CA1215659A - Variable speed drive unit - Google Patents
Variable speed drive unitInfo
- Publication number
- CA1215659A CA1215659A CA000417010A CA417010A CA1215659A CA 1215659 A CA1215659 A CA 1215659A CA 000417010 A CA000417010 A CA 000417010A CA 417010 A CA417010 A CA 417010A CA 1215659 A CA1215659 A CA 1215659A
- Authority
- CA
- Canada
- Prior art keywords
- fluid
- unit
- plates
- shafts
- accordance
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/14—Fluid pressure control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D48/04—Control by fluid pressure providing power assistance
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0209—Control by fluid pressure characterised by fluid valves having control pistons, e.g. spools
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
A variable speed drive unit having a clutch disc stack including input and output shafts, a first series of drive plates located in a fluid reservoir and supported for rotation by a rotatable housing of the unit rotated by one of said shafts, a second series of driven discs interleaved with the drive plates and supported for rotation with the other of said shafts, a piston slideably movable in a piston chamber located at one end of the interleaved plates and discs and adapted to compressively engage the interleaved plates and discs, and a control for the piston providing a gradually increasing rated profile without the need for electronic back-up or extraneous controls. The control includes a two position input flow control and a fixed output flow control, which output control can be selectively varied between operations of the unit to provide alternate rate profiles for engagement and disengagement of the input and output shafts of the unit.
A variable speed drive unit having a clutch disc stack including input and output shafts, a first series of drive plates located in a fluid reservoir and supported for rotation by a rotatable housing of the unit rotated by one of said shafts, a second series of driven discs interleaved with the drive plates and supported for rotation with the other of said shafts, a piston slideably movable in a piston chamber located at one end of the interleaved plates and discs and adapted to compressively engage the interleaved plates and discs, and a control for the piston providing a gradually increasing rated profile without the need for electronic back-up or extraneous controls. The control includes a two position input flow control and a fixed output flow control, which output control can be selectively varied between operations of the unit to provide alternate rate profiles for engagement and disengagement of the input and output shafts of the unit.
Description
(I S6S9 1 .
VARIABLE SPEED DRIVE UNIT
BACKGROUND AN SEYMOUR OF THE INVENTION
The present invention relates Jo a variable speed drive unit and more particularly to a variable speed drive having a box type clutch for conveyor drives or the like having input and output shafts, a clutch disc stack including a first series of drive plates located in a fluid reservoir and supported for rotation by a rotatable housing rotated by one of the shafts and a second series of driven discs interleaved with the drive plates and supported for rotation with the other of the shafts, and a piston actuator slide ably located at one end of the clutch disc stack and adapted to compressively engage the clutch disc stack.
Conventional variable speed drive units have a small clutch, a stepping motor, and a control panel it controlling the stepping motor, the motor and control panel comprising approximately 75 per cent of the cost of the unit;. The present invention has the object of providing a variable speed drive unit which needs no back-up such as a costly stepping motor and control unit. Another object is to provide such à unit which provides a variable speed drive unit having a self-controlling drive profile without the need for electronic back-up or extraneous controls.
A further object is to provide this drive profile as ramp or having a gradually increasing rate profile.
Universality in use as a drive unit in various types of applications and simplicity in operation make a drive unit much more valuable in the art than a unit having If . .
.
.
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only one specific application. Thus, it is yet another object of the present invention to provide the above objects in a universal and relatively simple to operate construction.
The present invention resides in an improved variable speed drive unit including an external housing, input and output shafts, a fluid reservoir, a rotatable housing secured to one of the shafts, clutch disc stack means including a first series of plates located in the fluid reservoir and supported for rotation by the rotatable housing and a second series of discs interleaved with the plates and supported for rotation with the other of the shafts. In the present invention, there is provided means for engaging the plates and discs which includes control means having input means with a first position providing fluid flow to the engaging means and a second position providing no fluid flow to the engaging means.
Output means is provided which has a fixed discharge flow rate during operation of the unit with means for varying the fixed discharge flow rates between operations of the unit.
Other objects and advantages of the instant invention will be apparent in the following specification, claims and drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
Figure 1 is a half cross sectional view of a variable speed drive unit embodying the principles of the present invention;
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lZ~56S9 Figure 2 is a side elevation Al view of the variable speed drive unit of Figure l;
Figure 3 is an end elevation Al view of the variable speed drive unit of figure 2 in the direction 3-3; and Figure 4 is a schematic diagram illustrating the oil flow into and out of the variable speed drive unit of the present invention, including a pump and a heat exchanger.
DESCRIPTION OF THE PREFERRED EMBODI~N~
With reference now to Figures 2 and 3 of the drawings and in accordance with a preferred embodiment of the subject invention, a variable speed drive unit is indicated generally at 10, having a drive shaft 12 capable of being mounted to a constant speed drive means (not shown) such as an electric motor or the like and having a driven shaft 14 mountable to an associated machine (not shown). The associated machine by way of example, can include such devices as extrudes, conveyors, pumps, fans, mixers, or any other driven machine that utilizes variable speed. As shall hereinafter become apparent, the variable speed drive unit 10 is adapted to selectively convert the constant rotary motion of the motor drive shaft 12 to a reduced variable speed range for the driven shaft 14 to suit the individual requirements thereof. Connector means between the shafts 12 and 14 and the components selected to be attached thereto are known in thwart and will not be discussed herein. " , S65S~ -) A main housing 16 completely encloses the rotate able clutch assembly 18 (Figure 1). The input 12 and output 14 shafts are rotatable supported within the main housing 16 by an interrelated bearing support system lo supporting four bearings 20~ 229 24, and 26 around the shafts 12 and 14. Two bearings 20 and 22 are associated with the input shaft 12 and two bearings 24 and 26 support the output shaft, bearing 22 actually extending between the shaft 12 and 14 as will be described later.
Two rotatable housing structures 28 and 30 extend radially from the shafts 12 and 14, respectively, within the main housing 16. The input shaft housing 28 is comprised of two radially extending end walls 32 and 34 axially spaced from one another and interconnected at the radially outer extremes thereof by a two piece annular skirt section 36 comprising, in cross Saxon first L-shaped member 38 bolted to end wall 32 at circumferential spaced intervals by bolts 40 and a second member 42 spaced radially and axially from first member 38 and fixedly secured to both first member 38 by circumferential spaced bolts 44 and end wall 34 by circumferential spaced set screws 46. A porting annuls 48 is fixedly secured by circumferential spaced bolts 50 to the main housing 16 around the output shaft 14. The annuls 48 has a radially extending flange 52 which mates with end wall 34 to form a labyrinth seal 54 and close off the interior of the main housing into two chambers, a working chamber 56 and a reservoir chamber 58.
The porting annuls 48 also has means forming the portion of-the bearing support system 18 supporting bearings 24 and I , I
_ ,, .
15~59 26 around the output shaft 14. The input shaft 12 is directly supported by the main housing 16 via bearing 20 held in place by sealed bearing assembly 60 including an annular seal 62 and two O-ring seals 64 and 66.
The output shaft housing 30 is comprised of an annular radially extending flange portion 68 and a C-shaped annular skirt portion 70 extending axially and radially outwardly from the flange portion 68. Output shaft housing , 30 is disposed entirely within the working chamber 56.
The radially inner, axially extending flange 72 ox the housing 30 also comprises a portion of the bearing support system 18 for bearing 22 as referred to above. The input shaft 12 has an annular axially extending flange 74 at one axial extreme whereof upon which bearing 22 is disposed and held in place by snap ring inn groove 78. In this manner, the output shaft 14 through flange 72 is used to support the input shaft 12 in an interrelated fashion through bearing 22.
The outer periphery of the annular C-shaped section 70 of the output housing 30 and the inner periphery of the annular L-shaped member 38 of input housing 2~9 each have axially extending splints 80 and 82 respectively at circumferential spaced intervals. The splints 80 of housing 30 are adapted to slide ably receive a series of internally bored clutch drive plates 84. The plates 84 are each provided with a plurality of circumferential spaced, radially inwardly extending notches adapted or splinted engagement with the plurality of splints 80.
~imilarly9 a series of friction discs 86 are interleaved ( ) lZ~5~i5~ 3 with each of the drive plates 84 and carried by the splints 82 formed on the inner periphery of member 38 of input housing 28. Retainer means comprising annular retainer members 88 and 90 and bolts 92 disposed at circumferential spaced locations thereof loosely retain the interleaved disposition of the plates 84 and the discs 86 and retain the plates 84 on the output housing 30 throughout the .
operation of the unit 10.
End wall 34, member 42, flange 52, and the radially outer surface 94 of the portion of the porting annuls 48 extending into the working chamber 56 form a sub chamber I in which an annular piston 98 moves axially between the surface 100 formed by the end wall 34 and flange 52 and a radially inwardly extending abutment flange 102 extending from member 42. The piston I has an annular driving piston head 104 which when actuated by increased oil pressure in sub chamber 96 is forced against the plates 84 and discs I
. The oil pressure of sub chamber 96 which controls the movement of the piston head 104 is determined by a mull tiplicity of orifice plugs 106 circumferential and radially spaced at positions about the end wall 34. The number of plugs is determined in accordance with the given torque transmitting capacity of the unit 10. Each plug 106 comprises a threaded body portion 108 thread able into a bore 110 in the end wall 34. The body portion 108 of each plug 106 includes an Orifice 112 through which oil can pass from sub chamber I to the reservoir chamber So.
I;
, The plugs 106 can be arranged and rearranged between orifice and non-orificed plugs by removal of the cover plate 113 (Figures 2 end I for ready access to the plugs.
It should be noted that the housing wall 16 is designed to be near enough to end wall 34 not to allow any plugs to fall into the machine when they are thread ably disengaged In the present invention, a hydraulic fluid media is directed across the radial abutting surfaces of each of the drive plates 84 and friction discs 86 to main-lain a positive oil film on each of the plates 84 and discs 86 which is subject to be viscously sheared whereby a con-trolled slippage, and a correspondingly reduced rotary motion to the output shaft 14 can be achieved by controlling the loading of the pressure between adjacent plates 84 and 86 as applied by the head portion 104 of the piston 98. The control of the movement of the piston I in the present invention is controlled completely within the system, as shall hereinafter be described, with no electronic input or control of any kind as previously utilized by prior art units.
As best illustrated in Figures 2 and 3, a centrifugal pump ll4 is fixedly secured to the main housing 16 having an inlet port 116 below the oil level in the outer chamber 58 of the unit. The pump 114 is preferably of the centrifugal dual intake type as manufactured by ..... ..
1` ~2~56S9 Rut man Mfg. Co. and identified as a "Gusher" Pump, Model ,' No. 11022-E, having two horsepower at 3460 rum (230/460 volts, three phase, with impeller #2292~3). The pump output 118 is directed, as illustrated schematically by Figure 4, into an ancillary heat exchanger 120 via conduit 122 through a pressure limit switch 124. A bypass conduit 126 is also included in order to use a smaller heat exchanger without having a prohibitive pressure drop. A pressure gauge 128 is included in the system to monitor the pressure drop through the heat exchanger 120 (22H, 1/2 hop., 170 rum to apprise the operator that sufficient operating pressure exists in the oil line 130 beyond the heat exchanger 120 as the line enters the drive unit 10. In the preferred embodiment, the pump 114 pumps 35 gym at approximately 32 pi (at which the limit switch 116 is set) into the heat exchanger 120. The bypass flow around the heat exchanger 120 through the bypass conduit 126 is approximately 11 gym as set by a 13J32 orifice 132. The oil is at an approximate pressure of 25 pi in the line 130 entering the drive unit lo a pressure drop of only 7 pi across I the heat exchanger 120.
A heater lo ow, 480 volts 134 is also mounted on the opposite side of the housing 16 from the pump 114 with its heating element 136 disposed in the oil reservoir 138 of the main chamber 58. The mount 140 for the heater 25 . 134 is identical Jo the mount 142 for the inlet port 116 of the pump 114 so that the pump 114 and heater 134 may be interchanged as space considerations externally around the unit permit or as otherwise desired. A cross wiring conduit 144 is disposed through the housing 16 to add to ;
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the ease of interchangeability of the pump ill and heater 134 and provide the option of presenting the power wires to the unit lo only from one side of the unit without exterior crossover.
In the subject invention, high limit 146 and low limit 148 temperature switches are included to control the heater 134. The housing 16, as illustrated in Figure 2, also includes an oil level sight 150, a covered quick connect stem oil fill 152, an oil drain 154, and a cooling oil over temperature switch 156~ as shown.
Oil from conduit 130 enters the drive unit 10 and breaks off in one direction to inlet port 158 of the porting annuls 48 figures 1 and 3). Referring now to Figure 3, the porting annuls 48 is utilized to convey hydraulic fluid from the inlet port 158 into the worlcing chamber 56 and to the bearings 20, 22, 24, and 26 via the output shaft 14 and the input shaft 12. The inlet passage-way 16D so the porting annuls 48 directs hydraulic fluid to two positions. The passageway 160 directly feeds Orifice 162 into working chamber 56 to supply oil to the discs By and plates 86 and also to bearing 24. Passageway . 160 also feeds into the output shaft lubricating system 164 via radial passageway 166 to lubricate bearings 26 and 22, and via input shift lubricating system 168, bearing 20.
Alternatively, the inlet port 158 may be bored axially through the input shaft 12 and communicate with the working chamfer 56 radially outwardly of the discs via a passageway (no shown) that would be formed in end wall 32 30 and member 38 . _ 6'~9 ) .
-- Conduit 130 also breaks off in a second direction to supply oil to the piston sub chamber 96.
Conduit 130 branches into conduit 170 which feeds oil through a 15 micron filter 172 to conduit 174 which communicates with a four-way single acting spring return solenoid valve 176. The valve 176 is the primary control for the operation of the unit 10. The four positions of the valve 176 are conduits 174, 178, and 180, and a plug 182. Conduit 178 communicates with orifice 184 and inlet port 186 in the porting annuls 48 to weed oil to the piston sub chamber 96 via passageway 188. Conduit 180 communicates as a drain to return oil to the reservoir chamber 58.
When the valve 176 is in the at rest position illustrated by Figure 4, oil passes through the filter 172 and is returned directly to the reservoir 5&. After the valve 176 is activated to the operating position (not shown), conduit 174 communicates with conduit 178, which in turn feeds oil under pressure to sub chamber 96. This oil forces the piston 98 toward the plates I and discs 86 Jo engage the drive shaft 12 to driven shaft 14 and drive the machine associated with driven shaft 14. The oil in sub chamber 96 is also bleeding through the orifices 112 back into the reservoir 58 at a selected rate such that the engagement of the shafts lo and 14 occurs as a swamp or gradually increasing rate profile until a steady state is attained in sub chamber 96 between the flow rates in and out.
Return of the valve 176 to the at rest position (as shown) stops the flow into sub chamber 96 while oil continues to bleed through the orifices 112. The oil pressure in working chamber 56 forces the piston 93 out of ` I 3 5~S9 engagement with the plates 84 and discs 86~ gain at a gradual rate OX ramp rate, until the shafts are once again disengaged as the plates 84 and discs 86 become further spaced apart An additional feature of the present invention is the maintenance of a positive pressure (above atmospheric in the oil system. this positive pressure is accomplished by injecting pressurized air above atmospheric) into the oil system through the oil reservoir 58 via air inlets 190, 10 191, and 192 (inlet 191 is out of position in Figure 1 for - purposes of clarity; see Figures 2 and 3 for proper location).
The pressurized air communicates with various parts of the oil system. Referring to Figure 1, air from inlet 191 enters the oil reservoir 58 directly via passageway 194 is and also positively pressures the oil system at bearing 26 via passageway 196. The pressure at bearing 26 at the portions of the oil system communicating with bearing 26 is further maintained by utilizing an O-ring seal 198 at the housing-bearing interface adjacent the bearing 26. Air 20 from inlet 192 enters the oil system in an identical manner.
Pressurized air also enters the oil system from air inlet 190 via passageway 200 directly into the oil reservoir I and via passageway 202 to the bearing 20 to positively pressurize the oil system at bearing 20 and I the portions of the oil system communicating with the bearing 20. Again an O-ring seal 204 is used to further maintain pressure in the oil system.
A pressurized oil system is particularly advantageous in the present invention where oil controls 30 the piston, lubricates 811 the moving parts and also engages '' the plates and the discs by a shearing action. With a , ., .
1 1 r _ _ issue positive pressure in the oil system, the status of the unit (hot or cold) will not become as critical to the performance of the unit as it the past. Breathers 206 are also included which along with the seals 198 and 204 will release air from the oil system as the pressure rises above a desired level during the operation of the unit 10.
Thus there is disclosed in the above description and in the drawings an improved variable speed drive unit . which fully and effectively accomplishes the objectives of the present invention. However, it will be apparent that variations and modifications of the disclosed embodiments may be made without departing from the principle of the invention or the scope of the appended claims.
~12-
VARIABLE SPEED DRIVE UNIT
BACKGROUND AN SEYMOUR OF THE INVENTION
The present invention relates Jo a variable speed drive unit and more particularly to a variable speed drive having a box type clutch for conveyor drives or the like having input and output shafts, a clutch disc stack including a first series of drive plates located in a fluid reservoir and supported for rotation by a rotatable housing rotated by one of the shafts and a second series of driven discs interleaved with the drive plates and supported for rotation with the other of the shafts, and a piston actuator slide ably located at one end of the clutch disc stack and adapted to compressively engage the clutch disc stack.
Conventional variable speed drive units have a small clutch, a stepping motor, and a control panel it controlling the stepping motor, the motor and control panel comprising approximately 75 per cent of the cost of the unit;. The present invention has the object of providing a variable speed drive unit which needs no back-up such as a costly stepping motor and control unit. Another object is to provide such à unit which provides a variable speed drive unit having a self-controlling drive profile without the need for electronic back-up or extraneous controls.
A further object is to provide this drive profile as ramp or having a gradually increasing rate profile.
Universality in use as a drive unit in various types of applications and simplicity in operation make a drive unit much more valuable in the art than a unit having If . .
.
.
i55~
only one specific application. Thus, it is yet another object of the present invention to provide the above objects in a universal and relatively simple to operate construction.
The present invention resides in an improved variable speed drive unit including an external housing, input and output shafts, a fluid reservoir, a rotatable housing secured to one of the shafts, clutch disc stack means including a first series of plates located in the fluid reservoir and supported for rotation by the rotatable housing and a second series of discs interleaved with the plates and supported for rotation with the other of the shafts. In the present invention, there is provided means for engaging the plates and discs which includes control means having input means with a first position providing fluid flow to the engaging means and a second position providing no fluid flow to the engaging means.
Output means is provided which has a fixed discharge flow rate during operation of the unit with means for varying the fixed discharge flow rates between operations of the unit.
Other objects and advantages of the instant invention will be apparent in the following specification, claims and drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
Figure 1 is a half cross sectional view of a variable speed drive unit embodying the principles of the present invention;
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lZ~56S9 Figure 2 is a side elevation Al view of the variable speed drive unit of Figure l;
Figure 3 is an end elevation Al view of the variable speed drive unit of figure 2 in the direction 3-3; and Figure 4 is a schematic diagram illustrating the oil flow into and out of the variable speed drive unit of the present invention, including a pump and a heat exchanger.
DESCRIPTION OF THE PREFERRED EMBODI~N~
With reference now to Figures 2 and 3 of the drawings and in accordance with a preferred embodiment of the subject invention, a variable speed drive unit is indicated generally at 10, having a drive shaft 12 capable of being mounted to a constant speed drive means (not shown) such as an electric motor or the like and having a driven shaft 14 mountable to an associated machine (not shown). The associated machine by way of example, can include such devices as extrudes, conveyors, pumps, fans, mixers, or any other driven machine that utilizes variable speed. As shall hereinafter become apparent, the variable speed drive unit 10 is adapted to selectively convert the constant rotary motion of the motor drive shaft 12 to a reduced variable speed range for the driven shaft 14 to suit the individual requirements thereof. Connector means between the shafts 12 and 14 and the components selected to be attached thereto are known in thwart and will not be discussed herein. " , S65S~ -) A main housing 16 completely encloses the rotate able clutch assembly 18 (Figure 1). The input 12 and output 14 shafts are rotatable supported within the main housing 16 by an interrelated bearing support system lo supporting four bearings 20~ 229 24, and 26 around the shafts 12 and 14. Two bearings 20 and 22 are associated with the input shaft 12 and two bearings 24 and 26 support the output shaft, bearing 22 actually extending between the shaft 12 and 14 as will be described later.
Two rotatable housing structures 28 and 30 extend radially from the shafts 12 and 14, respectively, within the main housing 16. The input shaft housing 28 is comprised of two radially extending end walls 32 and 34 axially spaced from one another and interconnected at the radially outer extremes thereof by a two piece annular skirt section 36 comprising, in cross Saxon first L-shaped member 38 bolted to end wall 32 at circumferential spaced intervals by bolts 40 and a second member 42 spaced radially and axially from first member 38 and fixedly secured to both first member 38 by circumferential spaced bolts 44 and end wall 34 by circumferential spaced set screws 46. A porting annuls 48 is fixedly secured by circumferential spaced bolts 50 to the main housing 16 around the output shaft 14. The annuls 48 has a radially extending flange 52 which mates with end wall 34 to form a labyrinth seal 54 and close off the interior of the main housing into two chambers, a working chamber 56 and a reservoir chamber 58.
The porting annuls 48 also has means forming the portion of-the bearing support system 18 supporting bearings 24 and I , I
_ ,, .
15~59 26 around the output shaft 14. The input shaft 12 is directly supported by the main housing 16 via bearing 20 held in place by sealed bearing assembly 60 including an annular seal 62 and two O-ring seals 64 and 66.
The output shaft housing 30 is comprised of an annular radially extending flange portion 68 and a C-shaped annular skirt portion 70 extending axially and radially outwardly from the flange portion 68. Output shaft housing , 30 is disposed entirely within the working chamber 56.
The radially inner, axially extending flange 72 ox the housing 30 also comprises a portion of the bearing support system 18 for bearing 22 as referred to above. The input shaft 12 has an annular axially extending flange 74 at one axial extreme whereof upon which bearing 22 is disposed and held in place by snap ring inn groove 78. In this manner, the output shaft 14 through flange 72 is used to support the input shaft 12 in an interrelated fashion through bearing 22.
The outer periphery of the annular C-shaped section 70 of the output housing 30 and the inner periphery of the annular L-shaped member 38 of input housing 2~9 each have axially extending splints 80 and 82 respectively at circumferential spaced intervals. The splints 80 of housing 30 are adapted to slide ably receive a series of internally bored clutch drive plates 84. The plates 84 are each provided with a plurality of circumferential spaced, radially inwardly extending notches adapted or splinted engagement with the plurality of splints 80.
~imilarly9 a series of friction discs 86 are interleaved ( ) lZ~5~i5~ 3 with each of the drive plates 84 and carried by the splints 82 formed on the inner periphery of member 38 of input housing 28. Retainer means comprising annular retainer members 88 and 90 and bolts 92 disposed at circumferential spaced locations thereof loosely retain the interleaved disposition of the plates 84 and the discs 86 and retain the plates 84 on the output housing 30 throughout the .
operation of the unit 10.
End wall 34, member 42, flange 52, and the radially outer surface 94 of the portion of the porting annuls 48 extending into the working chamber 56 form a sub chamber I in which an annular piston 98 moves axially between the surface 100 formed by the end wall 34 and flange 52 and a radially inwardly extending abutment flange 102 extending from member 42. The piston I has an annular driving piston head 104 which when actuated by increased oil pressure in sub chamber 96 is forced against the plates 84 and discs I
. The oil pressure of sub chamber 96 which controls the movement of the piston head 104 is determined by a mull tiplicity of orifice plugs 106 circumferential and radially spaced at positions about the end wall 34. The number of plugs is determined in accordance with the given torque transmitting capacity of the unit 10. Each plug 106 comprises a threaded body portion 108 thread able into a bore 110 in the end wall 34. The body portion 108 of each plug 106 includes an Orifice 112 through which oil can pass from sub chamber I to the reservoir chamber So.
I;
, The plugs 106 can be arranged and rearranged between orifice and non-orificed plugs by removal of the cover plate 113 (Figures 2 end I for ready access to the plugs.
It should be noted that the housing wall 16 is designed to be near enough to end wall 34 not to allow any plugs to fall into the machine when they are thread ably disengaged In the present invention, a hydraulic fluid media is directed across the radial abutting surfaces of each of the drive plates 84 and friction discs 86 to main-lain a positive oil film on each of the plates 84 and discs 86 which is subject to be viscously sheared whereby a con-trolled slippage, and a correspondingly reduced rotary motion to the output shaft 14 can be achieved by controlling the loading of the pressure between adjacent plates 84 and 86 as applied by the head portion 104 of the piston 98. The control of the movement of the piston I in the present invention is controlled completely within the system, as shall hereinafter be described, with no electronic input or control of any kind as previously utilized by prior art units.
As best illustrated in Figures 2 and 3, a centrifugal pump ll4 is fixedly secured to the main housing 16 having an inlet port 116 below the oil level in the outer chamber 58 of the unit. The pump 114 is preferably of the centrifugal dual intake type as manufactured by ..... ..
1` ~2~56S9 Rut man Mfg. Co. and identified as a "Gusher" Pump, Model ,' No. 11022-E, having two horsepower at 3460 rum (230/460 volts, three phase, with impeller #2292~3). The pump output 118 is directed, as illustrated schematically by Figure 4, into an ancillary heat exchanger 120 via conduit 122 through a pressure limit switch 124. A bypass conduit 126 is also included in order to use a smaller heat exchanger without having a prohibitive pressure drop. A pressure gauge 128 is included in the system to monitor the pressure drop through the heat exchanger 120 (22H, 1/2 hop., 170 rum to apprise the operator that sufficient operating pressure exists in the oil line 130 beyond the heat exchanger 120 as the line enters the drive unit 10. In the preferred embodiment, the pump 114 pumps 35 gym at approximately 32 pi (at which the limit switch 116 is set) into the heat exchanger 120. The bypass flow around the heat exchanger 120 through the bypass conduit 126 is approximately 11 gym as set by a 13J32 orifice 132. The oil is at an approximate pressure of 25 pi in the line 130 entering the drive unit lo a pressure drop of only 7 pi across I the heat exchanger 120.
A heater lo ow, 480 volts 134 is also mounted on the opposite side of the housing 16 from the pump 114 with its heating element 136 disposed in the oil reservoir 138 of the main chamber 58. The mount 140 for the heater 25 . 134 is identical Jo the mount 142 for the inlet port 116 of the pump 114 so that the pump 114 and heater 134 may be interchanged as space considerations externally around the unit permit or as otherwise desired. A cross wiring conduit 144 is disposed through the housing 16 to add to ;
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.
the ease of interchangeability of the pump ill and heater 134 and provide the option of presenting the power wires to the unit lo only from one side of the unit without exterior crossover.
In the subject invention, high limit 146 and low limit 148 temperature switches are included to control the heater 134. The housing 16, as illustrated in Figure 2, also includes an oil level sight 150, a covered quick connect stem oil fill 152, an oil drain 154, and a cooling oil over temperature switch 156~ as shown.
Oil from conduit 130 enters the drive unit 10 and breaks off in one direction to inlet port 158 of the porting annuls 48 figures 1 and 3). Referring now to Figure 3, the porting annuls 48 is utilized to convey hydraulic fluid from the inlet port 158 into the worlcing chamber 56 and to the bearings 20, 22, 24, and 26 via the output shaft 14 and the input shaft 12. The inlet passage-way 16D so the porting annuls 48 directs hydraulic fluid to two positions. The passageway 160 directly feeds Orifice 162 into working chamber 56 to supply oil to the discs By and plates 86 and also to bearing 24. Passageway . 160 also feeds into the output shaft lubricating system 164 via radial passageway 166 to lubricate bearings 26 and 22, and via input shift lubricating system 168, bearing 20.
Alternatively, the inlet port 158 may be bored axially through the input shaft 12 and communicate with the working chamfer 56 radially outwardly of the discs via a passageway (no shown) that would be formed in end wall 32 30 and member 38 . _ 6'~9 ) .
-- Conduit 130 also breaks off in a second direction to supply oil to the piston sub chamber 96.
Conduit 130 branches into conduit 170 which feeds oil through a 15 micron filter 172 to conduit 174 which communicates with a four-way single acting spring return solenoid valve 176. The valve 176 is the primary control for the operation of the unit 10. The four positions of the valve 176 are conduits 174, 178, and 180, and a plug 182. Conduit 178 communicates with orifice 184 and inlet port 186 in the porting annuls 48 to weed oil to the piston sub chamber 96 via passageway 188. Conduit 180 communicates as a drain to return oil to the reservoir chamber 58.
When the valve 176 is in the at rest position illustrated by Figure 4, oil passes through the filter 172 and is returned directly to the reservoir 5&. After the valve 176 is activated to the operating position (not shown), conduit 174 communicates with conduit 178, which in turn feeds oil under pressure to sub chamber 96. This oil forces the piston 98 toward the plates I and discs 86 Jo engage the drive shaft 12 to driven shaft 14 and drive the machine associated with driven shaft 14. The oil in sub chamber 96 is also bleeding through the orifices 112 back into the reservoir 58 at a selected rate such that the engagement of the shafts lo and 14 occurs as a swamp or gradually increasing rate profile until a steady state is attained in sub chamber 96 between the flow rates in and out.
Return of the valve 176 to the at rest position (as shown) stops the flow into sub chamber 96 while oil continues to bleed through the orifices 112. The oil pressure in working chamber 56 forces the piston 93 out of ` I 3 5~S9 engagement with the plates 84 and discs 86~ gain at a gradual rate OX ramp rate, until the shafts are once again disengaged as the plates 84 and discs 86 become further spaced apart An additional feature of the present invention is the maintenance of a positive pressure (above atmospheric in the oil system. this positive pressure is accomplished by injecting pressurized air above atmospheric) into the oil system through the oil reservoir 58 via air inlets 190, 10 191, and 192 (inlet 191 is out of position in Figure 1 for - purposes of clarity; see Figures 2 and 3 for proper location).
The pressurized air communicates with various parts of the oil system. Referring to Figure 1, air from inlet 191 enters the oil reservoir 58 directly via passageway 194 is and also positively pressures the oil system at bearing 26 via passageway 196. The pressure at bearing 26 at the portions of the oil system communicating with bearing 26 is further maintained by utilizing an O-ring seal 198 at the housing-bearing interface adjacent the bearing 26. Air 20 from inlet 192 enters the oil system in an identical manner.
Pressurized air also enters the oil system from air inlet 190 via passageway 200 directly into the oil reservoir I and via passageway 202 to the bearing 20 to positively pressurize the oil system at bearing 20 and I the portions of the oil system communicating with the bearing 20. Again an O-ring seal 204 is used to further maintain pressure in the oil system.
A pressurized oil system is particularly advantageous in the present invention where oil controls 30 the piston, lubricates 811 the moving parts and also engages '' the plates and the discs by a shearing action. With a , ., .
1 1 r _ _ issue positive pressure in the oil system, the status of the unit (hot or cold) will not become as critical to the performance of the unit as it the past. Breathers 206 are also included which along with the seals 198 and 204 will release air from the oil system as the pressure rises above a desired level during the operation of the unit 10.
Thus there is disclosed in the above description and in the drawings an improved variable speed drive unit . which fully and effectively accomplishes the objectives of the present invention. However, it will be apparent that variations and modifications of the disclosed embodiments may be made without departing from the principle of the invention or the scope of the appended claims.
~12-
Claims (17)
1. An improved variable speed drive unit comprising an external housing, input and output shafts, a fluid reservoir, a rotatable housing secured to one of said shafts, clutch disc stack means including a first series of plates located in said fluid reservoir and supported for rotation by said rotatable housing and a second series of discs interleaved with the plates and supported for rotation with the other of said shafts, having the improvement of:
a piston chamber disposed within said external housing;
piston means slideably disposed in said piston chamber at one end of said clutch disc stack means for compressively engaging said plates and discs together;
actuator means for controlling the movement of said piston means comprising:
two position actuator input means having a first position wherein fluid is directed into said piston chamber and a second position wherein fluid is restricted from entering said piston chamber; and actuator output means from said piston chamber, having one selected flow rate during operation of said unit, including means for varying said flow rate between operations of the unit;
wherein said actuator means controls the piston means to actuate the unit in a graduated profile.
a piston chamber disposed within said external housing;
piston means slideably disposed in said piston chamber at one end of said clutch disc stack means for compressively engaging said plates and discs together;
actuator means for controlling the movement of said piston means comprising:
two position actuator input means having a first position wherein fluid is directed into said piston chamber and a second position wherein fluid is restricted from entering said piston chamber; and actuator output means from said piston chamber, having one selected flow rate during operation of said unit, including means for varying said flow rate between operations of the unit;
wherein said actuator means controls the piston means to actuate the unit in a graduated profile.
2. A claim in accordance with claim 1, wherein said piston chamber includes a wall and said means for varying the flow rate of said actuator output means comprises a series of plugs selectively removably disposed in said piston chamber wall.
3. A claim in accordance with claim 2, wherein said plugs are orificed plugs.
4. A claim in accordance with claim 3, wherein said plugs are threadably removable.
5. A claim in accordance with claim 2 wherein said plugs include orificed and non-orificed plugs.
6. A claim in accordance with claim 2, wherein said plugs are circumferentially spaced.
7. A claim in accordance with claim 2, wherein said plugs are axially spaced.
8. A claim in accordance with claim 1, further comprising means for pressurizing said reservoir above atmosphere pressure.
9. A claim in accordance with claim 8, wherein said means for pressurizing said reservoir comprises means for injecting pressurized air into said reservoir.
10. An improved variable speed drive unit comprising an external housing, input and output shafts, a fluid reservoir, a rotatable housing secured to one of said shafts, clutch disc stack means including a first series of plates located in said fluid reservoir and supported for rotation by said rotatable housing and a second series of discs interleaved with the plates and supported for rotation with the other of said shafts, having the improvement of:
means for engaging said plates and discs comprising control means including input means having a first position providing fluid flow to said engaging means and a second position providing no fluid flow to said engaging means and output means having one selected discharge flow rate during operation of said unit, including means for selectively varying said discharge flow rate after the completion of one operation of the unit and before a subsequent operation of the unit.
means for engaging said plates and discs comprising control means including input means having a first position providing fluid flow to said engaging means and a second position providing no fluid flow to said engaging means and output means having one selected discharge flow rate during operation of said unit, including means for selectively varying said discharge flow rate after the completion of one operation of the unit and before a subsequent operation of the unit.
11. An improved variable speed drive unit comprising an external housing, input and output shafts, a fluid reservoir, a rotatable housing secured to one of said shafts, clutch disc stack means including a first series of plates located in said fluid reservoir and supported for rotation by said rotatable housing and a second series of discs interleaved with the plates and supported for rotation with the other of said shafts, having the improvement of:
means for engaging said plates and discs comprising control means including, input means having a first position providing fluid flow to said engaging means and a second position providing no fluid flow to said engaging means;
output means having a fixed discharge flow rate during operation of said unit;
means for varying said fixed discharge flow rates between operations ox said unit.
means for engaging said plates and discs comprising control means including, input means having a first position providing fluid flow to said engaging means and a second position providing no fluid flow to said engaging means;
output means having a fixed discharge flow rate during operation of said unit;
means for varying said fixed discharge flow rates between operations ox said unit.
12. A claim in accordance with claim 11, further comprising means for pumping fluid, heat exchanger means, conduit means connecting said unit, pumping means and heat exchanger means together, and means for partially bypassing the flow through said conduit means around said heat exchanger means to permit a smaller heat exchanger to be used.
13. A claim in accordance with claim 12, further comprising filter means between said heat exchanger and said unit, wherein said pumping means is run constantly and said fluid is filtered through said filter means, even when said input means is disposed in said second position.
14. An improved variable speed drive unit comprising:
an external housing including a fluid reservoir;
input and output shafts;
a rotatable housing secured to one of said shafts;
a fluid working chamber disposed within said rotatable housing;
a first series of plates located within said working chamber and supported for rotation by said rotatable housing;
a second series of discs interleaved with said plates and supported for rotation with the other of said shafts;
a piston chamber disposed within said external housing having a wall extending across one end thereof;
piston means slide ably disposed in said piston chamber at one end of said interleaved plates and discs for compressively engaging said plates and discs together, the other end of said piston means slideably disposed to move toward and away from said chamber wall;
valving means to said piston chamber, including means for controlling the flow of fluid into said piston chamber having a first position wherein fluid flows into said chamber and a second position stopping fluid from entering said chamber;
means for discharging fluid from said piston chamber at a selectively fixed flow rate, including means to vary said flow rate as desired between operations of said unit.
an external housing including a fluid reservoir;
input and output shafts;
a rotatable housing secured to one of said shafts;
a fluid working chamber disposed within said rotatable housing;
a first series of plates located within said working chamber and supported for rotation by said rotatable housing;
a second series of discs interleaved with said plates and supported for rotation with the other of said shafts;
a piston chamber disposed within said external housing having a wall extending across one end thereof;
piston means slide ably disposed in said piston chamber at one end of said interleaved plates and discs for compressively engaging said plates and discs together, the other end of said piston means slideably disposed to move toward and away from said chamber wall;
valving means to said piston chamber, including means for controlling the flow of fluid into said piston chamber having a first position wherein fluid flows into said chamber and a second position stopping fluid from entering said chamber;
means for discharging fluid from said piston chamber at a selectively fixed flow rate, including means to vary said flow rate as desired between operations of said unit.
15. A claim in accordance with claim 14, further comprising means for injecting pressurized air into said fluid reservoir to maintain a pressure above atmosphere therein.
16. A claim in accordance with claim 14, further comprising fluid pumping means bearing means for all rotating parts of the unit, and means for distributing fluid to said bearing means, rotatable housing working chamber, and piston chamber, said distributing means including orifice control means.
17. A claim in accordance with claim 16, wherein said pumping means comprises centrifugal pumping means.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US32771681A | 1981-12-04 | 1981-12-04 | |
| US327,716 | 1981-12-04 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1215659A true CA1215659A (en) | 1986-12-23 |
Family
ID=23277729
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000417010A Expired CA1215659A (en) | 1981-12-04 | 1982-12-03 | Variable speed drive unit |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JPS58149422A (en) |
| CA (1) | CA1215659A (en) |
| DE (1) | DE3243665C2 (en) |
| FR (1) | FR2517774B1 (en) |
| GB (1) | GB2110319B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2913226B1 (en) * | 2007-03-02 | 2009-06-05 | Equip Systemes Et Mecanismes S | TRANSMISSION DEVICE FOR MOTORIZED CHENILLE ENGINE. |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB725571A (en) * | 1952-02-06 | 1955-03-09 | Borg Warner | Improvements in or relating to clutches and clutch assemblies |
| FR1093488A (en) * | 1953-11-03 | 1955-05-05 | Device for rapid disengagement of couplings with multiple friction discs | |
| US3202253A (en) * | 1961-12-04 | 1965-08-24 | Clark Equipment Co | Clutch cooling means |
| US3352395A (en) * | 1966-02-18 | 1967-11-14 | Twin Disc Clutch Co | Friction clutch having centrifugally operated valve means |
| FR1557888A (en) * | 1968-01-05 | 1969-02-21 | ||
| US3647037A (en) * | 1969-05-28 | 1972-03-07 | Nissan Motor | Clutch with centrifugal dump valve |
| US3722645A (en) * | 1971-04-05 | 1973-03-27 | Sommer Co | Clutch unit |
| US4147245A (en) * | 1976-12-16 | 1979-04-03 | Tsentralny Nauchno-Issledovatelsky Avtomobilny I Avtomotorny Institut (Nami) | Hydraulically operated friction clutch |
-
1982
- 1982-11-25 DE DE19823243665 patent/DE3243665C2/en not_active Expired
- 1982-11-30 GB GB08234103A patent/GB2110319B/en not_active Expired
- 1982-12-01 FR FR8220151A patent/FR2517774B1/en not_active Expired
- 1982-12-03 CA CA000417010A patent/CA1215659A/en not_active Expired
- 1982-12-03 JP JP57212593A patent/JPS58149422A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| GB2110319A (en) | 1983-06-15 |
| JPS58149422A (en) | 1983-09-05 |
| GB2110319B (en) | 1985-10-02 |
| FR2517774B1 (en) | 1988-07-08 |
| DE3243665A1 (en) | 1983-06-09 |
| DE3243665C2 (en) | 1985-11-28 |
| FR2517774A1 (en) | 1983-06-10 |
| JPS6233455B2 (en) | 1987-07-21 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |