Roller clutch

Abstract

The present application provides a roller clutch which adopts a simple structure without adjustment, realizes reliable engagement, reduction of drag torque and long service life while achieving improved assembly convenience, miniaturization and cost reduction, a force applying member (135) which applies force to a torque transmission roller (130) arranged between an inner ring (110) and an outer ring (115) to one side in the circumferential direction is composed of an annular elastic body, a balance roller (160) or a force adjusting protrusion (118) as a force adjusting member paired with the torque transmission roller (130) is arranged on the other side in the circumferential direction of the torque transmission roller (130), and the force applying member (135) is composed to be wrapped around the torque transmission roller (130) and the force adjusting member in a cross-wound manner.

Description

Technical Field

[0001] This invention relates to a roller clutch that uses rollers as a torque transmission component. Background Technology

[0002] As a clutch that transmits or cuts off torque from the input shaft side to the output shaft side, a roller clutch with the following structure is known: a plurality of wedge-shaped spaces that narrow in the circumferential direction are formed between an inner ring and an outer ring that are mounted on the same shaft; cylindrical rollers are disposed in each of the plurality of wedge-shaped spaces; and a plurality of force-applying members that apply force to the rollers in the circumferential direction are disposed thereon (for example, see Patent Document 1).

[0003] In such a roller clutch, for example, when the inner ring rotates in one circumferential direction, the rollers engage with both the outer and inner rings, causing them to rotate as a unit. On the other hand, for example, when the inner ring rotates in another circumferential direction, the rollers overcome the force applied by the force-applying member and move to the other circumferential side, thus preventing the rollers from engaging with either the outer or inner rings, and causing the inner ring to rotate relative to the outer ring.

[0004] In addition, roller clutches configured in a manner that allows for bidirectional relative rotation of the inner and outer rings are also known (for example, see Patent Document 2).

[0005] Furthermore, although the roller clutches described in Patent Document 1 and Patent Document 2 are both outer ring retaining types that retain rollers on the outer ring side, inner ring retaining types that retain rollers on the inner ring side are also known (for example, see Patent Document 3).

[0006] Patent documents

[0007] Patent Document 1: Japanese Patent Application Publication No. 2007-255604

[0008] Patent Document 2: Japanese Patent Application Publication No. 2020-046071

[0009] Patent Document 3: Japanese Patent Publication No. 2021-523327 Summary of the Invention

[0010] Therefore, the roller clutches described in Patent Documents 1 to 3 all require multiple force-applying components corresponding to multiple rollers, resulting in an increase in the number of parts, higher manufacturing costs, and increased structural complexity.

[0011] Furthermore, as described in Patent Documents 1 and 2 above, in outer ring retaining type roller clutches, when the inner and outer rings engage and rotate as a single unit, centrifugal force generates a force attempting to move the rollers towards the widening side of the wedge-shaped space (the direction of widening). If the component of this centrifugal force is greater than the force applied by the force-applying member, the rollers will not engage with the inner and outer rings, and torque cannot be transmitted between the inner and outer rings. Therefore, in outer ring retaining type roller clutches, measures to counteract centrifugal force are required to improve high-speed rotation performance.

[0012] As a countermeasure against centrifugal force, measures such as increasing the force applied by the force-applying member according to the rotational speed of the input or output shaft can be considered. However, if such a structure is adopted, the wear durability will decrease due to increased sliding resistance, and the drag torque will also deteriorate. In particular, in clutches configured with switchable operating modes, such as the roller clutch described in Patent Document 2, a large switching thrust (selection force) is required when switching operating modes. Therefore, measures such as countermeasures against sliding part wear, strengthening of the selector section, and increasing the thrust of the drive unit that serves as the selector drive mechanism are required, which leads to problems of large size and high cost.

[0013] As mentioned above, outer ring retaining roller clutches are practically difficult to apply in high-speed drives, such as electric drive axles (E-Axle) where one-way clutches are required to have high-speed rotation performance due to the high-speed rotation of motors.

[0014] If it is an inner-ring retaining type roller clutch as described in Patent Document 3, the engagement of the inner and outer rings can be maintained even if the centrifugal force increases. However, in roller clutches configured with switchable operating modes, switching operating modes under conditions of high centrifugal force on the rollers requires a large switching thrust (selection force). Therefore, even inner-ring retaining type roller clutches require measures such as countermeasures against slippage wear, increased strength of the selector section, and increased thrust of the drive unit that serves as the selector drive mechanism, resulting in problems of large size and high cost.

[0015] This invention is made to solve such problems, and its purpose is to provide a roller clutch that adopts a simple structure that does not require adjustment, while achieving improved ease of assembly, miniaturization and low cost, as well as reliable engagement, reduced drag torque and long service life.

[0016] This invention relates to a roller clutch comprising an inner ring and an outer ring arranged coaxially and capable of relative rotation. Between the outer circumferential surface of the inner ring and the inner circumferential surface of the outer ring, a plurality of receiving portions are formed, each having a wedge-shaped space that narrows towards one side in the circumferential direction. Torque transmission rollers are disposed in each of the receiving portions. A force-applying member is configured to apply force to each torque transmission roller towards one side in the circumferential direction. The force-applying member is composed of an annular elastic body. A plurality of force-adjusting members corresponding to each torque transmission roller are arranged in pairs with the torque transmission rollers on the other side of the circumferential direction. The force-applying members are arranged in a cross-wound manner around the paired torque transmission rollers and the force-adjusting members, thereby solving the aforementioned problems.

[0017] According to the present invention, by making the force-applying member a ring-shaped elastic body, and by employing a structure in which the force-applying member is cross-wound around a force-adjusting member and a torque-transmitting roller disposed on the other side of the circumference of the torque-transmitting roller, it is possible to apply force to multiple torque-transmitting rollers in one circumferential direction without separately disposing the force-applying member on multiple torque-transmitting rollers. Therefore, the ring-shaped force-applying member enables unified control of the movement of multiple torque-transmitting rollers, and the simple structure requiring no adjustment achieves improved assembly convenience, miniaturization, and low cost while ensuring reliable engagement.

[0018] By employing a structure in which the force-applying component is positioned at the axial center of the torque-transmitting roller and is cross-wound around the paired torque-transmitting rollers and the force-applying adjustment component, skewness (tilting) of the torque-transmitting rollers due to eccentric loading by the force-applying component can be prevented. This allows for stable meshing while increasing the torque capacity by increasing the contact area between the torque-transmitting rollers and the inner and outer rings. Furthermore, even without increasing the force applied by the force-applying component, stable meshing during high-speed rotation can be achieved, reducing the influence of centrifugal force. Moreover, because the torque-transmitting rollers can be made symmetrically shaped, misassembly of the torque-transmitting rollers can be prevented.

[0019] Furthermore, because the structure uses flange members fixed at both ends of the outer ring to limit the axial displacement of the torque transmission rollers, the outer ring is easier to manufacture and its axial dimensions can be easily miniaturized. Therefore, it is possible to miniaturize and simplify the structure of the roller clutch, while also improving the assemblability of the torque transmission rollers and force-applying components.

[0020] Furthermore, since the force adjustment component is composed of circumferentially movable balancing rollers, and the centrifugal force acting on the balancing rollers is greater than the centrifugal force acting on the torque transmission rollers, the centrifugal force allows the balancing rollers to apply a load to the torque transmission rollers on one side of the circumference. Therefore, even without increasing the force applied by the force application component, stable meshing during high-speed rotation can be achieved, enabling torque transmission between the inner and outer rings. Additionally, wear can be suppressed, drag torque can be reduced, and a longer service life can be achieved.

[0021] By making the balancing rollers the same size and weight as the torque transmission rollers, a structurally balanced roller clutch can be constructed.

[0022] Furthermore, by making the force adjustment component consist of protrusions integrally set on the inner or outer ring, the number of parts can be reduced to lower costs, while miniaturization and structural simplification can be easily achieved.

[0023] Furthermore, in a structure where the operating mode can be switched via a selector, the selection force can be minimized during both low-speed and high-speed rotational selection. This reduces selector wear and lowers the strength requirements for the selector. Additionally, a driver with lower thrust can be used as the selector drive mechanism, enabling miniaturization and cost reduction. Attached Figure Description

[0024] Figure 1 This is an exploded perspective view showing a configuration example of the roller clutch according to the first embodiment of the present invention.

[0025] Figure 2 It is a dissection representation Figure 1 A perspective view of a portion of the roller clutch shown.

[0026] Figure 3 When cut with a plane perpendicular to the axis of rotation Figure 1 The cross-sectional view shown is of a roller clutch.

[0027] Figure 4 It is when cut by a plane along the axis of rotation. Figure 1 A partial sectional view of the roller clutch shown.

[0028] Figure 5 It means Figure 1 The diagram shows a three-dimensional view of the structure of the outer ring in a roller clutch.

[0029] Figure 6 It means Figure 1 A perspective view of the selector structure in a roller clutch.

[0030] Figure 7 It means Figure 1 A schematic diagram of a portion of a roller clutch as viewed from the radial outside.

[0031] Figure 8A This indicates when the action mode is in locked mode. Figure 1 The diagram shows the main structural components of a roller clutch.

[0032] Figure 8B This is a schematic diagram showing the state of the torque transmission rollers and balance rollers during high-speed rotation.

[0033] Figure 9A This indicates when the motion mode is switched to two-way free mode. Figure 1 A schematic diagram of a portion of a roller clutch as viewed from the radial outside.

[0034] Figure 9B This indicates the state when the action mode is in the two-way free mode. Figure 1 The diagram shows the main structural components of a roller clutch.

[0035] Figure 10 This is a perspective view showing a partial cutaway of another configuration example of the roller clutch according to the first embodiment of the present invention.

[0036] Figure 11 It is when cut by a plane along the axis of rotation. Figure 10 A partial sectional view of the roller clutch shown.

[0037] Figure 12 It means Figure 10 A schematic diagram of a portion of a roller clutch as viewed from the radial outside.

[0038] Figure 13 It means Figure 10 The diagram shows a three-dimensional view of the structure of the outer ring in a roller clutch.

[0039] Figure 14 This is a partial cross-sectional view showing another configuration example of the roller clutch according to the first embodiment of the present invention, cut along a plane pointing towards the axis of rotation.

[0040] Figure 15 It means Figure 14 A schematic diagram of a portion of a roller clutch as viewed from the radial outside.

[0041] Figure 16 It means Figure 14 The diagram shows a three-dimensional view of the structure of the outer ring in a roller clutch.

[0042] Figure 17 This is a perspective view showing a portion of a configuration example of the roller clutch according to the second embodiment of the present invention.

[0043] Figure 18 When cut with a plane perpendicular to the axis of rotation Figure 17 The cross-sectional view shown is of a roller clutch.

[0044] Figure 19 It means Figure 17 The diagram shows a three-dimensional view of the structure of the outer ring of a roller clutch.

[0045] Figure 20A This indicates when the action mode is in locked mode. Figure 17 The diagram shows the main structural components of a roller clutch.

[0046] Figure 20B This indicates the state when the action mode is in the two-way free mode. Figure 17 The diagram shows the main structural components of a roller clutch.

[0047] Symbol Explanation

[0048] 100 - Roller clutch; 110 - Inner ring; 111 - Large-diameter cylindrical part; 112 - Small-diameter cylindrical part; 115 - Outer ring; 116 - Force-applying component support protrusion; 117 - End wall; 118 - Force-applying adjustment protrusion; 120 - Receiving part; 121 - Wedge-shaped space; 122 - Cam surface; 123 - Roller holding space; 124 - Roller limiting surface; 125 - Roller pressing part receiving space; 126 - Conical surface; 127 - Force application Space for component configuration; 130 - Torque transmission roller; 131 - Loading groove for force-applying component; 135 - Force-applying component; 140 - Flange component; 140a - Flange component on one end; 140b - Flange component on the other end; 141 - Through hole; 145 - Pin component; 150 - Selector; 151 - Root; 152 - Roller pressing part; 153 - Taper; 160 - Balance roller; 161 - Loading groove for force-applying component; C - Rotation axis. Detailed Implementation

[0049] <First Embodiment>

[0050] like Figures 1 to 4 As shown, the roller clutch 100 according to the first embodiment includes an inner ring 110, an outer ring 115, a plurality of torque transmission rollers 130, a force application member 135, a flange member 140, and a selector 150. Figures 1 to 4 C in the figure represents the axis of rotation.

[0051] The inner ring 110 and the outer ring 115 are configured to rotate relative to each other on the same axis when the outer circumferential surface of the inner ring 110 and the inner circumferential surface of the outer ring 115 are close to each other and opposite to each other, thereby suppressing the eccentricity of the inner ring 110 and the outer ring 115.

[0052] Between the outer peripheral surface of the inner ring 110 and the inner peripheral surface of the outer ring 115, a plurality of receiving portions 120 are formed at predetermined intervals in the circumferential direction. In this embodiment, the outer peripheral surface of the inner ring 110 is cylindrical about the rotation axis C, and the receiving portions 120 are formed on the inner peripheral edge of the outer ring 115.

[0053] The inner ring 110 is made of, for example, sintered metal (including the case of impregnation with lubricant) or steel, and its outer peripheral surface has: a large-diameter cylindrical portion 111, which forms a contact surface (meshing surface) with the torque transmission roller 130; and a small-diameter cylindrical portion 112, which is continuous at one axial end of the large-diameter cylindrical portion 111.

[0054] The outer ring 115 is made of, for example, sintered metal (including those impregnated with lubricant) or steel, such as... Figure 5 As shown, an accommodating portion 120 is formed on the inner peripheral portion of one axial end face of a cylindrical substrate, thereby forming an outer ring 115. A recess is formed such that an end wall 117 is retained on the other axial end side of the outer ring 115, thereby forming the accommodating portion 120.

[0055] The receiving portion 120 has: a wedge-shaped space 121 that narrows towards one circumferential side; and a roller retaining space 123 that continues on the other circumferential side of the wedge-shaped space 121. The wedge-shaped space 121 has a cam surface 122 that extends radially inward toward one circumferential side. The roller retaining space 123 has a roller limiting surface 124 that extends radially outward toward one circumferential side.

[0056] Additionally, on one circumferential side of the wedge-shaped space 121, there is a continuous roller pressing portion receiving space 125 that can accommodate the roller pressing portion 152 of the selector 150, which forcibly moves the torque transmission roller 130 in the circumferential direction. The opening surface of the wall portion forming the circumferential side of the roller pressing portion receiving space 125 becomes a conical surface 126 that is inclined towards the other end in the axial direction and in the other circumferential direction.

[0057] Figure 5 116 in the figure is a force-applying member support protrusion, which is located on one side of the circumferential direction of each receiving part 120 on one end face of the outer ring 115.

[0058] Multiple torque transmission rollers 130 are each made of, for example, steel, and are configured to protrude axially outward from one end face of the outer ring 115 when housed within the receiving portion 120. A force-applying member mounting groove 131 is formed on the circumferential surface of the portion of the torque transmission roller 130 that protrudes further from one end face of the outer ring 115, extending over the entire circumferential span.

[0059] like Figure 4 As shown, the axial movement of the plurality of torque transmission rollers 130 is restricted by the end wall 117 and the flange member 140 on the other side of the axial direction in the receiving portion 120.

[0060] The force-applying member 135 is a component shared by multiple torque-transmitting rollers 130, and is composed of a ring-shaped elastic body. In this embodiment, a garter spring is used as the force-applying member 135, for example.

[0061] The force-applying component 135 is fitted into the force-applying component mounting groove 131 of each torque transmission roller 130 and the force-applying component support protrusion 116 of the outer ring 115.

[0062] The flange member 140 is, for example, a sheet metal ring plate. On one axial end of the outer ring 115, with the small-diameter cylindrical portion 112 of the inner ring 110 inserted, it is located coaxially with the inner ring 110 and the outer ring 115 and is fixed to the outer ring 115 by the pin member 145.

[0063] Multiple through holes 141 are formed on the flange member 140 at positions opposite to the roller pressing portion receiving spaces 125 on the outer ring 115. These holes are configured such that the roller pressing portion 152 of the selector 150 is inserted, and the holes penetrate in the thickness direction and extend upward in the axial direction.

[0064] Selector 150 is configured to switch between a one-way locking mode and a two-way free mode. The one-way locking mode prohibits relative rotation of the inner ring 110 and the outer ring 115 in one circumferential direction, while the two-way free mode allows relative rotation of the inner ring 110 and the outer ring 115 in two circumferential directions.

[0065] In this embodiment, the selector 150 is configured to move axially upward independently of the rotational movements of the inner ring 110 and the outer ring 115 via a driver (not shown). For example, when the operating mode is switched from a one-way locking mode to a two-way free mode, the torque transmission roller 130 is forcibly moved to the other side in the circumferential direction, thereby keeping the torque transmission roller 130 in a suspended state relative to the inner ring 110 and the outer ring 115.

[0066] Selector 150 is made of, for example, sheet metal, sintered metal, or steel, such as Figure 6As shown, it includes: a ring-shaped root portion 151; and multiple roller pressing portions 152 corresponding to multiple torque transmission rollers 130 respectively.

[0067] Each roller pressing portion 152 is formed by an integrally disposed columnar body on the other side of the root portion 151, extending toward the other end in the axial direction, and has a tapered portion 153 formed in a way that narrows in width toward the top end. The tapered portion 153 is formed such that the side of the circumferential side extends obliquely toward the other side in the circumferential direction along with toward the other end in the axial direction.

[0068] like Figure 7 As shown, a plurality of roller pressing portions 152 are inserted into through holes 141 formed on flange member 140, with the top portion located within roller pressing portion receiving space 125.

[0069] Therefore, in the roller clutch 100 of this embodiment, a plurality of force adjustment members, namely balance rollers 160, which correspond to a plurality of torque transmission rollers 130 respectively, are arranged in pairs with the torque transmission rollers 130 on the other side of the circumference of the torque transmission rollers 130.

[0070] Multiple balancing rollers 160 are, for example, made of steel, such as... Figure 7 As shown, when housed within the receiving portion 120, the roller 160 is shaped to protrude axially outward compared to one end face of the outer ring 115. On the circumferential surface of the portion of the balance roller 160 that protrudes further than one end face of the outer ring 115, a force-applying member mounting groove 161 is formed in such a way that it extends across the entire circumferential span.

[0071] like Figure 8A As shown, the force-applying member 135 is wrapped in a cross-wound manner on the pair of torque transmission rollers 130 and balance rollers 160, so that the inner circumference contacts the torque transmission rollers 130 and the outer circumference contacts the balance rollers 160.

[0072] Therefore, the force S1 of the force-applying member 135 acts on the torque transmission roller 130 in the inner ring direction, and the component force S1h along the cam surface 122 of the wedge-shaped space 121 acts on the torque transmission roller 130 in one circumferential direction (meshing direction).

[0073] On the other hand, the force S2 of the force-applying member 135 acts on the balance roller 160 in the outer ring direction, and the balance roller 160 is kept fixed by the component force S2h along the roller limiting surface 124 of the roller holding space 123 in the direction of the roller holding space 123, in the state of applying force to the other side in the circumferential direction.

[0074] In the roller clutch 100 of this embodiment, when the inner ring 110 and the outer ring 115 engage and rotate as a whole, the component C2h of the centrifugal force C2 acting on the balance roller 160 in the direction of the roller limiting surface 124 is greater than the component C1h of the centrifugal force C1 acting on the torque transmission roller 130 in the direction of the cam surface 122.

[0075] The magnitude of the centrifugal force acting on the balance roller 160 can be adjusted by appropriately changing the angle θ2 formed by the straight line L2 connecting the rotation axis C and the center of the balance roller 160 on the cross section perpendicular to the rotation axis relative to the roller limiting surface 124 in the accommodating part 120, the weight of the balance roller 160, or the amount of winding (winding angle) of the force-applying member 135 on the balance roller 160.

[0076] In this embodiment, the structure, size (shape), and weight of the balancing roller 160 are the same as those of the torque transmission roller 130, thereby structurally balancing the roller clutch 100. Furthermore, the amount of winding of the force-applying member 135 around the balancing roller 160 is approximately the same as the amount of winding around the torque transmission roller 130. That is, the force S1 applied by the force-applying member 135 acting on the torque transmission roller 130 is configured to be approximately equal to the force S2 applied on the balancing roller 160. Therefore, by configuring the angle θ2 formed by the straight line L2 connecting the rotation axis C and the center of the balancing roller 160 relative to the roller limiting surface 124 in the receiving portion 120 to be greater than the angle θ1 formed by the straight line L1 connecting the rotation axis C and the center of the torque transmission roller 130 relative to the cam surface 122 in the receiving portion 120, the component force C2h of the centrifugal force acting on the balancing roller 160 is greater than the component force C1h of the centrifugal force acting on the torque transmission roller 130.

[0077] In the roller clutch 100 described in this embodiment, when the operating mode is in the locked mode, the inner ring 110 is moved in one circumferential direction ( Figure 3 Rotate clockwise (in the middle), or rotate the outer ring 115 in the other direction (circumferentially). Figure 3 The torque transmission roller 130 rotates counterclockwise (in the same direction as the inner ring 110), thereby engaging with the inner ring 110 and the outer ring 115 to transmit torque between the inner ring 110 and the outer ring 115. On the other hand, when the inner ring 110 is rotated in the other circumferential direction, or when the outer ring 115 is rotated in one circumferential direction, the torque transmission roller 130 does not engage with the inner ring 110 and the outer ring 115, and one of the inner ring 110 and the outer ring 115 spins freely relative to the other.

[0078] When the inner ring 110 and the outer ring 115 mesh and rotate as a whole, if the component force C1h of the centrifugal force acting on the torque transmission roller 130 is less than the component force S1h of the force applied by the force-applying member 135 acting on the torque transmission roller 130, the state in which the balancing roller 160 is held and fixed in the roller holding space 123 in the receiving portion 120 is maintained. Thus, the force-applying member 135 can apply an appropriate force to the circumferential side of the torque transmission roller 130, thereby enabling the desired clutch function to be performed.

[0079] Furthermore, when the centrifugal force C1h acting on the torque transmission roller 130 is greater than the force S1h acting on the force-applying member 135 of the torque transmission roller 130 during high-speed rotation, the torque transmission roller 130 moves circumferentially to the other side along the cam surface 122, while the balancing roller 160 moves circumferentially to one side along the roller limiting surface 124. However, since the centrifugal force C2h acting on the balancing roller 160 is configured to be greater than the centrifugal force C1h acting on the torque transmission roller 130, the balancing roller 160 moves circumferentially earlier than the torque transmission roller 130, such as... Figure 8B As shown, a load is applied to the torque transmission roller 130 in the circumferential direction. Therefore, even when the outer ring retaining type roller clutch 100, which holds the torque transmission roller 130 on the outer ring side, is subjected to a large centrifugal force during high-speed rotation, it can maintain the engagement of the torque transmission roller 130 with the inner ring 110 and the outer ring 115.

[0080] Furthermore, in the roller clutch 100 according to this embodiment, the operating mode can be switched by moving the selector 150 axially. When the operating mode is switched from the locked mode (e.g., ...), Figure 7 When switching from the state shown to the bidirectional free mode, as follows: Figure 9A As shown, by moving the selector 150 to the other end in the axial direction, the root end portion of the roller pressing portion 152 of the selector 150 is brought into the roller pressing portion receiving space 125, and the torque-transmitting roller 130 is forced to move circumferentially to the other side. Thus, as... Figure 9B As shown, the torque transmission roller 130 can be kept in a suspended state relative to the inner ring 110 and the outer ring 115, with one of the inner ring 110 and the outer ring 115 spinning freely in both circumferential directions relative to the other.

[0081] As described above, in the roller clutch 100 of this embodiment, by making the force-applying member 135 a ring-shaped elastic body and configuring it such that the force applied to the torque transmission roller 130 can be adjusted by the balance roller 160, the operation of all torque transmission rollers 130 can be uniformly controlled. Therefore, reliable engagement can be achieved regardless of the magnitude of the centrifugal force acting on the torque transmission roller 130, and drag torque and wear can be minimized both at low and high speeds.

[0082] In the above embodiments, although the structure of the force-applying member 135 being respectively sleeved on one axial end of the torque transmission roller 130 and the balance roller 160 has been described, as follows... Figures 10 to 12 As shown, another possible structure is to have the force-applying member 135 wrapped around the pair of torque-transmitting rollers 130 and balance rollers 160 in a cross-wound manner at the axial center of each of the torque-transmitting rollers 130 and balance rollers 160.

[0083] In the roller clutch 100 described in this embodiment, such as Figure 13 As shown, the outer ring 115 is configured such that a recess containing a receiving portion 120 and a space 127 for arranging a force-applying member is formed in the inner peripheral portion of one axial end face of the cylindrical substrate, such that an end wall 117 is retained on the other axial end side of the outer ring 115. The structure of the receiving portion 120 is similar to... Figure 1 The outer ring 115 of the roller clutch 100 shown has the same receiving portion 120 as the roller clutch 100, and has a wedge-shaped space 121, a roller holding space 123 and a roller pressing portion receiving space 125.

[0084] In the outer ring 115 of this embodiment, the force-applying member support protrusion 116 is provided in the recess at a position radially outside the roller pressing part receiving space 125, and one end face of the axial direction is formed as a flat surface. In addition, the space between adjacent receiving parts 120 becomes the force-applying member placement space 127.

[0085] At the axial center of each of the torque transmission roller 130 and the balance roller 160, there are force-applying member mounting grooves 131 and 161 extending over the entire circumferential span. The force-applying member 135 is wrapped around the pair of torque transmission rollers 130 and balance rollers 160 in a cross-wound manner so that the inner circumference contacts the torque transmission roller 130 and the outer circumference contacts the balance roller 160.

[0086] In this embodiment, the torque transmission roller 130 and the balance roller 160 are respectively arranged in the receiving portion 120 in such a way that when the other end face of the axial ring 115 abuts against the end wall 117 on the other end side of the axial ring 115, they do not protrude further outward in the axial direction compared to one end face of the outer ring 115.

[0087] On one end face of the outer ring 115, a ring-shaped flange member 140 is fixed in an abutting state, thereby restricting the axial relative displacement of the torque transmission roller 130 and the balance roller 160.

[0088] By employing a structure in which the force-applying member 135 is arranged in a cross-wound manner around the pair of torque-transmitting rollers 130 and balancing rollers 160 at the axial center of the torque-transmitting rollers, it is possible to prevent the torque-transmitting rollers 130 from skewing (tilting) due to the eccentric loading of the force-applying member 135 on the torque-transmitting rollers 130. Thus, while achieving stable meshing, the torque capacity can be increased by increasing the contact area between the torque-transmitting rollers 130 and the inner and outer rings 110 and 115.

[0089] Furthermore, even without increasing the force applied by the force-applying member 135, it is possible to stabilize the meshing during high-speed rotation and reduce the influence of centrifugal force. Moreover, since the torque transmission roller 130 can be configured in a symmetrical shape, misassembly of the torque transmission roller 130 can be prevented.

[0090] In the above description, although a structure is used to limit the relative axial displacement of the torque transmission roller 130 and the balance roller 160 through the end wall 117 and flange member 140 on the other axial side of the outer ring 115, as... Figure 14 and Figure 15 As shown, the relative axial displacement of the torque transmission roller 130 and the balance roller 160 can also be limited by providing one end flange member 140a and the other end flange member 140b at both ends of the outer ring 115.

[0091] In the roller clutch 100 described in this embodiment, such as Figure 16 As shown, an outer ring 115 is formed by forming a receiving portion 120 and a force-applying member placement space 127 on the inner peripheral portion of one axial end face of a cylindrical substrate. The receiving portion 120 has a wedge-shaped space 121, a roller holding space 123, and a roller pressing portion receiving space 125, and is formed through in the thickness direction so that the respective axial other ends of the torque transmission roller 130 and the balancing roller 160 are exposed to the outside. A recess is formed such that an end wall 117 is retained on the other axial end side of the outer ring 115, thereby forming the force-applying member placement space 127. A force-applying member support protrusion 116 is provided at a position on the radially outer side of the roller pressing portion receiving space 125 on the end wall 117, so that the two axial end faces of the outer ring 115 are formed as flat surfaces.

[0092] In this embodiment, the torque transmission roller 130 and the balance roller 160 are respectively configured so that they do not protrude axially outward compared to one end face and the other end face of the outer ring 115.

[0093] At the axial center of the torque transmission roller 130 and the balance roller 160, there are force-applying component mounting grooves 131 and 161 that extend over the entire circumferential span, respectively.

[0094] The force-applying component 135 is wrapped in a cross-wound manner on the pair of torque transmission rollers 130 and balance rollers 160 so that the inner circumference contacts the torque transmission rollers 130 and the outer circumference contacts the balance rollers 160.

[0095] In this embodiment, the annular plate-shaped one-end flange member 140a and the annular plate-shaped other-end flange member 140b are respectively fixed to one end face and the other end face of the outer ring 115 in an abutting state, thereby restricting the relative axial displacement of the torque transmission roller 130 and the balance roller 160.

[0096] As in this embodiment, since the axial displacement of the torque transmission roller 130 is limited by a structure in which one end flange member 140a and the other end flange member 140b are respectively fixed to both ends of the outer ring 115, the outer ring 115 is easier to manufacture and its axial dimensions can be easily miniaturized. Therefore, the roller clutch 100 can be miniaturized and its structure simplified, while the assemblability of the torque transmission roller 130 and the force application member 135 can be improved.

[0097] <Second Implementation>

[0098] like Figure 17 and Figure 18 As shown, the roller clutch 100 according to the second embodiment of the present invention has the same structure as the roller clutch 100 according to the first embodiment, except that the structure of the force adjustment member is different. Figure 17 and Figure 18 In this document, the same symbols are used for the components that are identical to those in the roller clutch 100 of the first embodiment, and their descriptions are omitted.

[0099] like Figure 19 As shown, in this embodiment, on the circumferential side of each receiving portion 120 on one end face of the outer ring 115, a cylindrical force-adjusting protrusion 118, which is paired with the torque transmission roller 130 and serves as a force-adjusting member, is provided.

[0100] like Figure 20AAs shown, the force-applying member 135 is fitted onto the torque-transmitting roller 130, the force-applying member support protrusion 116, and the force-applying adjustment protrusion 118 in a cross-wound manner. Thus, the force applied by the force-applying member 135 is divided laterally in the direction of the cam surface 122 forming the wedge-shaped space 121, acting on the torque-transmitting roller 130, thereby applying a force to the torque-transmitting roller 130 in the circumferential direction.

[0101] Even in the roller clutch 100 described in this embodiment, when the operating mode is in the locked mode, the inner ring 110 will move in one circumferential direction ( Figure 20A Rotate clockwise (in the middle), or rotate the outer ring 115 in the other direction (circumferentially). Figure 20A The torque transmission roller 130 rotates counterclockwise (in the same direction as the inner ring 110), thereby engaging with the inner ring 110 and the outer ring 115 to transmit torque between the inner ring 110 and the outer ring 115. On the other hand, when the inner ring 110 is rotated in the opposite circumferential direction, or when the outer ring 115 is rotated in one circumferential direction, the torque transmission roller 130 does not engage with the inner ring 110 and the outer ring 115, and one of the inner ring 110 and the outer ring 115 spins freely relative to the other.

[0102] Additionally, the operating mode can be switched by moving the selector 150 axially upwards. When the operating mode is switched from the locked mode (e.g., ...), Figure 20A When switching to the bidirectional free mode (as shown), the selector 150 is moved to the other end of the axial direction, thereby causing the root end portion of the roller pressing part 152 of the selector 150 to enter the roller pressing part receiving space 125, and forcibly moving the torque transmission roller 130 to the other side of the circumference.

[0103] Therefore, as Figure 20B As shown, the torque transmission roller 130 can be kept in a suspended state relative to the inner ring 110 and the outer ring 115, with one of the inner ring 110 and the outer ring 115 spinning freely in both circumferential directions relative to the other.

[0104] According to the roller clutch 100 of this embodiment, the winding amount of the force-applying member 135 on the torque transmission roller 130 is adjusted by the force-applying adjustment protrusion 118. Therefore, it is not necessary to separately configure the force-applying member 135 for each of the multiple torque transmission rollers 130; force can be applied to each torque transmission roller 130 in a circumferential direction. The annular force-applying member 135 allows for unified control of the movement of the multiple torque transmission rollers 130. Thus, by adopting a simple structure that requires no adjustment, reliable engagement can be achieved while simultaneously improving assembly convenience, miniaturization, and cost reduction.

[0105] While the embodiments of the present invention have been described above, the present invention is not limited to the above-described structure.

[0106] For example, in the above-described embodiments, although the operating mode can be switched via a selector, it can also be configured to operate the roller clutch as a normal one-way clutch.

[0107] Furthermore, while the outer-ring retaining roller clutch has been described in the above embodiments, an inner-ring retaining roller clutch can also be used. In this type of clutch, the force adjustment member is composed of balancing rollers, and the centrifugal force acting on the balancing rollers is greater than the centrifugal force acting on the torque transmission rollers. This prevents excessive engagement force caused by centrifugal force during high-speed rotation. Consequently, the outer ring surface pressure and selection force can be reduced, and torque can be transmitted between the inner and outer rings. In addition, while suppressing wear, drag torque can be reduced, resulting in a longer service life.

[0108] Furthermore, in the first embodiment described above, although the angle formed by the straight line connecting the rotation axis and the center of the balancing roller relative to the roller limiting surface in the accommodating portion is configured to be greater than the angle formed by the straight line connecting the rotation axis and the center of the torque transmission roller relative to the cam surface in the accommodating portion, it can also be configured such that the component of the centrifugal force acting on the balancing roller is greater than the component of the centrifugal force acting on the torque transmission roller by the size or weight of the balancing roller.

[0109] Furthermore, even in the second embodiment described above, a structure can be adopted in which the force-applying member is wrapped in a cross-wound manner around the pair of torque-transmitting rollers and the force-applying adjustment protrusion at the axial center of the torque-transmitting roller. Alternatively, a structure can be adopted in which one end flange member and the other end flange member are respectively provided at both ends of the outer ring, thereby restricting the axial displacement of the torque-transmitting roller.

[0110] Furthermore, regarding the basic structure of the roller clutch, in the above-described embodiment, the contact surface (cam surface) of the torque transmission roller that divides the space into a wedge shape is constructed as a flat inclined surface, but the cam surface can also be a free-form surface.

[0111] In addition, the force-applying component is not limited to a clamping spring, but can be any ring-shaped elastic body.

[0112] Furthermore, the outer and inner rings can also adopt a modular structure that is integrated with other parts such as gears or shafts.

[0113] Furthermore, although the above-described embodiments employ a structure in which the flange member is fixed to the outer ring by pressing or riveting the pin member, it can also be fixed by fastening members such as bolts.

Claims

1. A roller clutch comprising an inner ring and an outer ring arranged coaxially and rotatable relative to each other, wherein a plurality of receiving portions having a wedge-shaped space narrowing towards one circumferential direction are formed between the outer circumferential surface of the inner ring and the inner circumferential surface of the outer ring, torque transmission rollers are disposed in each of the receiving portions, and a force-applying member is configured to apply a force towards one circumferential direction to each of the torque transmission rollers, characterized in that, The force-applying component is composed of a ring-shaped elastic body. Multiple force adjustment members corresponding to each of the torque transmission rollers are configured in pairs with the torque transmission rollers on the other side of the circumference of the torque transmission rollers. The force-applying component is wrapped in a cross-wound manner around the pair of torque-transmitting rollers and the force-applying adjustment component.

2. The roller clutch according to claim 1, characterized in that, in At the axial center of the torque transmission roller, the force-applying member is wrapped in a cross-wound manner around the pair of torque transmission rollers and the force-applying adjustment member.

3. The roller clutch according to claim 1, characterized in that, On both sides of the outer ring, flange members are fixed to restrict the axial displacement of the torque transmission roller.

4. The roller clutch according to claim 1, characterized in that, The force adjustment component is composed of balance rollers. The balancing rollers are disposed within the receiving portion. The angle formed by the straight line connecting the rotation axis and the center of the balancing roller on a section perpendicular to the rotation axis relative to the roller limiting surface in the receiving part, the weight of the balancing roller, or the amount of winding of the force-applying member on the balancing roller is configured such that the centrifugal force acting on the balancing roller is greater than the centrifugal force acting on the torque transmission roller.

5. The roller clutch according to claim 4, characterized in that, The balancing roller and the torque transmission roller are the same size and have the same weight.

6. The roller clutch according to claim 1, characterized in that, The force adjustment component is composed of cylindrical protrusions disposed on the inner ring or the outer ring.

7. The roller clutch according to claim 1, characterized in that, The device includes a selector configured to switch between a one-way locking mode and a two-way free mode. The one-way locking mode prohibits relative rotation of the inner and outer rings in one circumferential direction, while the two-way free mode allows relative rotation of the inner and outer rings in both circumferential directions. The selector is configured such that when the operating mode is switched from a one-way locking mode to a two-way free mode, the torque transmission roller is forcibly moved to the other side in the circumferential direction, thereby keeping the torque transmission roller in a suspended state relative to the outer ring and the inner ring.

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