KR20110063231A

KR20110063231A - Clutch

Info

Publication number: KR20110063231A
Application number: KR1020090120466A
Authority: KR
Inventors: 김종기
Original assignee: 김종기
Priority date: 2009-12-04
Filing date: 2009-12-04
Publication date: 2011-06-10

Abstract

The present invention is a clutch, and more particularly, at least one pair of electric wedges between the inner race and the outer race, a load bar is installed so that the rotational force of the inner race acts between the raceway and the inner race, and the inner race and the load bar. One of them relates to a clutch for transmitting and blocking power according to the position of a specific point where the rotational force of the inner race acts by providing a rotational force acting means so that the rotational force of the inner race acts on a specific point of the load bar.

Accordingly, the present invention is provided between the outer race 20, the inner race 10 rotatably installed in the outer race 20, and the outer race 20 and the inner race 10 is installed between the outer race At least one pair of electric wedges 34, the electric wedges which rotate together with the inner race 10 and connect or cut off power between the inner race 10 and the outer race 20 in the interior of the 20. 34) the load bar 32 for transmitting the rotational force of the inner race 10 and the inner race 10 and the load bar so that the rotational force of the inner race 10 acts on a specific point of the load bar 32; Rotating force operating means (50) provided in at least one of the (32), characterized in that to connect or disconnect the power according to the position of the specific point where the rotational force of the inner race 10 acts. .

Description

Clutch {clutch}

The present invention relates to a clutch, and more particularly, at least one pair of power wedges between an inner race and an outer race, and a load bar for transmitting the rotational force of the inner race between the power wedges and having an inner race and a load bar. It is equipped with a rotating force acting means so that the rotating force of the inner race acts on a specific point of the load bar, so as to connect or disconnect the power according to the position of the specific point where the rotating force of the inner race acts. It relates to a clutch that can be transmitted.

In general, the clutch has a function of transmitting or interrupting power by mechanical contact from the drive shaft to the driven shaft, and includes a one-way clutch and a two-way clutch.

One-way clutch cuts power by transmitting power in one direction and idling in the reverse direction. Representative one-way clutches include roller type with cylindrical roller pressed by spring, and spray type with sprag between outer race and inner race, but its structure is complicated and its life is short due to abrasion, High cost is required due to precision.

In addition, the bidirectional clutch transmits and cuts power in both directions, and in order to transfer large power, the friction clutch and the cone clutch have to apply lateral pressure to increase the structure of the clutch or to increase the friction on the friction surface. There is a disadvantage in that impact or friction sounds are generated during operation.

An object of the present invention for solving the above problems is to provide a clutch that can transmit a large power while minimizing the clutch and has a low failure.

The present invention for achieving the above object, the outer race, the inner race rotatably installed inside the outer race, and provided between the outer race and the inner race with the inner race in the interior of the outer race At least one pair of power wedges for rotating or connecting the power between the inner race and the outer race, a load bar for transmitting the rotational force of the inner race to the power wedge and the rotational force of the inner race is It includes a rotational force acting means provided on at least one of the inner race and the load bar to act on a specific point, characterized in that for connecting or disconnecting power in accordance with the position of the specific point on which the rotational force of the inner race is applied. do.

The present invention includes a pair of electric wedges and a load bar between the inner race and the outer race, and has a rotational force acting means so that the rotational force of the inner race acts on a specific point of the load bar in either the inner race or the load bar. By connecting and disconnecting the power according to the position of the specific point of the load bar where the rotational force of the inner race acts, it provides a clutch that is simple in structure and small in size and can transmit large power.

Below. The invention is described in detail with reference to the accompanying drawings.

First, in order to understand the basic principle of the present invention will be described with reference to FIG.

As shown in FIG. 1, a pair of electric wedges 34 are rotated in a rotational direction in the shape of a hollow cylindrical ring 20 divided into semi-circular plates again halfway (a quarter of a circular plate). A pair of electric wedges are symmetrically contacted and a load bar 32 having a rectangular rod shape, which is about the inner diameter length of the ring 20, is set in the inner diameter direction of the ring 20 (perpendicular to the axial direction of the ring 20). Install in close contact with 34).

At this time, the load bar 32 and the electric wedge 34 are configured to contact at p and p 'points near both ends of the inner circumferential surface of the ring 20, and the mutual contact portions p " It is preferable to bring the inner race surface closer to the outer race 20.

In addition, the outer diameter (circular portion) of the electric wedge 34 is set similar to the internal diameter of the ring 20 so as to smoothly rotate on the inner circumferential surface of the ring 20, and the load bar 32 and the electric wedge 34 are the outer race 20. The overall combined shape, which is in close contact with the inner circumferential surface of the shape, becomes a semicircular shape.

Subsequently, after the ring 20 is immobilized, a load is applied to a point a, which is the center of the load bar 32 (the center of the outer race 20), and the load bar 32 and a pair of electric wedges ( 34) is in contact with p, p 'near the inner circumferential surface of the outer race 20 and the pair of power wedges 34 in contact with the symmetrical P ", so the force acting on the load bar 32 is The outer circumferential surface of the electric wedge 34 is in close contact with the inner circumferential surface of the outer race 20 while being distributed to the left and right of the pair of electric wedges 34 to act as pressure.

Subsequently, even if the working point of the load is moved to the point b, the load bar 32 and the power wedge 34 do not rotate.

However, at the moment when the load exceeds point b, the load bar 32 and the electric wedge 34 rotate counterclockwise.

That is, the present invention utilizes the frictional force between the object and when the load acts between the point a and the point b, the friction force between the ring 20 and the electric wedge 34 is greater than the load acting on the load bar 32. Because of its size, the load bar 32 and the electric wedge 34 utilize the principle that they do not rotate counterclockwise.

This is the same as the basic principle of the patent document (No. 10-2009-0068271) filed by the applicant of the present invention. The present invention consists of three components of a pair of power wedge 34 and the load bar 32 as shown in FIG. 1, but in the patent document as shown in FIG. 2, the power wedge 34 and the load bar 32 of the present invention. In other words, the distance from b to b 'of FIG. 1 is larger than the distance from b to b; of FIG. Increased functionality allows for greater power or smaller products.

At this time, the distance from the point a, which is the rotation center of the load bar 32 (center of the ring 20) to the point b or the point b 'becomes larger as the inner diameter of the ring 20 becomes larger and the ring 20 and the electric wedge The degree of lubrication between the surfaces 34 and the material and shape of the friction surface are determined.

Hereinafter, various embodiments of the present invention clutch using the above principle will be described.

First, in order to avoid complications in the drawing representation of the embodiment of the clutch of FIGS. 3 to 10, which will be explained in the future, the load bar 32 and the pair of electric wedges 34 in FIG. Part 30 is indicated or described by name and reference numeral (number).

Now, the basic structure of the clutch 1 will be described with reference to FIGS. 3 and 4. FIGS. 3 and 4 show the outer race 20, the inner race 10, and the rolling piece 30 as the one-way clutch 1. And, it is configured to include a rotation force action means (50).

In FIG. 1, the ring 20 corresponds to the outer race 20, and the load bar 32 and the electric wedge 34 correspond to the rolling piece 30 in FIG. 1. The action of the load corresponds to the rotational force of the inner race 10, the acting point of the load in Figure 1 corresponds to the rotational force acting means (50).

The outer race 20 is formed in a hollow cylindrical shape.

The inner race 10 is rotatably coupled to the inside of the outer race 20, the outer circumferential surface facing the inner circumferential surface of the outer race 20, the transmission piece (electric wedge 34 and the load of a predetermined depth in the rotational direction) Bar 32} is formed an insertion groove 11 is inserted.

In this case, the inner race 10 may be rotatably coupled to the inside of the outer race 20, or only one end of the inner race 10 is rotatably coupled to the inside of the outer race 20. May be

Here, the insertion groove 11 into which the rolling piece 30 is inserted is preferably installed to be located inside the outer race 20.

On the other hand, the inner race 10 and the outer race 20 is connected to a variety of external devices that require a clutch action, respectively, these external devices are known in the drawings, so omitted.

In addition, the rolling piece 30 is inserted into the insertion groove 11 and rotates together with the inner race 10 in the interior of the outer race 20 and between the inner race 10 and the outer race 20. To connect or disconnect the power. At this time, the insertion groove 11 is formed in a semi-circular shape, the rolling piece 30 is inserted into the insertion groove 11 is formed in a semi-circular plate.

Of course, the insertion groove 11 and the rolling piece 30 may be a shape close to the semi-circle even if not exactly a semi-circle.

In addition, the rotating force acting means 50 is provided on at least one of the inner race 10 and the rolling piece 30 so that the rotating force of the inner race 10 acts on a specific point of the rolling piece 30. do. The rotational force acting means 50 is formed by protruding the electric support jaw 31 on at least one of the surfaces facing in the rotational direction of the inner race 10 and the rolling piece 30, the electric support jaw 31 is in close contact with the other.

In FIG. 3 and FIG. 4, the transmission support jaw 31 is formed on the transmission piece 30 side, and the location at which the transmission support jaw 31 is formed should be located between the load operating points b and b 'in FIG. do. The clutch 1 connects or disconnects power between the inner race 10 and the outer race 20 according to the position of a specific point where the rotational force of the inner race 10 acts.

That is, when a specific point where the rotational force of the inner race 10 acts is located between an arbitrary setting position (point b) and the center of rotation (point a) of the rolling piece 30, the rolling piece 30 and the outside As the frictional force between the races 20 becomes greater than the rotational force of the inner race 10, the rolling piece 30 does not rotate so that the power between the inner race 10 and the outer race 20 is connected, and the inner race. When the specific point at which the rotational force of (10) acts is located between an outer circumferential surface of the rolling element 30 from an arbitrary setting position (point b), the frictional force between the rolling element 30 and the outer race 20 is internal race ( It becomes smaller than the turning force of 10) and the rolling piece 30 is rotated so that the power connection between the inner race 10 and the outer race 20 is blocked.

Referring to FIG. 4, the clutch action will be described in detail. When the inner race 10 is rotated in the clockwise direction, the rotation force of the inner race 10 acts on the transmission supporting jaw 31 of the rolling piece 30. Since the transmission supporting jaw 31 is formed within the point b or the point b 'of FIG. 1, the transmission piece 30 having the transmission supporting jaw 31 cannot be rotated, that is, the inner race 10. The power is connected between the outer race 20 and the rotational force of the inner race 10 is transmitted to the outer race 20.

Subsequently, when the inner race 10 is rotated in a counterclockwise direction, the contact between the electric support jaw 31 of the rolling piece 30 and the inner race 10 is broken, and one end of the inner race 10 ( The left side part comes into contact with one end (left side part) of the rolling piece 30. That is, since the rolling piece 30 side point at which the rotational force of the inner race 10 acts is located outward from the point b or point b 'of FIG. 1, the rolling piece 30 is combined with the inner race 10. The inner race is revolved inside the outer race 20, that is, the power connection between the inner race 10 and the outer race 20 is cut off so that the rotational force of the inner race 10 is not transmitted to the outer race 20 will be.

As such, in order to connect power between the inner race 10 and the outer race 20, the rotational force of the inner race 10 should be acted between the point b and the point b 'of Figure 1, the inner race 10 In order to cut off power between the outer race 20 and the outer race 20, the rotational force of the inner race 10 must act in the outward direction of the point b and the point b '(the outer peripheral surface side direction of the transmission piece 30).

As described above, the clutches of FIGS. 3 and 4 are one-way clutches, which are simple in structure and have a small number of failures, and are capable of transmitting large power even in a small size.

5 is a one-way clutch having the same function as that of FIG. 4. In the clutch of FIG. 4, an insertion groove 11 is formed in a semi-circular shape so that one rolling piece 30 is inserted into the inner race 10. In Fig. 9, the inner race 10 of the rotation support jaw 16 is configured to symmetrically left and right in the shape of the annular insertion groove (11a) to face a pair (two) of the rolling piece (30). ) Is similar to the form.

In FIG. 5, unlike in FIG. 4, an elastic member 40 extending between the pivot support jaw 16 and the rolling piece 30 is inserted near the inner peripheral surface of the outer race 20 so that the rolling piece 30 is always present. It is provided to rotate in close contact with the inner circumferential surface of the outer race 20 so that there is no play in the clutch operation.

Here, the central portion of the inner race 10 is formed in a circular shape, so that the inner race 10 serves as a shaft (shaft) for transmitting power. do.

6 is a bidirectional clutch, which transmits and blocks power in both directions.

In the clutch of FIG. 6, the rotational force acting means 50 forms a support insertion groove 15 in the axial direction in the inner race 10, and inserts the variable electric support means 51 in the insertion groove 15. It is done by installation.

The support insertion groove 15 is formed at one side of the insertion groove 11 is in communication with the insertion groove (11). Therefore, when the variable power support means 51 is inserted into the insertion groove 15, the variable power support means 51 is in close contact with the rolling piece 30.

In addition, the support insertion groove 15 and the variable power support means 51 are formed to have a cross section of a rectangular shape, but each side of the support insert insertion groove 15 and the variable power support means 51 are inclined surface ( 15a and 51a are formed,

Therefore, when the variable power support means 51 is inserted into the support insertion groove 15, the variable power support means 51 is moved toward the rolling piece 30 by the inclined surfaces 15a and 51a. To close the inner circumference of the outer race.

Next, the operation of the bidirectional clutch of FIG. 6 will be described.

First, when the variable electric support means 51 is pushed in the axial direction, the variable electric support means 51 descends along the inclined surface 15a of the support insertion groove 15, while being in close contact with the rolling piece 30 and continuously variable. When the electric support means 51 is pushed further, the rolling piece 30 is spaced apart from the inner race 10 and the outer circumferential surface of the rolling piece 30 is brought into close contact with the inner circumferential surface of the outer race 20.

Subsequently, when the inner race 10 is rotated, it does not rotate in any direction.

That is, it is possible to transfer the rotational force of the inner race 10 to the outer race 20.

This is because the length (width) of the contact surface of the variable electric support means 51 in contact with the rolling piece 30 is formed equal to or smaller than the distance between the point b and the point b 'which are the load acting points in FIG.

In detail, the left and right ends of the variable electric support means 51 which are in contact with the rolling piece 30 have the same function as the rolling support jaw 31 formed in the rolling piece 30 of FIGS. 3 and 4. In this regard, the variable electric support means 51 is provided between the inner race 10 and the rolling element 30 to move the variable electric support means 51 to move the rolling element 30 to the inner circumferential surface of the outer race 20. Depending on whether or not close contact is to transmit and cut power in both directions.

Subsequently, when the variable electric support means 51 is pulled out, the contact between the rolling piece 30 and the variable electric support means 51 is released, that is, the structure for removing the electric support jaw 31 in FIG. Since the rotational force of the race 10 cannot be transmitted to the outer race 20, the rotational force of the inner race 10 cannot be transmitted to the outer race 20 and idle.

As described above, the bidirectional clutch of the present invention has a simple structure to easily transmit and block power.

On the other hand, the apparatus for sliding the variable motor support means 51 in the axial direction is omitted in the drawings and such a device may be used a variety of known devices.

In the present invention, only the configuration in which the inclined surface 51a is formed on the variable electric support means 51 to closely contact the rolling piece 30 to the inner circumferential surface of the outer race 20 has been described. Can also be used. That is, a hydraulic cylinder (not shown) and a cam (not shown). Any means capable of acting as an electric support jaw 31, such as a lever (not shown), can be implemented.

Next, referring to the embodiment of FIG. 7, a clutch in which two variable electric support means 51 are symmetrically configured between the inner race 10 and the rolling piece 30 can be used. Is provided.

Herein, the structures of the variable electric support means 51 and the support insertion groove 15 of FIG. 7 are the same as those of the variable electric support means 51 and the support insertion groove 15 of FIG. 6 described above. The description is omitted, and only two variable power support means 51 are configured symmetrically, unlike in FIG. 6. At this time, the two variable power support means 51 is located between point b and point b 'of FIG.

The operation principle of the embodiment of Figure 7 will be described in detail.

First, as shown in FIG. 6, when the two variable electric support means 51 are pushed in, the rolling piece 30 is in close contact with the inner circumferential surface of the outer race 20, and the two variable electric support means 51 are supported by the electric motor in FIG. 4. Since the jaw 31 has two forms on both sides, it is bidirectionally driven.

Subsequently, when only one right variable motor support unit 51 is pushed in FIG. 7, it becomes the same as the one-way clutch of FIG. 4, and when the inner race 10 is turned clockwise, power is transmitted to the outer race 20. Subsequently, when the inner race 10 is rotated in a counterclockwise direction, the inclined jaw 33 and the inner race 10 formed at both ends of the rolling piece 30 of FIG. 7 may be formed on the inner race 10. Since the turning force of the inner race 10 acts on the rolling piece 30 outside the point b in FIG. 1, the power of the inner race 10 cannot be transmitted to the outer race 20.

Next, when only the left variable motor support means 51 is pushed in, the one-way clutch which rotates the rotational force of the inner race 10 to the outer race 20 in the counterclockwise direction is contrary to the above. Then, when both of the two variable electric support means 51 are pulled out, the inner race 10 is idle in the outer race 20 by the same operation principle as the variable electric support means 51 is removed from FIG. 6.

Although not shown here, the inclined jaws 33 on both sides of FIG. 7 may be removed, and the elastic members 40 as shown in FIG. 5 may be installed at the positions thereof.

8 and 9 are one-way clutches, and only the parts different from the above-described embodiments will be described. The above-described embodiments form the insertion groove 11 in the inner race 10 to form the insertion groove ( 11) is inserted into the rolling piece 30, but in the embodiment of Figure 8 is omitted the insertion groove 11 formed in the inner race (10).

At this time, the rolling piece 30 is installed between the outer race 20 and the inner race 10. That is, one rolling piece 30 is configured to surround a portion of the outer circumferential surface of the inner race 10.

In addition, rotation support jaws 16 having mutually different lengths are formed on both sides of the outer circumferential surface of the inner race 10, and on the side of the rolling piece 30 facing the respective rotation support jaws 16, an electric support jaw ( 31) is formed.

Therefore, when the inner race 10 rotates in the clockwise direction, the rotational force of the inner race 10 is transmitted to the outer race 20, and when the inner race 10 rotates counterclockwise, the rotational force is transmitted. Not.

As such, in all embodiments of the present invention, insertion grooves 11 and 11a may be formed or omitted in the inner race 10 to install the rolling element 30.

Subsequently, FIG. 10 shows a rotation support jaw 16 formed at one side of the outer circumferential surface of the inner race 10 as shown as an embodiment of the one-way clutch, and is supported on the rolling piece 30 facing the rotation support jaw 16. The jaw 31 is formed.

In addition, one end of the rolling piece 30 is formed to surround the end of the rotation support jaw 16 is formed with a locking portion 37 to be caught by the rotation support jaw (16).

At this time, an elastic member 40 such as a spring is installed between the locking portion 37 and the pivot support jaw 16. In this case, when the one-way clutch idling (clockwise rotation) in FIG. 5, the pivot support jaw 16 rotates while pushing the rolling piece 30 clockwise while pressing the elastic member 40. ) Is rotated while dragging the rolling element 30 clockwise.

As described above, the embodiment of FIG. 10 has an advantage of smoothly rotating by reducing friction between the inner piece of the rolling piece 30 and the outer race 20 when the one-way clutch idles.

Here, the rolling piece 30 is configured by connecting two electric wedges 34 with the connecting pin 42 as shown in Figure (l) in Figure 12 so that the pair of electric wedges 34 to rotate together.

And Figure 11 relates to the electric wedge 34 which is a component of the rolling piece 30 described above to increase the friction between the outer peripheral surface of the electric wedge 34 and the inner peripheral surface of the outer race 20 in FIG. In this case, various friction increasing means are formed so that the outer circumferential surface of the electric wedge 34 and the inner circumferential surface of the outer race 20 which are in contact with each other may be formed in various shapes such as triangle, trapezoid, sawtooth, and semicircle. By forming it will be able to further increase the friction between the electric wedge 34 and the outer race (20).

In addition, as shown in FIG. 11, when a portion of the distal end of the teeth of the electric wedge 34 is in contact with the teeth of the electric wedge 34 and the female teeth of the outer race 20, the electric wedge 34 is removed. And the fat part 38 is in contact with the inner circumferential surface of the outer race 20 is not in contact with the inner circumferential surface and the frictional force of the electric wedge 34 and the outer race 20 is further increased (by the wedge action).

FIG. 12 shows various embodiments of the construction method (assembly type) of the two power wedges 34 and the load bars 32 in FIG. 1, wherein (a) shows the load bar 32 and the two power wedges. In the basic configuration, p and p 'are the contact points of the load bar 32 and the power wedge 34, and p "is the contact point between the power wedges 34.

(b) shows the inner race 10 in the form as shown in Figure 1 (c), (d) is inclined to the contact (p, p ') to the load bar 32, the power wedge 34 or both. When the portion 32a is formed and a force is applied to the load bar 32, the electric wedge 34 opens to the left and right to act as a wedge, thereby further strengthening the electric wedge 34 to the inner circumferential surface of the outer race 20. In addition, there is an effect that can further increase the width from 1b to b '.

Figure (e) is a load bar 32 in the form of a semi-circular reinforcement of strength and there is an inclined jaw 33 of Fig. 7, the weight portion 39 in a portion of the outer peripheral surface of the electric wedge 34 of (f) In the friction between the electric wedge 34 and the inner circumferential surface of the outer race 20, the contact force is concentrated on a part of the surface of the electric wedge 34 (not part of the weight), so that the overall friction increase effect can be seen. .

(g) is an embodiment in which a separate powered wedge 34b is inserted between the two powered wedges 34 and does not come into contact with the load bar 32. Figure (h) consists of two electric wedges (34) in the shape of a bow and one electric wedge (34a), when the rotational force of the inner race 10 is applied to the load bar 32, the electric wedge (34a) is left, The basic principle is as described above.

(i) is an enlargement of the insertion portion of the inner race 10 by forming the load bar 32 into the concave portion (32b), (j), (k) is composed of the electric wedge 34 in a semicircle shape. , Figure (1) is a diagram showing the rolling piece 30 of Figure 10 divided into the load bar 32 and the electric wedge (34).

1 is a conceptual diagram for explaining the operation principle of the clutch according to the present invention.

Figure 2 is a simplified view of the power wedge and the load bar of the present invention as one component.

3 to 10 are views showing various embodiments of the clutch according to the present invention, and FIG. 4 is a cross-sectional view taken along the line A-A of FIG.

11 is a view schematically showing the contact surface shape of the outer race and the electric wedge.

12 is a view schematically showing various configurations of the power wedge and the load bar.

Claims

With the outer race 20,

An inner race 10 rotatably installed in the outer race 20;

Installed between the outer race 20 and the inner race 10 is rotated together with the inner race 10 in the interior of the outer race 20, and the power between the inner race 10 and the outer race 20 A load bar 32 installed in close contact with the at least one pair of electric wedges 34 and the electric wedges 34 to connect or cut the wires;

And a rotational force acting means 50 provided on at least one of the inner race 10 and the load bar 32 so that the rotational force of the inner race 10 acts on a specific point of the load bar 32. ,

Clutch, characterized in that for connecting or disconnecting the power in accordance with the position of the specific point where the rotational force of the inner race (10) acts.

The method of claim 1

The load bar 34 is,

When the specific point where the rotational force of the inner race 10 acts is located between the rotation center of the load bar 32 from an arbitrary setting position, the friction force between the load bar 32 and the outer race 20 is the inner race ( It becomes greater than the turning force of 10) and connects the power of the inner race 10 and the outer race 20,

When the specific point where the rotational force of the inner race 10 is applied is located between the outer circumferential surface of the load bar 32 from an arbitrary setting position, the friction force between the electric wedge 34 and the outer race 20 is the inner race 10 Clutch characterized in that to cut the power between the inner race 10 and the outer race 20 while being smaller than the rotational force of the).

The method of claim 1,

The outer peripheral surface of the inner race 10 facing the inner circumferential surface of the outer race 20 is inserted of a predetermined depth in the rotational direction so that the load bar 32 in close contact with the electric wedge 34 and the electric wedge 34 is inserted. Clutch characterized in that the groove is formed.