EP3724504A1 - Variable lubricant vane pump - Google Patents

Variable lubricant vane pump

Info

Publication number
EP3724504A1
EP3724504A1 EP17816761.5A EP17816761A EP3724504A1 EP 3724504 A1 EP3724504 A1 EP 3724504A1 EP 17816761 A EP17816761 A EP 17816761A EP 3724504 A1 EP3724504 A1 EP 3724504A1
Authority
EP
European Patent Office
Prior art keywords
pump
pressure
control ring
pilot chamber
shiftable
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.)
Granted
Application number
EP17816761.5A
Other languages
German (de)
French (fr)
Other versions
EP3724504B1 (en
Inventor
Carmine Cuneo
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Pierburg Pump Technology GmbH
Original Assignee
Pierburg Pump Technology GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Pierburg Pump Technology GmbH filed Critical Pierburg Pump Technology GmbH
Publication of EP3724504A1 publication Critical patent/EP3724504A1/en
Application granted granted Critical
Publication of EP3724504B1 publication Critical patent/EP3724504B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • 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
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/18—Pressure
    • F04C2270/185—Controlled or regulated

Definitions

  • Variable lubricant wane pump for providing pressurized lubricant, in particular a mechanical variable displacement lubricant vane pump for providing pressurized lubricant for an Internal combustion engine
  • the variable lubricant vane pump is mechanically driven by the engine, for example via a gear or belt, and is fluidlcaliy coupled to the engine for pumping the pressurized lubricant to and through the engine,
  • WO 2015/074700 A1 discloses a typical variable lubricant vane pump for providing pressurized lubricant for an Internal combustion engine.
  • the variable lubricant vane pump is provided with a static pump housing, a shiftable control ring and a rotatable pump rotor comprising several rotor vanes rotating within the shiftable control ring.
  • the control ring is shiftable with respect to the pump rotor to thereby vary the eccentricity of the control ring with respect to the pump rotor for controlling the displacement and, as a result, the volumetric pump performance.
  • variable lubricant vane pump is provided with a control ring preload spring arranged within a spring chamber, and preloading and pushing the shiftable control ring into a high-eccentricity direction.
  • the pump is also provided with a pilot chamber which is loaded with the pump outlet pressure causing the shiftable control ring to move into a low-eccentricity direction against the control ring preload spring.
  • the pump Is provided with a control valve to regulate the hydraulic spring chamber pressure in a range between the pump outlet pressure and atmospheric pressure and, as a result to control the eccentricity of the control ring and thereby the volumetric pump performance.
  • the control valve allows providing different pump outlet set-pressure values.
  • variable lubricant pump Since the variable lubricant pump is mechanically driven by the engine, variations of the engine rotational speed cause variations of the volumetric pump performance. These pump performance variations are compensated by a closed-loop control of the eccentricity of the control ring via the control valve.
  • the closed-loop control of the control ring eccentricity can cause low-frequency oscillations of the control ring, In particular oscillations with frequencies in the range of 5 Hz to 50 Hz.
  • the control ring oscillations cause fluctuations of the pump outlet pressure and can reduce the pump efficiency.
  • the control ring oscillations are particularly present at relatively low pump outlet set pressures.
  • variable lubricant vane pump is provided with a static pump housing defining a pump inlet and a pump outlet.
  • the pump housing also defines a pump chamber wherein a shiftable control ring is provided.
  • the control ring can be supported at the pump housing being shiftable strictly linear or can be provided pivotable so that the control ring is moved along an arch-like path.
  • the variable lubricant vane pump according to the invention is also provided with a rotatable pump rotor located within the control ring.
  • the pump rotor comprises several rotor vanes defining several pump chamber compartments. The rotor vanes and, as a result, the pump chamber compartments rotate within the control ring.
  • the pump rotor axis of rotation Is static so that a shifting of the control ring changes the eccentricity of the pump rotor with respect to the surrounding control ring to thereby control the displacement and, as a result, the volumetric performance of the pump.
  • variable lubricant vane pump is also provided with a control ring preload spring preloading and pushing the shiftable control ring into a high-eccentricity direction.
  • the pump provides the highest displacement and, as a result, the highest volumetric performance for a defined rotational speed.
  • the preload spring is arranged within a hydraulic spring chamber being pressure controlled by a pressure control valve.
  • the pressure control valve is fluidically connected to a load pressure and to an atmospheric pressure.
  • the control valve can control the spring chamber pressure between the load pressure and the atmospheric pressure to control the control ring eccentricity and thereby the volumetric pump performance to define and assure at least two different pump set-pressure values.
  • the control ring preload spring is provided with a low stiffness to allow low pump set- pressure values.
  • the variable lubricant vane pump according to the invention is also provided with a pilot chamber which is hydraulically pressurized with the load pressure via a hydraulic pilot chamber load line.
  • the pilot chamber load line is the only hydraulic connection of the pilot chamber so that the flow rate into/out of the pilot chamber is determined by the throughput of the hydraulic load line.
  • the pilot chamber pressure causes a movement of the control ring against the preload spring into a low-eccentricity direction.
  • the variable lubricant vane pump according to the invention is also provided with a hydraulic restrictor element restricting the throughput of the pilot chamber load line and thereby restricting the total flow rate into/out of the pilot chamber. Since the control ring movement changes the pilot chamber volume, a restriction of the hydraulic flow rate into/out of the pilot chamber damps the control ring movement in both directions. As a result, control ring oscillations can be avoided or at least minimized.
  • the load pressure being provided to the pilot chamber and via the control valve to the spring chamber is a gallery pressure of the engine being provided with the lubricant.
  • the engine gallery pressure Is the controlled pressure parameter of the pump.
  • the internal combustion engine Is supplied with the pressurized lubricant coining from the pump outlet and having the pump outlet pressure.
  • the pressure parameter to be controlled is the combustion engines gallery pressure, not the pump outlet pressure.
  • the load pressure is the pump outlet pressure being provided to the engine.
  • the pump outlet pressure Is the controlled pressure parameter of the pump so that the engine Is provided with a controlled pressure.
  • the pilot chamber is pressurized with the pump outlet pressure via a hydraulic pilot chamber load line being defined by the pump housing and directly fluidically connecting the pump outlet to the pilot chamber.
  • the pilot chamber load line can be a bore within the pump housing.
  • the restrictor element is provided with a hydraulic cross section in the range of 0.25 mm 2 to 4 mm 2 . This allows a very efficient damping of the control ring movement.
  • the pressure control valve is a proportional valve allowing a continuous control of the spring chamber pressure and thereby of the control ring movement. As a result, the pump performance can be controlled very accurate allowing a continuously variable and stable control of the pump outlet set pressure or of the engine gallery set pressure, respectively.
  • the shiftable control ring is provided shiftable exactly linear with respect to the pump rotor axis of rotation. This allows a simple frictional bearing of the control ring within the control ring housing body not requiring any hinges or pivoting bearings.
  • the lubricant pump is provided with a set- pressure control unit.
  • the set-pressure control unit controls the pressure control valve to adjust the pump set pressure corresponding to the requirements of the engine.
  • the set- pressure control unit can receive a set-pressure value from an engine control unit or can provide a temperature-dependent pump set- pressure control.
  • figure 1 shows an arrangement of a first embodiment of a variable lubricant vane pump according to the invention together with an internal combustion engine wherein a pilot chamber and a control valve are provided with an engine gallery pressure, and
  • figure 2 shows an arrangement of a second embodiment of a variable lubricant vane pump according to the invention together with an internal combustion engine wherein a pilot chamber is directly hydraulically connected to a pump outlet via a hydraulic channel defined by a pump housing, and wherein the control valve is provided with a pump outlet pressure.
  • Figure 1 shows a schematic representation of a lubrication circuit arrangement of an internal combustion engine 100 including a variable lubricant vane pump 102 providing the engine 100 with pressurized lubricant.
  • the lubricant pump 102 is mechanically driven by the engine 100 so that the rotational speed of the lubricant pump 102 is proportional to the rotational speed of the engine 100.
  • the lubricant pump 102 sucks lubricant with atmospheric pressure PA from a lubricant tank 104 through a pump inlet 106 and provides pressurized lubricant with a pump outlet pressure PO through a pump outlet 108 via a lubricant supply line 110 to the engine 100.
  • the lubricant flows from the engine 100 via a lubricant return line 112 back to the lubricant tank 104.
  • the lubricant pump 102 comprises a pump housing 114 defining an inlet chamber 116, an outlet chamber 118, a pumping chamber 120 with a rotatable pump rotor 122 and with a shiftable control ring 124, a spring chamber 126 with a control ring preload spring 128, and defining a pilot chamber 130.
  • the pump Inlet chamber 116 is provided with lubricant with atmospheric pressure PA via the pump inlet 106.
  • the pump outlet chamber 118 is pressurized with the pump outlet pressure PO and is fluidlca!ly connected to the pump outlet 108.
  • the pump rotor 122 is located within the control ring 124 and rotates in clockwise direction about a static axis of rotation A.
  • the pump rotor 122 is provided with five rotor vanes 123 being supported radially slidable within corresponding vane slits.
  • the pump housing 114, the control ring 124 and the rotor vanes 123 define five rotating pumping chamber compartments 125.
  • the control ring 124 is radially supported by the pump housing 114 via two radially protruding plungers 129,131.
  • the control ring 124 fs shiftable exactly linear with respect to the pump rotor 122 whereby the first plunger 129 is moved within the spring chamber 126 and the second plunger 131 is moved within the pilot chamber 130.
  • the volumetric pump performance of the lubricant pump 102 can be controlled by moving the control ring 124 and thereby varying the eccentricity of the pump rotor 122 with respect to the surrounding control ring 124.
  • the control ring 124 Is preloaded by the control ring preload spring 128 pushing the control ring 124 into a high-eccentricity direction H. As a result, if no other forces in shifting direction of the control ring 124 are effective with respect to the control ring 124, the control ring 124 is pushed into the maximum-eccentricity position providing the maximum volumetric pump performance.
  • the control ring preload spring 128 is provided with a low stiffness to allow low pump set- pressure values.
  • the control ring 124 is loaded in the high-eccentricity direction H by the pressure of the spring chamber 126.
  • the spring chamber pressure is controlled by a pressure control valve 132.
  • the control valve 132 is a proportional valve and Is f!uidically connected to an engine gallery pressure inlet 134 being provided with an engine gallery pressure PG.
  • the control valve 132 Is also f!uidical!y connected to the lubricant tank 104 via a lubricant outlet 136.
  • the control valve 132 allows controlling the spring chamber pressure in a pressure range between the atmospheric pressure PA and the engine gallery pressure PG to define and assure different pump set-pressure values.
  • the pressure control valve 132 is controlled by a set- pressure control unit 133 to adapt the pump set pressure to the requirements of the engine.
  • the control ring 124 is loaded In an opposing low-eccentricity direction L by the pressure of the pilot chamber 130.
  • the pilot chamber 130 is f!uid!cally connected to the gallery pressure inlet 134 via a hydraulic pilot chamber load line 138. As a result, the pilot chamber is pressurized with the engine gallery pressure PG.
  • the radial position of the shiftable control ring 124 depends on the ratio of the spring chamber pressure to the pilot chamber pressure and, as a result, can be controlled via the control valve 132.
  • the pilot chamber load line 138 is provided with a restrictor element 140 restricting the throughput of the pilot chamber load line 138.
  • the restrictor element 140 is provided with a minimum hydraulic cross section in the range of 0.25 mm 2 to 4 mm 2 , whereas all other hydraulic lines have minimum hydraulic cross section of at least 7 mm 2 .
  • FIG. 2 shows a schematic representation of an alternative lubrication circuit arrangement with an alternative variable lubricant vane pump 202 according to the invention.
  • the features of the lubrication circuit and the lubricant pump 202 of figure 2 which correspond with the features of the lubrication circuit and the lubricant pump 102 of figure 1 have a reference number increased by 100.
  • the pressure control valve 232 is fluidically connected to the pump outlet chamber 218 via a valve supply line 242 and fluidically connected to the lubricant tank 204 via the lubricant outlet 236.
  • the control valve 232 allows controlling the pressure of the spring chamber 230 In a pressure range between the atmospheric pressure PA and the pump outlet pressure PO.
  • the pilot chamber 230 Is directly fluidically connected to the pump outlet chamber 218 via a pilot chamber load line 238 being defined by the pump housing 214. As a result, the pilot chamber 230 Is pressurized with the pump outlet pressure PO.
  • the pilot chamber load channel 238 is provided with restrictor element 240 being provided by an orifice 241 with a hydraulic cross section In the range of 0.25 mm 2 to 1 mm 2 .
  • the restrictor element 240 restricts the throughput of the pilot chamber load channel 238 and, as a result, damps the movement of the control ring 224,

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)

Abstract

A variable lubricant vane pump (102,202) for providing pressurized lubricant with a pump outlet pressure (PO), with a static pump housing (114,214) defining a pump inlet (106,206) and a pump outlet (108,208), a shiftable control ring (124,224) being shiftab!e with respect to a pump rotor (122,222) to thereby vary the eccentricity of the control ring (124,224) with respect to the pump rotor (122,222) for controlling the volumetric pump performance, the rotatabie pump rotor (122,222) comprising several rotor vanes (123,223) rotating within the shiftable control ring (124,224), a control ring preload spring (128,228) arranged within a spring chamber (126,226) preloading and pushing the shiftable control ring (124,224) into a high-eccentricity direction (H), a pressure control valve (132,232) controlling the spring chamber pressure between a load pressure (PG,PO) and a atmospheric pressure (PA) to thereby define at least two different pump set- pressure values, a pilot chamber (230) being pressurized with the load pressure (PG,PO) via a pilot chamber load line (138,238) providing the only hydraulic connection of the pilot chamber (130,230), the pilot chamber pressure causing the shiftable control ring (124,224) to move against the control ring preload spring (128,228) into a low-eccentricity direction (L), and a hydraulic restrictor element (140,240) restricting the throughput of the pilot chamber load channel (138,238).

Description

Variable lubricant wane pump The Invention Is directed to a variable lubricant vane pump for providing pressurized lubricant, in particular a mechanical variable displacement lubricant vane pump for providing pressurized lubricant for an Internal combustion engine, The variable lubricant vane pump is mechanically driven by the engine, for example via a gear or belt, and is fluidlcaliy coupled to the engine for pumping the pressurized lubricant to and through the engine, The pump outlet pressure or the lubricant gallery pressure !n the engine needs to be controlled and stabilized to a set pressure value.
WO 2015/074700 A1 discloses a typical variable lubricant vane pump for providing pressurized lubricant for an Internal combustion engine. The variable lubricant vane pump is provided with a static pump housing, a shiftable control ring and a rotatable pump rotor comprising several rotor vanes rotating within the shiftable control ring. The control ring is shiftable with respect to the pump rotor to thereby vary the eccentricity of the control ring with respect to the pump rotor for controlling the displacement and, as a result, the volumetric pump performance. The variable lubricant vane pump is provided with a control ring preload spring arranged within a spring chamber, and preloading and pushing the shiftable control ring into a high-eccentricity direction. The pump is also provided with a pilot chamber which is loaded with the pump outlet pressure causing the shiftable control ring to move into a low-eccentricity direction against the control ring preload spring. The pump Is provided with a control valve to regulate the hydraulic spring chamber pressure in a range between the pump outlet pressure and atmospheric pressure and, as a result to control the eccentricity of the control ring and thereby the volumetric pump performance. The control valve allows providing different pump outlet set-pressure values. Since the variable lubricant pump is mechanically driven by the engine, variations of the engine rotational speed cause variations of the volumetric pump performance. These pump performance variations are compensated by a closed-loop control of the eccentricity of the control ring via the control valve. However, the closed-loop control of the control ring eccentricity can cause low-frequency oscillations of the control ring, In particular oscillations with frequencies in the range of 5 Hz to 50 Hz. The control ring oscillations cause fluctuations of the pump outlet pressure and can reduce the pump efficiency. The control ring oscillations are particularly present at relatively low pump outlet set pressures.
It Is an object of the Invention to provide a simple variable lubricant vane pump which allows reliably providing a low pump set outlet pressure or engine lubricant gallery set pressure, respectively. This object Is achieved with a variable lubricant vane pump with the features of claim 1.
The variable lubricant vane pump according to the invention is provided with a static pump housing defining a pump inlet and a pump outlet. The pump housing also defines a pump chamber wherein a shiftable control ring is provided. The control ring can be supported at the pump housing being shiftable strictly linear or can be provided pivotable so that the control ring is moved along an arch-like path. The variable lubricant vane pump according to the invention is also provided with a rotatable pump rotor located within the control ring. The pump rotor comprises several rotor vanes defining several pump chamber compartments. The rotor vanes and, as a result, the pump chamber compartments rotate within the control ring. The pump rotor axis of rotation Is static so that a shifting of the control ring changes the eccentricity of the pump rotor with respect to the surrounding control ring to thereby control the displacement and, as a result, the volumetric performance of the pump.
The variable lubricant vane pump according to the invention is also provided with a control ring preload spring preloading and pushing the shiftable control ring into a high-eccentricity direction. In the maximum- eccentricity position, the pump provides the highest displacement and, as a result, the highest volumetric performance for a defined rotational speed. The preload spring is arranged within a hydraulic spring chamber being pressure controlled by a pressure control valve. The pressure control valve is fluidically connected to a load pressure and to an atmospheric pressure. The control valve can control the spring chamber pressure between the load pressure and the atmospheric pressure to control the control ring eccentricity and thereby the volumetric pump performance to define and assure at least two different pump set-pressure values. The control ring preload spring is provided with a low stiffness to allow low pump set- pressure values. The variable lubricant vane pump according to the invention is also provided with a pilot chamber which is hydraulically pressurized with the load pressure via a hydraulic pilot chamber load line. The pilot chamber load line is the only hydraulic connection of the pilot chamber so that the flow rate into/out of the pilot chamber is determined by the throughput of the hydraulic load line. The pilot chamber pressure causes a movement of the control ring against the preload spring into a low-eccentricity direction. The variable lubricant vane pump according to the invention is also provided with a hydraulic restrictor element restricting the throughput of the pilot chamber load line and thereby restricting the total flow rate into/out of the pilot chamber. Since the control ring movement changes the pilot chamber volume, a restriction of the hydraulic flow rate into/out of the pilot chamber damps the control ring movement in both directions. As a result, control ring oscillations can be avoided or at least minimized.
Preferably, the load pressure being provided to the pilot chamber and via the control valve to the spring chamber is a gallery pressure of the engine being provided with the lubricant. As a result, the engine gallery pressure Is the controlled pressure parameter of the pump. The internal combustion engine Is supplied with the pressurized lubricant coining from the pump outlet and having the pump outlet pressure. The pressure parameter to be controlled is the combustion engines gallery pressure, not the pump outlet pressure.
Alternatively, the load pressure is the pump outlet pressure being provided to the engine. As a result, the pump outlet pressure Is the controlled pressure parameter of the pump so that the engine Is provided with a controlled pressure.
In a preferred embodiment of the invention, the pilot chamber is pressurized with the pump outlet pressure via a hydraulic pilot chamber load line being defined by the pump housing and directly fluidically connecting the pump outlet to the pilot chamber. For example, the pilot chamber load line can be a bore within the pump housing. This allows a compact pump set-up not requiring any external hydraulic connection for the pilot chamber. Preferably, the restrictor element is provided with a hydraulic cross section in the range of 0.25 mm2 to 4 mm2. This allows a very efficient damping of the control ring movement. In a preferred embodiment of the Invention, the pressure control valve is a proportional valve allowing a continuous control of the spring chamber pressure and thereby of the control ring movement. As a result, the pump performance can be controlled very accurate allowing a continuously variable and stable control of the pump outlet set pressure or of the engine gallery set pressure, respectively.
Preferably, the shiftable control ring is provided shiftable exactly linear with respect to the pump rotor axis of rotation. This allows a simple frictional bearing of the control ring within the control ring housing body not requiring any hinges or pivoting bearings.
In a preferred embodiment of the invention, the lubricant pump is provided with a set- pressure control unit. The set-pressure control unit controls the pressure control valve to adjust the pump set pressure corresponding to the requirements of the engine. For example, the set- pressure control unit can receive a set-pressure value from an engine control unit or can provide a temperature-dependent pump set- pressure control. Two embodiments of the invention are described with reference to the enclosed drawings, wherein
figure 1 shows an arrangement of a first embodiment of a variable lubricant vane pump according to the invention together with an internal combustion engine wherein a pilot chamber and a control valve are provided with an engine gallery pressure, and
figure 2 shows an arrangement of a second embodiment of a variable lubricant vane pump according to the invention together with an internal combustion engine wherein a pilot chamber is directly hydraulically connected to a pump outlet via a hydraulic channel defined by a pump housing, and wherein the control valve is provided with a pump outlet pressure.
Figure 1 shows a schematic representation of a lubrication circuit arrangement of an internal combustion engine 100 including a variable lubricant vane pump 102 providing the engine 100 with pressurized lubricant. The lubricant pump 102 is mechanically driven by the engine 100 so that the rotational speed of the lubricant pump 102 is proportional to the rotational speed of the engine 100.
The lubricant pump 102 sucks lubricant with atmospheric pressure PA from a lubricant tank 104 through a pump inlet 106 and provides pressurized lubricant with a pump outlet pressure PO through a pump outlet 108 via a lubricant supply line 110 to the engine 100. The lubricant flows from the engine 100 via a lubricant return line 112 back to the lubricant tank 104. The lubricant pump 102 comprises a pump housing 114 defining an inlet chamber 116, an outlet chamber 118, a pumping chamber 120 with a rotatable pump rotor 122 and with a shiftable control ring 124, a spring chamber 126 with a control ring preload spring 128, and defining a pilot chamber 130. The pump Inlet chamber 116 is provided with lubricant with atmospheric pressure PA via the pump inlet 106. The pump outlet chamber 118 is pressurized with the pump outlet pressure PO and is fluidlca!ly connected to the pump outlet 108.
The pump rotor 122 is located within the control ring 124 and rotates in clockwise direction about a static axis of rotation A. The pump rotor 122 is provided with five rotor vanes 123 being supported radially slidable within corresponding vane slits. The pump housing 114, the control ring 124 and the rotor vanes 123 define five rotating pumping chamber compartments 125.
The control ring 124 is radially supported by the pump housing 114 via two radially protruding plungers 129,131. The control ring 124 fs shiftable exactly linear with respect to the pump rotor 122 whereby the first plunger 129 is moved within the spring chamber 126 and the second plunger 131 is moved within the pilot chamber 130. The volumetric pump performance of the lubricant pump 102 can be controlled by moving the control ring 124 and thereby varying the eccentricity of the pump rotor 122 with respect to the surrounding control ring 124.
The control ring 124 Is preloaded by the control ring preload spring 128 pushing the control ring 124 into a high-eccentricity direction H. As a result, if no other forces in shifting direction of the control ring 124 are effective with respect to the control ring 124, the control ring 124 is pushed into the maximum-eccentricity position providing the maximum volumetric pump performance. The control ring preload spring 128 is provided with a low stiffness to allow low pump set- pressure values.
The control ring 124 is loaded in the high-eccentricity direction H by the pressure of the spring chamber 126. The spring chamber pressure is controlled by a pressure control valve 132. The control valve 132 is a proportional valve and Is f!uidically connected to an engine gallery pressure inlet 134 being provided with an engine gallery pressure PG. The control valve 132 Is also f!uidical!y connected to the lubricant tank 104 via a lubricant outlet 136. As a result, the control valve 132 allows controlling the spring chamber pressure in a pressure range between the atmospheric pressure PA and the engine gallery pressure PG to define and assure different pump set-pressure values. The pressure control valve 132 is controlled by a set- pressure control unit 133 to adapt the pump set pressure to the requirements of the engine. The control ring 124 is loaded In an opposing low-eccentricity direction L by the pressure of the pilot chamber 130. The pilot chamber 130 is f!uid!cally connected to the gallery pressure inlet 134 via a hydraulic pilot chamber load line 138. As a result, the pilot chamber is pressurized with the engine gallery pressure PG.
The radial position of the shiftable control ring 124 depends on the ratio of the spring chamber pressure to the pilot chamber pressure and, as a result, can be controlled via the control valve 132.
During a movement of the control ring 124 the second control ring plunger
131 moves within the pilot chamber 130. As a result, the volume of the pilot chamber 130 changes thereby generating a lubricant flow into or out of the pilot chamber 130 via the pilot chamber load line 138. The pilot chamber load line 138 is provided with a restrictor element 140 restricting the throughput of the pilot chamber load line 138. The restrictor element 140 is provided with a minimum hydraulic cross section in the range of 0.25 mm2 to 4 mm2, whereas all other hydraulic lines have minimum hydraulic cross section of at least 7 mm2. As a result, the lubricant flow rate into/out of the pilot chamber 130 is restricted so that the movement of the control ring 124 is damped. The damping of the control ring 124 movement minimizes the control ring oscillations and, as a result, minimizes the pump outlet pressure fluctuations.
Figure 2 shows a schematic representation of an alternative lubrication circuit arrangement with an alternative variable lubricant vane pump 202 according to the invention. The features of the lubrication circuit and the lubricant pump 202 of figure 2 which correspond with the features of the lubrication circuit and the lubricant pump 102 of figure 1 have a reference number increased by 100. The pressure control valve 232 is fluidically connected to the pump outlet chamber 218 via a valve supply line 242 and fluidically connected to the lubricant tank 204 via the lubricant outlet 236. As a result, the control valve 232 allows controlling the pressure of the spring chamber 230 In a pressure range between the atmospheric pressure PA and the pump outlet pressure PO.
The pilot chamber 230 Is directly fluidically connected to the pump outlet chamber 218 via a pilot chamber load line 238 being defined by the pump housing 214. As a result, the pilot chamber 230 Is pressurized with the pump outlet pressure PO. The pilot chamber load channel 238 is provided with restrictor element 240 being provided by an orifice 241 with a hydraulic cross section In the range of 0.25 mm2 to 1 mm2. The restrictor element 240 restricts the throughput of the pilot chamber load channel 238 and, as a result, damps the movement of the control ring 224,
Reference list
100 Internal combustion engine
102 variable lubricant vane pump
104 lubricant tank
106 pump inlet
108 pump outlet
110 lubricant supply line
112 lubricant return line
114 pump housing
116 Inlet chamber
118 outlet chamber
120 pumping chamber
122 pump rotor
123 rotor vanes
124 shiftable control ring
125 pumping chamber compartments
126 spring chamber
128 control ring preload spring
129 first control ring plunger
130 pilot chamber
131 second control ring plunger
132 pressure control valve
133 set-pressure control unit
134 engine gallery pressure Inlet
136 lubricant outlet
138 pilot chamber load line
140 restrictor element
200 internal combustion engine
202 variable lubricant vane pump
204 lubricant tank
206 pump inlet 208 pump outlet
210 lubricant supply line
212 lubricant return line
214 pump housing
216 inlet chamber
218 outlet chamber
220 pumping chamber
222 pump rotor
223 rotor vanes
224 shiftable control ring
225 pumping chamber compartments
226 spring chamber
228 control ring preload spring
229 first control ring plunger
230 pilot chamber
231 second control ring plunger
232 pressure control valve
233 set-pressure control unit
236 lubricant outlet
238 pilot chamber load line
240 restrictor element
241 orifice
A static axis of rotation
H high-eccentricity direction
L low-eccentricity direction
PA atmospheric pressure
PG engine gallery pressure
PO pump outlet pressure

Claims

C L A I M S
1. A variable lubricant vane pump (102,202) for providing pressurized lubricant with a pump outlet pressure (PO), with
a static pump housing (114,214) defining a pump inlet (106,206) and a pump outlet (108,208),
a shiftable control ring (124,224) being shiftable with respect to a pump rotor (122,222) to thereby vary the eccentricity of the control ring (124,224) with respect to the pump rotor (122,222) for controlling the volumetric pump performance,
the rotatable pump rotor (122,222) comprising several rotor vanes (123,223) rotating within the shiftable control ring (124,224), a control ring preload spring (128,228) arranged within a spring chamber (126,226) preloading and pushing the shiftable control ring (124,224) into a high-eccentricity direction (H),
a pressure control valve (132,232) controlling the spring chamber pressure between a load pressure (PG,PO) and a atmospheric pressure (PA) to thereby define at least two different pump set- pressure values,
a pilot chamber (230) being pressurized with the load pressure (PG,PO) via a pilot chamber load line (138,238) providing the only hydraulic connection of the pilot chamber (130,230), the pilot chamber pressure causing the shiftable control ring (124,224) to move against the control ring preload spring (128,228) into a low- eccentricity direction (L), and
a hydraulic restrictor element (140,240) restricting the throughput of the pilot chamber load channel (138,238).
2. The variable lubricant vane pump (102) of claim 1, wherein the load pressure is an engine gallery pressure (PG).
3. The variable lubricant vane pump (202) of claim 1, wherein the load pressure is the pump outlet pressure (PO).
4. The variable lubricant vane pump (202) of claim 3, wherein the pilot chamber load line (238) is defined by the pump housing (214) and directly f!uldica!ly connects the pump outlet (208) to the pilot chamber (230).
5. The variable lubricant vane pump (102,202) of any preceding claim, wherein the restrictor element (140,240) is provided with a hydraulic cross section between 0.25 mm2 and 4 mm2.
6. The variable lubricant vane pump (102,202) of any preceding claim, wherein the pressure control valve (132,232) is a proportional valve.
7. The variable lubricant vane pump (102,202) of any preceding claim, wherein the shiftable control ring (124,224) is provided shiftable exactly linear with respect to the pump rotor (122,222).
8. The variable lubricant vane pump (102,202) of any preceding claim, wherein the lubricant pump (102,202) is provided with a set- pressure control unit (133,233) controlling the pressure control valve (132,232).
EP17816761.5A 2017-12-13 2017-12-13 Variable lubricant vane pump Active EP3724504B1 (en)

Applications Claiming Priority (1)

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PCT/EP2017/082638 WO2019114948A1 (en) 2017-12-13 2017-12-13 Variable lubricant vane pump

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EP3724504B1 EP3724504B1 (en) 2023-06-28

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US2742861A (en) * 1950-12-26 1956-04-24 Houdaille Industries Inc Stabilized variable displacement pump
US20160290335A1 (en) 2013-11-21 2016-10-06 Pierburg Pump Technology Gmbh Variable displacement lubricant pump
US10563652B2 (en) * 2014-07-18 2020-02-18 Melling Tool Company Variable displacement vane pump
JP2017137854A (en) 2016-01-29 2017-08-10 株式会社山田製作所 Variable displacement vane pump
CN109690023B (en) * 2016-10-12 2021-11-16 皮尔伯格泵技术有限责任公司 Automatic variable mechanical lubricating oil pump

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JP2020537086A (en) 2020-12-17
WO2019114948A1 (en) 2019-06-20
EP3724504B1 (en) 2023-06-28

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