JPH0222506Y2 - - Google Patents

Description

[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to a clutch and brake combination unit, and more particularly, to a clutch and brake combination unit that continuously circulates oil whenever the unit is in operation. The present invention relates to an oil-immersed clutch-brake unit integrally equipped with operative hydraulic pressure transmission means.

BACKGROUND OF THE INVENTION Various types of clutch-brake units have been employed to transfer rotational energy between a power source and the equipment driven by it.
Such devices provide a means for stopping and starting a driven device without shutting down the power source, thereby allowing other devices to be driven by a common power source and conserving power. be adopted for. By including a damping feature, more rapid deceleration can be obtained than that achieved by friction alone.

During operation, particularly during the initial stages of clutch and brake operation, such clutch-brake units generate a large amount of heat between their respective torque transmitting surfaces, causing wear. It is therefore desirable that these surfaces be provided with sufficient lubrication and cooling, especially during the early stages of their frictional engagement.

To provide this lubrication and cooling, the clutch
It is possible to add a separate auxiliary hydraulic feeder to the brake unit. However, for reasons of required capital, maintenance, and operational economy, it is desirable to avoid additional auxiliary pumping equipment for supplying this lubricant.

The object of the present invention is to provide a hydraulic transmission system that can provide sufficient lubrication and cooling to the torque transmission surface, especially during the initial stages of clutch actuation and braking operations, which require sufficient lubrication and cooling. An object of the present invention is to provide a clutch-brake unit integrally equipped with the following. The invention provides a durable clutch-brake unit that requires less maintenance than conventional units and eliminates the need for auxiliary external pumping means to circulate lubricant and coolant to the torque-transmitting surfaces. is provided. Furthermore, the present invention allows the user of the unit according to the present invention to achieve indirect cost reductions, since the operating time of the driven device is increased. Furthermore, according to the present invention, lubrication and cooling can be performed without using an auxiliary pumping device.

(Means for solving the problem) The clutch-brake unit according to the present invention has the following features:
It has a housing defining a central cavity between longitudinally opposed and spaced apart end walls.
An input shaft is provided extending through one of the end walls and into the cavity. An output shaft is also provided extending through the other end wall. A series of radially disposed clutch plates are mounted within the cavity for rotation with the input shaft. A respective series of radially disposed and axially spaced first and second friction plates are mounted within the cavity for rotation with the output shaft. A series of radially disposed brake plates are provided, the brake plates being non-rotatably arranged within the cavity and adapted to cooperate with a second series of friction plates to brake rotation of the output shaft. be activated. The clutch plate and the first series of friction plates are operated in conjunction to transfer rotational energy between the input and output shafts. The hydraulic delivery means circulates oil over the clutch plate, the first and second series of friction plates, and the brake plate in response to rotation of the input shaft;
It works to cool and lubricate them.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring to the drawings, a clutch-brake unit according to the present invention is shown generally at 10, comprising longitudinally spaced units 10 defining an internal cavity therebetween. It includes a generally cylindrical housing 12 having opposed end walls 14,16. The end wall 16 has a large opening 15 which is closed by a removable end wall 17. Housing 12 also has a longitudinally extending aperture 20 at the top of which is secured to housing 12 by a cover plate 22 secured to housing 12 by any suitable means such as a plurality of bolts or the like.
Closed by. In order to dissipate the heat generated during operation of the clutch-brake unit,
The housing 12 may also be provided with external heat radiating fins 24 projecting outwardly.

The input shaft 26 has an opening 2 in the end wall 14.
8 into the cavity 18 and is rotatably supported within the cavity by bearings 27,29. The input shaft 26 has an enlarged diameter annular support portion 30 at its inner end from which a plurality of drive ears 32 project axially outwardly. As shown, the clutch-brake
The unit 10 is provided with four drive ears 32 approximately equally spaced around its circumference, although the number of ears 32 may be increased or decreased for larger or smaller capacity clutch-brake units. A plurality of friction clutch plate members 34 are mounted to drive ears 32 and extend radially inwardly therefrom.
A plurality of oil pump impeller vanes 36 are also provided on drive ear 32 and extend generally radially outwardly from projection 32 over approximately the same extent as projection 32.

An output shaft 38 extends into the cavity 18 through an opening 40 in the removable end wall 17 and is journalled within the cavity 18 by a suitable bearing assembly 42. The output shaft 38 has an inner end portion 44 rotatably supported by a bearing 46 concentric with the input shaft 26 and engaging a radially inwardly directed annular shoulder 48 on the input shaft 26. Inner end portion 44 partially projects into an axially extending bore 50 in input shaft 26 . The output shaft 38 has an enlarged diameter portion 52
The portion 52 has a plurality of axially extending circumferentially spaced slots 54.
and a plurality of relatively shallow axially extending notches 56 between the slots. An annular notch 58 is provided approximately midway along the enlarged portion 52 and includes a split snap ring 6.
0 is inserted to divide the enlarged portion 52 into a clutch disk portion 62 and a brake disk portion 64. A plurality of clutch discs 66 and brake discs 68 each include a notch 56.
Complementary notches are provided which fit within the disks and are mounted in their respective sections 62, 64 for rotation with the output shaft 38.

A plurality of friction brake plates 70 are supported by a plurality of axially extending brake ears 72 which are non-rotatably supported on the removable end wall 17. Extending outwardly from section member 74 . As shown in FIG. 1, clutch plate member 34 is interposed between friction clutch disks 66 and brake plate 70 is interposed between brake disks 68.

An annular clutch actuation member 76 is located near the outer end of clutch disc portion 62 and is operatively connected to a brake actuation member 78 located near the outer end of brake disc portion 64 of output shaft 38. The brake actuating member 78 and the clutch actuating member 76 are arranged in a plurality of slots extending through the slot 54 arranged in an alternating relationship and holding the actuating members fixedly in a predetermined spaced relationship. They are connected to each other by screws 79 and rods 81. A piston actuating means, generally indicated at 83, is operatively connected to the actuating members 76, 78 to impart axial movement to the actuating members to actuate either the clutch portion or the brake portion of the clutch-brake unit 10. The operation and additional structural details of the clutch-brake unit 10 are substantially similar to those described in commonly assigned U.S. Pat. No. 3,969,898, entitled Clutch-Brake Unit. .

As shown in detail in FIG. 2, cavity 18 is centrally located between end walls 14, 16 and surrounds clutch disc 66, clutch plate 34 and brake disc 68, brake plate 70. It has a generally cylindrical portion 80. As shown, the diameter of this portion 80 is such that its inner wall portion 82 is in close proximity to and cooperates with the impeller blades 36 to provide a large volume centrifugal hydraulic pumping action.

As shown in detail in FIG. 3, impeller vanes 36 are preferably integrally formed with respective drive ears 32 and extend axially from an annular flange portion 88 on support portion 30. a radially outwardly extending projection formed in part by outwardly extending circumferentially spaced radially outwardly sloped sidewalls 84, 86; is preferred. The outer ends of the impeller vanes 36 include a chamfered or radially inwardly sloped surface 90 that allows oil to flow from the brake plate and disc as well as from a reservoir 92 provided in the lower portion of the housing 12 to the vanes. Promotes flow, thereby aiding the pumping action of the reservoir. The radially outer surface 93 of the impeller blades 36 is convex with a radius of curvature equal to the radius of the arc that each blade describes during rotation of the input shaft.

The vane 36 cooperates with the cylindrical portion 80 to open the storage tank 9.
2 to a pumping chamber 94 formed in part by a hanging projection 96 provided at the top of the housing 12 and integrally formed with the cover plate 22. The protrusion 96 has a first recess 98 overlying the passageway of the impeller blades 36 and spaced radially therefrom, and a second recess 100 overlying the brake plate member 70, also having a lateral cross section. It also has concave inclined surfaces 102 which serve to assist in directing oil flowing radially outwardly from brake plate member 70 into pumping chamber 94 .

An oil outlet passage 104 extends axially from the left end (as viewed in FIG. 1) of the pumping chamber 94 radially inwardly into the annular space 106 in the vicinity of the bearing 29 and surrounds the input shaft 26 of the housing 12 . It is located inside. The input shaft 26 is provided with a plurality of radially inwardly extending oil passages 108 in fluid communication with the space 106 and further provided in the input shaft 26 and connected to the end of the input shaft 38. It is also in fluid communication with a cylindrical bore 50 into which portion 44 fits. Preferably, the input shaft 26 has three equally spaced radial passages 108. The output shaft 38 has a hole 5 extending outwardly from the end portion 44.
an axially extending passageway 11 open to 0;
0 is provided, and this passage 110 is preferably coaxial with the axis of rotation of the output shaft 38.

a plurality of radially outwardly extending oil outlet passages 1;
12 is also provided along the output shaft 38,
A first series of passages 114 is radially aligned with clutch plate 34 and clutch friction disc 66, and a second series 116 is radially aligned with brake plate 70 and brake friction disc 68. aligned and positioned. Passage 112
each open into a selected one of the axially extending slots 54 in the enlarged diameter portion 52 of the output shaft 38.

As shown in detail in FIG. 5, a first series of passages 11 of radial oil outlet passages 112
4, each group is axially spaced 3
three approximately equally circumferentially spaced groups of passages 118, 12 of three passages 112;
It consists of 0,122. Passage 11 of these groups
8, 120, 122 are slightly staggered or displaced in the axial direction so that there are no two passages 112 each having a circumferentially aligned opening. Similarly, the second series of passages 116 of the radial outlet passages 112 is also comprised of three generally equally circumferentially spaced groups of passages 124, 126, 128, each group of three passages 112. These groups are also axially displaced so that there are no two passages 112, each with a circumferentially aligned opening. This alternation of oil outlet passages 112 directs the appropriate amount of oil between and over clutch plate 34, brake plate 70, clutch disc 66, and brake friction disc 68.

An additional oil outlet passage 130 extending radially outward also terminates at the end 1 of the axial passage 110.
32 which serves to supply lubricant to bearing assembly 42 and also to the interface between piston assembly 83 and outlet shaft 38.

Referring again to FIG. Supplemental external cooling may be required for larger capacity clutch-brake units, and in some units oil may be circulated through other auxiliary external equipment such as Sometimes it is desirable. Therefore, the cover plate 22 has 1
A pair of spaced apart openings 134, 136 are provided to which suitable conduits are connected via suitable attachment lines for directing oil to auxiliary equipment such as an oil cooler 138. Can be done. As shown, opening 134 opens directly into pumping chamber 94 to allow oil to flow to oil cooler 138 .
An opening 136 communicates with a downwardly or radially inwardly extending passageway 139 in the housing 12 to direct oil into the space 106 .
Although passageways 104, 139 and openings 134, 136 may be sized to direct only a small portion of the oil through oil cooler 138, passageway 104 also includes an enlarged diameter portion 140 near pumping chamber 94. The portion 140 is adapted to receive a plug, which plug is connected to the passageway 104.
is completely closed and almost all oil is removed from the oil cooler 138.
Allow it to flow through.

The overall operation of a clutch-brake unit that embodies the principles of the present invention will be explained. The torque transmission portion of the clutch includes a plurality of clutch plate members 34 and a plurality of clutch friction disks 66 arranged alternately, one of the disks 66 being connected to the clutch actuating member 7.
6 and another one of the discs 66 is located near the side of the center ring 60. These torque transmitting elements within the housing 12 are rotatable within an oil bath contained within the housing 12, with the result that a large portion of the kinetic energy generated in starting and stopping heavy loads is transferred to various sources. is transmitted by "shearing" the oil between the friction plates of the invention, thus not only considerably increasing the service life of these friction plates over those operating dry, but also increasing the maximum operating speed of the unit 10 of the present invention. also increases. The large-capacity centrifugal oil pump described above includes a clutch plate 34, a brake plate 70, a clutch friction disk 66, and a brake friction disk 6.
8 and supplies an appropriate amount of oil.

As input shaft 26 rotates, pump impeller vanes 36 actuate and begin to circulate oil from reservoir 92 to pumping chamber 94 and then through openings 134 , 136 or passage 104 to space 106 and then to radial passage 108 . and then to the input shaft 26. The oil then passes through the axial passage 110 of the output shaft 38 to the radial outlet passage 112.
flow to the clutch plate 34 and brake plate 70.
and flows outwardly onto the clutch disc 66, brake friction disc 68. The vanes 36 create sufficient pressure to allow the proper amount of oil to flow;
It should be noted that the flow of oil across the plates and disks is aided by the centrifugal force created by the rotation of the output shaft 38. Since the input shaft 26 is constantly rotating whenever the clutch-brake unit is engaged, the provision of impeller blades on the input shaft generates high heat, including when the output shaft is just beginning to rotate. An appropriate amount of oil is supplied to the clutch plate and clutch disk at all times.

When the input shaft 26 begins to rotate and the impeller blades on the input shaft begin to circulate oil as described above, the piston assembly 83 is actuated to cause the brake actuating member 78 and the clutch actuating member 76 to rotate. Simultaneously move to the right in the axial direction as seen in Figure 1. This movement releases the brake plate 70 and brake friction disc 68, which hitherto prevented rotation of the output shaft 38. Brake and clutch actuation members 70, 68
As the clutch continues to move, clutch plate 34 and clutch friction disk 66 move together between the sides of clutch actuating member 76 and ring 60 into a torque transmitting relationship. Then, the output shaft 38
begins to rotate as the slippage between clutch plate 34 and clutch disk 66 decreases. When the input shaft 26 is continuously rotating at or near full speed, the oil supplied through the passages 112 between each of the clutch plates and each of the clutch discs is continuously distributed, thereby causing the clutch to Lubricate and cool the plates and disks. To stop the clutch-brake unit, piston assembly 83 is stopped and actuating members 76, 78 are moved axially to the left as viewed in FIG. is released, pulling brake plate 70 and brake disc 68 together to apply braking torque to the output shaft. Also, as input shaft 26 continues to rotate at full speed, a suitable amount of oil is supplied across brake plate 70 and brake disc 68 to cool and lubricate them during braking operations.

Although it is clear that the preferred embodiment of the invention described above has been carefully considered to obtain the advantages and features described above, it will be understood that various modifications may be made to this embodiment without departing from the principles of the invention. Good morning.

(Effects of the invention) As is clear from the above explanation, according to the invention, the clutch plate, brake plate, and friction plate of the clutch-brake unit are always supplied with the hydraulic pressure while the unit is in operation, without providing an auxiliary hydraulic pressure feeding means. Oil can be circulated under pressure and good lubrication and cooling can be achieved. In particular, sufficient lubrication and cooling can be provided even in the early stages of frictional engagement, when a large amount of heat is generated and a large amount of wear may occur, thereby preventing wear on torque transmission elements such as clutch plates. , a durable clutch-brake unit can be provided.

[Brief explanation of the drawing]

Fig. 1 is a partially cutaway side view of a clutch-brake unit according to the present invention, and Fig. 2 is a side view of the clutch-brake unit according to the present invention.
3 is a perspective partial view of the blades of the impeller attached to the input shaft, and FIG. 4 is a cross section taken along line 4-4 in FIG. 1. FIG. 5 is an exploded view of a portion of the output shaft showing the arrangement of the radial oil outlet passages therein. 10...Unit, 12...Housing, 1
4, 16... end wall, 18... void, 26... input shaft, 34... clutch plate, 36... pressure feeding means, 38... output shaft, 66, 68... first and second Friction plate, 70...brake plate.

Claims (1)

[Claims for Utility Model Registration] In a clutch brake, an outer housing defining between opposed, longitudinally separated end walls a central cavity having an oil reservoir in the lower part thereof; an input shaft having an annular enlarged portion of increased diameter extending radially inwardly along an inner surface thereof and rotatably journalled in one of the end walls; a series of circumferentially spaced axially extending splines oriented along a portion of the outer surface of the enlarged portion;
an input shaft having a plurality of integral vanes directed radially outward; an oil passage means; a pump chamber surrounding an enlarged portion of the input shaft having the vanes; a pump chamber having an inlet port communicating with an oil reservoir and an outlet port communicating with one end of said oil passage means; a series of clutch plates having teeth on their outer periphery at which said input shaft is enlarged; a clutch plate attached to a spline of a portion such that an enlarged portion thereof defines a clutch working chamber around said clutch plate; and a clutch plate coaxial with said input shaft and extending into said cavity; an output shaft rotatably journaled in the other end wall, the output shaft having an end portion interdigitated within a portion of the input shaft and further extending radially outwardly along an outer surface of the output shaft; a series of circumferentially spaced axially extending splines directed toward the axially extending splines; an axially extending oil passageway open at said end portion; and an axially extending oil passageway extending outwardly from said axial oil passageway. an output shaft having a radial passage; a stationary, annular inner housing fixedly mounted to the outer housing; and a series of brake plates non-rotatably mounted within the stationary, annular inner housing; a brake disc, wherein the inner housing is adapted to define a brake activation chamber around the brake disc; and teeth along an inner periphery thereof, the teeth engaging the spline of the output shaft. a first shaft mounted on the output shaft in a spaced relationship in the axial direction when the first
and a second series of friction plates, said first series of friction plates adapted to cooperate with said clutch plate when actuated to transfer rotational energy from said input shaft to said output shaft. a second series of friction plates, the second series of friction plates being adapted to cooperate with the brake plate to brake rotational movement of the output shaft when actuated; an actuating means for selectively actuating one of the two series of friction plates, the other end of the oil passage means communicating with the portion of the input shaft, and the vane comprising: In response to rotation of the input shaft, oil is routed from the oil reservoir through the pump chamber, the oil passageway, the axial passageway, and the radial passageway to the clutch plate, the brake plate, and the first and a clutch and brake unit operable to pump across a second series of friction plates.