WO2006037260A1

WO2006037260A1 - Cam wedge type one-way clutch

Info

Publication number: WO2006037260A1
Application number: PCT/CN2005/000433
Authority: WO
Inventors: Hui Cao
Original assignee: Xiamen Boltun Co., Ltd.
Priority date: 2004-10-08
Filing date: 2005-04-01
Publication date: 2006-04-13

Abstract

This invention relates to a cam wedge type one-way clutch, which includes a outer race, an inner race, a cam wedge and a circular spring, wherein some cam wedges are arranged closely between said outer race and inner race. The distance between the outer race and the inner race is smaller than the long diameter of the cam but larger than the short diameter of said cam. Fulcrums are formed on said cam wedges. A annular spring is formed by coupling column type spool spring. Said annular spring is provided between the inner race and the fulcrums of said cam wedge and applies force to said fulcrums to make the cam wedge return to its original location during moving. The part with long diameter of said cam wedge always contacts with said outer race and the inner race. The device of this invention has the advantages as following: it has few components, low cost, high reliability, and simple and compact construction. The cam wedge has high compressive strength.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a cam wedge type overrunning clutch, which belongs to a mechanical transmission device and can be used for a transmission device in a loader gearbox, and can be applied to various overrunning, backstop, and indexing. In the transmission mechanism. BACKGROUND OF THE INVENTION Overrunning clutches, also known as one-way clutches or one-way bearings, are devices that can only transfer power from one steering. When the speed of the active raceway is the same as the speed of the driven raceway, the active raceway is driven to the driven raceway. When the speed of the active raceway is less than that of the driven raceway, the driven raceway can be freely driven.

Overrunning clutches are widely used in aircraft, tanks, military trucks, off-road vehicles, loaders, automobiles, mining machinery, machine tools, printing machinery, textile machinery, spring machinery and more. At present, the clutches used in various types of mechanical transmissions are mainly roller type overrunning clutches and wedge type one-way overrunning clutches.

The existing wedge type overrunning clutches are various, but many wedge type overrunning clutches have cages. The wedge type overrunning clutch shown in Fig. 1 has double cages A2 and A21, as shown in Fig. 1. The CN1103875C patent also has a cage B3, and the CN2473383Y patent shown in Fig. 2 also has a cage B4, so that there are many components, low safety and reliability in use, high product cost, complicated structure, and not compact, and the wedge is provided. The space of the block is small, and the relative volume of the wedge is designed to be small, so the compressive strength is correspondingly low.

In addition, as shown in Figures 1 and 4, these clutches are in contact with the outer ring A3 or C3 and the inner ring A4 or C4 during movement because the cam A1 or C1 is acted upon by the spring A5 or C5, even if it is "off" In the state of ", the cam A1 or C1 is still in contact with the outer ring A3 or C3 and the inner ring A4 or C4, and there is friction, so the noise is large during use and the service life is short. SUMMARY OF THE INVENTION It is an object of the present invention to provide a cam wedge type overrunning clutch which is low in overall device components, low in cost, high in safety and reliability, simple in structure, compact, and high in compressive strength of wedges.

Another object of the present invention is to provide a cam wedge type overrunning clutch, which can reduce noise and extend noise while reducing components of the device, reducing cost, improving safety and reliability, making the structure simple and compact, and having high compressive strength of the wedge. Service life.

In order to achieve the above object, the first solution of the present invention is: The cam wedge type overrunning clutch is mainly composed of an outer ring, an inner ring, a cam wedge and a ring spring, wherein: a plurality of cam wedges are disposed between the outer ring and the inner ring, and between the outer ring and the inner ring. The spacing is smaller than the long diameter of the cam and larger than the short diameter of the cam, the fulcrum is formed on the cam wedge, the annular spring is formed by the cylindrical winding spring end to end, and the annular spring is disposed between the inner ring and the fulcrum of the cam wedge, and The outward tension of the annular spring acts on the fulcrum of the cam wedge, causing the cam wedge to reset during movement, and the long diameter portion of the cam wedge is always in contact with the outer and inner rings.

When the structure is mounted on the two-shaft assembly in the loader gearbox, the cam wedge and the ring spring are assembled between the outer ring and the inner ring, and the inner ring is fixed to the input shaft by means of a spline or a pin, and at the same time, A bearing is mounted between the input shaft and the outer and outer ring gears, and then the bearing sleeve is fixed to the input shaft by screws, thereby positioning the bearing, and finally, the outer ring and the outer ring gear are screwed. In use, the outward tension of the annular spring acts on the fulcrum of the cam wedge to achieve clutching. When the speed of the outer ring gear is less than the speed of the input shaft, the inner ring is reversed relative to the outer ring, and the cam wedge and the outer ring are only slightly in contact with each other, and the overrunning clutch is in an "off" state; when the outer ring gear is faster than Or equal to the speed of the input shaft, when the inner ring rotates relative to the outer ring, the cam wedge gradually tilts to the radial direction, because the height of the cam wedge is greater than the distance between the outer ring and the inner ring, so that the outer ring and The inner ring catches the cam wedge, and the card is used for the cam wedge to clamp the outer ring and the inner ring at the same time, so that the outer ring rotates with the inner ring to output power, and the overrunning clutch is in the "closed" state. .

The second solution of the invention is:

A cam wedge type overrunning clutch is assembled on the bearing, wherein: a plurality of cam wedges abutting each other are disposed between the outer ring and the inner ring of the bearing, and the longitudinal diameter of the cam is larger than the spacing between the outer ring and the inner ring The short diameter of the cam is smaller than the distance between the outer ring and the inner ring, a fulcrum is formed on the cam wedge, and a circular spring is formed end to end by a cylindrical winding spring, and the annular spring is disposed between the inner ring and the fulcrum of the cam wedge. And the outward tension of the ring spring acts on the fulcrum of the cam wedge, so that the cam wedge is reset during the movement, and the long diameter portion of the cam wedge is always in contact with the outer ring and the inner ring.

The above bearings are ball bearings or roller bearings.

The end of the cam wedge is provided with a baffle that is fixed between the outer ring and the inner ring of the bearing.

The structure is disposed between the outer ring and the inner ring of the bearing in a manner that the cam wedges are placed against each other, and the cam wedge is always in contact with the outer ring and the inner ring of the bearing by the outward tension of the annular spring. Thereby the cam wedge is restrained between the outer and inner rings of the bearing, so that it is no longer necessary to add a special cage for limiting the cam wedge. In use, the outer tension of the annular spring acts on the fulcrum on the cam wedge, and the long diameter portion of the cam wedge is pre-tensioned on the raceway between the outer ring and the inner ring, and the clutch is engaged by friction.

The third solution of the invention is:

The cam wedge type overrunning clutch is mainly composed of an outer ring, a shaft, a cam wedge and a ring spring, wherein: a plurality of cam wedges are disposed between the outer cymbal and the shaft, and the outer ring The distance between the shaft and the shaft is smaller than the long diameter of the cam and larger than the short diameter of the cam. The fulcrum is formed on the cam wedge. The annular spring is formed by the end of the cylindrical winding spring. The annular spring is disposed at the fulcrum of the shaft and the cam wedge. And the outer tension of the annular spring acts on the fulcrum of the cam wedge, so that the cam wedge always contacts the inner race of the outer ring, and the outward tension of the annular spring is smaller than that of the outer ring and the reverse rotation of the shaft The sum of the centrifugal force and the inertial force is greater than the difference between the centrifugal force and the inertial force of the cam when the outer ring and the shaft rotate in the same direction, so that the cam and the outer raceway of the shaft are separated when the outer ring and the shaft rotate in opposite directions, and the outer cymbal and The cam is in contact with the outer raceway of the shaft when the shaft rotates in the same direction, thereby forming a non-contact cam clutch.

The inner shaft is fixedly disposed with an inner cymbal, and the plurality of cam wedges are disposed between the outer ring and the inner ring. The spacing between the outer ring and the inner ring is smaller than the long diameter of the cam and larger than the short diameter of the cam. Set between the inner ring and the fulcrum of the cam wedge.

When the structure is used, the outward tension of the annular spring acts on the fulcrum of the cam wedge to achieve the clutch, and the cam is in the "off" state and the shaft (or inner ring) by precisely designing the outward tension of the annular spring. The outer raceway is non-contact. When the speed of the outer ring exceeds a certain value, under the action of the centrifugal force and the inertial force against the outward tension of the ring spring, the small arc of the cam is closely adhered to the inner raceway of the outer ring, and the cam is smoothed by the influence of the inertial force. When the outer ring rotates, the large arc of the cam leaves the outer raceway of the shaft (or inner ring), that is, the cam and the outer raceway of the shaft (or inner ring) are not in contact, so there is no frictional sound of contact. , the noise is small, the service life is long, the overrunning clutch is in the state of "off"; when the speed of the outer ring is less than a certain value or at rest, under the action of the outward tension of the ring spring, the small 'circular surface of the cam is in contact with the outside The inner raceway of the ring, in the condition that the outward tension and the inertial force of the annular spring work together to overcome the centrifugal force, finally the cam is rotated along the outer ring until its large arc contacts the outer raceway of the shaft (or the inner ring). Since the long diameter of the cam is larger than the distance between the outer ring and the shaft (or the inner ring), under the clamping action of the cam, the overrunning clutch is in a "closed" state, and between the outer ring and the shaft (or the inner ring) Can be achieved between each other Drive.

The fulcrum on the cam wedge is formed at both ends of the cam wedge or in the middle of the cam wedge.

After adopting the above structure, the present invention has a significantly reduced component, reduced cost, correspondingly improved safety and reliability, a simpler and more compact structure, and a larger space for setting cams, cams, compared with the prior art. The volume can be designed to be relatively larger, so the compressive strength is greatly improved. BRIEF DESCRIPTION OF DRAWINGS FIG. 1 is a partial cross-sectional view of a conventional wedge type one-way overrunning clutch;

Figure 2 is a schematic structural view of a one-way bearing in the CN1103875C patent;

Figure 3 is a schematic structural view of a one-way bearing in the CN2473383Y patent;

Figure 4 is a partial cross-sectional view showing another conventional wedge type one-way overrunning clutch; Figure 5 is a cross-sectional view showing the structure of the first embodiment of the present invention; 6 is a schematic perspective structural view of a cam wedge according to an embodiment of the present invention;

Figure 7 is an assembly diagram of a first embodiment of the present invention applied to a two-axis assembly;

Figure 8 is an axial cross-sectional view of a second embodiment of the present invention, the bearing is a ball bearing; Figure 9 is a cross-sectional view taken along line A-A of Figure 8;

Figure 10 is a perspective view showing the structure of the cam wedge of Figure 8;

Figure 11 is an axial cross-sectional view of a third embodiment of the present invention, the bearing is a roller bearing;

Figure 12 is a cross-sectional view taken along line A-A of Figure 11;

Figure 13 is a cross-sectional view taken along line B-B of Figure 11;

Figure 14 is an axial cross-sectional view showing a fourth embodiment of the present invention;

Figure 15 is a radial cross-sectional view showing the state of the fourth embodiment of the present invention;

Figure 16 is a radial cross-sectional view showing the state of "off" of the fourth embodiment of the present invention. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring to Figure 5, a cam wedge type overrunning clutch disclosed by the present invention is mainly composed of an outer ring 7, an inner ring 3, a cam wedge 5, and a ring spring 4. A plurality of cam wedges 5 are disposed between the outer ring 7 and the inner ring 3 against each other, and the distance between the outer ring 7 and the inner ring 3 is smaller than the long diameter of the cam and larger than the short diameter of the cam, and both ends of the cam wedge 5 A fulcrum 53 is formed (a fulcrum may also be formed in the middle of the cam wedge 5). As shown in FIG. 6, the annular spring 4 is formed by a cylindrical winding spring end to end, and the annular spring 4 is disposed on the inner ring 3 and the cam wedge 5 Between the fulcrums 53, and acting on the fulcrum 53 by the outward tension of the spring, the cam wedge 5 is reset during the movement, and the long diameter portion of the cam wedge 5 is always in contact with the outer ring 7 and the inner ring 3.

When the embodiment is mounted on the two-shaft assembly in the loader gearbox, as shown in Fig. 7, the cam wedge 5 and the ring spring 4 are first assembled between the outer ring 7 and the inner ring 3, and the inner ring 3 is then passed by the flower The key or pin 2 is fixed to the input shaft 10, and at the same time, a bearing 9 is mounted between the input shaft 10 and the outer ring 7 and the outer ring gear 8, and then the bearing sleeve 1 is fixed to the input shaft 10 by screws 6. The bearing 9 is positioned, and finally, the outer jaw 7 and the outer ring gear 8 are fixed by screws 6.

When this embodiment is used, the outward tension of the annular spring 4 acts on the fulcrum 53 of the cam wedge 5 to effect clutching. When the speed of the outer ring gear 8 is less than the speed of the input shaft 10, the inner ring 3 is reversed relative to the outer ring 7, and the cam wedge 5 and the outer ring 7 are only slightly in contact with each other, and the overrunning clutch is in a "off" state; When the speed of the outer ring gear 8 is greater than or equal to the speed of the input shaft 10, when the inner ring 3 rotates relative to the outer ring 7, the cam wedge 5 gradually tilts to the radial direction, because the height of the cam wedge 5 is larger than the outer ring. The distance between the inner ring 7 and the inner ring 3 is such that the outer ring 7 and the inner ring 3 are caught by the cam wedge 5, and the card of the cam piece 5 is used for clamping, and the outer ring 7 and the inner ring 3 are simultaneously clamped, thereby making the outer ring 7 and the inner ring 3 simultaneously clamped. The ring 7 rotates with the inner ring 3 to output power, and the overrunning clutch is in a "closed" state.

Referring again to Figures 8 and 11, it is a cam wedge type overrunning clutch disclosed in the present invention. Two preferred embodiments assembled on the shaft 7|Ui, in conjunction with Figs. 9 and 13, a plurality of mutually opposed cam wedges 5 are disposed between the outer ring 7 and the inner ring 3 of the bearing, the length of the cam The diameter is larger than the distance between the outer ring 7 and the inner ring 3, and the short diameter of the cam is smaller than that between the outer ring 7 and the inner ring 3. The fulcrum 53 is formed on the cam wedge 5, and the cylindrical winding spring is connected end to end. An annular spring 4 is disposed between the inner ring 3 and the fulcrum 53 of the cam wedge 5, and acts on the fulcrum 53 of the cam wedge 5 by the outward tension of the annular spring 4, so that the cam wedge 5 is in motion In the reset, the long diameter portion of the cam wedge 5 is always in contact with the outer ring 7 and the inner ring 3.

Wherein, the bearing in the embodiment shown in FIG. 8 is a ball bearing, and the bearing is provided with a cage D1 at the end of the ball D, and the bearing in the embodiment shown in FIG. 11 is a roller bearing, as shown in FIG. This bearing is also provided with a cage D1 at the end of the roller D. Both of the above are provided with a baffle D2 at the end of the cam wedge 5, and the baffle D2 is fixed between the outer ring 7 and the inner bore 3 of the bearing.

In the above two embodiments, the fulcrum 53 on the cam wedge 5 is formed in the middle of the cam wedge 5. The specific structure is as shown in FIG. 10, and a radial groove 54 is opened in the middle of the cam wedge 5, and the groove bottom is formed. That is, the fulcrum 53a is directly formed. Of course, the fulcrum 53 on the cam wedge 5 is also formed at both ends of the cam wedge 5, i.e., two notches are formed symmetrically at both ends of the cam wedge 5, thereby forming a fulcrum 53, as shown in Fig. 6.

When the above two embodiments are used, the outer diameter of the annular spring 4 acts on the fulcrum 53 on the cam wedge 5, and the long diameter portion of the cam wedge 5 is pre-tensioned on the raceway between the outer ring 7 and the inner ring 3. And rely on friction to achieve clutching. When the inner ring 3 is reversed relative to the outer ring 7, the cam changing block 5 and the outer ring 7 are only in light contact sliding, and the one-way bearing is in a "off" state; when the inner ring 3 is rotated relative to the outer ring 7, the cam The wedge 5 is gradually inclined to the radial direction, because the height of the cam wedge 5 is greater than the distance between the outer ring 7 and the inner ring 3, so that the outer ring 7 and the inner ring 3 are caught by the cam wedge 5, by the cam wedge In the card making of the block 5, the outer ring 7 and the inner ring 3 are simultaneously clamped, so that the outer ring 7 rotates with the inner ring 3 to output power, and the one-way bearing is in a "closed" state.

Referring to FIG. 14, another cam wedge type overrunning clutch disclosed by the present invention is mainly composed of an outer ring 7, a shaft 11, a cam wedge 5, and a ring spring 4, etc., in order to mount the positioning cam wedge 5 and The ring spring 4 and the two sides of the cam wedge 5 are further provided with a baffle D2 and a retaining ring D3. A plurality of cam wedges 5 are disposed between the outer ring 7 and the shaft 11 against each other. The distance between the outer ring Ί and the shaft 11 is smaller than the long diameter of the cam 5 and larger than the short diameter of the cam 5, and the fulcrum is formed on the cam wedge 5. 53. As shown in FIGS. 14, 15, the annular spring 4 is formed by a cylindrical winding spring end to end. The annular spring 4 is disposed between the shaft 11 and the fulcrum 53 of the cam wedge 5, and passes through the outward tension of the annular spring 4. Acting on the fulcrum 53 of the cam wedge 5, the cam wedge 5 is always in contact with the inner race of the outer ring 7, and the outward tension of the annular spring 4 is smaller than the centrifugal force of the cam 5 when the outer ring 7 and the shaft 11 are rotated in opposite directions The sum of the inertial force and the difference between the centrifugal force and the inertial force of the cam 5 when the outer ring 7 and the shaft 11 rotate in the same direction, and the outer raceway of the cam 5 and the shaft 11 when the outer ring 7 and the shaft 11 rotate in the opposite direction Separation, and outer ring 7 When the shaft 11 rotates in the same direction as the shaft 11, the cam 5 comes into contact with the outer race of the shaft 11, as shown in Fig. 15, thereby forming a non-contact cam clutch.

Of course, the inner shaft 1 can also be fixedly sleeved with an inner cymbal (not shown), so that a plurality of cam wedges 5 are disposed between the outer ring 7 and the inner ring against each other, and the outer cymbal 7 and The distance between the inner rings is smaller than the long diameter of the cam 5 and larger than the short diameter of the cam 5, and the ring spring 4 is disposed between the inner ring and the fulcrum 53 of the cam wedge 5.

Compared with the prior art clutch, the key point is that the outward tension of the annular spring 4 acts on the fulcrum 53 of the cam wedge 5 to achieve the clutch, and the cam 5 is realized by precisely designing the outwardly long force of the annular spring 4. In the "off" state, it is not in contact with the outer race of the shaft 11 (or inner ring). The operation of this embodiment in actual use is briefly explained below.

As shown in Fig. 16, when the outer ring 7 rotates clockwise with respect to the shaft 11, the outer ring 7 and the shaft 11 rotate in opposite directions, and the outer ring 7 idles, and the outward tension of the ring spring 4 is weaker than the centrifugal force and the inertial force. Under the action of the centrifugal and inertial forces against the outward tension of the annular spring 4, the small arc of the cam 5 is brought into close contact with the inner race of the outer ring 7, and at the same time, the cam 5 is also rotated clockwise by the influence of the inertial force. At this time, the large arc of the cam 5 is away from the outer race of the shaft 11, that is, the cam 5 is not in contact with the outer race of the shaft L1, so there is no frictional sound of contact, the noise is small, and the use of extravagance is long. The overrunning clutch is in the "off" state. As shown in FIG. 15, when the outer ring 7 rotates counterclockwise or stationary with respect to the shaft 11, the outward tension of the ring spring 4 acts on the fulcrum 53 of the cam 5, so that the small circular arc surface of the cam 5 contacts the inside of the outer ring 7. The raceway, in the condition that the outward tension and the inertial force of the ring spring 4 cooperate to overcome the centrifugal force, finally causes the cam 5 to also rotate counterclockwise until its large arc contacts the outer race of the shaft 11, due to the length of the cam 5 The diameter is larger than the distance between the inner race of the outer ring 7 and the outer race of the shaft 11. Under the clamping action of the cam 5, the overrunning clutch is in a "closed" state, and between the outer ring 7 and the shaft 11 Realize the transmission between each other.

Claims

Rights request

1. The cam wedge type overrunning clutch is mainly composed of an outer ring, an inner ring, a cam wedge and a ring spring, and is characterized in that: a plurality of cam wedges are disposed between each other between the outer ring and the inner ring, and the outer ring and The spacing between the inner rings is smaller than the long diameter of the cam and larger than the short diameter of the cam. The cam wedges form a branch, and the annular spring is formed by the cylindrical winding springs connected end to end. The annular spring is disposed on the inner ring and the cam wedge. Between the fulcrums, and by the outward tension of the ring spring acting on the fulcrum of the cam wedge, the cam wedge is reset during movement, and the long diameter portion of the cam wedge is always in contact with the outer ring and the inner ring.

2. The cam wedge type overrunning clutch is assembled on the bearing, and is characterized in that: a plurality of cam wedges which are mutually abutted are arranged between the outer ring and the inner ring of the bearing, and the long diameter of the cam is larger than the outer ring and the inner ring The spacing between the cams and the short diameter of the cam is smaller than the spacing between the outer ring and the inner turn, the fulcrum is formed on the cam wedges, and the annular springs are connected end to end by a cylindrical winding spring, and the annular spring is disposed on the inner ring and the cam wedge. Between the fulcrums, and by the outward tension of the annular spring acting on the fulcrum of the cam wedge, the cam wedge is reset during movement, and the long diameter portion of the cam wedge is always in contact with the outer ring and the inner cymbal.

3. The cam wedge type overrunning clutch according to claim 2, wherein the bearing is a ball shaft or a roller shaft;

4. The cam wedge type overrunning clutch according to claim 2, wherein: the end of the cam wedge is provided with a baffle fixed between the outer ring and the inner ring of the bearing.

5. The cam wedge type super-intelligent clutch is mainly composed of an outer ring, a shaft, a cam wedge and a ring spring, and is characterized in that: a plurality of cam wedges are arranged adjacent to each other between the outer ring and the shaft, the outer ring and the shaft The spacing between the gaps is smaller than the long diameter of the cam and larger than the short diameter of the cam, the fulcrum is formed on the cam wedge, the annular spring is formed by the cylindrical winding springs, and the annular spring is disposed between the pivot points of the shaft and the cam wedge. And the outer tension of the annular spring acts on the fulcrum of the cam wedge, so that the cam wedge always contacts the inner race of the outer ring, and the outward tension of the annular spring is smaller than the centrifugal force of the cam when the outer cymbal and the shaft rotate in opposite directions. The sum of the inertial force and the difference between the centrifugal force and the inertial force of the cam when the outer ring and the shaft rotate in the same direction, so that the cam and the outer raceway of the shaft are separated when the outer ring and the shaft rotate in opposite directions, and the outer ring and the shaft are the same The cam contacts the outer race of the shaft when rotating or stationary, thereby forming a non-contact cam clutch.

6. The cam wedge type overrunning clutch according to claim 5, wherein: the inner sleeve is fixedly disposed on the shaft, and the plurality of cam wedges are disposed adjacent to each other between the outer ring and the inner ring, the outer ring and the inner ring. The spacing between the turns is less than the long diameter of the cam and greater than the short diameter of the cam, and the annular spring is disposed between the inner ridge and the fulcrum of the cam wedge.

7. A cam wedge overrunning clutch according to claim 1, 2 or 5 wherein: the fulcrum on the cam wedge is formed at either end of the cam wedge or in the middle of the cam wedge.