US20120093672A1 - Direct control linear variable displacement vane pump - Google Patents
Direct control linear variable displacement vane pump Download PDFInfo
- Publication number
- US20120093672A1 US20120093672A1 US13/254,207 US201013254207A US2012093672A1 US 20120093672 A1 US20120093672 A1 US 20120093672A1 US 201013254207 A US201013254207 A US 201013254207A US 2012093672 A1 US2012093672 A1 US 2012093672A1
- Authority
- US
- United States
- Prior art keywords
- slide
- pump
- pumping system
- fluid pumping
- actuator shaft
- 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.)
- Abandoned
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
- F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
- F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
- F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/16—Controlling lubricant pressure or quantity
-
- 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
- F16N—LUBRICATING
- F16N13/00—Lubricating-pumps
- F16N13/20—Rotary pumps
-
- 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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
- F16H57/0436—Pumps
Definitions
- the present disclosure relates to a fluid pumping system for an automobile. More specifically, the present disclosure relates to a variable displacement vane pump and control system for providing a continuously variable output flow independent of the operating speed of the pump.
- Mechanical systems such as internal combustion engines and automatic transmissions, typically include a lubrication pump to provide lubricating oil, under pressure, to many of the moving components and/or subsystems of the mechanical systems.
- the lubrication pump is driven by a rotating component of the mechanical system.
- the operating speed and output of the pump varies with the operating speed of the mechanical system.
- the lubrication requirements of the mechanical system typically do not directly correspond to the operating speed of the mechanical system.
- Previously known fixed displacement lubricating pumps were generally designed to provide sufficient flow at a relatively low speed corresponding to an engine idle speed and a maximum operating lubricant temperature. This design philosophy resulted in an oversupply of lubricating oil during a large portion of vehicle operation.
- a pressure relief valve was provided to return the surplus lubricating oil back into the pump inlet or oil sump to avoid over pressure conditions in the mechanical system.
- the overproduction of pressurized lubricating oil may be 500% of the mechanical system's needs. The result is a significant amount of energy being used to pressurize the lubricating oil which is subsequently exhausted through the relief valve.
- variable displacement vane pumps have been employed as lubrication oil pumps.
- Such pumps generally include a control ring, or other mechanism, which can be operated to alter the volumetric displacement of the pump and thus its output at an operating speed.
- a feedback mechanism is supplied with pressurized lubricating oil from the output of the pump to alter the displacement of the pump to avoid over pressure situations in the engine throughout the expected range of operating conditions of the mechanical system.
- variable displacement pumps provide some improvements in energy efficiency over fixed displacement pumps, a significant energy loss may result due to pump displacement being controlled, directly or indirectly, by the output pressure of the pump which changes with the operating speed of the mechanical system, rather than with the changing requirements of the mechanical system.
- variable displacement pump control system is described within U.S. Pat. No. 7,018,178.
- the control system includes an electric solenoid coupled to a variable displacement pump for varying the displacement of the pump during engine operation. While an electric solenoid may provide an additional degree of pump control, several disadvantages from its use exist.
- a solenoid typically requires a continuous supply of current to keep it active through operation of the pump. The electrical power consumption may offset the benefit of controlling the pump to minimize the amount of time that the pump provides excess lubricant flow.
- the maximum force capability of the solenoid is limited by the size of the electromagnet and the current applied thereto. For certain applications, the size of the electromagnet required to provide the desired force may be prohibitive for packaging the solenoid within an automotive environment. Accordingly, a need exists for an improved lubrication system for producing a desired lubricant flow while minimizing the energy required to do so.
- a fluid pumping system for a power transmission device includes a variable displacement vane pump having a housing containing a rotor, a plurality of vanes coupled to the rotor and a linearly translatable slide for varying the displacement of the pump by changing its eccentricity.
- a control system varies the displacement of the pump and provides a fluid output pressure selected from a continuously variable range of output pressures that are independent from the operating speed of the pump.
- the control system includes a linear actuator for moving the slide between minimum and maximum pump displacement positions.
- the linear actuator includes an electric stepper motor for bi-directionally translating an actuator shaft acting on the slide.
- a fluid pumping system for a power transmission device including a variable displacement vane pump having a linearly moveable slide for varying the displacement of the pump.
- a linear actuator moves the slide between maximum and minimum pump displacement positions.
- the linear actuator includes an electric motor for rotating a drive member.
- the drive member engages a driven actuator shaft to cause linear translation of the actuator shaft in response to rotation of the drive member.
- a control system includes a controller for signaling the actuator to extend or retract the actuator shaft to vary the pump displacement.
- FIG. 1 is a cross-sectional view of an exemplary directly controlled variable displacement vane pump
- FIG. 2 is an enlarged fragmentary perspective view of the pumping system depicted in FIG. 1 ;
- FIG. 3 is a fragmentary perspective view of a connector coupling the actuator shaft and the slide;
- FIG. 4 is a schematic of an open loop control system for controlling the variable displacement vane pump
- FIG. 5 is a schematic depicting a closed loop control system cooperating with the variable displacement vane pump
- FIG. 6 is a fragmentary perspective view of another variable displacement vane pump
- FIG. 7 is a plan view of a slide and actuator arrangement of the pump depicted in FIG. 6 ;
- FIG. 8 is a plan view of the housing for the pump shown in FIG. 6 .
- a pumping system 10 is shown plumbed in communication with an exemplary power transmission device 12 .
- Power transmission device 12 is shown schematically and may include any number of devices including an internal combustion engine, a transmission, a transfer case, an axle assembly or the like.
- Pumping system 10 includes a variable displacement pump 14 including a housing 16 with a flange 17 for mounting pump 14 to power transmission device 12 .
- housing 16 may be integrally formed with the power transmission device.
- An inlet 18 extends through housing 16 interconnecting a low pressure gallery 20 with a sump 22 storing the fluid to be pumped.
- An outlet 24 of housing 16 interconnects a high pressure chamber 26 with power transmission device 12 .
- Pump 14 includes a pump rotor 28 rotatably mounted within a rotor chamber 32 .
- a drive shaft 34 is part of power transmission device 12 and is fixed for rotation with pump rotor 28 to provide energy for pumping the lubricant.
- a plurality of pump vanes 36 are coupled to rotor 28 and radially slidable relative thereto. The radial outer end of each vane 36 engages an inner surface 38 of a slide 40 .
- a plurality of pumping chambers 44 are defined by inner surface 38 , pump rotor 28 and vanes 36 .
- Slide 40 includes a first arm 46 slidably positioned within a first recess 48 formed in housing 16 .
- Slide 40 also includes a second arm 50 slidably positioned within a second housing recess 52 .
- Slide 40 also includes substantially parallel opposite walls 54 , 56 positioned in close proximity to walls 58 , 60 of housing 16 , respectively. Based on the geometric features previously described, slide 40 may linearly translate between first and second positions but is restricted from rotation relative to housing 16 .
- Inner surface 38 of slide 40 has a circular cross-sectional shape.
- An outer surface 61 of rotor 28 also has a circular cross-sectional shape.
- a centerline of cylindrical surface 38 is eccentrically located with respect to the center of outer surface 61 . Accordingly, the volume of each pumping chamber 44 changes as rotor 28 rotates.
- the volume of chambers 44 increases at the low pressure side of the pump in communication with inlet 18 .
- Pumping chambers 44 decrease in size at the high pressure side in communication with outlet 24 of pump 14 .
- the change in volume of pumping chambers 44 generates the pumping action by drawing working fluid from sump 22 and delivering pressurized fluid from outlet port 24 .
- the output of pump 14 may be varied by translating slide 40 .
- the amount of eccentricity between inner surface 38 of slide 40 and the outer surface 61 of rotor 28 is a maximum when slide 40 is at the first position shown in FIG. 1 . Pump output flow is greatest at this position.
- eccentricity and the output of pump 14 are minimized and may be zero.
- a linear actuator assembly 62 is coupled to second arm 50 and is operable to move slide 40 along an axis 63 to the first position, the second position and any point therebetween. Accordingly, pump 14 may be controlled to output a fluid pressure selected from a continuously variable range of output pressures that are independent from the operating speed of the pump.
- a pressure balance chamber 64 surrounds a portion of slide 40 .
- Pressure balance chamber 64 is in fluid communication with pressurized fluid provided from outlet 24 .
- the shape and position of pressure balance chamber 64 effectively balances the forces acting on slide 40 thereby minimizing the force required to move slide 40 and vary the pump output.
- Pressure balance chamber 64 extends along one side of slide 40 on opposite sides of a line perpendicularly intersecting axis 63 and extending through the centerline of surface 38 . It should be appreciated that the pressure balanced arrangement may be desirable but is not a requisite portion of pumping system 10 . Without the pressure balancing chamber, actuator 62 may function but may be tasked to provide a greater input force to move slide 40 .
- actuator assembly 62 includes an electric stepper motor 70 including a stator 72 and a rotor 74 supported in a housing 75 .
- Rotor 74 is coupled to a nut 76 that is threadingly engaged with an externally threaded actuator shaft 78 .
- Housing 75 includes a flange 79 coupled to pump housing 16 . Flange 79 may alternatively be fixed to power transmission device 12 .
- FIG. 3 depicts actuator shaft 78 including a distal end 80 coupled to second arm 50 by a clip 82 .
- Actuator shaft 78 includes a groove 84 in receipt of a semi-circular portion 86 of clip 82 .
- Clip 82 also includes an elongated upper portion 88 that may be translated into a slot 90 formed within second arm 50 to couple actuator shaft 78 to slide 40 .
- actuator assembly 62 is in communication with a controller 100 , a power supply 102 and a drive 104 .
- Controller 100 may be programmed with an algorithm or algorithms referencing speed, pressure, flow or temperature maps to enable the controller to control the flow of the pump using an open loop control system as depicted in FIG. 4 .
- FIG. 5 depicts a closed loop control system including a pressure sensor 106 in communication with controller 100 .
- drive shaft 34 begins to rotate and drive rotor 28 .
- Lubricant pressure and flow begin to increase at outlet 24 .
- controller 100 locates slide 40 in the first position to provide maximum flow. As such, flow increases linearly with the speed of drive shaft 34 . At a particular speed, the flow produced by pump 14 will exceed the lubrication requirements of power transmission device 12 .
- controller 100 provides a signal to drive 104 .
- Drive 104 is in receipt of electrical power from power supply 102 .
- Drive 104 generates electrical pulses and supplies pulses to electric stepper motor 70 causing nut 76 to rotate in one of two directions to extend or retract actuator shaft 78 as signaled by controller 100 . Because actuator shaft 78 is directly coupled to slide 40 , the linear motion of actuator shaft 78 and slide 40 changes the eccentricity of the pump and thus the pump output flow.
- controller 100 continues to signal drive 104 to position slide 40 based on any one or more of speed, pressure, flow or temperature mappings of the control algorithm.
- a dedicated pressure sensor associated with pump 14 is not required.
- the closed loop feedback system depicted in FIG. 5 includes pressure sensor 106 providing a signal indicative of the pressure output by pump 14 to controller 100 .
- Controller 100 outputs a signal to drive 104 to position slide 40 and cause pump 14 to output a desired lubricant pressure.
- a coupling technique has been described to facilitate a ridged mounting of actuator housing 75 to pump housing 16 or another portion of power transmission device 12 .
- the connection allows actuator shaft 78 to linearly translate and transfer a force to linearly moveable slide 40 .
- any number of methods for fixing actuator shaft 78 to slide 40 such as pinning, riveting, welding, press-fitting, adhesive bonding or the like, are contemplated as being within the scope of the present disclosure.
- the closed loop control system was previously described as being in communication with a pressure sensor, it should be appreciated that any number of other sensors may be implemented to provide controller 100 with data for decision making relating to the control of actuator 62 and pumping system 10 .
- FIGS. 6 and 7 depict an alternate variable displacement pump identified at reference numeral 150 .
- Pump 150 is substantially similar to pump 14 . Accordingly, like elements will retain their previously introduced reference numerals including a prime suffix. Pump 150 differs from pump 14 in the manner in which slide 40 ′ is urged toward the first or maximum eccentricity position.
- One end of a compression spring 152 is positioned within a pocket 154 formed within slide 40 ′.
- An opposite end of spring 152 is positioned within a recess 156 formed in housing 16 ′.
- Spring 152 is continuously under compression to urge slide 40 ′ toward the first position.
- actuator 62 ′ is no longer required to move slide 40 ′ toward the first position.
- Actuator 62 ′ applies a force to move slide 40 ′ toward the second position.
- an adapter 158 may be fixed to actuator shaft 78 ′.
- Adapter 158 includes an end face 160 in contact with a land 162 formed on slide 40 ′. End face 160 and land 162 remain in contact with one another due to the force provided by compression spring 152 . At the first or most eccentric position, land 162 is forced into contact with a seat 164 formed on housing 16 ′.
- actuator 62 ′ may be selectively energized to extend actuator shaft 78 ′ and move slide 40 ′ from the first position toward the second position. Once electrical energy is no longer supplied to actuator 62 ′, the position of slide 40 ′ will be maintained due to the internal configuration of stepper motor 70 ′. To move slide 40 ′ toward the first position, actuator 62 ′ is energized once again to allow slide 40 ′ to translate under the force provided by spring 152 . An infinite number of positions between the first position providing maximum flow and the second position providing minimum flow may be obtained through control of actuator 62 ′ as previously discussed.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
Abstract
A fluid pumping system for a power transmission device includes a variable displacement vane pump having a housing containing a rotor, a plurality of vanes coupled to the rotor and a linearly translatable slide for varying the displacement of the pump. A control system varies the displacement of the pump and provides a fluid output pressure selected from a continuously variable range of output pressures which are independent from the operating speed of the pump. The control system includes a linear actuator for moving the slide between minimum and maximum pump displacement positions. The linear actuator includes an electric stepper motor for bi-directionally translating an actuator shaft acting on the slide.
Description
- This application claims the benefit of U.S. Provisional Application No. 61/157,601, filed on Mar. 5, 2009. The entire disclosure of the above application is incorporated herein by reference.
- The present disclosure relates to a fluid pumping system for an automobile. More specifically, the present disclosure relates to a variable displacement vane pump and control system for providing a continuously variable output flow independent of the operating speed of the pump.
- Mechanical systems, such as internal combustion engines and automatic transmissions, typically include a lubrication pump to provide lubricating oil, under pressure, to many of the moving components and/or subsystems of the mechanical systems. In most cases, the lubrication pump is driven by a rotating component of the mechanical system. The operating speed and output of the pump varies with the operating speed of the mechanical system. The lubrication requirements of the mechanical system, however, typically do not directly correspond to the operating speed of the mechanical system.
- Previously known fixed displacement lubricating pumps were generally designed to provide sufficient flow at a relatively low speed corresponding to an engine idle speed and a maximum operating lubricant temperature. This design philosophy resulted in an oversupply of lubricating oil during a large portion of vehicle operation. In at least one arrangement, a pressure relief valve was provided to return the surplus lubricating oil back into the pump inlet or oil sump to avoid over pressure conditions in the mechanical system. In some operating conditions, the overproduction of pressurized lubricating oil may be 500% of the mechanical system's needs. The result is a significant amount of energy being used to pressurize the lubricating oil which is subsequently exhausted through the relief valve.
- More recently, variable displacement vane pumps have been employed as lubrication oil pumps. Such pumps generally include a control ring, or other mechanism, which can be operated to alter the volumetric displacement of the pump and thus its output at an operating speed. Typically, a feedback mechanism is supplied with pressurized lubricating oil from the output of the pump to alter the displacement of the pump to avoid over pressure situations in the engine throughout the expected range of operating conditions of the mechanical system.
- While such variable displacement pumps provide some improvements in energy efficiency over fixed displacement pumps, a significant energy loss may result due to pump displacement being controlled, directly or indirectly, by the output pressure of the pump which changes with the operating speed of the mechanical system, rather than with the changing requirements of the mechanical system.
- Another variable displacement pump control system is described within U.S. Pat. No. 7,018,178. The control system includes an electric solenoid coupled to a variable displacement pump for varying the displacement of the pump during engine operation. While an electric solenoid may provide an additional degree of pump control, several disadvantages from its use exist. In particular, a solenoid typically requires a continuous supply of current to keep it active through operation of the pump. The electrical power consumption may offset the benefit of controlling the pump to minimize the amount of time that the pump provides excess lubricant flow. Furthermore, the maximum force capability of the solenoid is limited by the size of the electromagnet and the current applied thereto. For certain applications, the size of the electromagnet required to provide the desired force may be prohibitive for packaging the solenoid within an automotive environment. Accordingly, a need exists for an improved lubrication system for producing a desired lubricant flow while minimizing the energy required to do so.
- This section provides a general summary of the disclosure, and is not a comprehensive disclosure of its full scope or all of its features.
- A fluid pumping system for a power transmission device includes a variable displacement vane pump having a housing containing a rotor, a plurality of vanes coupled to the rotor and a linearly translatable slide for varying the displacement of the pump by changing its eccentricity. A control system varies the displacement of the pump and provides a fluid output pressure selected from a continuously variable range of output pressures that are independent from the operating speed of the pump. The control system includes a linear actuator for moving the slide between minimum and maximum pump displacement positions. The linear actuator includes an electric stepper motor for bi-directionally translating an actuator shaft acting on the slide.
- Furthermore, the present disclosure describes a fluid pumping system for a power transmission device including a variable displacement vane pump having a linearly moveable slide for varying the displacement of the pump. A linear actuator moves the slide between maximum and minimum pump displacement positions. The linear actuator includes an electric motor for rotating a drive member. The drive member engages a driven actuator shaft to cause linear translation of the actuator shaft in response to rotation of the drive member. A control system includes a controller for signaling the actuator to extend or retract the actuator shaft to vary the pump displacement.
- Further areas of applicability will become apparent from the description provided herein. The description and specific examples in this summary are intended for purposes of illustration only and are not intended to limit the scope of the present disclosure.
- The drawings described herein are for illustrative purposes only of selected embodiments and not all possible implementations, and are not intended to limit the scope of the present disclosure.
-
FIG. 1 is a cross-sectional view of an exemplary directly controlled variable displacement vane pump; -
FIG. 2 is an enlarged fragmentary perspective view of the pumping system depicted inFIG. 1 ; -
FIG. 3 is a fragmentary perspective view of a connector coupling the actuator shaft and the slide; -
FIG. 4 is a schematic of an open loop control system for controlling the variable displacement vane pump; -
FIG. 5 is a schematic depicting a closed loop control system cooperating with the variable displacement vane pump; -
FIG. 6 is a fragmentary perspective view of another variable displacement vane pump; -
FIG. 7 is a plan view of a slide and actuator arrangement of the pump depicted inFIG. 6 ; and -
FIG. 8 is a plan view of the housing for the pump shown inFIG. 6 . - Corresponding reference numerals indicate corresponding parts throughout the several views of the drawings.
- Example embodiments will now be described more fully with reference to the accompanying drawings.
- With reference to
FIGS. 1-3 , apumping system 10 is shown plumbed in communication with an exemplarypower transmission device 12.Power transmission device 12 is shown schematically and may include any number of devices including an internal combustion engine, a transmission, a transfer case, an axle assembly or the like.Pumping system 10 includes avariable displacement pump 14 including ahousing 16 with aflange 17 formounting pump 14 topower transmission device 12. Alternatively,housing 16 may be integrally formed with the power transmission device. Aninlet 18 extends throughhousing 16 interconnecting alow pressure gallery 20 with asump 22 storing the fluid to be pumped. Anoutlet 24 ofhousing 16 interconnects ahigh pressure chamber 26 withpower transmission device 12. -
Pump 14 includes apump rotor 28 rotatably mounted within arotor chamber 32. Adrive shaft 34 is part ofpower transmission device 12 and is fixed for rotation withpump rotor 28 to provide energy for pumping the lubricant. A plurality ofpump vanes 36 are coupled torotor 28 and radially slidable relative thereto. The radial outer end of eachvane 36 engages aninner surface 38 of aslide 40. A plurality of pumpingchambers 44 are defined byinner surface 38,pump rotor 28 andvanes 36. -
Slide 40 includes afirst arm 46 slidably positioned within afirst recess 48 formed inhousing 16.Slide 40 also includes asecond arm 50 slidably positioned within asecond housing recess 52.Slide 40 also includes substantially parallelopposite walls walls housing 16, respectively. Based on the geometric features previously described, slide 40 may linearly translate between first and second positions but is restricted from rotation relative tohousing 16. -
Inner surface 38 ofslide 40 has a circular cross-sectional shape. Anouter surface 61 ofrotor 28 also has a circular cross-sectional shape. A centerline ofcylindrical surface 38 is eccentrically located with respect to the center ofouter surface 61. Accordingly, the volume of each pumpingchamber 44 changes asrotor 28 rotates. The volume ofchambers 44 increases at the low pressure side of the pump in communication withinlet 18. Pumpingchambers 44 decrease in size at the high pressure side in communication withoutlet 24 ofpump 14. The change in volume of pumpingchambers 44 generates the pumping action by drawing working fluid fromsump 22 and delivering pressurized fluid fromoutlet port 24. - The output of
pump 14 may be varied by translatingslide 40. In particular, the amount of eccentricity betweeninner surface 38 ofslide 40 and theouter surface 61 ofrotor 28 is a maximum whenslide 40 is at the first position shown inFIG. 1 . Pump output flow is greatest at this position. Whenslide 40 is at the second position, eccentricity and the output ofpump 14 are minimized and may be zero. - A
linear actuator assembly 62 is coupled tosecond arm 50 and is operable to moveslide 40 along anaxis 63 to the first position, the second position and any point therebetween. Accordingly, pump 14 may be controlled to output a fluid pressure selected from a continuously variable range of output pressures that are independent from the operating speed of the pump. - To reduce the magnitude of force required to be provided by
actuator assembly 62, apressure balance chamber 64 surrounds a portion ofslide 40.Pressure balance chamber 64 is in fluid communication with pressurized fluid provided fromoutlet 24. The shape and position ofpressure balance chamber 64 effectively balances the forces acting onslide 40 thereby minimizing the force required to moveslide 40 and vary the pump output.Pressure balance chamber 64 extends along one side ofslide 40 on opposite sides of a line perpendicularly intersectingaxis 63 and extending through the centerline ofsurface 38. It should be appreciated that the pressure balanced arrangement may be desirable but is not a requisite portion of pumpingsystem 10. Without the pressure balancing chamber,actuator 62 may function but may be tasked to provide a greater input force to moveslide 40. - As shown in
FIGS. 2 and 3 ,actuator assembly 62 includes anelectric stepper motor 70 including astator 72 and arotor 74 supported in ahousing 75.Rotor 74 is coupled to anut 76 that is threadingly engaged with an externally threadedactuator shaft 78.Housing 75 includes aflange 79 coupled to pumphousing 16.Flange 79 may alternatively be fixed topower transmission device 12. -
FIG. 3 depictsactuator shaft 78 including adistal end 80 coupled tosecond arm 50 by aclip 82.Actuator shaft 78 includes agroove 84 in receipt of asemi-circular portion 86 ofclip 82.Clip 82 also includes an elongatedupper portion 88 that may be translated into aslot 90 formed withinsecond arm 50 to coupleactuator shaft 78 to slide 40. - Referring to
FIG. 4 ,actuator assembly 62 is in communication with acontroller 100, apower supply 102 and adrive 104.Controller 100 may be programmed with an algorithm or algorithms referencing speed, pressure, flow or temperature maps to enable the controller to control the flow of the pump using an open loop control system as depicted inFIG. 4 .FIG. 5 depicts a closed loop control system including apressure sensor 106 in communication withcontroller 100. - In operation, drive
shaft 34 begins to rotate and driverotor 28. Lubricant pressure and flow begin to increase atoutlet 24. At start-up,controller 100 locates slide 40 in the first position to provide maximum flow. As such, flow increases linearly with the speed ofdrive shaft 34. At a particular speed, the flow produced bypump 14 will exceed the lubrication requirements ofpower transmission device 12. At this time,controller 100 provides a signal to drive 104. Drive 104 is in receipt of electrical power frompower supply 102. Drive 104 generates electrical pulses and supplies pulses toelectric stepper motor 70 causingnut 76 to rotate in one of two directions to extend or retractactuator shaft 78 as signaled bycontroller 100. Becauseactuator shaft 78 is directly coupled to slide 40, the linear motion ofactuator shaft 78 and slide 40 changes the eccentricity of the pump and thus the pump output flow. - When the open loop control system of
FIG. 4 is implemented,controller 100 continues to signal drive 104 to positionslide 40 based on any one or more of speed, pressure, flow or temperature mappings of the control algorithm. A dedicated pressure sensor associated withpump 14 is not required. Alternatively, the closed loop feedback system depicted inFIG. 5 includespressure sensor 106 providing a signal indicative of the pressure output bypump 14 tocontroller 100.Controller 100 outputs a signal to drive 104 to positionslide 40 and cause pump 14 to output a desired lubricant pressure. - A coupling technique has been described to facilitate a ridged mounting of
actuator housing 75 to pumphousing 16 or another portion ofpower transmission device 12. The connection allowsactuator shaft 78 to linearly translate and transfer a force to linearlymoveable slide 40. It should be appreciated that any number of methods for fixingactuator shaft 78 to slide 40 such as pinning, riveting, welding, press-fitting, adhesive bonding or the like, are contemplated as being within the scope of the present disclosure. Furthermore, while the closed loop control system was previously described as being in communication with a pressure sensor, it should be appreciated that any number of other sensors may be implemented to providecontroller 100 with data for decision making relating to the control ofactuator 62 andpumping system 10. -
FIGS. 6 and 7 depict an alternate variable displacement pump identified atreference numeral 150.Pump 150 is substantially similar to pump 14. Accordingly, like elements will retain their previously introduced reference numerals including a prime suffix.Pump 150 differs frompump 14 in the manner in which slide 40′ is urged toward the first or maximum eccentricity position. One end of acompression spring 152 is positioned within apocket 154 formed withinslide 40′. An opposite end ofspring 152 is positioned within arecess 156 formed inhousing 16′.Spring 152 is continuously under compression to urgeslide 40′ toward the first position. - Through this arrangement,
actuator 62′ is no longer required to moveslide 40′ toward the first position.Actuator 62′ applies a force to moveslide 40′ toward the second position. As such, anadapter 158 may be fixed toactuator shaft 78′.Adapter 158 includes anend face 160 in contact with aland 162 formed onslide 40′.End face 160 andland 162 remain in contact with one another due to the force provided bycompression spring 152. At the first or most eccentric position,land 162 is forced into contact with aseat 164 formed onhousing 16′. - During pump operation,
actuator 62′ may be selectively energized to extendactuator shaft 78′ and moveslide 40′ from the first position toward the second position. Once electrical energy is no longer supplied to actuator 62′, the position ofslide 40′ will be maintained due to the internal configuration ofstepper motor 70′. To moveslide 40′ toward the first position, actuator 62′ is energized once again to allowslide 40′ to translate under the force provided byspring 152. An infinite number of positions between the first position providing maximum flow and the second position providing minimum flow may be obtained through control ofactuator 62′ as previously discussed. - Furthermore, the foregoing discussion discloses and describes merely exemplary embodiments of the present disclosure. One skilled in the art will readily recognize from such discussion, and from the accompanying drawings and claims, that various changes, modifications and variations may be made therein without departing from the spirit and scope of the disclosure as defined in the following claims.
Claims (22)
1. A fluid pumping system for a power transmission device, comprising:
a variable displacement vane pump having a housing containing a rotor, a plurality of vanes coupled to the rotor and a linearly translatable slide for varying the displacement of the pump; and
a control system for varying the displacement of the pump and providing a fluid output pressure selected from a continuously variable range of output pressures which are independent from the operating speed of the pump, the control system including a linear actuator for moving the slide between minimum and maximum pump displacement positions, the linear actuator including an electric stepper motor for bi-directionally translating an actuator shaft acting on the slide.
2. The fluid pumping system of claim 1 wherein the housing includes a pressure balance chamber in communication with the slide and in receipt of pressurized working fluid, the fluid balancing forces acting on the slide wherein the resultant force on the slide approaches zero.
3. The fluid pumping system of claim 2 wherein the control system includes a controller in communication with a drive providing electrical pulses to the stepper motor.
4. The fluid pumping system of claim 1 wherein the slide includes a first arm having substantially parallel opposite faces positioned proximate substantially parallel opposite walls of a recess formed in the housing, the first arm restricting relative rotation between the slide and the housing.
5. The fluid pumping system of claim 4 wherein the slide includes a second arm having substantially parallel opposite faces positioned proximate substantially parallel opposite walls of another recess formed in the housing, the second arm restricting relative rotation between the slide and the housing, wherein the first and second arms are diametrically opposed to one another.
6. The fluid pumping system of claim 5 wherein the second arm includes a pocket in receipt of the actuator shaft.
7. The fluid pumping system of claim 6 further including a clip interconnecting the actuator shaft and the second arm.
8. The fluid pumping system of claim 2 wherein the slide includes a bore in receipt of the vanes and the pressure balance chamber extends along one side of the slide to allow fluid to act on portions of the slide on opposite sides of a centerline extending through the slide bore.
9. The fluid pumping system of claim 1 wherein the actuator shaft and the slide each translate parallel to one another.
10. The fluid pumping system of claim 9 wherein the slide includes a bore in receipt of the vanes, the translation line of the actuator shaft intersecting a centerline of the slide bore.
11. The fluid pumping system of claim 1 further including a spring urging the slide into contact with the actuator shaft, wherein the actuator shaft is not fixed to the slide.
12. A fluid pumping system for a power transmission device, comprising:
a variable displacement vane pump including a linearly moveable slide for varying the displacement of the pump;
a linear actuator for moving the slide between maximum and minimum pump displacement positions, the linear actuator including an electric motor for rotating a drive member, the drive member engaging a driven actuator shaft to cause linear translation of the actuator shaft in response to rotation of the drive member; and
a control system including a controller for signaling the actuator to extend or retract the actuator shaft to vary the pump displacement.
13. The fluid pumping system of claim 12 wherein the controller operates in an open loop control mode and is not in receipt of a signal indicative of the pressure being output by the pump.
14. The fluid pumping system of claim 12 wherein the controller operates in a closed loop mode in response to a signal indicative of the pressure output by the pump.
15. The fluid pumping system of claim 12 wherein the electric motor is a stepper motor operable to position the slide at various positions between the minimum and maximum displacement positions.
16. The fluid pumping system of claim 12 wherein the pump includes a housing with a pressure balance chamber in communication with the slide and in receipt of pressurized working fluid, the fluid balancing forces acting on the slide wherein the resultant force on the slide approaches zero.
17. The fluid pumping system of claim 16 wherein the slide includes a first arm having substantially parallel opposite faces positioned proximate substantially parallel opposite walls of a recess formed in the housing, the first arm restricting relative rotation between the slide and the housing.
18. The fluid pumping system of claim 17 wherein the slide includes a second arm having substantially parallel opposite faces positioned proximate substantially parallel opposite walls of another recess formed in the housing, the second arm restricting relative rotation between the slide and the housing, wherein the first and second arms are diametrically opposed to one another.
19. The fluid pumping system of claim 18 wherein the second arm includes a pocket in receipt of the actuator shaft.
20. The fluid pumping system of claim 19 further including a clip interconnecting the actuator shaft and the second arm.
21. The fluid pumping system of claim 12 further including a spring urging the slide into contact with the actuator shaft, wherein the actuator shaft is not fixed to the slide.
22. The fluid pumping system of claim 12 wherein the actuator shaft and the slide each translate along the same line.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/254,207 US20120093672A1 (en) | 2009-03-05 | 2010-02-23 | Direct control linear variable displacement vane pump |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US15760109P | 2009-03-05 | 2009-03-05 | |
PCT/CA2010/000269 WO2010099599A1 (en) | 2009-03-05 | 2010-02-23 | Direct control linear variable displacement vane pump |
US13/254,207 US20120093672A1 (en) | 2009-03-05 | 2010-02-23 | Direct control linear variable displacement vane pump |
Publications (1)
Publication Number | Publication Date |
---|---|
US20120093672A1 true US20120093672A1 (en) | 2012-04-19 |
Family
ID=42709165
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/254,207 Abandoned US20120093672A1 (en) | 2009-03-05 | 2010-02-23 | Direct control linear variable displacement vane pump |
Country Status (8)
Country | Link |
---|---|
US (1) | US20120093672A1 (en) |
EP (1) | EP2404062A4 (en) |
JP (1) | JP2012519253A (en) |
KR (1) | KR20120006977A (en) |
CN (1) | CN102333956A (en) |
BR (1) | BRPI1010521A2 (en) |
CA (1) | CA2753511A1 (en) |
WO (1) | WO2010099599A1 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016209171A1 (en) * | 2016-05-25 | 2017-11-30 | Mahle International Gmbh | Pendulum slider machine, in particular oil pump, for an internal combustion engine of a motor vehicle |
EP3382169A1 (en) * | 2017-03-27 | 2018-10-03 | Robert Bosch GmbH | Oil pump with electrically variable displacement |
US10253772B2 (en) | 2016-05-12 | 2019-04-09 | Stackpole International Engineered Products, Ltd. | Pump with control system including a control system for directing delivery of pressurized lubricant |
US12038082B1 (en) * | 2020-12-30 | 2024-07-16 | Huawei Digital Power Technologies Co., Ltd. | Control method and apparatus |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103363279B (en) * | 2012-04-05 | 2016-09-07 | 同济大学 | A kind of vane type stepless variable lubricating oil pump of step motor control |
KR101333959B1 (en) * | 2012-05-31 | 2013-11-27 | 울산대학교 산학협력단 | Variable oil pump with inner actuator |
ITTO20130735A1 (en) * | 2013-09-11 | 2015-03-12 | Vhit Spa | VARIABLE DISPLACEMENT PUMP WITH ELECTRIC CONTROL ADJUSTMENT AND ADJUSTMENT METHOD OF ITS DISPLACEMENT |
CN103742775A (en) * | 2013-12-30 | 2014-04-23 | 东风汽车公司 | Vane variable displacement oil pump |
CN104314637B (en) * | 2014-08-19 | 2018-03-02 | 湖南机油泵股份有限公司 | The lubricating oil pump of internal combustion engine |
CN110714917B (en) * | 2019-10-09 | 2021-05-28 | 太原理工大学 | Variable mechanism of single-acting vane pump for continuously and proportionally adjusting flow |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3650642A (en) * | 1970-04-14 | 1972-03-21 | Chandler Evans Inc | Pumping system including variable displacement vane pump |
US4439117A (en) * | 1982-08-17 | 1984-03-27 | The Bendix Corporation | Variable displacement vane pump |
US5171133A (en) * | 1990-06-08 | 1992-12-15 | Lucas Industries | Fuel pump having an adjustable spring clip to regulate flow |
US6763797B1 (en) * | 2003-01-24 | 2004-07-20 | General Motors Corporation | Engine oil system with variable displacement pump |
US20040247463A1 (en) * | 2001-09-12 | 2004-12-09 | Clement Kiefer | Variable-delivery vane pump |
US20080069704A1 (en) * | 2004-01-09 | 2008-03-20 | Pierburg S.P.A. | Pumping System |
US20080240935A1 (en) * | 2007-03-28 | 2008-10-02 | Goodrich Pump & Engine Control Systems, Inc. | Balanced variable displacement vane pump with floating face seals and biased vane seals |
US20090074598A1 (en) * | 2004-10-25 | 2009-03-19 | Cezar Tanasuca | Variable Capacity Vane Pump with Force Reducing Chamber on Displacement Ring |
US20090324438A1 (en) * | 2008-06-26 | 2009-12-31 | Hamilton Sundstrand Corporation | Variable flow pumping system |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6131675A (en) * | 1984-07-24 | 1986-02-14 | Nippon Denso Co Ltd | Variable capacity radial plunger pump |
ES2153356T3 (en) * | 1991-12-13 | 2001-03-01 | Abbott Lab | DETECTION OF TRICYCLE ANTIDEPRESSOR DRUGS IN THE PRESENCE OF INTERFERENCE SUBSTANCES. |
DE4302610C2 (en) * | 1993-01-30 | 1996-08-08 | Daimler Benz Ag | Process for regulating the pump output of lubricant pumps and lubricant pump therefor |
DE4319200C1 (en) * | 1993-06-09 | 1994-07-21 | Glyco Metall Werke | Multi-stage controller for lubricant pumps with continuously variable delivery volumes |
DE10103386A1 (en) * | 2001-01-26 | 2002-10-10 | Audi Ag | Volumetric flow regulated lubricant pump, especially for internal combustion engine, has pressure dependent and temperature dependent volumetric flow regulation |
US20070231161A1 (en) * | 2004-09-20 | 2007-10-04 | Mathew Williamson | Pump with Selectable Outlet Pressure |
US7640736B2 (en) * | 2005-07-22 | 2010-01-05 | Ashradan Holdings Ltd. | Self-contained hydraulic actuator system |
-
2010
- 2010-02-23 CN CN201080009310XA patent/CN102333956A/en active Pending
- 2010-02-23 WO PCT/CA2010/000269 patent/WO2010099599A1/en active Application Filing
- 2010-02-23 CA CA2753511A patent/CA2753511A1/en not_active Abandoned
- 2010-02-23 JP JP2011552286A patent/JP2012519253A/en active Pending
- 2010-02-23 BR BRPI1010521A patent/BRPI1010521A2/en not_active IP Right Cessation
- 2010-02-23 KR KR1020117020776A patent/KR20120006977A/en not_active Application Discontinuation
- 2010-02-23 US US13/254,207 patent/US20120093672A1/en not_active Abandoned
- 2010-02-23 EP EP10748251.5A patent/EP2404062A4/en not_active Withdrawn
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3650642A (en) * | 1970-04-14 | 1972-03-21 | Chandler Evans Inc | Pumping system including variable displacement vane pump |
US4439117A (en) * | 1982-08-17 | 1984-03-27 | The Bendix Corporation | Variable displacement vane pump |
US5171133A (en) * | 1990-06-08 | 1992-12-15 | Lucas Industries | Fuel pump having an adjustable spring clip to regulate flow |
US20040247463A1 (en) * | 2001-09-12 | 2004-12-09 | Clement Kiefer | Variable-delivery vane pump |
US6763797B1 (en) * | 2003-01-24 | 2004-07-20 | General Motors Corporation | Engine oil system with variable displacement pump |
US20080069704A1 (en) * | 2004-01-09 | 2008-03-20 | Pierburg S.P.A. | Pumping System |
US20090074598A1 (en) * | 2004-10-25 | 2009-03-19 | Cezar Tanasuca | Variable Capacity Vane Pump with Force Reducing Chamber on Displacement Ring |
US20080240935A1 (en) * | 2007-03-28 | 2008-10-02 | Goodrich Pump & Engine Control Systems, Inc. | Balanced variable displacement vane pump with floating face seals and biased vane seals |
US20090324438A1 (en) * | 2008-06-26 | 2009-12-31 | Hamilton Sundstrand Corporation | Variable flow pumping system |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10253772B2 (en) | 2016-05-12 | 2019-04-09 | Stackpole International Engineered Products, Ltd. | Pump with control system including a control system for directing delivery of pressurized lubricant |
DE102016209171A1 (en) * | 2016-05-25 | 2017-11-30 | Mahle International Gmbh | Pendulum slider machine, in particular oil pump, for an internal combustion engine of a motor vehicle |
EP3382169A1 (en) * | 2017-03-27 | 2018-10-03 | Robert Bosch GmbH | Oil pump with electrically variable displacement |
US12038082B1 (en) * | 2020-12-30 | 2024-07-16 | Huawei Digital Power Technologies Co., Ltd. | Control method and apparatus |
Also Published As
Publication number | Publication date |
---|---|
EP2404062A1 (en) | 2012-01-11 |
CN102333956A (en) | 2012-01-25 |
BRPI1010521A2 (en) | 2016-03-15 |
JP2012519253A (en) | 2012-08-23 |
EP2404062A4 (en) | 2014-01-15 |
CA2753511A1 (en) | 2010-09-10 |
KR20120006977A (en) | 2012-01-19 |
WO2010099599A1 (en) | 2010-09-10 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US20120093672A1 (en) | Direct control linear variable displacement vane pump | |
US8597003B2 (en) | Direct control variable displacement vane pump | |
KR101177595B1 (en) | Variable capacity vane pump with dual control chambers | |
US9903367B2 (en) | Variable displacement oil pump | |
JP4776203B2 (en) | Variable displacement vane pump with variable target adjuster | |
US10167752B2 (en) | Engine oil pump with electronic oil pressure control | |
US9765778B2 (en) | Variable displacement rotary pump and displacement regulation method | |
US20160290335A1 (en) | Variable displacement lubricant pump | |
CN107923393B (en) | Variable displacement oil pump | |
EP3087275B1 (en) | Variable displacement pump for fluids with modulated regulation, and method for regulating its displacement | |
US8834140B2 (en) | Leakage loss flow control and associated media flow delivery assembly | |
US20080019846A1 (en) | Variable displacement gerotor pump | |
US11905948B2 (en) | Variable displacement oil pump including swing member | |
CN112105818B (en) | Variable mechanical lubricating oil pump for automobile | |
JP4061142B2 (en) | Variable displacement vane pump with variable target adjuster | |
EP1820935A1 (en) | Vane pump housing | |
CA2581120C (en) | Speed-related control mechanism for a pump and control method | |
KR102637516B1 (en) | Variable Oil Pump Assembly | |
JP2020526703A (en) | Variable capacity lubricating oil vane pump | |
EP1156207A1 (en) | Pump for feeding fuel to an internal combustion engine | |
EP2716912A1 (en) | Balanced pressure dual pump | |
KR101437661B1 (en) | Variable output gerotor pump with controlling disk |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: STT TECHNOLOGIES INC., A JOINT VENTURE OF MAGNA PO Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:CHANG, PETER LIT MING;STRATULAT, FLORIN;HADAR, GIL;AND OTHERS;SIGNING DATES FROM 20090111 TO 20090128;REEL/FRAME:027662/0319 |
|
AS | Assignment |
Owner name: MAGNA POWERTRAIN INC., CANADA Free format text: MERGER;ASSIGNOR:STT TECHNOLOGIES INC.;REEL/FRAME:030259/0622 Effective date: 20121201 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |