WO2012113437A1 - A variable displacement lubricant pump with a pressure control valve having a preload control arrangement - Google Patents

A variable displacement lubricant pump with a pressure control valve having a preload control arrangement Download PDF

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Publication number
WO2012113437A1
WO2012113437A1 PCT/EP2011/052490 EP2011052490W WO2012113437A1 WO 2012113437 A1 WO2012113437 A1 WO 2012113437A1 EP 2011052490 W EP2011052490 W EP 2011052490W WO 2012113437 A1 WO2012113437 A1 WO 2012113437A1
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WO
WIPO (PCT)
Prior art keywords
preload
control
pressure
plunger
pump
Prior art date
Application number
PCT/EP2011/052490
Other languages
French (fr)
Inventor
Carmine Cuneo
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
Priority to CN201180068194.3A priority Critical patent/CN103380300B/en
Priority to US13/983,576 priority patent/US9394891B2/en
Priority to EP11706793.4A priority patent/EP2678565B1/en
Priority to JP2013554797A priority patent/JP5762573B2/en
Priority to PCT/EP2011/052490 priority patent/WO2012113437A1/en
Publication of WO2012113437A1 publication Critical patent/WO2012113437A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/05—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by internal-combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • 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
    • 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
    • F04C2/3441—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 the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3442—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 the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
    • 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
    • F04C2210/00—Fluid
    • F04C2210/20—Fluid liquid, i.e. incompressible
    • F04C2210/206—Oil
    • 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

  • the present invention refers to a variable displacement lubricant pump for providing pressurized lubricant for an Internal combustion engine.
  • the mechanical pump comprises a pump rotor with radially slidable vanes rotating in a radially shiftable control ring, whereby the control ring is pushed by a first control chamber Into high pumping volume direction.
  • the pump comprises a pressure control system for controlling the discharge pressure of the pressurized lubricant at the pump outlet port.
  • the pump is provided with a first pressure conduit which connects the pump outlet port with the first control chamber, and the pump is also provided with a pressure control valve which controls the pressure in the first pressure control chamber.
  • a variable displacement lubricant pump of the state of the art is known from WO 2005/026553 Al.
  • the pressure control valve keeps the pressure of the pressurized lubricant provided by the pump at a more or less constant level, independent of the rotational speed of the pump rotor. This is realized by opening and closing a pressure control port of the control valve, whereby the pressure control chamber of the pump is connected or disconnected to the atmospheric pressure in the lubricant tank.
  • the lubricant pressure demand of the engine is not constant but depends on some working conditions of the engine, for example the lubricant temperature and the rotational speed of the engine.
  • variable-displacement lubricant vane pump with the features of claim 1.
  • the variable displacement lubricant pump is provided with a pump rotor with radially slidable vanes rotating in a shiftable control ring.
  • the pump is provided with a first pressure control chamber for pushing the control ring into a high pumping volume direction.
  • the first pressure control chamber is connected to the pump outlet port by the first pressure conduit.
  • the pressure control valve for controlling the pressure in the first pressure control chamber comprises a control plunger, an input pressure plunger and a control spring.
  • the control plunger opens and closes a control port in a cylinder wall of the control valve.
  • the control port is connected with an outlet port of the control chamber.
  • the pressure in the first pressure control chamber increases so that the control ring is pushed into high pumping volume direction.
  • the pressure in the first pressure control chamber decreases to more or less atmospheric pressure so that the control ring can move into a low pumping volume direction.
  • the position of the control plunger is determined by the lubricant discharge pressure of the pump which is directed to an input pressure plunger which is charged with the pump outlet pressure.
  • the input pressure plunger is directly connected with the control plunger.
  • a control spring is provided which preloads the control plunger Into a closed position against the pump outlet pressure charging the input pressure plunger. The spring force of the control spring and the pump outlet pressure acting on the input pressure plunger force the control plunger into an equilibrium position.
  • the pump is provided with a preload control arrangement for controlling the preload of the control spring.
  • the preload control arrangement comprises a preload plunger, a preload cylinder inlet and the preload control valve.
  • the preload plunger is axially moving in the preload cylinder and supports the basis of the control spring so that the spring pretension of the control plunger can be varied between two values.
  • the preload plunger is axlally arranged in the preload cylinder, whereby the cylinder is provided with pressurized lubricant which can be the pressurized lubricant of the pump outlet port.
  • the preload control valve can charge the preload cylinder with the pressure of the pressurized lubricant so that the preload plunger is moved Into a high preload position which is a high nominal pressure position as well.
  • the preload control valve can provide a more or less atmospheric pressure In the preload cylinder so that the preload plunger moves into and maintains In a low preload position which is the low nominal pressure position.
  • the preload control valve can be provided between the pump outlet port and the preload cylinder inlet, whereby the preload cylinder outlet is connected to atmospheric pressure via a throttle valve.
  • the preload cylinder outlet is connected to the lubricant tank by a preload control discharge conduit, whereby the preload control valve Is provided in line with the preload control discharge conduit so that the preload control valve Is provided between the preload cylinder outlet and atmospheric pressure.
  • a throttle valve is provided in line with the preload control charge conduit which connects the pump outlet port with the preload cylinder inlet.
  • control valve cylinder wall and the preload cylinder are parts of one single Integrated valve housing. This makes the production and assembling of the pump, and in particular of the pressure control valve including the preload control arrangement, simple and cost effective.
  • a ventilation port is provided In the valve housing axlally between the control plunger and the preload plunger.
  • the ventilation port is arranged In a position outside the movement range of the control plunger and the preload plunger so that the ventilation port is never blocked or closed by said plungers.
  • the ventilation port allows a variation of the cavity between the control plunger, the preload plunger and the valve housing.
  • the ventilation port is connected to the lubricant tank.
  • the axial distal side of the preload plunger is provided with an offset nose for keeping the preload plunger always at a minimum distance from the preload cylinder front end wall.
  • This arrangement avoids a direct contact of the plane front end of the preload plunger with the plane cylinder front end wall. Since the preload cylinder outlet is preferably provided in the cylinder front end wall, the offset nose of the preload plunger avoids a blocking of the preload cylinder outlet.
  • the preload plunger is provided with a spring guide sleeve at the proximal side of the preload plunger.
  • the basis of the control spring is radially supported by the spring guide sleeve so that slipping of the control spring basis at the preload plunger Is avoided.
  • the preload cylinder is larger in diameter than the control valve cylinder wall, and the step between them Is defining a stop ring for the preload plunger.
  • figure 1 shows a lubricant pumping system including a variable displacement vane pump and a control valve, and figure 2 the control valve of figure 1 in a detailed longitudinal section.
  • FIG. 1 shows a schematic representation of a variable displacement lubricant pump 10 as a part of a pumping system 100 for supplying an Internal combustion engine 70 with pressurized lubricant.
  • the pump 10 is mechanically directly driven by the engine 70 and comprises a pump housing 11 having a cavity 16 in which a radially shiftable control ring 12 translates.
  • the control ring 12 encircles a pump rotor 13 which is provided with numerous radially slidable vanes 14, whereby the vanes 14 are rotating Inside the shiftable control ring 12.
  • the pump housing 11 is closed by two pump side walls 15 of which one Is not shown in the drawing.
  • the pump side walls 15, the vanes 14, the pump rotor 13 and the control ring 12 define five rotating pump chambers 17.
  • One of the side walls 15 is provided with a pump chamber inlet opening 18 and with a pump chamber outlet opening 19.
  • the control ring 12 is provided with a first control ring plunger 24 housed in part in a first pressure control chamber 25 and Is provided with a second control ring plunger 22 housed in part in a second control chamber 23 opposite the first pressure control chamber 25.
  • the plungers 22, 24 are prismatic in cross section.
  • the control ring 12 and the plungers 22, 24 are one single Integral part.
  • Both control chambers 25, 23 are defined by the pump housing 11.
  • the pump housing 11 also comprises a pump inlet port 20 for sucking the lubricant from a lubricant tank 50 and a pump outlet port 21 for feeding lubricant with a discharge pressure to the engine 70.
  • An engine supply conduit 80 extends from the pump outlet port 21 to the engine 70 to supply the engine 70 with pressurized lubricant.
  • the lubricant discharge pressure at the pump outlet port 21 is transmitted to the second control chamber 23 via a pressure conduit 81. Additionally, the lubricant leaving the pump outlet port 21 is conducted to the first pressure control chamber 25 via a conduits 82,87 and through a pressure throttle valve 67 In which a calibrated pressure drop occurs as the lubricant flows through.
  • the pump outlet port 21 Is also connected to an Input pressure port 61 of a pressure control valve 60 by a conduit 82,88.
  • the pressure control valve 60 keeps the outlet pressure at the pump outlet port 21 at a constant nominal pressure value independently of the rotational speed of the engine 70 by regulating the radial position of the control ring 12.
  • the radial position of the control ring 12 is controlled by controlling the pressure in the first control chamber 25.
  • the pressure control valve 60 is able to control two different nominal pressure values by changing the position of a preload plunger 42 serving as a basis for a control spring 68.
  • the control valve 60 is provided with a single integral valve housing 90 which comprises two different functional parts, i.e. a pressure control arrangement 94 and the preload control arrangement 30.
  • the valve housing 90 is provided with two different cylindrical parts of different diameters: the pressure control cylinder wall 65 with a low diameter housing the pressure control arrangement 94 and the preload cylinder 31 with a higher diameter housing the preload plunger 42.
  • the transition between the preload cylinder 31 and the pressure control cylinder wall 36 is realized by a circular stop ring 41 with a radial ring-like surface.
  • the pressure control arrangement 94 inside the cylinder wail 65 is one integral part which is axially shiftable and which consists of an input pressure plunger 62, a control plunger 64 and a plunger shaft 63 connecting the input pressure plunger 62 and the control plunger 64.
  • the Input pressure plunger 62 is charged with the pump discharge pressure via the input pressure port 61.
  • the pump discharge pressure pushing the input pressure plunger 62 is acting against the spring force of a control spring 68 axially pushing the control plunger 64.
  • the pressure control arrangement 94 controls the discharge of the first control chamber 25 via conduit 83 by closing and opening a control port 66 in the cylinder wall 65.
  • the control plunger 64 closes the control port 66 in a closing position and opens the control port 66 in the open position. In an open position of the control plunger 64 the lubricant of the control chamber 25 can be discharged via a conduit 83, the control port 66, a control valve discharge port 97 and a discharge conduit 84 to the lubric
  • the basis of the control spring 68 is supported by the preload plunger 42 which is axially shiftable within the preload cylinder 31.
  • the preload plunger 42 can be switched between two axial positions, i.e. a high discharge pressure position in which the control spring 68 is compressed and a discharge pressure position in which the control spring 68 is expanded.
  • the preload plunger 42 is provided with a cylindrical plunger body 44 which is provided with an offset nose 45 at the distal axial side and with a cylindrical spring guide sleeve 43 at the proximal side of the plunger body 44.
  • the offset nose 45 guarantees a minimum distance of the plunger body 44 with respect to the front end wall 42 of the preload cylinder 31. This minimum distance guarantees that the inlet 34 and the outlet 36 can never be blocked or closed by the plunger body 44.
  • the cylindrical spring guide sleeve 43 centers the basis of the control spring 68 at the plunger body 44 so that the control spring 68 can not be jammed between the preload plunger 42 and the stop ring 41.
  • the outer diameter of the spring guide sleeve 43 is less than the inner diameter of the cylinder wall 65.
  • the preload cylinder outlet 36 is connected to the lubricant tank 50 by a preload control discharge conduit 40, whereby the preload control valve 38 is provided in line with the preload control discharge conduit 40.
  • the preload cylinder Inlet 34 Is connected to the pump outlet port 21 via a preload control charge conduit 32, whereby the throttle valve 33 Is provided In line with the preload control charge conduit 32.
  • the preload control valve 38 is closed, the lubricant with the pump discharge pressure pushes the preload plunger 42 up Into the high discharge pressure position.
  • the preload control valve 38 is open, the lubricant inside the preload cylinder 31 is discharged to the lubricant tank 50 so that the preload plunger 42 moves into a low discharge pressure position as shown in figure 2.
  • the preload control valve 38 is a solenoid valve and is controlled by a digital engine control unit (not shown) which adapts the nominal discharge pressure dependent on, for example, the lubricant temperature, the engine temperature etc.
  • the cylinder wall 65 is provided with a ventilation port 46 which is connected via a ventilation conduit 48 with the lubricant tank 50 so that the pressure in the cavity between the control plunger 64 and the preload plunger 42 is always at a more or less atmospheric pressure.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Rotary Pumps (AREA)

Abstract

The present disclosure refers to a variable displacement lubricant pump (10) for providing pressurized lubricant for an internal combustion engine (70). The mechanical pump ( 10) comprises a pump rotor (13) with radially slidable vanes (14) rotating in a shiftable control ring (12). A pressure control system for controlling the discharge pressure of the pressurized lubricant comprises: a first pressure control chamber (25), a first pressure conduit (82, 87), and a pressure control valve (60). The pressure control valve (60) comprises: a control plunger (64), an input pressure plunger (62), and a control spring (68). A preload control arrangement (30) for controlling the preload of the control spring (68) comprises: a preload plunger (42) axially moving in a preload cylinder (31) and supporting the basis of the control spring (68), a preload cylinder inlet (34) for providing pressurized lubricant into the preload cylinder (31), and a preioad control valve (38) for controlling the lubricant pressure in the preload cylinder (31).

Description

A VARIABLE DISPLACEMENT LUBRICANT PUMP WITH A PRESSURE CONTROL VALVE HAVING A PRELOAD CONTROL ARRANGEMENT
The present invention refers to a variable displacement lubricant pump for providing pressurized lubricant for an Internal combustion engine.
The mechanical pump comprises a pump rotor with radially slidable vanes rotating in a radially shiftable control ring, whereby the control ring is pushed by a first control chamber Into high pumping volume direction. The pump comprises a pressure control system for controlling the discharge pressure of the pressurized lubricant at the pump outlet port. The pump is provided with a first pressure conduit which connects the pump outlet port with the first control chamber, and the pump is also provided with a pressure control valve which controls the pressure in the first pressure control chamber.
A variable displacement lubricant pump of the state of the art is known from WO 2005/026553 Al. The pressure control valve keeps the pressure of the pressurized lubricant provided by the pump at a more or less constant level, independent of the rotational speed of the pump rotor. This is realized by opening and closing a pressure control port of the control valve, whereby the pressure control chamber of the pump is connected or disconnected to the atmospheric pressure in the lubricant tank. However, the lubricant pressure demand of the engine is not constant but depends on some working conditions of the engine, for example the lubricant temperature and the rotational speed of the engine.
It is an object of the present invention to provide a variable displacement lubricant pump with a simple control system which provides two levels of nominal pressure of the pressurized lubricant leaving the pump.
This object is solved with a variable-displacement lubricant vane pump with the features of claim 1. The variable displacement lubricant pump is provided with a pump rotor with radially slidable vanes rotating in a shiftable control ring. The pump is provided with a first pressure control chamber for pushing the control ring into a high pumping volume direction. The first pressure control chamber is connected to the pump outlet port by the first pressure conduit. The pressure control valve for controlling the pressure in the first pressure control chamber comprises a control plunger, an input pressure plunger and a control spring. The control plunger opens and closes a control port in a cylinder wall of the control valve. The control port is connected with an outlet port of the control chamber.
When the control plunger blocks and closes the control port, the pressure in the first pressure control chamber increases so that the control ring is pushed into high pumping volume direction. When the control plunger does not close the control port of the pressure control valve, the pressure in the first pressure control chamber decreases to more or less atmospheric pressure so that the control ring can move into a low pumping volume direction.
The position of the control plunger is determined by the lubricant discharge pressure of the pump which is directed to an input pressure plunger which is charged with the pump outlet pressure. The input pressure plunger is directly connected with the control plunger. A control spring is provided which preloads the control plunger Into a closed position against the pump outlet pressure charging the input pressure plunger. The spring force of the control spring and the pump outlet pressure acting on the input pressure plunger force the control plunger into an equilibrium position.
The pump is provided with a preload control arrangement for controlling the preload of the control spring. The preload control arrangement comprises a preload plunger, a preload cylinder inlet and the preload control valve. The preload plunger is axially moving in the preload cylinder and supports the basis of the control spring so that the spring pretension of the control plunger can be varied between two values. The preload plunger is axlally arranged in the preload cylinder, whereby the cylinder is provided with pressurized lubricant which can be the pressurized lubricant of the pump outlet port. The preload control valve can charge the preload cylinder with the pressure of the pressurized lubricant so that the preload plunger is moved Into a high preload position which is a high nominal pressure position as well. Alternatively, the preload control valve can provide a more or less atmospheric pressure In the preload cylinder so that the preload plunger moves into and maintains In a low preload position which is the low nominal pressure position.
The concept and the construction of this preload control arrangement is simple and guarantees high reliability and a long mechanical life.
In principle, the preload control valve can be provided between the pump outlet port and the preload cylinder inlet, whereby the preload cylinder outlet is connected to atmospheric pressure via a throttle valve. Preferably, the preload cylinder outlet is connected to the lubricant tank by a preload control discharge conduit, whereby the preload control valve Is provided in line with the preload control discharge conduit so that the preload control valve Is provided between the preload cylinder outlet and atmospheric pressure. Preferably, a throttle valve is provided in line with the preload control charge conduit which connects the pump outlet port with the preload cylinder inlet.
According to a preferred embodiment, the control valve cylinder wall and the preload cylinder are parts of one single Integrated valve housing. This makes the production and assembling of the pump, and in particular of the pressure control valve including the preload control arrangement, simple and cost effective.
Preferably a ventilation port is provided In the valve housing axlally between the control plunger and the preload plunger. The ventilation port is arranged In a position outside the movement range of the control plunger and the preload plunger so that the ventilation port is never blocked or closed by said plungers. The ventilation port allows a variation of the cavity between the control plunger, the preload plunger and the valve housing. Preferably, the ventilation port is connected to the lubricant tank.
According to a preferred embodiment, the axial distal side of the preload plunger is provided with an offset nose for keeping the preload plunger always at a minimum distance from the preload cylinder front end wall. This arrangement avoids a direct contact of the plane front end of the preload plunger with the plane cylinder front end wall. Since the preload cylinder outlet is preferably provided in the cylinder front end wall, the offset nose of the preload plunger avoids a blocking of the preload cylinder outlet.
Preferably the preload plunger is provided with a spring guide sleeve at the proximal side of the preload plunger. The basis of the control spring is radially supported by the spring guide sleeve so that slipping of the control spring basis at the preload plunger Is avoided.
According to a preferred embodiment, the preload cylinder is larger in diameter than the control valve cylinder wall, and the step between them Is defining a stop ring for the preload plunger.
The following is a detailed description of an embodiment of the invention with reference to the drawings, wherein:
figure 1 shows a lubricant pumping system including a variable displacement vane pump and a control valve, and figure 2 the control valve of figure 1 in a detailed longitudinal section.
Figure 1 shows a schematic representation of a variable displacement lubricant pump 10 as a part of a pumping system 100 for supplying an Internal combustion engine 70 with pressurized lubricant. The pump 10 is mechanically directly driven by the engine 70 and comprises a pump housing 11 having a cavity 16 in which a radially shiftable control ring 12 translates.
The control ring 12 encircles a pump rotor 13 which is provided with numerous radially slidable vanes 14, whereby the vanes 14 are rotating Inside the shiftable control ring 12. The pump housing 11 is closed by two pump side walls 15 of which one Is not shown in the drawing. The pump side walls 15, the vanes 14, the pump rotor 13 and the control ring 12 define five rotating pump chambers 17. One of the side walls 15 is provided with a pump chamber inlet opening 18 and with a pump chamber outlet opening 19.
The control ring 12 is provided with a first control ring plunger 24 housed in part in a first pressure control chamber 25 and Is provided with a second control ring plunger 22 housed in part in a second control chamber 23 opposite the first pressure control chamber 25. The plungers 22, 24 are prismatic in cross section. The control ring 12 and the plungers 22, 24 are one single Integral part.
A pretensioned control chamber spring 28 inside the first pressure control chamber 25 exerts a pushing force to the first plunger 24. Both control chambers 25, 23 are defined by the pump housing 11. The pump housing 11 also comprises a pump inlet port 20 for sucking the lubricant from a lubricant tank 50 and a pump outlet port 21 for feeding lubricant with a discharge pressure to the engine 70. An engine supply conduit 80 extends from the pump outlet port 21 to the engine 70 to supply the engine 70 with pressurized lubricant.
The lubricant discharge pressure at the pump outlet port 21 is transmitted to the second control chamber 23 via a pressure conduit 81. Additionally, the lubricant leaving the pump outlet port 21 is conducted to the first pressure control chamber 25 via a conduits 82,87 and through a pressure throttle valve 67 In which a calibrated pressure drop occurs as the lubricant flows through.
The pump outlet port 21 Is also connected to an Input pressure port 61 of a pressure control valve 60 by a conduit 82,88. The pressure control valve 60 keeps the outlet pressure at the pump outlet port 21 at a constant nominal pressure value independently of the rotational speed of the engine 70 by regulating the radial position of the control ring 12. The radial position of the control ring 12 is controlled by controlling the pressure in the first control chamber 25.
The pressure control valve 60 is able to control two different nominal pressure values by changing the position of a preload plunger 42 serving as a basis for a control spring 68. The control valve 60 is provided with a single integral valve housing 90 which comprises two different functional parts, i.e. a pressure control arrangement 94 and the preload control arrangement 30. The valve housing 90 is provided with two different cylindrical parts of different diameters: the pressure control cylinder wall 65 with a low diameter housing the pressure control arrangement 94 and the preload cylinder 31 with a higher diameter housing the preload plunger 42. The transition between the preload cylinder 31 and the pressure control cylinder wall 36 is realized by a circular stop ring 41 with a radial ring-like surface.
The pressure control arrangement 94 inside the cylinder wail 65 is one integral part which is axially shiftable and which consists of an input pressure plunger 62, a control plunger 64 and a plunger shaft 63 connecting the input pressure plunger 62 and the control plunger 64. The Input pressure plunger 62 is charged with the pump discharge pressure via the input pressure port 61. The pump discharge pressure pushing the input pressure plunger 62 is acting against the spring force of a control spring 68 axially pushing the control plunger 64. The pressure control arrangement 94 controls the discharge of the first control chamber 25 via conduit 83 by closing and opening a control port 66 in the cylinder wall 65. The control plunger 64 closes the control port 66 in a closing position and opens the control port 66 in the open position. In an open position of the control plunger 64 the lubricant of the control chamber 25 can be discharged via a conduit 83, the control port 66, a control valve discharge port 97 and a discharge conduit 84 to the lubricant tank 50.
The basis of the control spring 68 is supported by the preload plunger 42 which is axially shiftable within the preload cylinder 31. The preload plunger 42 can be switched between two axial positions, i.e. a high discharge pressure position in which the control spring 68 is compressed and a discharge pressure position in which the control spring 68 is expanded.
The preload plunger 42 is provided with a cylindrical plunger body 44 which is provided with an offset nose 45 at the distal axial side and with a cylindrical spring guide sleeve 43 at the proximal side of the plunger body 44. The offset nose 45 guarantees a minimum distance of the plunger body 44 with respect to the front end wall 42 of the preload cylinder 31. This minimum distance guarantees that the inlet 34 and the outlet 36 can never be blocked or closed by the plunger body 44. The cylindrical spring guide sleeve 43 centers the basis of the control spring 68 at the plunger body 44 so that the control spring 68 can not be jammed between the preload plunger 42 and the stop ring 41. The outer diameter of the spring guide sleeve 43 is less than the inner diameter of the cylinder wall 65. The axial movement of the preload plunger 42 is restricted by the front end wall 92 at one side and by the stop ring 41 at the other side.
The preload cylinder outlet 36 is connected to the lubricant tank 50 by a preload control discharge conduit 40, whereby the preload control valve 38 is provided in line with the preload control discharge conduit 40. The preload cylinder Inlet 34 Is connected to the pump outlet port 21 via a preload control charge conduit 32, whereby the throttle valve 33 Is provided In line with the preload control charge conduit 32. When the preload control valve 38 is closed, the lubricant with the pump discharge pressure pushes the preload plunger 42 up Into the high discharge pressure position. When the preload control valve 38 is open, the lubricant inside the preload cylinder 31 is discharged to the lubricant tank 50 so that the preload plunger 42 moves into a low discharge pressure position as shown in figure 2. The preload control valve 38 is a solenoid valve and is controlled by a digital engine control unit (not shown) which adapts the nominal discharge pressure dependent on, for example, the lubricant temperature, the engine temperature etc.
The cylinder wall 65 is provided with a ventilation port 46 which is connected via a ventilation conduit 48 with the lubricant tank 50 so that the pressure in the cavity between the control plunger 64 and the preload plunger 42 is always at a more or less atmospheric pressure.

Claims

C L A I M S
A variable displacement lubricant pump (10) coupled to and driven by an internal combustion engine (70) for pumping pressurized lubricant to the engine (70), comprising:
a pump rotor (13) with radially slidable vanes (14) rotating in a shiftable control ring (12),
a pressure control system for controlling the discharge pressure of the pressurized lubricant, the control system comprising a first pressure control chamber (25) for pushing the control ring (12) into high pumping volume direction,
a first pressure conduit (82, 87) connecting a pump outlet port (21) with the first control chamber (25), and
a pressure control valve (60) controlling the pressure in the first pressure control chamber (25), the pressure control valve (60) comprising:
a control plunger (64) for opening and closing a control port (66) In a cylinder wall (65) of the control valve (60), whereby the control port (66) is connected with an outlet port (99) of the control chamber (25),
an Input pressure plunger (62) being charged with the pump outlet pressure and being connected with the control plunger (64), and
a control spring (68) preloading the control plunger (64) into a closed position against the pump outlet pressure,
characterised by a preload control arrangement (30) for controlling the preload of the control spring (68), the preload control arrangement comprising: a preload plunger (42) axlally moving in a preload cylinder (31) and supporting the basis of the control spring (68),
a preload cylinder Inlet (34) for providing pressurized lubricant into the preload cylinder (31), and
a preload control valve (38) for controlling the lubricant pressure in the preload cylinder (31).
The variable displacement lubricant pump (10) of claim 1, wherein a preload cylinder outlet (36) is provided which Is connected to a lubricant tank (50) by a preload control discharge conduit (40), whereby the preload control valve (38) Is provided in line with the preload control discharge conduit (40).
The variable displacement lubricant pump (10) of claim 1 or 2, wherein the preload control charge conduit (32) is provided between the pump outlet port (21) and the preload cylinder inlet (34), whereby the throttle valve (33) Is provided in line with the preload control charge conduit (32).
The variable displacement lubricant pump (10) of one of the preceding claims, whereby the control valve cylinder wall (65) and the preload cylinder (31) are parts of one single Integral valve housing (90).
The variable displacement lubricant pump (10) of one of the preceding claims, wherein a ventilation port (46) is provided in the valve housing between the control plunger (64) and the preload plunger (42). The variable displacement lubricant pump (10) of one of the preceding claims, whereby the distal side of the preload plunger (42) is provided with an offset nose (45) for keeping the preload plunger (42) always at a minimum distance from a preload cylinder front end wall (92) wherein the preload cylinder outlet (36) is provided.
The variable displacement lubricant pump (10) of one of the preceding claims, wherein the preload plunger (42) is provided with a spring guide sleeve (43) at its proximal side.
The variable displacement lubricant pump (10) of one of the preceding claims, wherein the preload cylinder (31) is larger in diameter than the control valve cylinder wall (65) and the step between them is defining a stop ring (41) for the preload plunger.
PCT/EP2011/052490 2011-02-21 2011-02-21 A variable displacement lubricant pump with a pressure control valve having a preload control arrangement WO2012113437A1 (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CN201180068194.3A CN103380300B (en) 2011-02-21 2011-02-21 Comprise the variable-displacement lubricant pump of the pressure controlled valve with preloading control gear
US13/983,576 US9394891B2 (en) 2011-02-21 2011-02-21 Variable displacement lubricant pump with a pressure control valve having a preload control arrangement
EP11706793.4A EP2678565B1 (en) 2011-02-21 2011-02-21 A variable displacement lubricant pump with a pressure control valve having a preload control arrangement
JP2013554797A JP5762573B2 (en) 2011-02-21 2011-02-21 Variable displacement lubricating oil pump having a pressure control valve with a preload control device
PCT/EP2011/052490 WO2012113437A1 (en) 2011-02-21 2011-02-21 A variable displacement lubricant pump with a pressure control valve having a preload control arrangement

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EP2678565A1 (en) 2014-01-01
EP2678565B1 (en) 2018-04-04
CN103380300A (en) 2013-10-30
CN103380300B (en) 2016-01-13
JP5762573B2 (en) 2015-08-12
US20140030120A1 (en) 2014-01-30
US9394891B2 (en) 2016-07-19
JP2014506655A (en) 2014-03-17

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