WO2012149931A2 - Pompe à cylindrée variable - Google Patents

Pompe à cylindrée variable Download PDF

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Publication number
WO2012149931A2
WO2012149931A2 PCT/DE2012/100117 DE2012100117W WO2012149931A2 WO 2012149931 A2 WO2012149931 A2 WO 2012149931A2 DE 2012100117 W DE2012100117 W DE 2012100117W WO 2012149931 A2 WO2012149931 A2 WO 2012149931A2
Authority
WO
WIPO (PCT)
Prior art keywords
control valve
control
pressure
variable displacement
displacement pump
Prior art date
Application number
PCT/DE2012/100117
Other languages
German (de)
English (en)
Other versions
WO2012149931A3 (fr
Inventor
Ludger Holtmann
Doan Van Nguyen
Thilo MAUSER
Ante BODROZIC
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 DE112012001968.7T priority Critical patent/DE112012001968A5/de
Publication of WO2012149931A2 publication Critical patent/WO2012149931A2/fr
Publication of WO2012149931A3 publication Critical patent/WO2012149931A3/fr

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
    • 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
    • F04C14/226—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 by pivoting the cam around an eccentric axis
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/811—Actuator for control, e.g. pneumatic, hydraulic, electric
    • 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 invention relates to a variable displacement pump for the regulated supply of several consumers, with a cam ring which is movable to adjust the stroke of the variable displacement pump, and with a control valve device.
  • the object of the invention is to simplify the regulated supply of several consumers with a variable displacement pump, which comprises a lifting ring, which is movable to adjust the stroke of the variable displacement pump, and a control valve device.
  • the object is in a variable displacement pump for the regulated supply of multiple consumers, with a cam ring which is movable to adjust the stroke of the variable displacement pump, and with a control valve device, achieved in that the control valve device is hydraulically connected to a control chamber and a compensation chamber, from which in opposite directions compressive forces are exerted on the lifting ring and their pressures or volumes are controlled by means of the control valve device.
  • the variable displacement pump is preferably designed as a vane pump with a rotor and vanes within the cam ring.
  • the variable displacement pump is designed in particular as a one-stroke hydraulic pump. Single stroke means that the variable displacement pump has a suction area and a pressure range, which are limited by the blades between the rotor and the lifting ring.
  • the cam ring is arranged, for example, between a compensation piston and a control piston.
  • the compensating piston is acted upon by the pressure from the compensation chamber.
  • the control piston is acted upon by the pressure from the control chamber.
  • the pressure from the two chambers is transferred to the cam ring via the two pistons.
  • About the pressure in the two chambers both a Aufregeln and a Abregein the variable displacement is possible.
  • control valve device comprises a control valve with a control valve piston which has a control control edge between a control pressure port and a system pressure port or a tank pressure port, via which the control chamber can be connected either to a system pressure or a tank pressure.
  • control pressure is controlled in the control chamber.
  • variable displacement pump has at least one secondary consumer control edge via which at least one secondary consumer can be connected to the system pressure. If the system pressure is too low, the connection between the secondary consumer and the system pressure is interrupted.
  • the secondary consumer control edge is arranged so that a supply of secondary consumers is ensured with hydraulic medium before the control control edges are effective.
  • variable displacement pump Another preferred embodiment of the variable displacement pump is characterized in that the control valve piston is acted upon at a second end with a secondary system pressure.
  • the former system pressure is also called primary system pressure or primary pressure.
  • secondary system pressure is referred to as secondary pressure or Abregeltik.
  • variable displacement pump is characterized in that the control valve piston at a first end with a primary system pressure is applied.
  • the primary system pressure is preferably the pressure provided at the outlet of the variable displacement pump.
  • variable displacement pump is characterized in that the control valve piston is acted upon at a first end with a control pressure.
  • the control pressure is provided, for example, by a control circuit.
  • the control pressure is, for example, the control pressure of a transmission in which the variable displacement pump according to the invention is installed.
  • variable displacement pump is characterized in that the control valve piston is acted upon at a first end with a control pressure.
  • the control pressure is provided, for example, by a control circuit.
  • variable displacement pump is characterized in that the control valve piston is acted upon at the first end with a spring force.
  • the spring force of the control valve piston is biased, for example, in a position in which the control chamber connected to the tank and the connection between the system pressure and the secondary consumer is interrupted.
  • variable displacement pump Another preferred embodiment of the variable displacement pump is characterized in that the control valve piston is acted upon at a second end with the system pressure.
  • the control valve piston is driven at its second end against the action of acting on its first end spring force with the system pressure.
  • variable displacement pump is characterized in that the control valve piston is acted upon at a first end with the tank pressure. As a result, movements of the control valve piston are possible in normal operation.
  • a further preferred embodiment of the variable displacement pump is characterized in that the control valve piston is acted upon at the first end with a spring force. By the spring force of the control valve piston is biased, for example, in a position in which the control chamber connected to the tank pressure and the connection between the control chamber and the system pressure is interrupted.
  • a further preferred embodiment of the variable displacement pump is characterized in that the control valve piston can be acted upon at a second end via a control valve with the system pressure.
  • the control valve is biased, for example by means of a spring, preferably in a position in which the control valve piston is not acted upon by the system pressure.
  • a connection between the second end of the control valve piston and the system pressure may be interrupted by, for example, the control valve.
  • the second end of the control valve piston can also be acted upon by a secondary consumer pressure when the connection to the system pressure is interrupted by the control valve.
  • variable displacement pump is characterized in that the control valve is designed as a 3/3-way valve with a connection connection, a system pressure connection and a secondary consumer pressure connection. Through the connection port, the control valve is connected to the second end of the control valve piston.
  • the control valve is preferably designed as a proportional valve.
  • variable displacement pump is characterized in that the control valve is designed as a 3/3-way valve with a system pressure port, a Maunoverdruckan gleich and a tank pressure port.
  • the control valve is connected to the system pressure, in particular the primary system pressure, via the system pressure connection.
  • the control valve is connected, for example, to a secondary consumer, in particular the secondary system pressure.
  • the control valve is connected to the tank pressure via the tank pressure connection, in particular the inlet pressure of the variable displacement pump.
  • the control valve comprises a control valve piston provided with two control edges, which is acted upon at a first end with a control pressure and at a second end with the system pressure. At its first end of the control valve piston is preferably additionally acted upon by a spring force. By the spring force of the control valve piston is biased to a position in which all connections of the control valve are closed by the control piston.
  • control valve is designed as a 2/2-way valve with a system pressure connection and a secondary consumer pressure connection.
  • the control valve comprises a control valve piston, which is preferably acted on at a first end with a control pressure and at a second end with the system pressure.
  • the control valve piston is preferably additionally acted upon by a spring force, by which the control piston is biased into a position in which the two ports of the control valve are closed.
  • the control valve is preferably designed as a proportional valve.
  • variable displacement pump is characterized in that the control valve piston is acted upon at a second end with a secondary consumer pressure.
  • the secondary consumer pressure is used to control the stroke of the variable displacement pump via the control valve.
  • variable displacement pump is characterized in that the control valve is designed as an inlet control valve or drain control valve.
  • control valve is designed as an inlet control valve or drain control valve.
  • variable displacement pump is characterized in that in the control chamber and / or the compensation chamber, a spring is arranged, which exerts a spring force on the lifting ring.
  • the spring force acts preferably alsregelnd, that is, the cam is adjusted by the spring force in the direction of increasing flow.
  • control valve piston is additionally acted upon by control pressure at a first end and spring force at a second end. This ensures that there is a linear relationship between the control pressure and the primary pressure.
  • a further preferred embodiment is characterized in that the control valve piston is additionally acted upon at a second end with control pressure and with Federkaft. This makes it possible to establish a linear relationship between the control pressure and the primary pressure.
  • variable displacement pump is preferably a vane pump with a rotor
  • wing slots which serve to guide wings, which are extendable from the wing slots radially outward in the direction of a stroke contour, which is provided on the cam ring.
  • the invention further relates to a method for operating an advance
  • variable pump The variable displacement pump according to the invention is particularly suitable for transmission applications.
  • Figure 1 shows an inlet control with a combined control piston.
  • Figure 2 shows an inlet control with an additional control valve.
  • Figure 3 shows a flow control with a combined control piston.
  • Figure 4 shows a flow control with an additional control valve.
  • FIG. 5 shows an inlet control with an additional control valve and a secondary consumer pressure.
  • FIG. 6 shows a sequence control with an additional control valve and a secondary consumer pressure.
  • a variable displacement pump 1 according to different embodiments in each case in a hydraulic system to supply different
  • variable displacement pump 1 serves to hydraulic medium, in particular hydraulic oil or transmission oil, from a
  • Hydraulic medium reservoir 4 which is also referred to as a tank, to several
  • the consumers 5, 6, 7 are each indicated by a throttle symbol. By means of corresponding tank symbols, it is indicated that the consumers 5, 6, 7 are connected to the hydraulic medium reservoir 4.
  • the consumer 5 is preferably a primary circuit of a transmission.
  • the consumer 6 is preferably a secondary circuit of the transmission.
  • the consumer 7 is preferably a lubrication circuit of the transmission or an internal combustion engine.
  • a pressure reducing valve 8 is connected between the consumers 6 and 7. The pressure reducing valve 8 is controlled via a control circuit 9.
  • the variable displacement pump 1 is designed as a vane pump with an adjustable cam ring 10.
  • a rotor is arranged with radially extending slots, in which wings are guided in the radial direction.
  • the wings lie with their radially outer ends to a stroke contour, which is provided on the inside of the cam ring 10.
  • variable displacement pump 1 When the rotor of the variable displacement pump 1 rotates in a drive direction of rotation indicated by an arrow, an increase in volume occurs in the region of a suction space between the rotor and the lifting ring 10, which causes the hydraulic medium to be drawn from the tank 4. At the same time it comes in a pressure range between the rotor and cam 10 to a volume reduction, which causes a conveying of the hydraulic medium to the consumers 5 to 7.
  • the delivery rate of the variable displacement pump 1 can be varied by adjusting the cam ring 10 relative to the rotor.
  • adjusting the cam ring 10 leads, for example a pivoting movement about a bearing surface, which may be provided on a housing or on a spacer ring of the variable displacement pump 1.
  • the cam ring 10 is disposed between a compensation piston and a control piston (not shown).
  • the compensating piston is acted upon at a piston surface facing away from the cam ring 10 with a compensating pressure which prevails in a compensation chamber 11.
  • the control piston is acted upon on a piston ring facing away from the cam 10 with a control pressure which prevails in a control chamber 12.
  • the two chambers 1 1, 12 are oppositely arranged so that forces are applied by the pressure prevailing in them via the piston on the lifting ring, which have opposite directions of action.
  • the compensation chamber 1 1 is preferably acted upon by a system pressure which is provided at the outlet of the variable displacement pump 1.
  • the compensation chamber 1 1 is connected via a connecting line 13 shown in dashed lines with the output of the variable displacement pump 1.
  • the control chamber 12 is connected via a control line 14 to a control valve 15.
  • the adjusting movement of the cam ring 10 depends on the operation of the variable displacement pump 1 from the pressures prevailing in the two chambers 1 1, 12.
  • the compensation chamber 1 1 is arranged on the right and the control chamber 12 on the left.
  • the compensation chamber 1 1 on the left and the control chamber 12 is arranged on the right.
  • a spring is additionally arranged, through which a Jerusalemregelnd acting spring force on the corresponding adjustment piston or the cam ring 10 is exercised.
  • the control pressure in the control chamber 12 is controlled by the control valve 15, via which the control chamber 12 can be connected depending on demand with the system pressure or the tank pressure. This results in a high dynamic, even at low system pressures, since throttling of the control lines can be omitted.
  • the pressurized surfaces of the compensation piston and the control piston are advantageously designed so that the control pressure corresponds to half the compensation pressure.
  • the control valve 15 comprises a control valve piston 16 which is movable in a valve bore back and forth to regulate the control pressure in the control chamber 12.
  • the control valve piston 16 is biased by a spring in its illustrated position.
  • control chamber 12 of the spring and the compensation chamber 1 1 is arranged opposite, so that the amount of oil to increase the stroke of the variable displacement pump 1 in the control chamber 12 is reduced and the amount of oil in the compensation chamber 1 1 is increased ,
  • the control chamber 12 is subjected to a higher pressure.
  • a first, left in Figure 1 end of the control valve piston 16 is acted upon via a control line 18 with the control pressure from the control circuit 9.
  • a second, in Figure 1 right end of the control valve piston 16 is acted upon via a control line 19 to the system pressure.
  • the tank line 22 is connected to a tank connection of the control valve 15.
  • a system pressure line 24 is connected to a system pressure connection of the control valve 15.
  • the control line 14 is connected to a control pressure connection of the control valve 15.
  • a sub-consumer pressure line 29 is connected to a sub-consumer pressure port of the control valve 15.
  • the secondary consumer pressure line 29 connects the control valve 15 with the consumers 6 and 7.
  • the control valve piston 16 has a first control control edge 26, a second
  • control valve 15 with the two control control edges 26 and 27 is also called
  • Two-edge controller designates. With the two-edge controller can advantageously be a preferred pressure ratio between the control and compensation pressure of about 1 to 2 are shown. This ensures that the control valve 15, as compared to a single-edge controller, the same high dynamics during down and up.
  • the two-edge controller has the advantage over a four-cornered controller that the two-edge controller is easier to control and less expensive to produce.
  • the first, left in Figure 2 end of the control valve piston 16 is acted upon via a tank pressure line 31 with tank pressure.
  • the second, in Figure 2 right end of the control valve piston 16 is acted upon via a connecting line 32 via a control valve 40 with the system pressure.
  • a tank pressure line 33 is connected to a tank pressure port of the control valve 15.
  • a system pressure line 34 is connected to a system pressure port of the control valve 15.
  • the control line 14 is connected to a control pressure connection of the control valve 15.
  • the control valve piston 16 has a first control control edge 36 and a second control control edge 37.
  • the control valve 15 is controlled via the connecting line 32 by the control valve 40.
  • the control valve 40 is designed as a 3/3-way valve with a system pressure connection, a Maunoverdruckan gleich and a connection for the connecting line 32.
  • a system pressure line 42 is connected to the system pressure port of the control valve 40.
  • a secondary consumer pressure line 44 is connected to the secondary consumer pressure port of the control valve 40.
  • Via a control line 46 a first, left in Figure 2 end of a control valve piston of the control valve 40 is acted upon by the control pressure of the control circuit 9.
  • a second, in Figure 2 right end of the control piston of the control valve 40 is acted upon via a control line 47 to the system pressure.
  • the consumers 6 and 7 are released or supplied with hydraulic medium by the control valve piston of the control valve 40. If the consumers 6 and 7 are sufficiently supplied with hydraulic medium, then the system pressure is switched via the connecting line 32 to the second, in Figure 2 right end of the control valve piston 16 of the control valve 15 at a further increasing system pressure.
  • the connection between the control chamber 12 and the tank pressure on the first control edge 36 of the control valve piston 16 is closed.
  • the control chamber 12 is connected to the system pressure.
  • the admission of the control chamber 12 with the system pressure Abregein the variable displacement pump 1 is effected.
  • control control chamber 12 and the compensation chamber 1 1 are arranged opposite to Figure 1 reversed.
  • a tank pressure line 51 extends to a Tankdruckan- connection of the control valve 15.
  • a tank pressure line 52 connects a spring chamber, in which a spring is arranged, with the tank pressure.
  • system pressure lines 54 and 55 extend to two system pressure connections of the control valve 15.
  • a secondary consumer pressure line 58 is connected to a secondary consumer pressure connection of the control valve 15.
  • the stroke of the variable displacement pump 1 decreases when the volume or the pressure in the control chamber 12 decreases and / or the volume or the pressure in the compensation chamber 1 1 increases.
  • control chamber 12 in contrast to the embodiment shown in Figure 2, is connected at switched or regulated system pressure on the Regel mortkante 37 with the tank pressure to reduce the stroke of the variable.
  • control piston 16 via the connecting line 32 by the proportional control valve 40 with applied to the system pressure.
  • the control chamber 12 via the control valve control edge 36 is increasingly connected to the system pressure to increase the stroke of the variable displacement pump 1.
  • FIGS. 5 and 6 show similar representations as in FIGS. 2 and 4.
  • the second, right-hand end of the control valve piston 16 of the control valve 15 is acted upon via a connecting line 62 with the secondary consumer pressure which prevails in a secondary consumer pressure line 64.
  • the secondary consumer pressure line 64 serves to supply the consumers 6 and 7 with hydraulic medium.
  • the secondary consumer pressure line 64 can via a control valve 70 with the
  • the control valve 70 is designed as a 2/2-way valve with a system pressure port and a Maunoverdruckan gleich.
  • the control valve 70 comprises a control valve piston which is controlled via a control line 71 with the control pressure of the control circuit 9. At its opposite end, the control valve piston of the control valve 70 is controlled via a control line 72 to the system pressure.
  • a system pressure line 73 is connected to the system pressure port of the control valve 70.
  • a secondary consumer pressure line 74 is connected, which starts from the secondary consumer pressure line 64.
  • FIGS. 7 and 8 Exemplary embodiments are shown in FIGS. 7 and 8, in which elements of the exemplary embodiments from FIGS. 1 and 4 are combined with one another and with further features. To designate the same or similar parts, the same reference numerals are used. In order to avoid repetition, the following will mainly deal with the differences between the individual embodiments.
  • a first end, left in FIG. 7, of the control valve piston 16 is provided with a spring force and via a control line 78 subjected to the system pressure which is provided at the output of the variable displacement pump 1 and which is also referred to as the primary system pressure.
  • a second, in Figure 7 right end of the control valve piston 16 is connected via a control line 79 to the secondary consumer pressure line 44.
  • the secondary consumer pressure line 44 and the control line 79 the second end of the control valve piston 16 is acted upon by a secondary system pressure, which is provided in the secondary consumer pressure line for a secondary consumer.
  • the control valve 15 shown in Figure 7 comprises a control pressure port to which the control pressure line 14 is connected, a tank pressure port to which a tank pressure line 80 is connected, and a system pressure port to which a system pressure line 82 is connected. Via the system pressure line 82, the control valve is connected to the primary system pressure.
  • the control valve 15 is preceded by a control valve 84, which is similar to the control valve 40 of Figure 4.
  • a control valve 84 which is similar to the control valve 40 of Figure 4.
  • the system pressure line 42 and the secondary consumer pressure line 44 is connected.
  • the control valve 84 as a third connection to a tank pressure port to which a tank pressure line 85 is connected.
  • the control valve 84 is connected to the inlet pressure of the variable displacement pump 1, which corresponds to the tank pressure.
  • the control valve 84 is, as the control valve 40, driven via the control lines 46 and 47.
  • the control valve 15 with the primary system pressure which is also referred to as primary pressure
  • the secondary consumer pressure from the secondary consumer pressure line 44 which is also referred to as a secondary system pressure or secondary pressure.
  • the primary system pressure is used to adapt the desired pressure level.
  • the primary system pressure is applied via the control line 78 to a smaller area at the left end of the control valve piston 16 in FIG. 7 in a direction opposite to the secondary pressure, which acts on the right end of the control valve piston 16 in FIG.
  • the secondary pressure acts via the control line 79 on a larger surface of the control valve piston sixteenth
  • FIG. 8 The embodiment shown in Figure 8 is similar to the embodiment shown in Figure 7. To designate the same or similar parts, the same reference numerals are used.
  • the left end of the control valve piston 16 is driven in contrast to the previous embodiment in addition to the spring force via a control line 92 with the control pressure of the control circuit 9.
  • the control pressure of the control circuit 9 and the secondary pressure of the secondary consumer pressure line 44 act in opposite directions on the two ends of the control valve piston sixteenth
  • the target pressure setting is carried out by the control pressure of the control circuit 9.
  • the control valve piston 16 is connected via the control line 79 to the control circuit 9.
  • the control pressure causes a force on the control valve piston 16 and generates an additional reaction to the control valve piston 16 in the direction "Avemregeln". This has the advantage that the pump can steplessly adjust the primary pressure of the transmission itself.
  • control chamber 12 is connected to the tank pressure via the second control control edge 37 when the system pressure is switched or regulated in order to reduce the stroke of the variable displacement pump 1.
  • the control valve piston 16 is acted upon via the control line 14 by the proportional regulating valve 15 with the control pressure of the control circuit 9.
  • the control valve piston 16 is acted upon at its second end via the line 90 with the control pressure. With increasing system pressure, this results in an additional effect of the control pressure on the control valve piston 16 and thus a reaction to the control valve piston 16 in the direction "Abregein".
  • the thus caused adjustment of the cam ring of the variable displacement pump 1 has a reduction of the pump stroke result.
  • the control chamber 12 is increasingly pressurized with system pressure via the first control control edge 36, thus producing an increase in the pump stroke. This ensures that there is a linear relationship between the control pressure and the primary pressure and thus a higher control stability.
  • FIG. 10 shows a further embodiment, a so-called supply control, of the invention.
  • the compensation chamber 1 1 is spring-loaded and connected via the connecting line 13 to the system pressure.
  • the control chamber 12 is connected via the first control edge 36 of the control valve piston 16 to the tank pressure.
  • the control pressure acts via the control line 91 on the control valve piston 16, so that this undergoes an additional component in the direction "Aufregeln”. If the system pressure rises, the control valve piston 16 is moved to tion "Abregein" moves and connected via the second control edge 37 of the control valve piston 16, the control chamber 12 with the system pressure to reduce the stroke of the variable displacement pump 1. This can be a linear relationship between the control pressure and the primary pressure produce and thereby achieve a higher control stability.

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

Abstract

L'invention concerne une pompe à cylindrée variable permettant de réguler l'alimentation de plusieurs consommateurs, laquelle pompe à cylindrée variable comprend une bague de commande de cylindrée, pouvant être déplacée afin de régler la cylindrée de la pompe à cylindrée variable, ainsi qu'un dispositif régulateur. L'invention est caractérisée en ce que le dispositif régulateur est en liaison hydraulique avec une chambre de régulation et une chambre de compensation, à partir desquelles des forces de pression peuvent être exercées, dans des directions opposées, sur la bague de commande de cylindrée et dont les pressions ou volumes peuvent être réglés au moyen du dispositif régulateur.
PCT/DE2012/100117 2011-05-04 2012-04-26 Pompe à cylindrée variable WO2012149931A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112012001968.7T DE112012001968A5 (de) 2011-05-04 2012-04-26 Verstellpumpe

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011050096 2011-05-04
DE102011050096.0 2011-05-04

Publications (2)

Publication Number Publication Date
WO2012149931A2 true WO2012149931A2 (fr) 2012-11-08
WO2012149931A3 WO2012149931A3 (fr) 2013-09-26

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Application Number Title Priority Date Filing Date
PCT/DE2012/100117 WO2012149931A2 (fr) 2011-05-04 2012-04-26 Pompe à cylindrée variable

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DE (1) DE112012001968A5 (fr)
WO (1) WO2012149931A2 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015003960A3 (fr) * 2013-07-08 2015-06-04 Magna Powertrain Bad Homburg GmbH Pompe à cylindrée variable et commande de boîte de vitesses
WO2015193149A1 (fr) 2014-06-20 2015-12-23 Magna Powertrain Bad Homburg GmbH Système de pivotement pour bague de réglage de cylindrée
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
WO2016125639A1 (fr) * 2015-02-06 2016-08-11 日立オートモティブシステムズ株式会社 Pompe à déplacement variable

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DE3913414A1 (de) * 1989-04-24 1990-10-25 Walter Schopf Mehrkreis-regelpumpe
JPH03210084A (ja) * 1990-01-09 1991-09-13 Nissan Motor Co Ltd 可変容量ベーンポンプ
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WO2015003960A3 (fr) * 2013-07-08 2015-06-04 Magna Powertrain Bad Homburg GmbH Pompe à cylindrée variable et commande de boîte de vitesses
CN105308321A (zh) * 2013-07-08 2016-02-03 麦格纳动力系巴德霍姆堡有限责任公司 变量泵和变速器控制装置
US10060524B2 (en) 2013-07-08 2018-08-28 Magna Powertrain Bad Homburg GmbH Variable displacement pump and gearbox control system
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
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
WO2016125639A1 (fr) * 2015-02-06 2016-08-11 日立オートモティブシステムズ株式会社 Pompe à déplacement variable
CN107208632A (zh) * 2015-02-06 2017-09-26 日立汽车系统株式会社 可变容量型泵
CN107208632B (zh) * 2015-02-06 2019-05-10 日立汽车系统株式会社 可变容量型泵
US10677245B2 (en) 2015-02-06 2020-06-09 Hitachi Automotive Systems, Ltd. Variable displacement pump

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