US20120061184A1 - Transmission Pump - Google Patents
Transmission Pump Download PDFInfo
- Publication number
- US20120061184A1 US20120061184A1 US13/232,959 US201113232959A US2012061184A1 US 20120061184 A1 US20120061184 A1 US 20120061184A1 US 201113232959 A US201113232959 A US 201113232959A US 2012061184 A1 US2012061184 A1 US 2012061184A1
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- Prior art keywords
- chamber
- outlet
- pump
- outlet chamber
- relief
- Prior art date
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Classifications
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- 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
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
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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
- F16N—LUBRICATING
- F16N13/00—Lubricating-pumps
- F16N13/20—Rotary pumps
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- 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
- F04C14/10—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
- F04C14/16—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using lift valves
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- 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
- F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
- F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
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- 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
- F04C14/28—Safety arrangements; Monitoring
-
- 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
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/103—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement
- F04C2/105—Details concerning timing or distribution valves
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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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0402—Cleaning of lubricants, e.g. filters or magnets
- F16H57/0404—Lubricant filters
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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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0412—Cooling or heating; Control of temperature
-
- 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
- F16H57/0435—Pressure control for supplying lubricant; Circuits or valves therefor
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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
- 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
-
- 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
- F16N13/22—Lubricating-pumps with distributing equipment
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- 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
- F01M1/18—Indicating or safety devices
- F01M1/20—Indicating or safety devices concerning lubricant pressure
-
- 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
- F01M1/02—Pressure lubrication using lubricating pumps
- F01M2001/0207—Pressure lubrication using lubricating pumps characterised by the type of pump
- F01M2001/0238—Rotary pumps
Definitions
- This invention provides both a pump and a lubrication and cooling system with a pump which includes a pump housing, a rotor, a relief valve and a bypass valve.
- the relief valve is configured to relieve pump pressure when the pump pressure is indicative of an abnormal restriction of flow.
- the bypass valve is configured to direct fluid flow from an outlet chamber of the pump to an intake chamber of the pump when pressure in the outlet chamber is at a value associated with a predetermined speed of rotor rotation.
- This invention also overcomes the pump cavitation at elevated speeds by directing unneeded fluid flow directly from the outlet chamber to an intake chamber by way of the bypass valve. Flow of fluid to the lubrication system is maintained in the event of a restriction in either a cooler or a filter by way of the relief valve.
- FIG. 1 is a schematic view of a transmission lubrication and cooling system including a pump.
- FIG. 2 is a perspective view of the pump of FIG. 1 .
- FIG. 3 is a perspective view of a housing of the pump of FIG. 2 .
- FIG. 4 is a perspective view of a cover plate of the pump of FIG. 2 .
- FIG. 5 is a perspective view of a rotor of the pump of FIG. 2 .
- FIG. 6 is a perspective view of a pump idler of FIG. 2 .
- FIG. 7 is a top view of the pump of FIG. 2 .
- FIG. 8 is a rear view of the pump of FIG. 2 .
- FIG. 9 is a rear view of the pump of FIG. 8 with the cover plate removed.
- FIG. 10 is a sectional view of the pump of FIG. 8 in the direction of arrows 10 .
- FIG. 11 is a sectional view of the pump of FIG. 7 in the direction of arrows 11 .
- top, bottom, and other directional terms such as front, rear, upper and lower are only used to provide the relative orientation of surfaces and features of the components and system, and are not indicative of the absolute position or orientation of any component or feature.
- FIG. 1 shows a transmission lubrication and cooling system 20 including a lubrication and cooling circuit 22 , a pump 24 and a sump 26 .
- a suction channel 28 is disposed between and fluidly connects sump 26 and pump 24 .
- a cooler 30 and a filter 32 are fluidly connected to pump 24 by cooling and filter channel 34 .
- a lubrication channel 36 is connected to cooling and filter channel 34 .
- Lubrication channel 36 serves as a conduit of fluid to lubrication system 38 .
- An optional return channel 40 may be used to return fluid to sump 26 .
- Pump 24 includes a relief valve 42 and a bypass valve 44 . Both valves 42 and 44 are incorporated into a housing 46 of pump 24 .
- a cover plate 48 is disposed on a rear or back side of pump housing 46 . Cover plate 48 defines outlet port 50 .
- a suction port 52 of pump 24 is connected to sump 26 by suction channel 28 .
- the illustrated pump is a gerotor style pump, and includes a pump rotor or inner rotor 54 and a pump idler or outer rotor 56 , both of which are disposed inside of pump housing 46 .
- rotor 54 having four lobes and idler 56 having five teeth
- rotor 54 having five lobes and idler 56 having six teeth
- the invention is not intended to be limited to pumps having a particular count of meshing features.
- a pump shaft 58 is rotatably fixed to pump rotor 54 by a key (not shown) or equivalent means.
- Pump shaft 58 rotates about an axis of rotation 60 normal to the pump rotor 54 .
- a drive gear 62 is disposed outside of housing 46 and is rotatably fixed to shaft 58 by a key or equivalent means.
- Drive gear 62 is an exemplary means by which torque and speed is transferred to shaft 58 and rotor 54 .
- the illustrated drive means is not intended to be limiting.
- Housing 46 includes a rotor chamber 64 in which each of rotor 54 and idler 56 are disposed. Other features of housing 46 include an intake chamber 66 which connects directly to suction port 52 and a pump inlet chamber 68 which is fluidly connected with and open to rotor chamber 64 . Additionally, an outlet chamber 70 is fluidly connected with both rotor chamber 64 and outlet port 50 .
- relief valve 42 is operably disposed between an outlet chamber 70 and a relief port 72 .
- a plurality of ports 72 may be provided.
- Valve 42 is configured to open to operably fluidly connect outlet chamber 70 with relief port 72 .
- a relief valve plug 74 is disposed in housing 46 to retain relief valve bias spring 76 .
- Spring 76 biases relief valve check ball 78 against relief valve ball seat 80 .
- a relief channel 82 fluidly connects relief port 72 with lubrication channel 36 .
- Bypass valve 44 is operably disposed between outlet chamber 70 and intake chamber 66 .
- Valve 44 is fluidly connected to intake chamber 66 by a bypass channel 84 .
- a bypass passage 86 fluidly connects valve 44 with outlet chamber 70 .
- Valve 44 is configured to open to operably fluidly connect outlet chamber 70 with intake chamber 66 .
- a bypass valve plug 88 is disposed in housing 46 to retain bypass valve bias spring 90 .
- Spring 90 biases bypass valve check ball 92 against bypass valve ball seat 94 .
- Passage 86 defines a restrictive orifice through which fluid reaching valve 44 must pass.
- a travel limit pin 96 may electively be configured to limit the displacement of check ball 92 from seat 94 is disposed in housing 46 .
- Pin 96 may be formed as part of plug 88 , or may be a separate component.
- Pump 24 relies on a conventional gerotor arrangement to draw and pressurize its operating fluid.
- the operation of such pumps is well known and illustrated in references such as U.S. Pat. No. 4,041,703.
- each of relief valve 42 and bypass valve 44 are in a closed condition, with all of the fluid displaced by the rotation of rotor 54 being drawn from sump 26 through suction channel 28 and passing through outlet port 50 , through cooler 30 and filter 32 and lubrication system 38 .
- Examples of conditions constituting an abnormal restriction include a plugged or partially plugged cooler 30 , and a plugged or partially plugged filter 32 .
- An abnormal restriction might also result from high fluid viscosity at start-up due to a low ambient temperature.
- bypass valve 44 opens to allow operating fluid to flow from outlet chamber 70 to intake chamber 66 where it joins fluid being drawn up from sump 26 through channel 28 .
- the quantity of fluid reaching intake chamber beneficially helps avoid cavitation of the pump. While alternative solutions might include increasing the sizing of the suction channel and optimizing the location of the pump relative to the sump, the present invention enables greater flexibility in the location of the pump.
- the restriction provided by the orifice sizing of passage 86 reduces the rate of flow to the intake chamber.
- the combination of spring selection and orifice sizing enable one skilled in the art to provide a pressure and flow combination suited for the application at hand.
- Intake chamber 66 has a greater cross sectional area in the flow direction than suction channel 28 , accommodating the additional volumetric flow past bypass valve 44 and facilitating an increased volumetric flow into adjoining inlet chamber 66 which feeds operating fluid to rotating rotor 54 . All of the pressurized operating fluid in outlet provided by the rotation of rotor 54 , excepting that which travels past valve 44 , exits through outlet port 50 and passes through cooler 30 , filter 32 and lubrication system 38 . An exemplary range of pressure at which valve 44 opens is 67 pounds per square inch (psi) to 71 psi.
- relief valve 42 opens to allow operating fluid to flow from outlet chamber 70 to lubrication system 38 via relief channel 82 . Routing the flow from the relief valve to the lubrication system instead of directly to the sump enables system 20 to maintain the flow of operating fluid critical lubrication of the transmission, thereby avoiding damage to the transmission.
- operating fluid flows past bypass valve 44 .
- the amount of fluid, if any, passing through cooler 30 and filter 32 will depend on the extent of blockage.
- An exemplary range of pressure at which valve 42 opens is 114 psi to 142 psi.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
Abstract
This invention provides both a pump and a lubrication and cooling system with a pump which includes a pump housing, a rotor, a relief valve and a bypass valve. The relief valve is configured to relieve pump pressure when the pump pressure is indicative of an abnormal restriction of flow. The bypass valve is configured to direct fluid flow from an outlet chamber of the pump to an intake chamber of the pump when pressure in the outlet chamber is at a value associated with a predetermined speed of rotor rotation.
Description
- This application claims the benefit of U.S. Provisional Application No. 61/382,603, filed Sep. 14, 2010, which is hereby incorporated by reference in their entireties.
- It is desired to provide a lubrication and cooling system for a transmission and a pump for use in such a system which responds to fluid flow restrictions that might occur in a cooler or in a filter. It is also desired to provide such a system and pump which is able to reduce the opportunity for pump cavitation at elevated speeds pump speeds.
- This invention provides both a pump and a lubrication and cooling system with a pump which includes a pump housing, a rotor, a relief valve and a bypass valve. The relief valve is configured to relieve pump pressure when the pump pressure is indicative of an abnormal restriction of flow. The bypass valve is configured to direct fluid flow from an outlet chamber of the pump to an intake chamber of the pump when pressure in the outlet chamber is at a value associated with a predetermined speed of rotor rotation.
- This invention also overcomes the pump cavitation at elevated speeds by directing unneeded fluid flow directly from the outlet chamber to an intake chamber by way of the bypass valve. Flow of fluid to the lubrication system is maintained in the event of a restriction in either a cooler or a filter by way of the relief valve.
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FIG. 1 is a schematic view of a transmission lubrication and cooling system including a pump. -
FIG. 2 is a perspective view of the pump ofFIG. 1 . -
FIG. 3 is a perspective view of a housing of the pump ofFIG. 2 . -
FIG. 4 is a perspective view of a cover plate of the pump ofFIG. 2 . -
FIG. 5 is a perspective view of a rotor of the pump ofFIG. 2 . -
FIG. 6 is a perspective view of a pump idler ofFIG. 2 . -
FIG. 7 is a top view of the pump ofFIG. 2 . -
FIG. 8 is a rear view of the pump ofFIG. 2 . -
FIG. 9 is a rear view of the pump ofFIG. 8 with the cover plate removed. -
FIG. 10 is a sectional view of the pump ofFIG. 8 in the direction ofarrows 10. -
FIG. 11 is a sectional view of the pump ofFIG. 7 in the direction ofarrows 11. - The terms top, bottom, and other directional terms such as front, rear, upper and lower are only used to provide the relative orientation of surfaces and features of the components and system, and are not indicative of the absolute position or orientation of any component or feature.
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FIG. 1 shows a transmission lubrication andcooling system 20 including a lubrication and cooling circuit 22, apump 24 and a sump 26. Asuction channel 28 is disposed between and fluidly connects sump 26 andpump 24. Acooler 30 and afilter 32 are fluidly connected topump 24 by cooling andfilter channel 34. A lubrication channel 36 is connected to cooling andfilter channel 34. Lubrication channel 36 serves as a conduit of fluid tolubrication system 38. An optional return channel 40 may be used to return fluid to sump 26. -
Pump 24 includes a relief valve 42 and a bypass valve 44. Both valves 42 and 44 are incorporated into a housing 46 ofpump 24. Acover plate 48 is disposed on a rear or back side of pump housing 46.Cover plate 48 defines outlet port 50. - A
suction port 52 ofpump 24 is connected to sump 26 bysuction channel 28. The illustrated pump is a gerotor style pump, and includes a pump rotor or inner rotor 54 and a pump idler or outer rotor 56, both of which are disposed inside of pump housing 46. As suggested by the figures which variously show rotor 54 having four lobes and idler 56 having five teeth, and rotor 54 having five lobes and idler 56 having six teeth, the invention is not intended to be limited to pumps having a particular count of meshing features. A pump shaft 58 is rotatably fixed to pump rotor 54 by a key (not shown) or equivalent means. Pump shaft 58 rotates about an axis of rotation 60 normal to the pump rotor 54. A drive gear 62 is disposed outside of housing 46 and is rotatably fixed to shaft 58 by a key or equivalent means. Drive gear 62 is an exemplary means by which torque and speed is transferred to shaft 58 and rotor 54. The illustrated drive means is not intended to be limiting. - Housing 46 includes a rotor chamber 64 in which each of rotor 54 and idler 56 are disposed. Other features of housing 46 include an
intake chamber 66 which connects directly tosuction port 52 and a pump inlet chamber 68 which is fluidly connected with and open to rotor chamber 64. Additionally, an outlet chamber 70 is fluidly connected with both rotor chamber 64 and outlet port 50. - As best seen in
FIG. 11 , relief valve 42 is operably disposed between an outlet chamber 70 and a relief port 72. A plurality of ports 72 may be provided. Valve 42 is configured to open to operably fluidly connect outlet chamber 70 with relief port 72. In the embodiment illustrated, a relief valve plug 74 is disposed in housing 46 to retain relief valve bias spring 76. Spring 76 biases reliefvalve check ball 78 against relief valve ball seat 80. Arelief channel 82 fluidly connects relief port 72 with lubrication channel 36. - Bypass valve 44 is operably disposed between outlet chamber 70 and
intake chamber 66. Valve 44 is fluidly connected tointake chamber 66 by a bypass channel 84. A bypass passage 86 fluidly connects valve 44 with outlet chamber 70. Valve 44 is configured to open to operably fluidly connect outlet chamber 70 withintake chamber 66. In the embodiment illustrated, abypass valve plug 88 is disposed in housing 46 to retain bypass valve bias spring 90. Spring 90 biases bypass valve check ball 92 against bypass valve ball seat 94. Passage 86 defines a restrictive orifice through which fluid reaching valve 44 must pass. A travel limit pin 96 may electively be configured to limit the displacement of check ball 92 from seat 94 is disposed in housing 46. Pin 96 may be formed as part ofplug 88, or may be a separate component. - A description of the invention operation follows.
Pump 24 relies on a conventional gerotor arrangement to draw and pressurize its operating fluid. The operation of such pumps is well known and illustrated in references such as U.S. Pat. No. 4,041,703. In a first condition, at relatively low rotational speeds of shaft 58 and rotor 54, with no abnormal restrictions in cooling andfiltering channel 34, each of relief valve 42 and bypass valve 44 are in a closed condition, with all of the fluid displaced by the rotation of rotor 54 being drawn from sump 26 throughsuction channel 28 and passing through outlet port 50, through cooler 30 andfilter 32 andlubrication system 38. Examples of conditions constituting an abnormal restriction include a plugged or partially plugged cooler 30, and a plugged or partially pluggedfilter 32. An abnormal restriction might also result from high fluid viscosity at start-up due to a low ambient temperature. - In a second condition, at a first pressure within outlet chamber 70 corresponding to a predetermined speed of rotor 54, bypass valve 44 opens to allow operating fluid to flow from outlet chamber 70 to
intake chamber 66 where it joins fluid being drawn up from sump 26 throughchannel 28. The quantity of fluid reaching intake chamber beneficially helps avoid cavitation of the pump. While alternative solutions might include increasing the sizing of the suction channel and optimizing the location of the pump relative to the sump, the present invention enables greater flexibility in the location of the pump. The restriction provided by the orifice sizing of passage 86 reduces the rate of flow to the intake chamber. The combination of spring selection and orifice sizing enable one skilled in the art to provide a pressure and flow combination suited for the application at hand.Intake chamber 66 has a greater cross sectional area in the flow direction thansuction channel 28, accommodating the additional volumetric flow past bypass valve 44 and facilitating an increased volumetric flow into adjoininginlet chamber 66 which feeds operating fluid to rotating rotor 54. All of the pressurized operating fluid in outlet provided by the rotation of rotor 54, excepting that which travels past valve 44, exits through outlet port 50 and passes through cooler 30,filter 32 andlubrication system 38. An exemplary range of pressure at which valve 44 opens is 67 pounds per square inch (psi) to 71 psi. - In a third condition, as the operating fluid within outlet chamber 70 reaches a second pressure indicative of an abnormal restriction of flow in cooling and
filtering channel 34, relief valve 42 opens to allow operating fluid to flow from outlet chamber 70 tolubrication system 38 viarelief channel 82. Routing the flow from the relief valve to the lubrication system instead of directly to the sump enablessystem 20 to maintain the flow of operating fluid critical lubrication of the transmission, thereby avoiding damage to the transmission. As in the second condition, operating fluid flows past bypass valve 44. The amount of fluid, if any, passing through cooler 30 andfilter 32 will depend on the extent of blockage. An exemplary range of pressure at which valve 42 opens is 114 psi to 142 psi. The appropriate range of pressures for any particular application of the inventive system will vary with that application. Factors influencing pressure ranges for both the bypass and relief valves include, but are not limited to, the viscosity of the operating fluid, the anticipated operating temperatures, and the anticipated back pressure of the system under normal operating conditions. - The scope of the invention is set forth in the claims below.
Claims (8)
1. A pump comprising:
a pump housing defining
a suction port,
an outlet port,
a rotor chamber disposed between the suction port and the outlet port,
an intake chamber fluidly connected to the suction port,
an inlet chamber fluidly connected to the intake chamber and fluidly connected to the rotor chamber,
an outlet chamber fluidly connected to the rotor chamber and fluidly connected to the outlet port;
a rotor rotatably disposed in the rotor chamber having a first portion in fluid communication with the outlet chamber and having a second portion in fluid communication with the inlet chamber;
a relief valve operably disposed between the outlet chamber and a relief port though the housing and configured to operably fluidly connect the outlet chamber with the relief port when a pressure in the outlet chamber is at or above a first value indicative of an abnormal restriction of flow from the outlet chamber; and
a bypass valve operably disposed between the outlet chamber and the intake chamber and configured to operably fluidly connect the outlet chamber with the intake chamber when the pressure in the outlet chamber is at or above a second value less than the first value and indicative of a pressure in the outlet chamber at or above a pressure associated with a predetermined speed of rotation of the rotor.
2. A pump as claimed in claim 1 wherein a restrictive orifice is disposed between the outlet chamber and the bypass valve.
3. A pump as claimed in claim 1 wherein the relief valve includes a relief check ball and a spring biasing the relief check ball to a closed position and the bypass valve includes a bypass check ball and a spring biasing the bypass check ball to a closed position.
4. A pump as claimed in claim 3 wherein the bypass valve includes a travel limit pin configured to limit the displacement of bypass check ball away from a seated position.
5. A lubrication and cooling system for a transmission comprising:
a pump including:
a pump housing defining
a suction port,
an outlet port;
a rotor chamber disposed between the suction port and the outlet port,
an intake chamber fluidly connected to the suction port,
an inlet chamber fluidly connected to the intake chamber and fluidly connected to the rotor chamber,
an outlet chamber fluidly connected to the rotor chamber and fluidly connected to the outlet port;
a rotor rotatably disposed in the rotor chamber having a first portion in fluid communication with the outlet chamber and having a second portion in fluid communication with the inlet chamber;
a relief valve operably disposed between the outlet chamber and a relief port though the housing and configured to operably fluidly connect the outlet chamber with the relief port when a pressure in the outlet chamber is at or above a first value indicative of an abnormal restriction of flow from the outlet chamber; and
a bypass valve operably disposed between the outlet chamber and the intake chamber and configured to operably fluidly connect the outlet chamber with the intake chamber when the pressure in the outlet chamber is at or above a second value less than the first value and indicative of a pressure in the outlet chamber at or above a pressure associated with a predetermined speed of rotation of the rotor
a lubrication and cooling fluid circuit including
a cooling and filtering channel on which a cooler and a filter are operably disposed and fluidly connecting the outlet port of the pump with a lubrication channel;
the lubrication channel configured to distribute fluid to predetermined points within the transmission; and
a relief channel fluidly connecting the relief port to the lubrication channel.
6. A lubrication and cooling system as claimed in claim 5 wherein a restrictive orifice is disposed between the outlet chamber and the bypass valve.
7. A lubrication and cooling system as claimed in claim 7 wherein the relief valve includes a relief check ball and a spring biasing the relief check ball to a closed position and the bypass valve includes a bypass check ball and a spring biasing the bypass check ball to a closed position.
8. A lubrication and cooling system as claimed in claim 7 wherein the bypass valve includes a travel limit pin configured to limit the displacement of bypass check ball away from a seated position.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/232,959 US20120061184A1 (en) | 2010-09-14 | 2011-09-14 | Transmission Pump |
US14/615,890 US9909715B2 (en) | 2010-09-14 | 2015-02-06 | Transmission pump |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US38260310P | 2010-09-14 | 2010-09-14 | |
US13/232,959 US20120061184A1 (en) | 2010-09-14 | 2011-09-14 | Transmission Pump |
Related Child Applications (1)
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US14/615,890 Continuation US9909715B2 (en) | 2010-09-14 | 2015-02-06 | Transmission pump |
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US14/615,890 Active US9909715B2 (en) | 2010-09-14 | 2015-02-06 | Transmission pump |
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CN103511602A (en) * | 2013-10-30 | 2014-01-15 | 盛瑞传动股份有限公司 | Gearbox oil pump with oil discharge groove |
CN103557424A (en) * | 2013-10-29 | 2014-02-05 | 浙江吉利控股集团有限公司 | Variable displacement oil pump regulation mechanism |
US20150141192A1 (en) * | 2013-08-23 | 2015-05-21 | American Axle & Manufacturing, Inc. | Clutched power transmitting device with filter element |
US20150153001A1 (en) * | 2010-09-14 | 2015-06-04 | Eaton Corporation | Transmission Pump |
CN104964151A (en) * | 2015-07-03 | 2015-10-07 | 南京高德机械有限公司 | Diesel engine oil pump |
CN105240673A (en) * | 2015-11-04 | 2016-01-13 | 湖南机油泵股份有限公司 | Rotor type double-stage oil pump |
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US9366334B2 (en) * | 2014-05-06 | 2016-06-14 | Borgwarner Inc. | Lubrication system and transfer case incorporating the same |
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USD782945S1 (en) * | 2015-07-10 | 2017-04-04 | George D. Stuckey | Front cover plate |
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WO2017140503A1 (en) * | 2016-02-19 | 2017-08-24 | Ibs Filtran Kunststoff-/Metallerzeugnisse Gmbh | Hydraulic oil filter system for a motor vehicle transmission |
US20180100600A1 (en) * | 2016-10-11 | 2018-04-12 | Honda Motor Co., Ltd. | Control valve unit |
US20190145295A1 (en) * | 2017-11-16 | 2019-05-16 | GM Global Technology Operations LLC | Flow control system to eliminate air ingestion |
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US4368802A (en) * | 1980-07-03 | 1983-01-18 | Rockwell International Corporation | Pressurized lubrication system |
US5544540A (en) * | 1994-12-29 | 1996-08-13 | Dana Corporation | Gerotor pump for vehicle transmission lubrication system |
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US9163715B2 (en) * | 2013-08-23 | 2015-10-20 | American Axle & Manufacturing, Inc. | Clutched power transmitting device with filter element |
CN103557424A (en) * | 2013-10-29 | 2014-02-05 | 浙江吉利控股集团有限公司 | Variable displacement oil pump regulation mechanism |
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US9366334B2 (en) * | 2014-05-06 | 2016-06-14 | Borgwarner Inc. | Lubrication system and transfer case incorporating the same |
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USD782945S1 (en) * | 2015-07-10 | 2017-04-04 | George D. Stuckey | Front cover plate |
CN105240673A (en) * | 2015-11-04 | 2016-01-13 | 湖南机油泵股份有限公司 | Rotor type double-stage oil pump |
CN106764369A (en) * | 2015-11-23 | 2017-05-31 | 湖南机油泵股份有限公司 | A kind of adjustable lubricating oil pump of new oil mass |
CN106764368A (en) * | 2015-11-23 | 2017-05-31 | 湖南机油泵股份有限公司 | A kind of novel gear type oil pump |
CN105402583A (en) * | 2015-12-15 | 2016-03-16 | 湖南湘衡泵业有限责任公司 | Rotor type oil pump |
CN108700182A (en) * | 2016-02-19 | 2018-10-23 | Ibs菲尔特兰塑料金属产品有限公司 | Pressure oil filtration system for vehicle transmission |
WO2017140503A1 (en) * | 2016-02-19 | 2017-08-24 | Ibs Filtran Kunststoff-/Metallerzeugnisse Gmbh | Hydraulic oil filter system for a motor vehicle transmission |
KR20180112042A (en) * | 2016-02-19 | 2018-10-11 | 이베에스 필트란 쿤스츠토프-/메탈러조이그니세 게엠베하 | Hydraulic oil filter system for automobile transmission |
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CN105889733A (en) * | 2016-04-11 | 2016-08-24 | 湖北三江船艇科技有限公司 | Parallel type rotor oil pump of ship gasoline engine |
US20180100600A1 (en) * | 2016-10-11 | 2018-04-12 | Honda Motor Co., Ltd. | Control valve unit |
US10415716B2 (en) * | 2016-10-11 | 2019-09-17 | Honda Motor Co., Ltd. | Control valve unit |
US11618556B2 (en) * | 2017-06-27 | 2023-04-04 | Kawasaki Jukogyo Kabushiki Kaisha | Lubrication pressue control of a power transmission device for helicopter |
US20190145295A1 (en) * | 2017-11-16 | 2019-05-16 | GM Global Technology Operations LLC | Flow control system to eliminate air ingestion |
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CN112610682A (en) * | 2020-12-15 | 2021-04-06 | 苏州绿控传动科技股份有限公司 | Active lubricating and cooling system for new energy automobile transmission |
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