WO2010006705A2 - Pompe à cylindrée variable - Google Patents

Pompe à cylindrée variable Download PDF

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Publication number
WO2010006705A2
WO2010006705A2 PCT/EP2009/004772 EP2009004772W WO2010006705A2 WO 2010006705 A2 WO2010006705 A2 WO 2010006705A2 EP 2009004772 W EP2009004772 W EP 2009004772W WO 2010006705 A2 WO2010006705 A2 WO 2010006705A2
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
variable displacement
displacement pump
control
pump according
Prior art date
Application number
PCT/EP2009/004772
Other languages
German (de)
English (en)
Other versions
WO2010006705A8 (fr
WO2010006705A3 (fr
Inventor
Doan Van Nguyen
Hans Jürgen LAUTH
Original Assignee
Ixetic Bad Homburg 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 Ixetic Bad Homburg Gmbh filed Critical Ixetic Bad Homburg Gmbh
Priority to ES09776916.0T priority Critical patent/ES2567089T3/es
Priority to DE112009001577T priority patent/DE112009001577A5/de
Priority to EP09776916.0A priority patent/EP2307726B1/fr
Publication of WO2010006705A2 publication Critical patent/WO2010006705A2/fr
Publication of WO2010006705A3 publication Critical patent/WO2010006705A3/fr
Publication of WO2010006705A8 publication Critical patent/WO2010006705A8/fr

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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
    • 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
    • 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
    • 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
    • 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
    • F04C2270/52—Conditions after a throttle
    • 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
    • F04C2270/58—Valve parameters

Definitions

  • the invention relates to a variable displacement pump with a cam ring which is adjustable in dependence on the pressure in a first Verstelldruckraum and a second Verstelldruckraum, and with a flow regulator, which is designed as a slide valve with a plurality of control edges having flow control piston which is acted upon by a differential pressure, which prevails before and after a hydraulic resistance in a high-pressure area, and with a pressure valve.
  • the object of the invention is a variable displacement pump with a cam ring which is adjustable in dependence on the pressure in a first Verstell réelleraum and a second Verstell réelleraum, and with a flow regulator, which is designed as a slide valve with a plurality of control edges having flow control piston, with a differential pressure is applied, which prevails before and after a hydraulic resistance in a high-pressure area, and with a pressure valve, in order to optimize the stability and dynamics of the pressure control.
  • the object is with a variable displacement pump with a cam ring which is adjustable in dependence on the pressure in a first Verstelldruckraum and a second Verstelldruckraum, and with a flow regulator, which is designed as a slide valve with a plurality of control edges having flow control piston which is acted upon by a differential pressure , which prevails before and after a hydraulic resistance in a high-pressure region, and with a pressure valve, achieved in that the pressure valve is designed as a slide valve with a pressure regulating piston having a pressure control edge and is applied to a pressure control surface with the pressure before or possibly behind the hydraulic resistance in the high-pressure area prevails.
  • the hydraulic resistor is preferably arranged in an output line or delivery line of the variable displacement pump.
  • both the flow regulator and the pressure valve are designed as a piston valve or piston valve.
  • Such valves are used in hydraulic controls to regulate high pressures and high volume flows with relatively little effort in a small volume of construction.
  • the pressure valve is not designed directly as a pressure relief valve or pressure relief valve, but as a pressure regulator to regulate the adjustment pressure in one of the Verstell horrinsta depending on the pressure between the working pressure chamber, in particular a pressure kidney, the variable displacement pump and the output line or promotion line prevails.
  • the combination of the two designed as a slide valve regulator ensures that the pumped amount of the variable can be kept largely constant regardless of the pump speed and the load pressure.
  • the pump pressure is regulated via the pressure regulator with the help of the cam ring. This can reduce the power consumption of the pump and avoid the risk of overheating the pump at maximum pressure.
  • both the amount provided by the variable displacement pump or the volume flow provided by the variable displacement pump and the pressure provided by the variable displacement pump can be varied in a simple manner.
  • the use of two independently operating valve pistons allows the volume and pressure control to be optimized separately, thus satisfying the high requirements regarding control quality and dynamics.
  • the variable displacement pump according to the invention is compact and inexpensive to produce.
  • the hydraulic resistance is preferably a fixed or constant hydraulic resistance, such as a constant diameter orifice or restrictor.
  • variable displacement pump is characterized in that the pressure valve in dependence on the pressure prevailing between the working pressure chamber of the variable displacement and the hydraulic resistance, via the flow regulator with one of the Verstelldruckschreib is connectable to regulate the pressure before the hydraulic resistance.
  • the volume control is isolated from the pressure control or independent, and therefore, the valve components for the flow regulator and the pressure regulator can be optimized independently.
  • variable displacement pump is characterized in that one of the Verstelldruckschreib via the flow regulator and an outlet throttle with a Pressure relief space or tank communicates.
  • the outlet throttle allows a pressure reduction in the associated adjustment pressure chamber.
  • variable displacement pump is characterized in that the pressure regulating piston of the pressure valve has exactly one control edge.
  • the equipped with this pressure regulating piston pressure regulator is also referred to as a single edge regulator.
  • variable displacement pump is characterized in that the flow control piston of the flow regulator has exactly two control edges.
  • An equipped with such a flow control piston flow regulator is also referred to as a two-edge controller.
  • variable displacement pump is characterized in that the flow control piston of the flow regulator has four control edges.
  • An equipped with such a flow control piston flow regulator is also referred to as a four-edge regulator.
  • a further preferred embodiment of the variable displacement pump is characterized in that the flow regulator is combined with the pressure valve so that the pressure upstream of the hydraulic resistance can be regulated independently of the volume flow through the hydraulic resistance via the adjustable lifting ring.
  • the pressure before the hydraulic resistance is the pressure that prevails between the working pressure chamber of the variable displacement pump and the hydraulic resistance.
  • the pressure valve is designed according to an essential aspect of the invention as a pressure regulator, which operates separately from the flow regulator and can be tuned. The invention makes it possible in a simple manner to vary both the volume flow, that is to say the quantity, and the pressure of the variable displacement pump.
  • variable displacement pump is characterized in that the pressure valve has a pressure connection, in particular a pressure connection groove or a pressure connection bore, which can be acted upon by the pressure between the working pressure chamber of the variable displacement pump and the hydraulic pressure dependent on the position of the pressure control edge Resistance prevails.
  • a connection between the pressure connection and the working pressure chamber of the variable displacement pump is through the pressure control edge or one associated piston land on the pressure control piston interrupted.
  • a connection is released from the working pressure chamber of the variable displacement pump via the pressure connection to one of the adjustment pressure chambers.
  • a further preferred exemplary embodiment of the variable displacement pump is characterized in that the pressure connection is connected to a connection connection provided on the flow regulator, in particular a connecting groove or connecting bore, which in turn communicates with one of the adjusting pressure chambers.
  • the connection port is preferably in communication with a pressure relief space, such as a tank, via an additional throttle.
  • variable displacement pump is characterized in that the pressure valve is integrated in the flow regulator. This space can be saved.
  • a further preferred exemplary embodiment of the variable displacement pump is characterized in that the pressure regulating piston can be moved back and forth inside the flow control piston. This provides, among other things, the advantage that the two pistons can be accommodated in a single receiving space or cylinder and connecting lines between the pressure valve and the flow regulator omitted.
  • variable displacement pump is characterized in that the hydraulic resistance is designed as a diaphragm.
  • the hydraulic resistance can also be designed as a throttle, in particular as a constant throttle.
  • variable displacement pump is characterized in that a variable throttle is connected in parallel to the hydraulic resistance.
  • the variable throttle is preferably designed as an electric valve, which comprises a particular adjustable throttle for volume flow adjustment.
  • a further preferred embodiment of the variable displacement pump is characterized in that the pressure regulating piston is biased by a spring whose biasing force is adjustable via an electromagnet.
  • the electromagnet is preferably a proportional magnet.
  • variable displacement pump is characterized in that the pressure valve is pilot-controlled by a pilot valve.
  • the pressure valve can also be controlled directly.
  • a further preferred embodiment of the variable displacement pump is characterized in that one of the Verstell réelle by means of the quantity regulator and / or the pressure valve or the quantity and pressure regulator is acted upon or acted upon by a control pressure.
  • the control pressure is generated by means of the quantity regulator and / or the pressure valve or the quantity and pressure regulator from the differential pressure between the high pressure in the high pressure region and the pressure, in particular low pressure, in the pressure relief space or tank.
  • One of the Verstell réelleschreib is connected to the tank or Druckentlastungsrum in connection.
  • the other of the adjustment pressure chambers can be acted upon or acted upon by the control pressure in order to adjust the lifting ring.
  • variable displacement pump is characterized in that the control pressure is connected via one or the outlet throttle to one or the pressure relief space or tank.
  • the outlet throttle is preferably designed as a constant throttle.
  • the inlet is regulated in the pressurized with the control pressure Verstelldruckraum. Therefore, this design is also referred to as supply control.
  • the drain from the adjusting pressure chamber acted upon by the control pressure is kept constant via the outlet throttle designed as a constant throttle.
  • variable displacement pump is characterized in that the control pressure is connected via an inlet throttle with the high-pressure region in connection.
  • the inlet throttle is preferably designed as a constant throttle, so that the feed to the flow regulator and / or pressure valve is also constant.
  • variable displacement pump is characterized in that the control pressure via the flow regulator and / or the pressure valve or the flow and pressure regulator with one or the pressure relief space or tank is connected or is in communication.
  • sequence is regulated from the pressure applied to the control pressure chamber. Therefore, this embodiment is also referred to as sequence control.
  • variable displacement pump is designed as a vane pump with a rotor having radially extending vane slots, which serve to guide wings, which are extendable radially outward from the vane slots in the direction of a stroke contour, the the adjustable cam ring is provided.
  • the variable displacement pump according to the invention is preferably used to suck in a hydraulic medium, in particular hydraulic oil from a tank to pressurize and to promote at least one consumer.
  • the consumer is, for example, a power steering device of a motor vehicle.
  • FIG. 1 shows a hydraulic circuit diagram of a variable displacement pump according to the invention with a
  • FIG. 2 shows a similar embodiment as in Figure 1 with an additional variable throttle
  • Figure 3 shows a similar embodiment as in Figure 1 with a pressure regulator whose
  • Figure 4 shows a similar embodiment as in Figure 1, in which the embodiments of Figures 2 and 3 are combined with each other;
  • Figure 5 shows a similar embodiment as in Figure 1, wherein the pressure regulator a
  • Pressure control piston comprises, which is movable in a flow control piston of the flow regulator back and forth;
  • FIG. 6 shows a similar exemplary embodiment as in FIG. 5 with an additional, variable throttle
  • Figure 7 shows a similar embodiment as in Figure 1 with a pilot valve for
  • Figure 8 shows a similar embodiment as in Figure 5 with a pilot valve for
  • a variable displacement pump 1 is shown in simplified form with a merely indicated pump housing 2 in cross-section and with a rotor 4 within a hydraulic circuit diagram.
  • the rotor 4 is driven by a drive shaft 5 counterclockwise, as indicated by an arrow.
  • variable displacement pump 1 is preferably a hydraulic pump, which is designed as a vane pump.
  • a hydraulic pump which is designed as a vane pump.
  • rotor 4 radially extending slots 6 are provided, in which wings 8 are guided in the radial direction.
  • the wings 8 bear with their radially outer ends to a Hubkontur 9, which is provided on the inside of a cam ring 10.
  • the cam ring 10 of the vane pump is adjustable, slidably or pivotably arranged in the pump housing 2 to vary the flow rate of the vane pump. Therefore, the vane pump is also referred to as a variable displacement pump.
  • the cam ring 10 of the variable displacement pump 1 is limited within the pump housing 2 two Verstell horritin 1 1, 12, which are separated by sealing means 14, 15 from each other.
  • On the right side of the cam 10 is an actuating piston 18, which is biased by an actuating piston spring 19 which is biased in an actuating piston receiving space 20.
  • the lifting ring 10 is held with its left side in contact with a stop surface 16 which is provided on the pump housing 2.
  • the variable displacement pump 1 comprises a suction kidney 21 and a pressure kidney 22, both of which are indicated by dashed lines.
  • the suction kidney 21 communicates with a pressure relief space or tank 24, which contains hydraulic medium, in particular hydraulic oil.
  • a pressure relief space or tank 24 which contains hydraulic medium, in particular hydraulic oil.
  • the region of the variable displacement pump 1 with the pressure kidney 22 is also referred to as the working pressure chamber 22.
  • the working pressure chamber 22 is connected via a hydraulic line 27 to the delivery line 25 in connection.
  • the lines described in the context of the present invention may be embodied as separate lines or as channels which extend through housing parts of the variable displacement pump.
  • a hydraulic resistor 28 is provided between the working pressure chamber 22 and the consumer 26, which is designed for example as a diaphragm or as a constant throttle.
  • the working pressure chamber 22 is also connected via the hydraulic line 27 and a further hydraulic line 29 with the actuating piston receiving chamber 20 in connection.
  • the right Verstell réelleraum 12 of the variable displacement pump 1 communicates with the tank 24 and the suction kidney 21 in connection.
  • the pressure in the actuator piston receiving space 20 and the biasing force of the actuator piston spring 19 ensures that the cam ring 10 is initially held in contact with the stop surface 16.
  • the pressure in the left Verstell réelleraum 11 increases, then the cam ring 10 moves from left to right or pivots about a pivot axis, which is arranged in the vicinity of the seal 15.
  • the stroke volume of the variable displacement pump 1 can be reduced from a maximum displacement to a minimum displacement.
  • the pressure in the Verstelldruckabri 11, 12 as a function of the delivered volume flow and the differential pressure regulated, which prevails in front of or behind the hydraulic resistance 28 in the delivery line or output line 25.
  • the pressure in the adjusting pressure space 11 is controlled by means of a quantity regulator 30 which comprises a quantity regulator piston 31 which delimits a space 32 at one of its ends. At the other end of the flow control piston 31 engages a spring 33. The spring 33 is clamped so that the flow control piston 31 is biased in the illustrated closed position.
  • a collar 34 is provided, which is also referred to as a piston land. The collar 34 has a left control edge 35 and a right control edge 36. Because of the two control edges 35, 36, the flow regulator 30 is also referred to as a two-edge flow regulator.
  • the flow regulator 30 has in the region of the collar 34 a connection connection 38, which communicates with a pressure connection 39 of a pressure regulator 40.
  • the space 32 of the quantity regulator 30 is connected via a hydraulic line 41 to the delivery line 25 in connection.
  • the associated branching point is arranged between the working pressure chamber 22 and the hydraulic resistor 28.
  • Another hydraulic line 42 connects a spring chamber 43, in which the spring 33 is arranged, at a further branch point, which is arranged behind the hydraulic resistor 28, likewise with the delivery line 25.
  • the flow regulator 30 comprises a further connection 44, in which a further collar or piston web is arranged, which is formed on the flow control piston 31.
  • the port 44 is connected to the tank 24.
  • a further connecting line which is equipped with a small throttle, in the flow regulator 30.
  • the further connecting line with the small throttle is also connected to the tank 24.
  • the flow control piston 31 has a further collar 47.
  • the further collar 47 defines an annular space communicating with the tank 24 via a connecting line 45. Via another connecting line 46, the annular space communicates with a spring chamber 49 of the pressure regulator 40.
  • a spring 48 of the pressure regulator 40 is biased.
  • the spring chamber 49 is above a Compensation line 50 with an annular space 51 in connection, which is bounded at the spring 48 remote from the end of a pressure regulating piston 52 by a piston pin 54.
  • the piston pin 54 is non-positively connected to the pressure regulating piston 52 and limited with its free end a pressure chamber 56 which is acted upon via a hydraulic line 57 with the pressure in front of or behind the hydraulic resistor 28. With the same pressure, a further pressure chamber 58 is acted upon, which is designed as an annulus.
  • the annular space 58 extends between a collar 59, from which the piston pin 54 extends, and a further collar 60, which is also referred to as a piston web.
  • a pressure control edge 61 is formed at the collar 60. Since it is at the pressure control edge 61 is the only control edge of the D 'ruck control piston 52, the pressure regulator 40 is also referred to as edging in pressure regulator.
  • the pressure control edge 61 is simultaneously inlet edge for the adjustment pressure in the Verstelldruckraum 11.
  • An outlet throttle 62 allows a pressure reduction in the Verstelltikraum 11.
  • the outlet throttle 62 creates a throttled connection between the annulus of the flow regulator 30 and the tank 24th
  • the pressure control piston 52 is located in Figures 1 to 4 and 7 in its closed position in which a connection between the annular space 58 and the pressure port 39 is interrupted by the collar 60 with the control edge 61.
  • the pressure control piston 52 moves to the right due to a pressure increase in the pressure chamber 56 against the biasing force of the spring 48, the connection between the annular space 58 and the Druckan gleichnut 39 is released from the pressure control edge 61, so that hydraulic medium from the annular space 58 via the pressure port 39th and the connection terminal 38 of the flow regulator 30 in the Verstelldruckraum 11 passes.
  • the flow regulator 30 operates independently of the pressure regulator 40. As the volume flow in the delivery line 25 increases, the pressure in front of the hydraulic resistor 28 increases. The resulting pressure difference acts between the space 32 and the spring chamber 43 of the flow regulator 30. Due to the increasing pressure in front of the hydraulic resistor 28 of the flow control piston 31 is moved against the biasing force of the spring 33 to the right until the control edge 35 on the collar 34 a Releases connection between the space 32 and the connection terminal 38, so that hydraulic medium from the room 32 passes into the Verstell réelleraum 11. In this case, the right control edge 36 of the collar 34 closes a connection between the tank 24 and the left Verstelldruckraum 11.
  • a variable restrictor 68 is connected in parallel to the hydraulic resistor 28.
  • the variable throttle is designed as electrically controlled 2/2-way valve with a closed position and a throttle position.
  • the variable throttle 68 creates a bypass past the hydraulic resistor 28 in its throttle position.
  • the biasing force of the spring 48 can be varied by a spring piston 70 which engages in the spring chamber 49 on the spring 48.
  • the spring piston 70 is limited by an electromagnet 71 in the axial direction displaced.
  • the electromagnet 71 is preferably designed as a proportional magnet and is driven via an electrical amplifier 72.
  • the spring actuator piston 70 is moved toward the pressure regulating piston 52 by means of the electromagnet 71, the spring 48 in the spring chamber 49 between the pressure control piston 52 and the spring actuator piston 70 is further compressed so that the associated spring biasing force increases.
  • the spring biasing force can be reduced by the spring piston 70 is moved by means of the electromagnet 71 of the pressure regulating piston 52 away.
  • a variable restrictor 68 is connected in parallel to the hydraulic resistor 28 in order to enable a volume flow adjustment in a simple manner.
  • the biasing force of a spring 48 of the pressure regulator 40 by means of an electromagnet 71, which is driven by an electric booster 72, are adjusted via the spring piston 70 to vary the maximum pressure of the variable displacement pump 1.
  • a pilot valve 75 which summarizes a prestressed spring.
  • the pilot valve opens only when the pressure in the spring chamber 49 exceeds a predetermined by the biasing force of the spring of the pilot valve 75 value.
  • the spring chamber 49 is connected via the compensation line 50, in which in the embodiment shown in Figure 7, an additional throttle 76 is provided with a pressure chamber 77 which is bounded by the spring 48 remote from the end of the pressure regulating piston 52.
  • the piston pin 54 shown in Figures 1 to 4 is not present in the embodiment shown in Figure 7.
  • the pressure chamber 77 is acted upon by the pressure before or after or behind the hydraulic resistor 28.
  • FIGS. 5, 6 and 8 show exemplary embodiments with a combined quantity and pressure regulator 80, in which a flow regulator as described above and a pressure regulator as described above are combined in a particularly compact design.
  • the flow regulator comprises a flow control piston 81, which is acted upon at one end with the biasing force of a spring 82.
  • a flow control piston 81 On the flow control piston 81, two control edges 84, 85 are provided, which are arranged in the region of a terminal 86.
  • the connection 86 is connected via a connecting line 88 with the left Verstelldruckraum 11 of the variable displacement pump 1 in connection.
  • the end of the quantity control piston 81 facing away from the spring 82 is acted upon via a hydraulic line 91 with the pressure which prevails between the working pressure chamber 22 of the variable displacement pump 1 and the hydraulic resistance 28.
  • Via a further hydraulic line 92 the spring chamber, in which the spring 82 is arranged, communicates with the delivery line 25.
  • the hydraulic resistance 28 is arranged between the branch points of the hydraulic lines 91, 92 in the delivery line 25.
  • the pressure regulator of the combined quantity and pressure regulator 80 comprises a pressure control piston 95, which is received in the flow control piston 81 movable back and forth. One end of the pressure control piston 95 is acted upon by the biasing force of a spring 96 which is biased in the flow control piston 81 against the associated end of the pressure regulating piston 95. At its end facing away from the spring 96, the pressure control piston 95 has a piston pin 98, which is acted upon in a pressure chamber 99 with the pressure in front of the hydraulic resistor 28.
  • the port 86 is in the pressure control via a throttle bore or outlet throttle 100, which corresponds to the outlet throttle 62 in Figure 1 and has the same function as this, with an annular space in the interior of the flow control piston 81 in connection.
  • the annular space is connected via a central bore with a spring chamber in connection, in which the spring 96 of the pressure regulating piston 95 is arranged.
  • Via a further bore 97 is a ring-like pressure chamber within the flow control piston 81 with a space 94 outside of the spring 82 opposite end of the flow control piston 81 in connection.
  • the space 94 is acted upon by the hydraulic line 91 with the pressure in front of the hydraulic resistor 28.
  • the inner annular pressure chamber which is assigned to the pressure regulator, is closed by a control edge 101 of the pressure regulating piston 95.
  • the control edge 101 is a connection between the inner annular pressure space, which is also referred to as inner annulus, and the terminal 86 free, so that hydraulic medium from the inner annular space via the terminal 86 and the connecting line 88 enters the left Verstelldruckraum 11. Since the pressure regulating piston 95 has only one control edge 101, the pressure regulator is also referred to as a single-edge pressure regulator. Similarly, the flow regulator with the flow control piston 81 with its two control edges 84, 85 referred to as a two-edge flow regulator.
  • the spring chamber in which the spring 96 is arranged, communicates with an annular space 103, which communicates with the tank 24.
  • This connection allows the escape or compensation of hydraulic medium from the interior of the flow control piston 81 when the pressure regulating piston 95 moves in the flow control piston 81.
  • the flow regulator with the flow control piston 81 having the two control edges 84 and 85 works in principle as well as the flow regulator 30 described in Figures 1 to 4 and 7. It is essential that the two control pistons 81 and 95 have separate control edges and independently work, although the pressure control piston 95 is received in the flow control piston 81 back and forth movable.
  • variable throttle 108 is connected in parallel to the hydraulic resistor 28.
  • the variable throttle 108 has the same function as the variable throttle 68 already described in FIGS. 2 and 3. Therefore, in order to avoid repetition, reference is made to the preceding description of FIGS. 2 and 3.
  • a pilot valve 115 upstream of the pressure regulator of the combined quantity and pressure regulator 80.
  • the pilot valve 115 is arranged in a connecting line 110, which connects the annular space 103 with the tank 24.
  • the pilot valve 115 has the same function as the pilot valve 75 shown in FIG. 7. Therefore, in order to avoid repetition, reference is made to the foregoing description of FIG. In the exemplary embodiments illustrated in FIGS. 1 to 8, the adjustment pressure space is
  • variable displacement pump 1 via the connection terminal 38 of the pressure regulator 40 and the output from the combined flow and pressure regulator 80 connecting line 88 can be acted upon with a control pressure.
  • the control pressure is via the outlet throttle 62; 100 relieved in the tank 24.
  • the outlet throttle 62; 100 is designed as a constant throttle.
  • the inlet is regulated into the adjusting pressure chamber 11 that is acted upon by the control pressure.
  • This control is also referred to as supply control for the control pressure of the variable displacement pump 1.
  • Figures 9 to 16 show similar embodiments as in Figures 1 to 8, but are equipped instead of a supply control with a flow control. In the sequence control, the inflow of the control pressure is kept constant, while the flow of the control pressure to the tank 24 is regulated down, so the flow is regulated.
  • the adjustment pressure space is
  • variable displacement pump 1 via the pressure port 39 of the pressure regulator 40 and the connection port 116 of the flow regulator 30 or one of the combined flow and pressure regulator 80 outgoing connecting line 117 can be acted upon by the control pressure.
  • the control piston spring 19 is also acted upon via the Verstelldruckraum 12 with the control pressure.
  • the actuating piston is not combined with the actuating piston spring 19.
  • An actuating piston 118 is arranged on the actuating piston spring 19 opposite side of the cam ring 10. The actuating piston 118 protrudes into the Verstell réelleraum 11 and is connected on its side remote from the cam ring 10 with the high-pressure region, that is acted upon by the delivery pressure of the variable displacement pump 1.
  • the adjustment pressure chamber 11 is connected via the connecting line 88 with the tank 24 in connection.
  • an inlet throttle 120 designed as a constant throttle
  • the inflow of the control pressure into the adjusting pressure chamber 12 is kept constant with the exemplary embodiments illustrated in FIGS. 9 to 16.
  • the flow of the control pressure is controlled by a control edge of the mass flow control piston 31; 81 to the tank 24 down regulated.
  • control pressure acts in the embodiments illustrated in Figures 9 to 16 on Druckwirk vom on the right side of the ring ring 10 in the Verstelldruckraum 12.
  • the left side of the ring ring 10 is always in the Verstell réelleraum 11 with the tank pressure acted upon and can only be pressed by the additional high-pressure actuator piston 118 in the zero stroke position.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention concerne une pompe à cylindrée variable comportant une bague de commande de cylindrée, qui est mobile en fonction de la pression régnant dans une première chambre de pression variable et dans une deuxième chambre de pression variable, un régulateur de débit à tiroir comportant un piston de régulation de débit qui présente plusieurs rampes de distribution et qui est soumis à une pression différentielle régnant en amont et en aval d'une résistance hydraulique, ainsi qu'une soupape de pression. L'invention est caractérisée en ce que la soupape de pression est une soupape à tiroir pourvue d'un piston de régulation de débit qui présente une rampe de distribution de pression, une surface de distribution de pression étant soumise à la pression qui règne dans une zone de haute pression en amont ou éventuellement en aval de la résistance hydraulique.
PCT/EP2009/004772 2008-07-15 2009-07-02 Pompe à cylindrée variable WO2010006705A2 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
ES09776916.0T ES2567089T3 (es) 2008-07-15 2009-07-02 Bomba de desplazamiento variable con un regulador de caudal y una válvula de presión
DE112009001577T DE112009001577A5 (de) 2008-07-15 2009-07-02 Verstellpumpe
EP09776916.0A EP2307726B1 (fr) 2008-07-15 2009-07-02 Pompe à cylindrée variable

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008033788.9 2008-07-15
DE102008033788 2008-07-15

Publications (3)

Publication Number Publication Date
WO2010006705A2 true WO2010006705A2 (fr) 2010-01-21
WO2010006705A3 WO2010006705A3 (fr) 2010-06-17
WO2010006705A8 WO2010006705A8 (fr) 2010-12-02

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PCT/EP2009/004772 WO2010006705A2 (fr) 2008-07-15 2009-07-02 Pompe à cylindrée variable

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EP (1) EP2307726B1 (fr)
DE (1) DE112009001577A5 (fr)
ES (1) ES2567089T3 (fr)
WO (1) WO2010006705A2 (fr)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012149929A2 (fr) * 2011-05-05 2012-11-08 Ixetic Bad Homburg Gmbh Pompe à cylindrée variable
WO2012149931A3 (fr) * 2011-05-04 2013-09-26 Ixetic Bad Homburg Gmbh Pompe à cylindrée variable
EP2573398A3 (fr) * 2011-09-23 2014-10-08 MAHLE International GmbH Système de lubrifiant à soupape de contrôle de capacité
CN104612967A (zh) * 2014-12-01 2015-05-13 宁波圣龙汽车动力系统股份有限公司 可变排量机油泵控制回路
WO2015137209A1 (fr) * 2014-03-13 2015-09-17 カヤバ工業株式会社 Pompe à palettes et son procédé de production
WO2015193149A1 (fr) 2014-06-20 2015-12-23 Magna Powertrain Bad Homburg GmbH Système de pivotement pour bague de réglage de cylindrée
US20160177949A1 (en) * 2014-12-19 2016-06-23 Hitachi Automotive Systems Steering, Ltd. Pump apparatus
DE102016216681A1 (de) 2015-09-11 2017-04-13 Magna Powertrain Bad Homburg GmbH Verstellpumpe mit Unterflügelversorgung und Verfahren
WO2017084710A1 (fr) * 2015-11-19 2017-05-26 Pierburg Pump Technology Gmbh Pompe à lubrifiant à cylindrée variable
EP3173625A1 (fr) 2015-11-26 2017-05-31 Robert Bosch Gmbh Pompe à débit variable comprenant une bague de réglage présentant un bras de réglage destiné à corriger le débit de la pompe à débit variable
CN114215744A (zh) * 2021-12-28 2022-03-22 湖南机油泵股份有限公司 采用滑阀和开关电磁阀联合控制的两级变量机油泵及系统

Citations (5)

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Publication number Priority date Publication date Assignee Title
US2878756A (en) * 1955-08-30 1959-03-24 Houdaille Industries Inc Variable displacement pump and pressure responsive control means therefor
EP1148244A2 (fr) * 2000-04-18 2001-10-24 Showa Corporation Pompe volumétrique à déplacement variable
US20010036412A1 (en) * 2000-04-27 2001-11-01 Hideo Konishi Variable displacement pump
US20020085923A1 (en) * 2000-12-15 2002-07-04 Unisia Jkc Steering Systems Co, Ltd. Variable displacement pump
EP1801419A2 (fr) * 2005-12-26 2007-06-27 Hitachi, Ltd. Pompe à palettes à déplacement variable

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2878756A (en) * 1955-08-30 1959-03-24 Houdaille Industries Inc Variable displacement pump and pressure responsive control means therefor
EP1148244A2 (fr) * 2000-04-18 2001-10-24 Showa Corporation Pompe volumétrique à déplacement variable
US20010036412A1 (en) * 2000-04-27 2001-11-01 Hideo Konishi Variable displacement pump
US20020085923A1 (en) * 2000-12-15 2002-07-04 Unisia Jkc Steering Systems Co, Ltd. Variable displacement pump
EP1801419A2 (fr) * 2005-12-26 2007-06-27 Hitachi, Ltd. Pompe à palettes à déplacement variable

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012149931A3 (fr) * 2011-05-04 2013-09-26 Ixetic Bad Homburg Gmbh Pompe à cylindrée variable
WO2012149929A3 (fr) * 2011-05-05 2013-09-19 Ixetic Bad Homburg Gmbh Pompe à cylindrée variable
WO2012149929A2 (fr) * 2011-05-05 2012-11-08 Ixetic Bad Homburg Gmbh Pompe à cylindrée variable
EP2573398A3 (fr) * 2011-09-23 2014-10-08 MAHLE International GmbH Système de lubrifiant à soupape de contrôle de capacité
CN106062368A (zh) * 2014-03-13 2016-10-26 Ｋｙｂ株式会社 叶片泵及其制造方法
WO2015137209A1 (fr) * 2014-03-13 2015-09-17 カヤバ工業株式会社 Pompe à palettes et son procédé de production
JP2015175253A (ja) * 2014-03-13 2015-10-05 カヤバ工業株式会社 ベーンポンプ及びその製造方法
CN106062368B (zh) * 2014-03-13 2017-07-04 Ｋｙｂ株式会社 叶片泵及其制造方法
WO2015193149A1 (fr) 2014-06-20 2015-12-23 Magna Powertrain Bad Homburg GmbH Système de pivotement pour bague de réglage de cylindrée
DE102014211878A1 (de) 2014-06-20 2015-12-24 Magna Powertrain Bad Homburg GmbH Schwenkanordnung für einen Hubring
CN104612967A (zh) * 2014-12-01 2015-05-13 宁波圣龙汽车动力系统股份有限公司 可变排量机油泵控制回路
CN105715543A (zh) * 2014-12-19 2016-06-29 日立汽车系统转向器株式会社 泵装置
JP2016118112A (ja) * 2014-12-19 2016-06-30 日立オートモティブシステムズステアリング株式会社 ポンプ装置
US20160177949A1 (en) * 2014-12-19 2016-06-23 Hitachi Automotive Systems Steering, Ltd. Pump apparatus
DE102016216681A1 (de) 2015-09-11 2017-04-13 Magna Powertrain Bad Homburg GmbH Verstellpumpe mit Unterflügelversorgung und Verfahren
WO2017084710A1 (fr) * 2015-11-19 2017-05-26 Pierburg Pump Technology Gmbh Pompe à lubrifiant à cylindrée variable
EP3173625A1 (fr) 2015-11-26 2017-05-31 Robert Bosch Gmbh Pompe à débit variable comprenant une bague de réglage présentant un bras de réglage destiné à corriger le débit de la pompe à débit variable
DE102015223414A1 (de) 2015-11-26 2017-06-01 Robert Bosch Gmbh Verstellpumpe mit einem einen Verstellarm aufweisenden Verstellring zur Fördermengenverstellung der Verstellpumpe
CN114215744A (zh) * 2021-12-28 2022-03-22 湖南机油泵股份有限公司 采用滑阀和开关电磁阀联合控制的两级变量机油泵及系统
CN114215744B (zh) * 2021-12-28 2023-04-07 湖南机油泵股份有限公司 采用滑阀和开关电磁阀联合控制的两级变量机油泵及系统

Also Published As

Publication number Publication date
WO2010006705A8 (fr) 2010-12-02
DE112009001577A5 (de) 2012-02-23
ES2567089T3 (es) 2016-04-19
WO2010006705A3 (fr) 2010-06-17
EP2307726A2 (fr) 2011-04-13
EP2307726B1 (fr) 2016-01-27

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