket 51 to operate the fixed bracket 51. According to the structure that can adjust the frictional resistance of the control wheel (30). Power is generated from the motor engaged with the gear on the outer ring 20 side, and the power is transmitted to the side mirror head on the inner ring 10 side, and the rotary resistor 50 is supported by the vehicle body.

[Application Example 2]

27 and 28 show an example in which the outer ring control clutch bearing assembly of the present invention is applied to a bidirectional clutch which can be set in direction.

This application example is based on the forward and reverse operation of the manual control lever 52 fixed to one side of the control wheel 30 so as to neutralize the rotational direction of the output inner ring 10, prevent clockwise rotation or counterclockwise rotation. Allows you to perform additional functions that can be set as either prevention. In addition to the structure of the clutch bearing assembly of the present invention shown in Fig. 14, the configuration is a ball plunger that is resilient in the spline (axial wedge ring support piece 132 of the present invention) of the control wheel 30. Each of the inner ring 20, the outer ring 20 can be implemented by further provided with a mounting groove corresponding to each of the ball plunger to maintain a slight positional deviation so that any one of the ball plunger can be selectively seated Do.

[Application Example 3]

The present invention is applicable to the output shaft of the motor. That is, the outer ring is coupled to the motor housing, the control wheel is coupled to the rotor shaft of the motor to provide a rotational force, the inner ring is coupled to the output shaft of the motor to form a structure for transmitting the rotational force of the motor.

This prevents the motor or the transmission from being adversely affected by excessive reverse input torque, and thus is suitable for a device in which the output member may be displaced due to the reverse input torque, and with a rotary drive such as a motor, a reducer, or a clutch. As a single assembly, a compact and lightweight device can be realized.

[Application Example 4]

The present invention is applicable to a motor brake clutch of a motor. That is, the drive shaft of the motor is coupled to the control wheel to provide rotational force, the output shaft is coupled to the inner ring to output the rotational force of the motor, and the multi-plate disc installed in the motor housing is coupled to the outer ring to provide friction resistance at all times. Form a structure.

[Application Example 5]

The present invention is applicable to a brake system for a vehicle mounted on a wheel motor or a driving wheel. That is, the output shaft of the motor is coupled to the control wheel to transmit rotational force, the vehicle wheel is coupled to the inner ring, and if one or more disks are coupled to the outer ring, the caliper coupled to the vehicle body has a relatively large frictional resistance to the disk. The caliper may control the control wheel while the disc is locked, and thus may be used as an antilock brake or parking brake of the wheel motor. In addition, regenerative braking is also possible by releasing the caliper.

[Application Example 6]

The present invention is applicable to the angle adjusting device of the chair back. That is, the seat fixing plate is coupled to the outer ring, the backrest fixing plate is coupled to the inner ring, and the operation member for adjusting the rotation of the backrest is coupled to the control wheel. Sensitivity is very smooth and fine adjustment is possible.

Alternatively, the present invention can also be applied to an electric chair or a sliding device of a vehicle. That is, the clutch bearing assembly of the present invention is installed between the motor and the chair, and in the case of using a reduction gear such as a worm and a worm wheel, the torque transmission efficiency was not good and the rated capacity of the motor had to be increased. According to the example, since the reverse input torque can be prevented from being transmitted and the transmission efficiency can be improved, a small motor can be used.

[Application Example 7]

The present invention is applicable to a steering device (power steering device) of a vehicle. That is, the handle shaft is coupled to the control wheel, the vehicle body is coupled to the outer ring, the steering gear shaft is coupled to the inner ring, the torsion bar penetrates the inner and control wheels and is coupled to the handle shaft and the steering gear shaft and is in a neutral position. Provides elasticity that allows it to

As a result, it is possible to prevent a steering shock (Kick Back) phenomenon such as the steering wheel shake caused by the uneven road surface environment while driving, and to improve the steering stability.

[Application Example 8]

The present invention is applicable to an electric fire door. This application is more reliable because the door can be opened or closed manually so that the fire door can be opened and closed manually by manipulating the fire door in the event of a power cut or emergency. Provide the safety.

[Application Example 9]

The present invention is applicable to a paper feeder of a fax machine or a copy machine. That is, the drive shaft of the motor is coupled to the outer ring, the feed roller is coupled to the inner ring, and the rotating resistor installed on the frame is coupled to the control wheel to provide rotational resistance. This can bring about the advantage that normal paper feeding is possible while the paper can be easily taken out when the paper feeder jams.

[Application Example 10]

The present invention is applicable to the clutch device of the power assist motor. That is, the shaft of the motor rotatably supported by the housing is coupled to the inner ring, the rotor of the motor is coupled to the outer ring, and the rotary resistor installed in the housing is coupled to the control wheel to provide selective rotational resistance. Therefore, if there is no rotational resistance, the rotor of the motor can be non-rotated to reduce the inertia, and if the rotational resistance is loaded, driving or power assisted regenerative braking can be performed. In addition, this application example can be usefully used for a future four-wheel drive motor vehicle.

[Application Example 11]

The present invention can be applied to a manpower driven vehicle such as a manual wheelchair, a rickshaw or a bicycle. That is, a wheel shaft having a braking resistance is rotatably supported on the vehicle body and coupled to the inner ring, the wheel hub is coupled to the outer ring, and a handrim having forward and backward setting means contacting the wheel forms a structure coupled to the control wheel. . In addition, it provides a braking resistance by the pressing action of the disk and the caliper coupled to the wheel shaft. The control wheel may be coupled to or separated from the wheel shaft or the vehicle body to implement the parking brake.

[Application Example 12]

The present invention is applicable to a washing machine. That is, the motor output shaft coupled to the sun gear of the planetary transmission is coupled through the inner ring, the extended shaft member of the washing tank is coupled to the outer ring, the ring gear of the planetary gear is fastened to the shaft member, the outer peripheral surface of the shaft member The band brake is provided, and the pressure actuator mounted on the fixed side adjusts the contact between the control wheel and the rotating resistor so as to have a rotational resistance. In this case, the rotary resistor provides a rotational resistance to the control wheel so that the washing blade and the washing tank can rotate together in the dehydration mode, or the washing wing and the washing tank can rotate together or rotate in opposite directions in the washing mode. It operates separately from the control wheel.

In this application example, since the clutch bearing assembly of the inner ring control type can be applied, space and cost can be reduced.

[Application Example 13]

The present invention is applicable to a conveying apparatus using a screw. That is, the drive unit is coupled to the control wheel to provide a rotational force, the frame is coupled to the outer ring, the female screw is coupled to the inner ring, and has a male screw screwed with the female screw, the male screw shaft in accordance with the rotation of the female screw Translation can be done in the direction. Such a configuration is applicable to a machine tool, a patient bed, or a rear wheel motor and a threaded portion of a four-wheel drive vehicle.

[Application Example 14]

The present invention is applicable to the differential clutch of the vehicle (Center Differential Clutch). That is, the drive shaft is coupled to the inner ring, the driven shaft is coupled to the outer ring, and the fixture is connected to the control wheel to provide rotational resistance. In the part time type four-wheel drive system, the drive shaft and the driven shaft rotate at the same speed to maintain a separate state during normal driving, and the drive shaft and the driven shaft are automatically engaged when the driving wheel slips and idle. To transmit the driving force.

[Application Example 15]

The present invention is applicable to a differential limiting device (LSD) of a vehicle. That is, the differential housing is coupled to the outer ring, the wheel shaft is coupled to the inner ring, and the rotational resistor installed in the housing contacts the control wheel when the actuator is input with power to provide rotational resistance. Therefore, when one of the driving wheels is slipped and the driving force is lost, the differential function of the vehicle may be limited by coupling the housing and the wheel shaft.

[Application Example 16]

The present invention is applicable to a transmission. An inner ring and an outer ring are respectively coupled to an inner circumferential surface of the transmission shaft and the gear, and a control wheel and an outer ring are coupled by a rotating resistor, and a pressing member is mounted on the fixed body to control contact and separation of the rotating resistor. In addition, a clutch, a gear shift, or a synchronizer may be further provided to couple or separate the gear to the shaft so as to realize a gear ratio of various stages.

[Application Example 17]

The present invention can be applied to a complex drive device using an engine and an electric motor. That is, the motor shaft is installed on the transmission input shaft is coupled to the outer ring, the engine output shaft is coupled to the inner ring, the actuator (electronic clutch) is coupled to the control wheel to provide a rotational resistance, the outer ring when the power input of the actuator Friction resistance is generated at the start.

In the case of a hybrid engine, a combustion engine and an electric motor are used in series or in parallel, and the motor driving mode, engine starting mode, battery charging mode, thrust increasing mode, and regenerative braking mode are used depending on the driving situation. And so on.

In the case of applying the separate clutch bearing assembly of the present invention, the motor driving mode does not transmit the forward and reverse rotation of the motor for forward and reverse of the vehicle to the engine, and in the engine start mode, The engine is started by transmitting the rotation to the engine, whereas the battery charging mode and the thrust increasing mode may perform opposite power transmission functions to transmit the rotation of the engine to the motor.

According to the present invention as described above, the reverse input prevention clutch bearing assembly, as a basic mechanical element, such as a reverse input locking clutch, reverse input separation clutch or a one-way clutch that can select the locking direction, and a bearing for simple rotational support, etc. Not only can all functions be implemented in a single assembly, but also can be applied to a wide variety of fields by automatically converting and operating according to the characteristics of the above functions according to the system to which the configuration of the present invention is applied. To provide a constructive structure. That is, according to the apparatus of the present invention, the rotational force input from the input shaft is smoothly transmitted to the output shaft, and the rotational force reversely input from the output shaft is operated by itself without additional external control so as not to be transmitted to the input shaft by locking or separating the output shaft. It is possible to achieve a high device reliability while achieving a lightweight and compact structure.

In addition, according to an embodiment of the present invention, in the system to be applied can be configured in the form of locking or detachment to apply the optimal reverse input prevention structure suitable for it, as well as depending on the position of the accessory in the system The position of the control wheel can be freely arranged on the inner or outer ring so as to eliminate the interference on the operation, and the torque limiting type and the torque free form can be configured according to the operating torque of the clutch, thereby significantly improving its utility. You can.

In addition, according to the apparatus of the present invention, unlike the conventional case, since the durability of the rolling elements such as the rollers installed therein in a row instead of a double row exhibits sufficient durability, the manufacturing cost can be significantly reduced. Therefore, it is possible to improve assembly productivity and realize product miniaturization by minimizing required parts.

Although the present invention has been described with reference to the embodiments shown in the accompanying drawings, this may be regarded as exemplary, and a person of ordinary skill in the art may conceive various modifications and equivalent embodiments therefrom. It should be understood that such equivalent embodiments are also included within the claims of the present invention. Therefore, the true scope of protection of the present invention should be determined only by the appended claims.

Claims (19)

Inner and outer rings arranged to have concentric raceway surfaces of different radii; A plurality of rolling elements arranged in a circumference such that an outer circumferential surface is slid between the raceways facing the inner and outer rings; Retainers for supporting them so that the arrangement of the rolling elements can be maintained; A control wheel coupled to one of the inner ring and the outer ring and coupled to each other to maintain a clearance in the rotational direction thereof; And A pair of wedge ring assemblies for controlling the rotation of the inner ring, the outer ring, and the control wheel in the axial direction and the rotational direction so as to maintain a relative difference in rotational speed, thereby transmitting or blocking torque between two members selected therefrom; Reverse input prevention clutch bearing assembly comprising a. The method of claim 1, Reverse input preventing clutch bearing assembly, characterized in that the fixing body is fixed to any one of the inner ring and the outer ring to prevent rotation is generated. The method of claim 2, Reverse fixing clutch bearing assembly, characterized in that consisting of a housing. The method of claim 2, And the fixed body is a fixed shaft fitted with the inner ring and the outer ring. The method of claim 1, The rolling element is a reverse input prevention clutch bearing assembly, characterized in that consisting of a cylindrical roller in contact with the raceway surface of the inner ring and outer ring. The method of claim 1, The control wheel, which is installed in contact with the inner ring side, a power transmission body that can be combined in a pair with a multi-faceted corresponding power transmission body formed on the circumference of the inner ring is formed on the circumference of the control wheel, The reverse input preventive clutch bearing assembly, characterized in that the power transmission is made while forming a rotational direction of play when the two power transmission type body is coupled, the delay as much as the play. The method of claim 1, The control wheel is provided in contact with the outer ring side, the power transmission body that can be combined in a pair with a multi-faceted corresponding power transmission body formed on the circumference of the outer ring is formed on the circumference of the control wheel, The reverse input prevention clutch bearing assembly, characterized in that the rotational clearance is formed when the power transmission body is coupled, the power transmission is made while being delayed by the clearance. The method according to claim 6 or 7, The power transmission body is a reverse input clutch bearing assembly, characterized in that consisting of a spline and a spline groove. The method of claim 1, The control wheel has a rotational neutral restoring spring which allows centering at the same clearance so that both side wall surfaces thereof do not come into contact with each other when combined with either of the inner and outer rings without applying external power. Reverse input prevention clutch bearing assembly further comprises. The method of claim 9, The rotational direction neutral restoring spring is reverse input prevention clutch bearing assembly, characterized in that consisting of a coil spring. The method of claim 1, The control wheel is rotated by rotation of the input shaft with rotational resistance, such as a physical frictional force with the surface of the fixed body on which the control wheel is separately supported, when either of the inner and outer rings are engaged with the input shaft. Reverse input clutch bearing assembly, characterized in that the rotation resistor is further provided to enable. The method of claim 11, The rotational resistor, the reverse input prevention clutch bearing assembly, characterized in that the both ends are clamped by a fixed body installed on one side to surround the outer circumference of the control wheel and a ring-type clamp to induce frictional resistance between the contact surfaces. The method of claim 1, The one side of the circumference of the control wheel, the manual operation lever which can set the direction of rotation of the inner ring in any one direction by manual operation, characterized in that the reverse input prevention clutch bearing assembly further. The method of claim 1, The wedge ring assembly, An inclined surface in the axial direction that corresponds to an inclined surface formed on one of the circumferences of the inner and outer rings, and the inclined surface of any of the inner and outer rings by an axial movement stroke that moves forward and returns to the original position along the axial direction; An axial wedge ring in which the degree of adhesion is changed; Return means for returning the axial wedge ring to its original position without external force applied thereto; Rotating direction wedges arranged concentrically adjacent to the retainer to receive a portion of the rolling element and limit the rotation of the rolling element are formed toward the circumferential surface of the rolling element and with the axial wedge ring. A rotational wedge ring disposed adjacent thereto so as to be interlockable; A rotational wedge ring neutral restoring spring which provides an elastic coupling force so that the retainer and the rotational wedge ring rotate while the rotational force is greater than a predetermined elasticity so that the retainer and the rotational wedge ring rotate together at different rotational speeds; And Reverse direction preventing clutch bearing assembly, characterized in that it comprises a; rotation direction locking cam for elastically interlocking between the rotation direction wedge ring and the control wheel. The method of claim 14, The return means for the axial wedge ring has a cylindrical central body portion accommodated in a plurality of mounting holes formed at equal intervals along the circumferential predetermined line of the inner ring, and is ubiquitous to both sides of the cylindrical end of the central body portion. The formed eccentric shaft is inserted between the circumferential guide grooves formed along the circumference of the axial wedge ring and the axial guide grooves formed on the circumference of the control wheel, respectively, the shaft being eccentrically rotated with the seating hole of the inner ring as the center of rotation. Reverse input prevention clutch bearing assembly, characterized in that consisting of a directional drive cam. The method of claim 14, The return means of the axial wedge ring is disposed adjacent to one side of the axial wedge ring, the axial wedge ring neutral restoring spring in the form of a ring-shaped leaf spring that presses the axial wedge ring directly in the axial direction by contact. Reverse input prevention clutch bearing assembly, characterized in that consisting of. The method of claim 16, The axial wedge ring neutral restoring spring may be disposed on an opposite side of the axial wedge ring with a push pin configured to press the axial wedge ring in a direction in which the axial wedge ring neutral restoring spring is compressed. The push pin is composed of a pair, the reverse input preventing clutch bearing assembly, characterized in that coupled to the axial direction along the seat hole formed through the outer ring in the axial direction when the control wheel is rotated . The method of claim 14, The rotation direction locking cam has a locking cam shaft formed with a cam action surface unilaterally disposed on one side, and is coupled to the circumference of the control wheel to surround the locking cam shaft so that the locking cam shaft can be rotated to the left and right sides or returned to its original state. Reverse input preventing clutch bearing assembly comprising a cam spring to provide elasticity. The method of claim 14, The rotation direction locking cam, reverse input preventing clutch bearing assembly, characterized in that consisting of a spring bent in the 'W' shape.

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