DE2944008A1 - CLUTCH BRAKE UNIT - Google Patents

Description

Clutch brake unit

The present invention relates generally to a clutch brake unit and in particular to a novel and improved clutch brake unit immersed in oil, the integrally formed oil pumping devices for carrying out a continuous Has oil circulation during operation of the unit.

Clutch brake units of the most varied of embodiments have long been in use to transfer rotational energy between an energy source and to be transmitted to a device to be driven by this. Such units are normally used to provide a device for alternately stopping and starting up such a device, without the need to shut down the energy source in order to save energy in this way and the To enable operation of other facilities that are powered by a common energy source can. By installing the braking devices, a faster deceleration of the output shaft is possible than would be the case through friction alone.

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Generate during operation and especially during initial periods of clutch actuation and braking Such clutch brake units large amounts of heat, so that between the respective torque transmitted A relatively large amount of wear occurs. It is therefore desirable to provide facilities which both lubricate and cool these surfaces. For the sake of economy both in maintenance and in operation as well as the required investments, however, it is advantageous if additional auxiliary pumping devices to deliver this lubricant can be avoided.

According to the invention, therefore, an improved clutch brake unit is created, which is an integral part of the Comprises a high volume centrifugal oil pumping device formed on the output shaft and which is in operation; whenever the input shaft rotates. In addition, oil passage facilities are provided, to continuously circulate the oil through the unit and this over almost all of them Distribute torque-transmitting surfaces and thereby prevent excessive local wear. Additionally for this purpose, precautions are taken that the oil pumping devices in an effective manner the whole or one Part of the oil through an external auxiliary device, for example an oil cooler or a filtration

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facility, can circulate. Accordingly, the present invention provides a durable clutch brake assembly before, which requires much less maintenance and an external auxiliary pumping device for Eliminates the need for circulation of the lubricant. It also offers reduced maintenance for the user the present invention indirect cost savings, since the driven device has a a larger proportion of the time is available for normal operation.

Additional advantages and features of the present invention will become apparent from the following description as well as the claims and the drawing. Show it:

Figure 1 is a partially sectioned side view of an embodiment of a clutch brake unit constructed according to the invention;

Figure 2 shows a cross section through the clutch brake unit of Figure 1 along the line 2-2 in Figure 1;

Figure 3 is a partial perspective view of an impeller vane that is featured on the input shaft

see is;

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Figure 4 is a partial cross-section of the input shaft along line 4-4 in Figure 1; and

Figure 5 shows a developed part of the output shaft, the arrangement of the provided therein radial oil outlet channels is shown.

The clutch brake unit shown in the figures and constructed according to the invention is denoted by the reference number 10 and comprises a generally cylindrical shape molded housing 12, the two longitudinally spaced has mutually arranged end walls 14 and 16 which partially form an inner chamber 18 between them. The end wall 16 is provided with a large opening 15 which is closed by a removable end wall 17. The housing 12 is also with a longitudinal direction extending opening 20 is provided on its upper side, which is closed by means of a cover plate 22 which is attached to the housing 12 in any arbitrary manner, for example by a plurality of bolts o.a., is attached. The housing 12 can also be provided with outwardly projecting heat radiating fins 24, if so desired, the thereto contribute to destroying the heat energy developed during the operation of the clutch brake unit.

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An input shaft 26 extends into the channels through an opening 28 provided in the end wall 14 1Ö and is rotatably arranged therein by means of bearings 27 and 29. The input shaft 26 is at its inner end with an annular bearing portion 30 with an enlarged Provided diameter, from which a plurality of drive lugs 32 protrude axially outward. How one As can be seen from the drawing, the clutch brake unit 10 is provided with four drive lugs 32 which, to the bearing portion 30 are arranged at substantially equal intervals. For clutch brake units with greater or lesser capacity, a greater or lesser number of such drive lugs can be provided be. A plurality of friction clutch plate elements 34 is mounted on the drive lugs 32, which extend radially inward therefrom. In addition, there is a large number of on the drive lugs 32 olpumplaufradflügein 36 is provided, referring to on the tabs extending generally radially outwardly in substantially one direction therewith.

Into the chamber 18 extends through one in the removable End wall 17 provided opening 40 an output shaft 38, which via a suitable bearing unit 42 is rotatably mounted in the chamber. The output shaft 38 extends coaxially with the input shaft 26

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and has an inner end portion 44 which is rotatably disposed in a bearing 46 which engages with a annular radially inwardly directed shoulder 48 on input shaft 26 is engaged. The end section 44 projects partially into an axially extending bore 50 in the input shaft is arranged. The output shaft 38 has a portion 52 with an enlarged diameter in which a plurality of axially extending, circumferentially spaced slots 54 and one A plurality of relatively flat, axially extending notches 56 are provided between the slots 54 is. Furthermore, an annular notch 58 is provided approximately in the middle of section 52, in FIG which is fitted with a split snap ring 60 that connects section 52 into a clutch disk section 62 and brake disk portion 64 divides. A plurality of clutch discs 66 and brake discs 68 are each provided with complementary shaped notches that mate with the notches 58 and on corresponding Sections 62 and 64 are mounted so that they are rotatable together with the output shaft 38.

A plurality of friction brake plates 70 is mounted on a plurality of axially projecting brake lugs 72, extending from a bearing member 74 which is non-rotatably attached to the removable end wall 17 and from

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this is supported, extend outwards. As shown in FIG. 1, the clutch plates 34 are arranged between the clutch friction disks 66 and the brake plates 70 between the brake friction disks 68.

An annular clutch actuator is adjacent to the outer end of the clutch disc portion 76 arranged and connected to a brake actuator 78, which is to the outer end of the brake disc portion 64 of the output shaft 38 is arranged adjacent. The brake actuator 78 and the Clutch actuating elements 76 are connected to one another via a plurality of screws 79 and rods 81, which are alternately arranged and extend through slots 54 so that they are the actuators Lock 72 and 78 firmly at a predetermined distance. A piston actuator generally designated 83 is connected to the actuating elements 76 and 78 and can move them in the axial direction, see above that in this way either the clutch or the brake cutout of the clutch brake unit 10 is actuated can be. How the clutch brake unit works 10 and the additional structural details of the same essentially correspond to those in in U.S. Patent 3,969,898.

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As best seen in Figure 2, the chamber 18 is of generally cylindrical section 80 provided centrally between the end walls 14 and 16 is arranged and the clutch disks and plates 66 and 34 and the brake disks and plates 68 and 70 surrounds. The diameter of the section 80 is so large that the inner wall section 82 is in close proximity to the impeller blades 36 and with them cooperates to act as a high volume centrifugal oil pump to act.

As can best be seen from FIG. 3, each drive lug 32 is preferably formed in one piece with an impeller vane 36, the impeller vane being one comprises radially outwardly extending projection, which is partially spaced apart in the circumferential direction, radially outwardly diverging side walls 84 and 86 are formed, which extend from the annular flange 88, which is formed on the bearing portion 30, extend axially outward. The outer end of the impeller blade 36 includes a beveled or radially inwardly sloping surface 90 which serves to direct the flow of oil into the To facilitate wings, for example from the brake plates and discs as well as from the one in the lower section of the housing 12 provided memory 92, and thereby to support the pumping action. The radially outer Surface 93 of impeller blade 36 is convex

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and has a radius of curvature corresponding to the radius of the arc taken by each wing during the Rotation of the input shaft is circumscribed.

The impeller blades 36 work with the cylindrically shaped Section 80 works together to pump oil from reservoir 92 into a pumping chamber 94 located at the top of the housing 12 is provided and is formed in part by a depending projection 96 which is integrally formed on the cover plate 22 is shaped. The protrusion 96 has a first concave surface 98 that defines the path of the impeller blades 36 is superimposed and spaced in the radial direction therefrom, and a second concave surface 100, the the brake plate elements 70 superimposed, and an inclined also formed concave in cross section Surface 102 connecting surfaces 98 and 100 which help to keep the flow of oil from the To steer brake plate members 70 radially outward into the pumping chamber 94.

Oil louse
In the housing 12, a / laßkanal 104 is provided, which extends from the left end (as seen in Figure 1) of the pump chamber 94 radially inward and axially to the left to an annular space 106 in the vicinity of the bearing 29 and surrounds the input shaft 26. The input shaft 26 is radially inward with a plurality of it

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extending oil passages 108 which are in fluid communication with the space 106 and the cylindrical bore 50 provided in the input shaft 26 and into which the end portion 44 of the output shaft 38 is fitted. The input shaft preferably has 26 three equally spaced radial channels 108. The output shaft 38 is with a itself axially extending channel 110 is provided, which extends from the end portion 44 into the bore 50 outward opens and which preferably extends coaxially to the axis of rotation of the output shaft 38.

A plurality of radially outwardly extending oil outlet channels are also along the output shaft 38 112 are provided, of which a first row 114 is in radial alignment with the clutch plates 34 and the clutch friction plates 66 and a second axially spaced row 116 in radial alignment with the Brake plates 70 and the brake friction disks 68 is arranged. Each of these channels 112 opens into selected ones axially extending slots 54, which on the section 52 of the output shaft 38 with enlarged Diameter are provided.

As best seen in Figure 5, the first row 114 of the radial oil outlet passages 112 includes three substantially uniformly in the circumferential direction

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spaced groups 118, 120 and 122, each group comprises three of these axially spaced channels 112. Each group 118, 120 and 122 is offset in a zigzag fashion or arranged slightly shifted in the axial direction, so that under no circumstances do two channels 112 have openings, which are aligned with one another in the circumferential direction. Similarly, the second row includes 116 of the radial oil outlet channels 112 are also three in the circumferential direction substantially equally spaced groups 124, 126 and 128, each of which has three channels 112 has. Again, each group is slightly shifted in the axial direction, so that in no case two Channels 112 aligned with one another in the circumferential direction Openings aufweus-vL. Πι-. ·. · Zigzag ver «ei; zU; The arrangement of the oil outlet channels 112 ensures that between and over each of the clutch and brake plates 34 and 70 and clutch and brake friction discs 66 and an adequate oil supply is directed.

At the output end 132 of the axial channel 110 is also a additional, radially outwardly extending oil outlet channel 130 arranged, the oil for lubricating the Bearing unit 42 and the interface area between the piston unit 83 and the output shaft feeds.

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For large capacity clutch brake units, additional external cooling may or may not be necessary In some units it may be desirable to have oil supplied by other external auxiliary devices, for example To let filters and the like circulate. As can be seen from Figure 1, the cover plate 22 is therefore with two spaced openings 134 and 136 to which suitable lines can be connected via suitable fittings to convey the oil to such auxiliary devices, for example an oil cooler 138 to be able to supply. As can be seen from the illustration The opening 134 extends directly into the pumping chamber 94 and allows oil to flow to the oil cooler 138. The opening 136 communicates with a downwardly or radially inwardly extending channel 139 in connection, which is provided in the housing 12 and serves to direct the oil into the space 106. While the channels 104, 139 and the openings 134 and 136 may have dimensions such that only a portion of the oil passes through the Oil cooler 138 is directed, the channel 104 in the vicinity of the pump chamber 94 can also have a section 140 be equipped with an enlarged diameter that can accommodate a plug to thereby open the channel 104 to be able to close completely and to ensure that almost all of the oil flow through the Oil cooler 138 is steered.

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The following now describes the overall operation of the invention trained clutch brake unit 10 described. The torque-transmitting section of the clutch is by an alternating arrangement of a plurality of clutch plate elements 34 and a plurality of Clutch friction disks 66 characterized, with one of the disks 66 in the vicinity of the end face of the clutch actuator 76 and one of the disks 66 is arranged in the vicinity of the central ring 60. This torque Transferring elements within the housing 12 are intended to rotate in an oil bath which is arranged in the housing 12 is, with the result that a fairly high percentage of the starting and braking of heavy Loads generated kinetic energy by shearing the oil between the various friction plates transferred and in this way not only the service life of these friction plates compared to those that work dry, but also the maximum working speed of the unit 10 is increased. The above described high-volume centrifugal oil pump provides an adequate supply of oil via the clutch plates 34, brake plates 70, clutch friction plates 66 and brake friction plates 68 sure.

As the input shaft 26 rotates, the pump blades 36 begin circulating the oil from the accumulator

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92 into pumping chamber 94, then through either openings 134 and 136 or channel 104 to space 106 and via the radial channels 108 into the input shaft 26. The oil then flows through the axial channel 110 in the Exit route 3ö to the radial outlet channels 112 and to the outside via the clutch and brake plates 34 and 70 and the clutch and brake disks, respectively 66 and 68. Although vanes 36 create sufficient pressure to ensure adequate oil flow, the flow of oil over the plates and disks is still supported by centrifugal force, which is generated by the rotation of the output shaft 38. Since the input shaft 26 is always continuous rotates when the clutch brake unit is in operation, represents the arrangement of those located on it Impeller vanes ensure that the clutch plates and discs have an adequate oil supply at all times obtained even when the output shaft is just starting to rotate, with a large amount of heat is produced.

When the input shaft 26 has started to rotate

with

and when the impeller blades arranged on it / the circulation of the oil has started, as described above, can actuate the piston unit 83 and thereby a simultaneous axial movement of the brake actuation element 78 and the clutch actuation element 76 in FIG. 1

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to the right. This movement causes the brake plates 70 and the brake friction disks 68, the have previously prevented rotation of the output shaft 38, released. Another movement then causes that the clutch plates 34 and clutch friction plates 66 come together between the sides of the clutch B actuator 76 and the ring 60 move into a torque transmitting state. The exit wave 38 begins to rotate as the slip between the clutch plates 34 and the discs 66 decreases. When the input shaft 26 rotates continuously at full or near full speed, it becomes continuous Oil distribution ensured through the channels 112 between each of the clutch plates and disks and achieved in that these are both lubricated and cooled. To the clutch brake unit the above process only needs to be reversed, with the piston unit 83 being put out of operation an axial movement of the actuating elements 76 and 78 to the left in Figure 1 causes a release of the Clutch plates and discs 34 and 66 and a contraction of the brake plates 70 and discs 68 has the consequence to achieve a braking torque for the output shaft. When the input shaft 26 with rotates at full speed, an adequate supply of oil is directed through the brake plates 70 and discs 68 to to cool and lubricate them during the entire braking process.

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Claims (1)

Pa »entaiAalts DIdI Ina. π. Hauck G.M. SUMMER COMPANY, Inc. Diol Phys W Schmitz 26233 Groesbeck Highway, £ _,, _{ng E.} Graalfs Warren, Michigan 48Ο89 _Dipl | _ng . w. Wehnert U.S.A. OQ // nnQ Dipl. Phy ». W. Carstens Zo HH U Uo Dr.-Ing. W. Döring ^M " ⁵⁰⁷² Mozartstrasse 23 ROOO Munich 2 October 24, 1979 Claims 1. Clutch brake unit, characterized by a housing which has a central cavity between opposite, limited longitudinally spaced end walls, an input shaft extending into the Cavity extending through one of the end walls, an output shaft extending through the other end wall, one Series of radially arranged clutch plates mounted in the cavity for rotation with the input shaft are, first and second rows of radially disposed, axially spaced friction plates contained in the cavity mounted for rotation with the output shaft, a series of radially arranged brake plates, which are in the Cavity are non-rotatably mounted and can be actuated to cooperate with the second row of friction plates and thereby braking the rotation of the output shaft, the clutch plates and the First row of friction plates can be actuated to move between the input shaft and the output shaft To transmit rotational energy, and with on the input shaft mounted oil pumping devices that deliver oil via the / 2 030032/0512 Can circulate clutch plates, the first and second rows of friction plates and the brake plates, to cool them depending on the rotation of the input shaft. 2. clutch brake unit according to claim 1, characterized in that that the housing is provided with an oil channel in order to direct the oil from the pumping devices, and that the input shaft is provided with oil passages which are in fluid communication with the housing oil passage stand to bring oil to the clutch plates and the first and second rows of the friction plates and brake plates to direct. 3. clutch brake unit according to claim 2, characterized in that the output shaft has an axially extending Has channel which is in fluid communication with the oil channels of the input shaft, and that one A plurality of channels extending in the radial direction form the connection between the axial channel and the tteibplatten manufactures. 4. clutch brake unit according to claim 3 »characterized in that the radial oil channels of the output shaft are arranged in circumferentially spaced groups, each group zigzag in the axial direction is staggered to align two / 3 030032/0512 β -3 - to avoid any channels in the circumferential direction. 5. clutch brake unit according to claim 4, characterized in that the plurality of each in the radial direction extending channels is spaced apart in the axial direction and in the circumferential direction. 6. clutch brake unit according to claim 1, characterized in that the oil pumping devices have a plurality of include circumferentially spaced wings that are arranged on the input shaft and which are in close g Rotate the vicinity of the side walls of the housing and can cooperate with them to pump the oil by centrifugal action. 7. clutch brake unit according to claim 6, characterized in that each wing partially through radially outside diverging side walls is formed. 8. clutch brake unit according to claim 7, characterized in that that the input shaft is provided with a plurality of drive noses projecting in the axial direction and that the wings
is / are elongated in the axial direction and protrude radially outward from the drive lugs. 030032/0512 29Ü008 9. clutch brake unit according to claim 8, characterized in that that the drive lugs and vanes from an annular Flanechabechnitt of the input shaft axially protrude outwards. 10. clutch brake unit according to claim 9 »characterized in that that the drive lugs and wings are formed in one piece with the input shaft. 11. clutch brake unit characterized by a housing between opposite, spaced in the longitudinal direction End walls delimiting a central cavity and an oil reservoir in a lower section thereof, an input shaft extending into the cavity and rotatably supported in one of the end walls is a series of clutch plates mounted on the input shaft within the cavity and together with this can rotate a series of brake plates which cannot rotate within the cavity are mounted and spaced from the clutch plates, an output shaft that is coaxial is arranged to the input shaft, extends into the cavity and is rotatable in the other end wall is mounted, first and second rows of friction plates spaced apart in the axial direction are mounted on the output shaft, the first / 5 030032/0512 2 9 Z- A ~ 0 O δ Series of flats can interact with the clutch plates when actuated to generate rotational energy from the input shaft to the output shaft, and being the second row of plates can cooperate with the brake plates when they have been actuated to the rotational movement of the To brake output shaft, actuators for selectively actuating a number of the first and second row of friction plates, a pumping chamber in the housing, oil pumping devices attached to the input shaft are provided and capable of pumping oil from the reservoir into the pumping chamber, and oil channel devices, to get oil from the pumping chamber via the first and second rows of friction plates, the clutch plates and the Guide brake plates. 12. clutch brake unit according to claim 11, characterized in that that the oil pumping means comprise at least one wing provided on the input shaft is and can rotate together with this in order to transfer oil from the reservoir into the pumping chamber. 13 · Clutch brake unit according to claim 12, characterized in that that a drive lug is provided on the output shaft, and that the wing in the radial direction protrudes from the drive nose. 030032/0512 29U "008 14. clutch brake unit according to claim 13, characterized in that that the wing protrudes outward in the radial direction from the nose and partly through in the circumferential direction spaced, diverging side walls is limited. 15 · Clutch brake unit according to claim 11, characterized in that that the oil pumping means comprise a plurality of circumferentially spaced vanes which are provided on the input shaft and rotate in close proximity to the side walls of the housing and with these together we'-aii can in order to by centrifugal action to pump the oil. 16. Clutch brake unit according to claim 15, characterized in that that the pumping chamber has an inlet opening through the side wall. 17. Clutch brake unit according to claim 11, characterized in that that the oil channel devices have an axially extending channel in the output shaft and a plurality of radially extending channels between the axial channel and connect the friction plates. / 7 030032/0512 18. clutch brake unit according to claim 17 »characterized in that the plurality of themselves in the radial direction extending channels in the axial direction and in the circumferential direction is spaced from each other. 19 · Clutch brake unit according to claim 17 »characterized in that the input shaft is provided with oil ducts is to direct the oil from the housing to the axially extending channel. 20. Clutch brake unit according to claim 19, characterized in that the housing contains a first oil channel for the oil from the pump chamber in the input shaft through the housing, and a second channel, to get the oil from an outside source to the input shaft to direct. 21. Clutch brake unit according to claim 20, characterized in that a selected channel is blocked. 22. Clutch brake unit according to claim 20, characterized in that the pumping chamber is provided with an opening to lead oil to the external source. 23. Clutch brake unit according to claim 22, characterized in that the external source is an oil cooler. /8th 030032/0512 24. Clutch brake unit according to claim 19, characterized in that that the oil passages of the input shaft a plurality of circumferentially spaced apart in Radially extending channels include. 25. clutch brake unit according to claim 18, characterized in that that the radial oil channels of the output shaft are arranged in circumferentially spaced groups with each group zigzag staggered axially to align two to avoid any channels in the circumferential direction. 26. Clutch brake unit according to claim 25, characterized in that that the groups are axially aligned with the first and second rows of friction plates are so that they have a continuous Öletrom over this depending on the rotation of the input shaft can lead. 27. Clutch brake unit according to claim 11, characterized in that that the oil pumping devices comprise a high volume centrifugal pump. 28. Clutch brake unit according to claim 27, characterized in that that the central cavity has a generally cylindrically shaped ab- / 9 030032/0512 cut with a predetermined diameter that on the input shaft a plurality of circumferentially spaced drive lugs is provided and that of each drive lug at least one impeller blade protrudes radially outward, the impeller blades inside of the cylindrical section circumscribe a circle during the rotation of the input shaft, the diameter of which is only slightly smaller than the specified diameter. 29 Clutch brake unit according to Claim 28, characterized in that that the input shaft has four lugs and that the clutch plates are mounted on the lugs and protrude radially inward therefrom. 30. Clutch brake unit, characterized by a housing which ^{delimits a * 1} central cylindrical cavity and an oil reservoir between opposite, longitudinally spaced end walls, an input shaft which extends into the cavity and is rotatably supported in one of the end walls and on which an annular one An enlarged diameter splash portion is provided, a plurality of circumferentially spaced drive lugs axially protruding from the annular flange portion, a plurality of oil pump impeller blades extending in the axial direction 030032/0512 2 "9 ¹ UOOS projecting outwardly from the flange portion and radially from the drive lugs, each Wing is limited in part by radially outwardly diverging side walls, a series of clutch plates that are mounted on the drive lugs and can rotate together with the input shaft, an output shaft arranged coaxially with the input shaft, which extends into the cavity and is rotatably mounted in the other end wall, wherein the output shaft has an end portion which is connected to a portion of the ^ input shaft and a axially extending oil passage opening out from the end portion is matched, a row of brake plates which are non-rotatably mounted in the cavity, first and second rows of friction plates, which are mounted axially spaced apart on the output shaft, wherein the first row of plates can cooperate with the clutch plates when actuated to generate rotational energy from the input shaft to the output shaft, and the second row of plates with the Brake plates can interact, when actuated, to increase the rotational movement of the output shaft to brake, actuating devices for the optional actuation of a friction plate from the first and second row of friction plates, a pumping chamber in d the housing, which is located in the cylindrical cavity / 11 030032/0512 29U008 opens, and oil channel devices in the housing, wherein the impeller blades rotate in close proximity to the cylindrical cavity portion of the housing and oil from the reservoir through the pump chamber, the Ölkanaleinri chtungen, the axial channel, the radial channels and across the clutch plates, the brake plates, and the first and second rows of friction plates in dependence pump from the rotation of the input shaft. / 12 030032/0512