JPS605140Y2 - clutch brake device - Google Patents

Description

[Detailed explanation of the invention] This invention relates to a clutch brake device.
In particular, the present invention relates to a clutch/brake device that transmits rotational motion of one mechanical member to another mechanical member in one direction.

In order to transmit the rotational motion of one mechanical member to another mechanical member in one direction, a steel ball is provided between the driving member and the driven member so that when the driving member rotates in one direction, the steel ball engaging the two members together by causing them to be immovable and moving the two members together by freeing the steel ball when the drive member rotates in the opposite direction. There are devices conventionally known as freewheel clutches or ball clutches, such as those commonly used on bicycles, that disengage.

In such conventional devices as described above, the capacity, or horsepower or torque, that the device can transmit is quite limited due to the limited number of steel balls that can be configured in the device.

Furthermore, a conventional single freewheel clutch is only capable of transmitting rotational motion in one fixed direction.

Additionally, there is no way to disengage the driven member from the drive member while the drive member is rotating in the direction in which the driven member is driven.

In view of the above-mentioned shortcomings of the conventional freewheel clutch, this invention provides a novel latch brake device having a plurality of wedges capable of gripping a drive shaft rotating in one direction, and in such a device, teeth,
Relatively small wedges allow a larger number of wedges to be used, and thus such a device can transmit a relatively large amount of horsepower or torque.

The wedge is also movable towards and away from the drive shaft, thus providing the option of engaging or disengaging the driven member with respect to the drive member regardless of the direction of rotation.

Therefore, the main objective of this invention is to provide a clutch device for transmitting rotary motion in one direction, which is capable of transmitting relatively large horsepower or torque.

Another object of the invention is to provide a clutch-brake device for unidirectionally transmitting rotary motion, in which the direction of the rotary motion to be transmitted can be selected.

Yet another object of the invention is to provide a clutch-brake device for transmitting rotational motion in one direction in which a driven member can be selectively engaged or disengaged with respect to a driving member. That's true.

In FIG. 1, a first embodiment of the clutch brake device of this invention is shown.

This includes a drive shaft 1 as a rotational driving member, a first ring 2 as a circular driven member, a second ring 3 as a second circular driven member, a first disc 5, a second disc 6, and a second circular driven member. 3 disk 7, outer casing 8, inner casing 9, outer collar 43 as a second collar member
and an internal collar 41 as a collar member;
and the second rings 2 and 3 each have a plurality of wedges 2
1 and a mood block 22.

The drive shaft 1 is connected to a drive unit with suitable couplings (not shown) and is shown as a drive member.

The first ring 2 and the second ring 3 are each configured to selectively transmit rotational movement of the drive shaft 1 via a plurality of wedges 21 and a fulcrum block 22,
and is shown as a driven member.

Referring now to FIG. 2, the first disk 5 is rotatably mounted on the drive shaft 1.

A pairing member 53 is used to prevent the first disk 5 from moving in the axial direction.

The first disk 5 is provided with an annular groove 51 on its inner side, and a retaining ring 28 as a retaining means, which will be explained later.
is placed there slidingly.

The first ring 2 has a plurality of shoulders 24 shown in FIG.
and an inner periphery having an inner surface 25 between each two shoulders, said inner surface 25 tapering along the axial direction shown in FIG.

A fulcrum block 22 is provided around the interior of the first ring 2, one between each two shoulders 24, and each fulcrum block 22
The wedge 21 shown in FIG. 3 is mounted thereon so as to surround the drive shaft 1 with the wedge 21.

As shown in FIG. 6, the fulcrum block is provided with a bottom portion 222 having a tapered surface along the longitudinal or axial direction so as to cooperate with the inner peripheral inner surface 25 of the first ring 2; Therefore, the fulcrum block 22 and the first ring 2
When there is a relative axial movement between them, the fulcrum block 22 is moved radially towards or away from the drive shaft 1.

At the other end opposite the bottom 222 of the fulcrum block 22,
A rounded upper edge or nose 221 is formed having a center of curvature M as shown in the drawings and is adapted to pivotally receive the wedge 21 thereon.

Referring to FIG. 5, the wedge 21 has a convex upper edge 211.
and a concave bottom 212, as well as side grooves 213 on each side.
is formed.

Because the concave bottom 212 is so formed, it fits with the nose 221 of the fulcrum block 22 and therefore the wedge 2
1 pivots on the nose 221 about the center of curvature M.

Wedge 21 is mounted on fulcrum block 22 as described above.

A compression spring 26 is provided in the side groove 213 as a first elastic means.
is provided, and the ends of this spring are wedge grooves 21.
3, and the other end is held by a projection 21 formed on a retaining ring 28 as shown in FIG. It is elastically biased in the direction.

The protrusion 281 extends towards the groove 213 so as to maintain a predetermined wedge position with respect to the retaining ring.

Referring to Figure 7, retaining ring 28 as a retaining means.
is provided with a suitable number of cutouts 282, perhaps four, on the side facing the first disc 5, in which the first
A stud 55 fixedly provided in the annular groove 51 of the disc 5 is adapted, which stud 55 holds the retaining ring 28 in a predetermined angular position, i.e. in the first
It has a pair of springs 56 as second elastic means for elastically maintaining it in the working position relative to the disk 5.

A spring 56 causes the retaining ring 28 to hold the first disc 5
can be rotated several degrees with respect to

Therefore, when the retaining ring is rotated several degrees, the side groove 21
All wedges 21 with projections 281 of retaining rings 28 extending to 3 pivot about their respective fulcrum blocks.

Because the wedge 21 is so configured, with the retaining ring 28 in the working position, the angle of inclination α as shown in FIG. 8 is maintained.

The inclination angle α is two lines L that intersect at a point P on the upper edge 211 of the wedge 21.

and K, where L is the straight line defined by the center O of the drive shaft 1 and the point P, normal to the circumference, and the line L1 is the point P of the wedge and the point where the wedge is attached. This is the straight line that passes through the center of curvature M of the nose of the fulcrum block, or the axis of the wedge.

In order to ensure that the clutch device operates without failure, the angle of inclination α is equal to the angle of friction θ of the curve of the drive shaft 1 with respect to the upper edge 211 of the wedge 21.

(Figure 11).

Returning to FIGS. 1 and 2, the first disc 5 is fixedly connected to the outer casing 8 by bolts 59;
The outer casing 8 is fastened to the first ring 2 as explained below, so that the angular position of the first disc 5 with respect to the first ring 2 is predetermined and fixed, and the angular position of the first disc 5 with respect to the first disc 5 is fixed. This allows for axial movement of the ring 2 of the ring 1.

The first ring 2 also includes a first push rod 4, which will be explained later.
An external groove 29A is provided around the external periphery with a notch 29B for receiving the flange 421 of No. 2.

A first ring 2 having a plurality of wedges 21 and a fulcrum block 22 disposed therein as described above is mounted coaxially on the drive shaft 1 as shown in FIG.

A suitable number of mating teeth 29, perhaps three, are formed on its outer periphery to slidably receive the key 58 to connect the outer casing 8 thereto.

There is a second disk 6 on each side thereof with the same annular groove 51 and the same retaining ring 28 of the groove, which second disk 6 rotates coaxially over the inner side of the first ring 2 The disk 6, which is freely structured, is provided with three holes 61 (Fig. 2) arranged at equal intervals around the circumference, through which the push rod 42 is inserted, and the push rod 42 is inserted. One end of the rod 42 is formed with a flange 421 to be engaged with the outer groove 29A of the first ring 2, and the other end is fixed to the inner collar 41 as will be explained later.

The second disc 6 is provided with an external flange part 62 which is held axially by the external casing 8 and internal casing 9 shown in FIG. 1, with respect to which its axial position is fixed.

A second ring 3 with an external groove 39 has a first ring 2
The same shoulder 24, wedge 21, fulcrum block 22 and retaining ring 28 are provided, with the exception that wedge 2
1 is configured to form an opposite angle of inclination with respect to the wedge of the first ring 2 as will be explained later and is mounted axially next to the second disc 6 on the drive shaft 1.

A suitable number of mating teeth 33, perhaps three, are formed on its outer periphery to receive keys 95 to which the inner casing is connected.

The second ring 3 has a flange 32 provided with three cuts 31 corresponding to the holes 61 of the second disk 6 so as to define a passage for the push rod 42 .

A third disc 7 having the same annular groove 51 in which the same retaining ring 28 is arranged is rotatably mounted axially adjacent to the second ring 3 on the drive shaft 1 and is provided with three holes 71 corresponding to the holes 61 of the second disk 6 and three other holes 72 located between each two holes 71.

The first push rod 42 and the second push rod 44 are slidably inserted through the hole 71 and the hole 72, respectively.

One end of the second push rod 44 is provided with a flange 441 to be engaged with the external groove 39 of the second ring 3, and the other end is fixed to an external collar 43, which will be described later.

Bearing means 73 are provided on the third disc 7 to prevent the third disc 7 from moving axially.

The third disc 7 is fixedly connected to the outer casing 8 with bolts 59 shown in FIG.

On the outside of the third disk 7, an inner collar 41 and an outer collar 43 are arranged coaxially.

The inner collar 41 is slidably attached to the drive shaft 1 and is provided with three outwardly extending flanges 412 equally spaced around the periphery, to which the first push rod 42 is fixed. be done.

An outer collar 43 is slidably mounted over the inner collar 41 and has an inwardly extending flange 432 disposed between each two flanges 412 of the inner collar 41, the flange 442 having a The second push rod 44 is fixed.

The inner collar 41 is adapted to be moved axially towards or away from the third disk 7 by means of a suitable displacement device, not shown, so that it can be moved axially towards or away from the third disk 7.
The push rod 42 and the first ring 2 are pushed or pulled in the axial direction accordingly.

The external collar 43 is moved to the third position by another moving device (not shown).
7 or away from the third disk 7, so that the second push rod 44 and the second ring 3 are pushed or pulled axially accordingly. or

The inner collar 41 and the outer collar 43 each have a spring 41.
S and 43S are provided to facilitate outward movement of the inner and outer collars or outward movement of the first and second rings, respectively.

The outer casing 8 has a first inner peripheral surface 8 provided with a first joint tooth profile 81 that corresponds to the joint tooth profile 29 of the first ring 2.
3 and a second inner circumferential surface provided with a mating tooth profile 82 matching the mating tooth profile 33 of the second ring 3 for receiving a key 86, this outer casing 8 having a 2 disk 6 and the second ring 3 and is axially held by the first disk 5 and the third disk 7.

The inner casing 9 has an outer peripheral surface 93 provided with a joint tooth profile 91 that corresponds to the second joint tooth profile 82 of the outer casing 8 and a joint tooth profile 9 that matches the joint tooth profile 33 of the second ring 3.
2, the inner casing 9 is provided between the outer casing 8 and the second ring 3 and the second disc 6 and the outer casing 8
, as well as the first disk 5 via the third disk 7
is held axially by

The outer casing 8 has a key 58 slidably inserted into the abutment teeth 81 and 29 and a key 86 slidably mounted onto the first ring 2 and also tightly inserted into the abutment teeth 82 and 91. is fixedly connected to the inner casing 9 at.

The inner casing 9 is slidably mounted onto the second ring 3 with a key 95 that is slidably inserted into the mating teeth 92 and 33.

Therefore, the first disk 5, the first ring 2, the second
disk 61. second ring 3, third disk 7,
Inner collar 41 and outer collar 43, outer casing 8 and inner casing 9 can rotate together as an integral unit.

The operation of the clutch device of this invention will be explained with reference to FIGS. 8 to 11.

Since the configuration of the second ring 3 is identical to the first ring 2 except for the direction of the wedge inclination angle, the operation of the device will be described by way of example with reference to the first ring 2.

8, 9 and 11, the drive shaft 1 rotates counterclockwise and the wedge 21 resists the rotational movement of the drive shaft 1 when brought into contact with the drive shaft 1. The wedge 21 of the first ring 2 is shown schematically with an angle of inclination in the direction of rotation (hereinafter referred to as one against rotational movement).

As previously explained, the wedge 21 may be moved toward or away from the drive shaft by actuating the inner collar 41 axially inward or outward.

As soon as the wedge 21 is moved towards the counterclockwise rotating drive shaft 1 and brought into contact with the drive shaft 1, a frictional force F is generated at the contact point P.

The frictional force F acts to cause the wedge 21 to rotate or pivot about the center of curvature M of the nose of the fulcrum block 22, thus causing the wedge 21 to rotate between the drive shaft 1 and the fulcrum block 2.
It acts so that it does not move between the two.

In addition to the frictional force F, at the point of contact, a normal force N is formed acting perpendicular to the circumferential surface of the drive shaft 1, resulting in a resultant force R action at an angle equal to the friction angle θ, which is applied to the wedge 2
1 acts to keep it stationary.

This is because, as described above, the inclination angle α is equal to the friction angle of, but does not become larger than it.

As a result, the wedge 21 is forced to grip the drive shaft 1 and the first ring 2 engages the drive shaft 1, so that they rotate together.

When the inner collar 41 is actuated to move axially outwards to pull the first ring along the same direction, the wedge 21, biased by the spring 26, moves away from the drive shaft 1. is moved, and thus releases the first jam, and thus moves the first ring 2 from the drive shaft 1.
disengage.

If the drive shaft 1 rotates clockwise, or if the first ring 2 fixedly connected to the outer casing 8, which is further coupled to an external load, rotates faster than the drive shaft 1, the frictional force F is Reversing its direction, the wedge 21 can be made to rotate freely and thus release one jam, so that the first ring 2
is uncoupled from the drive shaft 1.

The configuration of the second ring 3 is identical to that of the first ring 2, with the exception that the wedge inclination angle of the second ring 3 is in the opposite direction with respect to that of the first ring 2. .

In other words, the inclination angle of the wedge of the second ring 3 is along the direction of rotation of the drive shaft, whereas that of the first ring 2 is opposite to the direction of rotation of the drive shaft, or The opposite may be true.

The second ring 3 is operable together with the outer collar 43 to move axially, while the axial movement of the wedge 21 is prohibited by the second and third discs 6 and 7, whereby the second Performs the same function as ring 2 of 1, but in the opposite direction of rotation.

The second embodiment of the clutch brake device of this invention is the first embodiment.
This is shown in Figure 2.

In a second embodiment, each wedge is formed with a hole 215 as shown in FIG. , each 2 as shown in FIG.
The hole 215 of the wedge 21 is inserted into the space between the adjacent wedges.
The extension 231 is shaped to pass through.

The spacers 23 are so formed that, as in the first embodiment, the wedges are tilted and resiliently retained with respect to the drive shaft 1 at an angle of inclination α, and yet the wedges spring back towards the respective fulcrum block. Keep it energized.

A retaining ring 28 having projections 281 each corresponding to and extending into the side grooves 213 of the wedges 21 actuates the wedges together to ensure that all wedges actuate simultaneously and uniformly. It is provided so as to be connected to.

Springs 26 and 56 used in the first embodiment have been eliminated in the second embodiment.

That is, the elasticity of the material of the spacer 23 itself acts as a first elastic means to resiliently bias the wedge 21 in the direction of the fulcrum block 22.

Further, each spacer 23 acts as a second elastic means and a holding means, and by fitting the wedge 21 in its shape, the posture of the wedge 21 itself is restricted, and the spacers 23 are connected in an annular manner by the extension part 231. The mutual positions are maintained in a constant state by

The clutch device of the invention described above can be operated in several ways as follows.

When both the inner and outer collars 41 and 43 are actuated to move axially outwardly, all wedges 2
1 is moved radially outwards and no rotational movement of the drive shaft is transmitted.

When the inner and outer collars 41 and 43 are actuated to move axially inwardly, all the wedges 21 are moved radially inwardly and the rotational movement of the drive shaft causes the drive shaft to move in one direction. When the drive shaft rotates, it is transmitted by the first ring, and when the drive shaft rotates in the opposite direction, it is transmitted by the second ring.

When either the inner collar or the outer collar is actuated to move axially inwardly, the corresponding first or second ring wedge is moved radially inwardly and rotation of the drive shaft Motion is transmitted only in the specified direction.

The clutch device of this invention may be used when a reciprocating rotational movement is transferred to a unidirectional rotational movement or when it is not desired for the driving member to be driven by the driven member.

The device may also be used with an external casing that is statically fixed as an automatic brake that allows a member to rotate in one direction, but stops it the moment it attempts to rotate in the opposite direction. and would be a useful device for use in place of traditional handbrakes for motorized vehicles.

In order to use the device of the invention as a handbrake for a motorized vehicle, the outer casing 8 is provided with suitable means.
For example, it may be secured by a brake band and either the inner or outer collar is held in the inner position to keep either ring in the operative state, and the device then becomes a one-way automatic brake; It is quite useful when you have to start from a stop on a slope.

By properly operating the internal or external collar, the vehicle can start moving uphill from a standstill in a forward or reverse direction without rolling down the slope.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view, partially cut away, of a first embodiment of the invention. FIG. 2 is an exploded perspective view of the first embodiment shown in FIG. 1, with each component member partially cut away. FIG. 3 is a schematic diagram showing the structure of the wedge of the embodiment shown in FIG. 1. FIG. 4 is a sectional view of the driven member or ring of the embodiment shown in FIG. 1. FIG. 5 is an enlarged perspective view of the wedge used in the embodiment shown in FIG. 1, showing the upper and lower sides. FIG. 6 is an enlarged perspective view of the fulcrum block used in the embodiment shown in FIG. 1. FIG. 7 is a fragmentary perspective view of the retaining ring assembled with the disk. FIG. 8 is a schematic diagram showing the principle of operation of the clutch brake device of this invention. FIG. 9 is a schematic diagram showing a wedge gripping the drive shaft. FIG. 10 is a schematic diagram showing a wedge for releasing the drive shaft. FIG. 11 is a force polygon showing the relationship between the friction force and the angular position of the wedge with respect to the circumferential surface of the drive shaft. FIG. 12 is a perspective view, partially cut away, of a second embodiment of the invention. FIG. 13 is a schematic diagram showing the structure of the wedge and spacer of the second embodiment shown in FIG. 12. FIG. 14 is a perspective view of a wedge used in the second embodiment. FIG. 15 is a schematic cross-sectional view showing the formation of a spacer in the second embodiment. In the figure, 1 is the drive shaft, 2 is the first hinge, and 3 is the drive shaft.
5 is a second ring; 5 is a first disk; 6 is a second disk; 7 is a third disk; 8 is an outer casing; 9 is an inner casing; 43 is an outer collar; 41 is inside

Claims (5)

[Scope of utility model registration request] (1) a rotary drive member having a longitudinal axis and a circumferential surface; a circular driven member coaxially mounted on the drive member and having an inner periphery and an outer periphery; and a circular driven member disposed around the rotary drive member. a plurality of wedges, each wedge being pivotally mounted on a fulcrum block configured on the inner circumference of the driven member, and having a point in contact with the circumferential surface, a rotation center, and the point. and a first elastic means having a wedge shaft passing through the rotation center, one end of which engages the wedge and elastically biases the wedge toward the fulcrum block, and the wedge shaft is connected to the contact point. holding means for maintaining the attitude of each of the wedges so as to pass through the drive member and form a predetermined inclination angle on one side with respect to a normal line perpendicular to the circumferential surface of the driving member; a second elastic means for resiliently biasing the wedge via the holding means in a direction in which a displacement from the inclination angle is O in order to elastically hold the wedge; an inner surface formed on the fulcrum block and tapered with respect to the longitudinal axis; and a tapered bottom surface formed on the fulcrum block and corresponding to and slidingly engaged with the inner surface. and a collar member having a push rod adapted to move the circular driven member in an axial direction, the wedge actuating means for moving the wedge in the direction of the rotary drive member. Device. (2) A plurality of spacers made of an elastic material are fitted between each of the wedges, and the plurality of spacers are connected to each other by an extension part integrally formed therewith, and the extension part surrounds the drive member. The clutch brake according to claim 1, wherein the clutch brake constitutes the first and second elastic means and the holding means by passing through a hole formed in the wedge so as to link the wedge to the clutch brake. Device. (3) said wedges are each provided with a side groove, and said retaining means is a retaining ring having a plurality of protrusions corresponding to said wedges, each protrusion being a uniform and simultaneous part of said wedge; Clutch-brake device according to claim 1, which extends into corresponding side grooves of each wedge to operatively connect the wedges to ensure movement. (4) The circular driven member is provided with two disc members coaxially attached to two opposite sides thereof, each disc member having an annular groove and the retainer slidably fitted in the annular groove. a ring, the first elastic means each having one end retained by a protrusion formed on one side of the wedge, and a protrusion formed on one side of the retaining ring. a compression spring having opposite ends retained by a second resilient means, each pair retaining a protrusion formed on the other side of the retaining ring so that the retaining ring is pre-coupled with the disc member; Utility model registration claim No. 3, which is a pair of springs adapted to be elastically maintained in a defined angular relationship.
Clutch brake device as described in section. (5) The clutch according to claim 1, wherein the circular driven member is provided with an external casing mechanically connected to the circular driven member, and the circular driven member is slidable with respect to the external casing. Brake device.