DE10222131C5 - Positive displacement pump with delivery volume adjustment - Google Patents

Positive displacement pump with delivery volume adjustment

Info

Publication number
DE10222131C5
DE10222131C5 DE2002122131 DE10222131A DE10222131C5 DE 10222131 C5 DE10222131 C5 DE 10222131C5 DE 2002122131 DE2002122131 DE 2002122131 DE 10222131 A DE10222131 A DE 10222131A DE 10222131 C5 DE10222131 C5 DE 10222131C5
Authority
DE
Germany
Prior art keywords
pressure
fluid
pump
piston
pressure chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
DE2002122131
Other languages
German (de)
Other versions
DE10222131A1 (en
DE10222131B4 (en
Inventor
Gerold 88427 Missel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SCHWäBISCHE HüTTENWERKE AUTOMOTIVE GMBH & CO. , DE
Original Assignee
Schwabische Huettenwerke Automotive & Co Kg 73433 GmbH
Schwaebische Huettenwerke Automotive 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
Family has litigation
Application filed by Schwabische Huettenwerke Automotive & Co Kg 73433 GmbH, Schwaebische Huettenwerke Automotive GmbH filed Critical Schwabische Huettenwerke Automotive & Co Kg 73433 GmbH
Priority to DE2002122131 priority Critical patent/DE10222131C5/en
Publication of DE10222131A1 publication Critical patent/DE10222131A1/en
Application granted granted Critical
Publication of DE10222131B4 publication Critical patent/DE10222131B4/en
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=29265354&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=DE10222131(C5) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Publication of DE10222131C5 publication Critical patent/DE10222131C5/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/10Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/185Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by varying the useful pumping length of the cooperating members in the axial direction
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/08Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/08Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/08Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms

Abstract

External gear pump with adjustable specific delivery volume, comprising:
a) a housing (3) containing a delivery chamber (4) into which at least one inlet (5) for fluid at a low pressure side of the pump and at least one outlet (6) for fluid at a high pressure side of the pump,
b) at least two in the delivery chamber (4) accommodated, rotatably driven externally toothed spur gears (1, 2), which are in mesh with each other in a conveying engagement, namely meshing to promote the fluid from the inlet (5) to the outlet (6) , wherein the conveyor wheels (1, 2) are adjustable so that by adjusting the conveyor wheels (1, 2) relative to each other, the specific delivery volume of the pump is adjusted,
c) a piston (7/8) which is coupled for the adjustment of the conveyor wheels (1, 2) with at least one of the conveyor wheels (1, 2) and forms a pivot bearing for this at least one of the conveyor wheels,
d) wherein by an axial displacement of the piston (7/8) an axial engagement length of the piston ...

Description

  • The invention relates to a positive displacement pump with an adjustment of its specific delivery volume. The pump comprises at least two rotatably mounted conveying wheels, which are in a conveying engagement with each other to promote a working fluid under pressure increase from a low pressure side of the pump to a high pressure side of the pump in a rotary drive of at least one of the conveyor wheels. In preferred uses, the pump is used to supply an internal combustion engine with lubricating oil, i. H. it forms in this use the lubricating oil pump of the engine. The specific delivery volume is understood to mean the delivery volume of the pump [delivery volume / rotational speed] which is related to a rotational speed of one of the delivery wheels.
  • In displacement pumps, such as gear pumps, the specific delivery volume is constant and the delivery volume therefore proportional to the speed of the conveyor wheels, as long as the degree of filling of the conveyor cells formed by the conveyor cells is 100%.
  • In many applications, this proportionality is disturbing. In a press, for example, a high delivery quantity of pressure oil is necessary for the rapid traverse, but in the final phase of the working stroke of the press, only high pressure is required, while the demand for oil delivery volume goes back to zero. Since the drive speed of the pump usually remains constant, resulting in a high pressure surplus oil flow, the energy loss flows back into an oil tank.
  • Disturbing is an excess of oil flow, for example, in engine lubrication pumps and oil supply pumps of automatic transmissions of motor vehicles. Although these units require at low engine speed and thus low pump speed, especially at idle, a minimum delivery volume and at high speed a minimum oil pressure, but the fluid requirement at higher speed is well below the proportional line.
  • The specific delivery volume of pumps should be adapted to the needs of the consumer, such as an internal combustion engine, an automatic transmission or a press, d. H. it should be adjustable. The adjustment of the specific delivery volume takes place in known positive displacement pumps by adjusting the conveying engagement of the conveyor wheels. For this purpose, a whole series of adjustment mechanisms are known.
  • State of the art
  • In the DE 198 47 132 C2 an external gear pump is described, the specific delivery volume is regulated, so that it increases from a predetermined limit speed with further increasing input speed of the pump only disproportionate to the speed or even remains constant. The pump has two externally toothed spur gears, which are accommodated in a delivery chamber of the pump and mesh with each other. The conveying engagement is formed by the tooth engagement of the two spur gears. To limit the specific delivery volume of the pump, one of the two spur gears is rotatably mounted on a piston. The piston is slidably received in a housing of the pump and is applied for the purpose of its displacement on a piston side with the pumped by the pump fluid from the high pressure side of the pump. The fluid pressure counteracts a spring element on the opposite side of the piston. From the equilibrium of forces of fluid pressure and spring force results in the displacement position of the piston and thus also the axial position of the spur gear mounted on the piston relative to the other, non-displaceable spur gear. It is therefore changed by the sliding movement of the piston, the axial engagement length of the two spur gears and thereby the specific delivery volume of the pump. The piston is acted upon by the fluid of the high pressure side so that with increasing fluid pressure, the engagement length of the two spur gears against the restoring spring force of the spring element is reduced.
  • With regard to the adjustment of the specific delivery volume comparable external gear pumps are from the DE 41 21 074 A1 and the DE 35 28 651 A1 known.
  • From the EP 1 182 351 A1 An internal gear pump is also known whose specific delivery volume is adjustable. The pump has an externally toothed internal gear and an internally toothed ring gear, which are rotatably received about eccentric axes of rotation in a delivery chamber of the pump housing and are rotationally driven for fluid delivery. The two conveyor wheels form in the direction of rotation of a point deepest meshing to a point of lowest meshing expanding delivery cells and from the point of lowest meshing to the point of deepest meshing compressed delivery cells. In the area of the expanding delivery cells, an inlet opens into the delivery chamber and in the region of the compressing delivery cells an outlet opens into the chamber. The expanding fluid cells draw fluid from the inlet and the compressing delivery cells displace the fluid through the outlet. In order to adjust the specific delivery volume of the pump, the ring gear is rotatably mounted in an eccentric ring. The eccentric ring is likewise rotatably mounted in the housing about an axis of rotation which is eccentric to the axis of rotation of the ring gear. By adjusting the angular position of the Eccentric ring relative to the inlet and the outlet, the adjustment of the specific delivery volume is made. In order to adjust the rotational angular position of the eccentric ring, a piston acts via a rack on the eccentric ring, so that axial piston movements are transmitted in Verstelldrehbewegungen of the eccentric ring. The piston is, as already the piston in the known external gear pumps, acted upon on one side with the fluid pressure of the high pressure side and the fluid pressure counteracting the spring force of a restoring spring element.
  • The known adjustment mechanisms require large restoring forces during the entire pump operation. If the restoring element, which counteracts the fluid pressure acting on the piston, is a spring element, the spring space accommodating the spring element must be very long because of the required spring forces. Optionally, the spring element must be designed as a multiple spring, for example double spring.
  • From the DE 100 43 842 A1 is a gear pump known whose specific delivery volume is adjustable. The pump comprises a displacement-changing displacement unit which is displaceable between a first pressure chamber and a second pressure chamber, wherein in the second pressure chamber acting on the displacement unit compression spring is arranged. The pressure chambers are in hydraulic operative connection via a connecting line in which a throttle is arranged. The second pressure chamber is connected via the throttle in all operating states of the pump with the high pressure side.
  • task
  • It is an object of the invention to provide a positive displacement pump, which has a space-saving, inexpensive and stable in continuous operation adjustment for an adjustment of the specific delivery volume of the pump.
  • The invention relates to a positive displacement pump, namely external gear pump whose specific delivery volume is adjustable and which comprises a housing with a delivery chamber, at least two conveyor wheels received in the delivery chamber and an adjustment device for the adjustment of their specific delivery volume. In the delivery chamber open at least one inlet and at least one outlet for a fluid to be pumped by the pump. The inlet is connected to a low pressure side of the pump and the outlet is connected to a high pressure side of the pump. As a low-pressure side, the entire fluid guidance system from a fluid reservoir to the inlet into the delivery chamber, d. H. the entire fluid guide system understood upstream of the inlet including the fluid supply channels formed in the housing. The high-pressure side is understood to mean the entire fluid-guiding system immediately downstream of the outlet from the delivery chamber to at least one next aggregate, which is supplied with the fluid by the pump. If a plurality of units must be supplied, that part of the fluid management system forms the high-pressure side, which extends from the outflow downstream to at least including the last of the units to be supplied.
  • The at least two, preferably exactly two, conveyor wheels are rotationally drivable and are in a conveying engagement with one another in order to convey the fluid under pressure increase from the inlet to the outlet. In order to be able to adjust the specific delivery volume of the pump, the delivery wheels are adjustable relative to each other or relative to the inflow or relative to the outflow or relative to the inflow and outflow.
  • The adjusting device comprises a piston which is coupled for the adjustment of the conveyor wheels with at least one of the conveyor wheels. The coupling consists in that one of the conveying wheels, as in the known external gear pumps, rotatably mounted on the piston and is axially displaceable together with the piston and relative to the other conveying wheel.
  • The adjusting device further includes a first pressure chamber and a second pressure chamber each for acting on the piston with the fluid pressure of the high pressure side. The piston projects with a first piston surface into the first pressure chamber and with a second piston surface into the second pressure chamber. The fluid pressure acting on the piston in the first pressure chamber counteracts the fluid pressure acting on the piston in the second pressure chamber. The two pressure chambers are each connected via a fluid connection with the high pressure side.
  • The adjusting device further comprises a spring element, preferably a mechanical spring, which counteracts the fluid pressure acting on the piston in the first pressure chamber. A spring chamber, in which the spring element is arranged, is preferably formed by the second pressure chamber. In principle, however, it would also be conceivable that the spring element is arranged outside the second pressure chamber and counteracts the fluid pressure in the first pressure chamber.
  • In an initial position of the piston, the fluid pressures in the two pressure chambers are preferably the same, so that the spring element is not loaded in the rest position with fluid pressure. The fluid pressures can in principle, however, in the Starting position to be chosen differently. Thus, the fluid pressure in the second pressure chamber may be smaller than the fluid pressure in the first pressure chamber to maintain the spring element in the initial position of the piston under a bias. In the initial position of the piston, the position of the conveyor wheels is preferably such that the pump has its largest specific delivery volume. By the adjusting movement of the piston against the spring force of the spring element, the specific delivery volume is thus reduced in this preferred embodiment. But it is also quite another course of the specific delivery volume above the speed conceivable in which the specific delivery volume of one of the initial position of the piston corresponding output value increases with increasing speed, for example, first and falls when exceeding a maximum specific delivery volume corresponding drive speed.
  • The adjusting device furthermore has a regulator which regulates the fluid pressure of at least one of the two pressure chambers as a function of a control variable of the high-pressure side which determines the fluid delivery, so that a delivery characteristic of the pump that is advantageous with respect to the specific delivery volume is achieved. The control variable is taken from the high-pressure side and is the fluid pressure and will be referred to below as a fluid control pressure to distinguish from other fluid pressures, to indicate the use as a controlled variable. In particular, the fluid control pressure can be applied directly to a regulator designed as a fluidic regulator in order to influence the regulator.
  • By the controller, the pressure of the second pressure chamber is changed, for example, with increasing fluid control pressure continuously or more preferably reduced in one or more stages. It would also be conceivable to regulate the pressures in both pressure chambers in a coordinated manner in order to obtain the desired delivery characteristic.
  • The controller is preferably a multi-state controller, which can assume a plurality of discrete switching states or switching positions. Which of the switching positions the controller occupies is determined by the controlled variable. If, according to the patent, the control variable is the fluid control pressure and, as a regulator, a fluidic regulator; in particular a control valve, used, the switching position is preferably determined by the difference between the force exerted by the fluid control pressure, and a restoring force counteracting the fluid control pressure. In a simple, particularly preferred embodiment, the regulator is a two-state regulator, which connects the second pressure chamber in a first of two switching positions with the high pressure side of the pump and in the second switching position with the low pressure side of the pump. Preferably, a control valve forms the regulator, more preferably a multi-way valve with at least two switching positions.
  • The positive displacement pump is an external gear pump. The first and the second impeller are each formed by an externally toothed spur gear. The delivery chamber is essentially formed by the lateral surfaces of the housing, which surround the meshed spur gears, and sealing surfaces which face axially opposite the end faces of the spur gears. One of the two spur gears is rotatably mounted on the piston and axially geradverschiebbar together with the piston in the housing relative to the other spur gear. The piston forms the so movably mounted spur axially facing sealing surfaces of the delivery chamber. The first pressure chamber and the second pressure chamber are in this embodiment in the axial extension to both sides of the displaceable spur gear. Preferred details of an external gear pump are in the DE 198 47 132 C2 described.
  • Furthermore, reference is made to the subclaims with regard to further particularly preferred features of the invention.
  • embodiment
  • With reference to figures, a preferred embodiment of the invention will be described below. Show it:
  • 1 an external gear pump in a longitudinal section and
  • 2 the external gear pump in a cross section.
  • 1 in a longitudinal section and 2 in the cross section AA show an external gear pump, which is regulated with respect to their specific delivery volume so that in a lower speed range, the delivery volume of the pump and together with it the fluid pressure of the high pressure side with the speed increase more than in an upper region. In the exemplary embodiment, the control is two-stage with a constant specific delivery volume in the lower speed range up to the limit speed. When the limit speed is reached, the pump is stopped, ie the specific delivery volume is reduced so that the fluid pressure remains constant for a further increase in speed.
  • A housing 3 The pump forms a delivery chamber 4 in which a first conveyor wheel 1 about its axis of rotation D 1 and a second impeller 2 are rotatably received about its axis of rotation D 2 . The conveyor wheels 1 and 2 are externally toothed spur gears. The both external gears are with 1a and 2a designated. The conveyor wheels 1 and 2 are with their gearing 1a and 2a in a meshing tooth engagement. In the engagement area of the conveyor wheels 1 and 2 flows to one side of an inlet 5 and to an opposite side an outlet 6 how best in 2 can be seen. In a rotary drive of the conveyor wheels 1 and 2 becomes fluid from the inlet by the tooth engagement 5 sucked in and out through the outlet 6 displaced under pressure increase. In 2 is this conveying operation by directional arrows for the fluid and the direction of rotation of the conveyor wheels 1 and 2 indicated. The entire fluid guide in and outside the pump up to the pressure increase is understood in the context of the invention as a low pressure side.
  • The rotary drive of the conveyor wheels 1 and 2 via a drive shaft, that of the housing 3 is rotatably mounted. The conveyor wheel 1 is mounted on the drive shaft torsion and verschiebegesichert. The driven conveyor wheel 1 can relative to the housing 3 only perform rotational movements about its axis of rotation D 1 .
  • The second conveyor wheel 2 is between two piston bodies 7 and 8th on a connecting section, which is the two piston body 7 and 8th connects to each other, about its axis of rotation D 2 rotatably mounted and relative to the piston bodies 7 and 8th not movable. The two piston bodies 7 and 8th form a double-acting piston in a bore of the housing 3 along the axis of rotation D 2 of the conveyor wheel 2 back and forth is straight. By a sliding movement, the piston 7 / 8th together with the second conveyor wheel 2 relative to the first conveyor wheel 1 performs, the axial length of the meshing of the two conveyor wheels 1 and 2 and as a result, the specific delivery volume of the pump changed.
  • The housing 3 forms to one side of the piston 7 / 8th a first pressure room 9 and on the other side of the piston 7 / 8th a second pressure chamber 10 , the first pressure chamber 9 along the axis of rotation D 2 is opposite. The piston 7 / 8th seals with his piston body 7 the first pressure room 9 and with his piston body 8th the second pressure chamber 10 from. The in the first pressure chamber 9 with a pressure P 9 acted upon piston surface of the piston body 7 is the same size as the one in the second pressure chamber 10 with a pressure P 10 acted upon piston surface of the piston body 8th , so that on both opposite sides of the piston the same force on the piston 7 / 8th works when in the two pressure chambers 9 and 10 the same pressure works.
  • In the second pressure chamber 10 is a mechanical compression spring as a spring element 13 added. The spring element 13 is axially at a bottom of the pressure chamber 10 and axially opposite to the piston body 8th supported. When the spring element 13 axially under compressive stress, it acts in the first pressure chamber 9 on the piston 7 / 8th acting fluid pressure P 9 against. The second pressure chamber 10 at the same time also forms the spring space, ie the installation space, for the spring element 13 ,
  • To the pressure chambers 9 and 10 being able to put pressure on becomes the first pressure chamber 9 from a first fluid connection 11 connected to the high pressure side. To the second pressure chamber 10 to connect to the high pressure side is a second fluid connection 12 intended. The second fluid connection 12 is via a control valve 15 connected to the high pressure side. The control valve 15 is a directional control valve with two switch positions. The control valve 15 joins in a 1 shown first switching position the second fluid connection 12 with the first fluid connection 11 and thus creates the connection of the second pressure chamber 10 to the high pressure side. In a second switching position, it blocks the first fluid connection 11 , so the first pressure chamber 9 remains connected to the high pressure side, and connects the second pressure chamber 10 with the low pressure side. In the embodiment, the second pressure chamber 10 in the second switching position of the control valve 15 with a fluid reservoir 20 connected. In preferred uses of the pump, for example as a lubricating oil pump for an internal combustion engine, it is the fluid reservoir 20 around a fluid sump.
  • The fluid connections 11 and 12 are arranged in the immediate vicinity of the pump, preferably they are in the housing 3 the pump integrated. Preferably, the control valve is also 15 in the case 3 integrated or at least outside of the housing 3 assembled. The first pressure room 9 and in the first switching position of the control valve 15 also the second pressure chamber 10 Thus, they preferably receive their pressurized fluid from within the housing 3 , In principle, however, it would also be conceivable for them to supply their pressurized fluid from a suitable point on the high-pressure side downstream of the housing 3 Respectively.
  • The control valve 15 is switched in response to a fluid control pressure P R. It is powered by a reset element 16 , Which is designed in the embodiment as a mechanical spring element, held in the first switching position, which is a starting position of the control valve 15 and the piston 7 / 8th equivalent. The reset element 16 counteracts the fluid control pressure P R. As soon as the fluid control pressure P R has reached a limiting pressure, the control valve jumps 15 against the restoring force of the return element 16 from the first switching position to its second switching position.
  • The fluid control pressure P R is removed from the high pressure side of the pump. Basically, he can indeed directly in the delivery chamber 4 at the high pressure side, at the outlet 6 , from inside the case 3 behind the delivery chamber 4 or in the immediate vicinity downstream of the housing 3 However, according to the patent, the fluid control pressure P R is removed at a point on the high pressure side at which the fluid pressure corresponds as closely as possible to the fluid pressure of a consumer to be supplied by the pump with the fluid. If the consumer is, for example, the reciprocating engine of a motor vehicle, the fluid control pressure P R is preferably the pressure of the so-called main gallery. Accordingly, the control valve 15 connected via a fluid connection with the relevant point of the high pressure side. A suitable location for the decrease of the fluid control pressure P R is located in particular between the consumer and a last filter in front of the consumer.
  • The operation of the pump control is described below for a preferred use of the pump as a lubricating oil pump for a reciprocating engine, wherein it is assumed that the pump is driven by the crankshaft of the engine directly or via a transmission and thus in dependence on the speed of the engine.
  • The setting of the control valve 15 is such that it occupies its first switching position in a lower speed range of the engine, which may extend, for example, a passenger car to 1500 or 2000 revolutions per minute, in which there are both pressure chambers 9 and 10 connects to the high pressure side and prevails in both pressure chambers, the same pressure P 9 = P 10 of the high pressure side. The pressure P 10 in the second pressure chamber 10 is therefore in the lower engine speed range as high as the pressure P 9 in the first pressure chamber 9 , In the lower speed range, especially in engine idling, the largest possible specific volume is desired to ensure the supply of lubricating oil to the engine, even at low speeds can. In the first switching position of the control valve 15 is the axial engagement length of the two conveyor wheels 1 and 2 therefore, as in 1 shown, maximum. The maximum engagement length corresponds in the embodiment of the length of the two equal length conveyor wheels 1 and 2 , It will zero promotion, especially at standstill of the conveyor wheels 1 and 2 , and, as I said, in the lower speed range of the engine and thus also in the lower speed range of the conveyor wheels 1 and 2 to one of the control valve 15 maintained predetermined limit speed.
  • The first conveyor wheel 1 is rotatably driven about its axis of rotation D 1 of the crankshaft ago and drives on the meshing the second impeller 2 also about its axis of rotation D 2 . The meshing action lube oil from the low pressure side, ie from the oil sump 20 through the inlet 5 in the delivery chamber 4 sucked. In the delivery chamber 4 the fluid is conveyed through a delivery chamber, which is from the outer surfaces of the housing 3 around the tooth tip circles of the conveyor wheels 1 and 2 around and sealed by axial sealing surfaces, to the outlet 6 , The axial sealing surfaces are for the feed wheel 1 from the case 3 and for the conveyor wheel 2 from the two piston bodies 7 and 8th educated. On the high pressure side of the pump, the oil is pumped to the engine via an oil filter, cooled behind the engine in a cooler, and finally into the sump 20 returned and relaxed to the pressure of the low pressure side.
  • If the engine speed and thus also the pump speed are increased, then the fluid control pressure P R increases according to the pump characteristic. If the limit speed is reached, and the fluid control pressure P R is so large that under its action, the control valve 15 switches to its second switching position. The second pressure chamber 10 is in the second switching position of the control valve 15 with the low pressure side, namely with the sump 20 connected. In the second switching state of the control valve 15 thus stand the first pressure chamber 9 under the high pressure P 9 of the high pressure side and the second pressure chamber 10 under the negligible pressure P 10 of the low pressure side. The piston 7 / 8th and together with it rotatably mounted by him second conveyor wheel 2 are under the action of the pressure P 9 against the elasticity force of the spring element 13 moved axially. By shifting the engagement length of the conveyor wheels 1 and 2 and concomitantly reduces the specific delivery volume of the pump. The reduction of the specific delivery volume has a lowering of the fluid pressure on the high pressure side, ie the fluid control pressure P R result. If the fluid control pressure P R falls below the limit, the control valve drops 15 back to its first switching position, in which there is the second pressure chamber 10 over the two fluid connections 11 and 12 with the first pressure chamber 9 combines. The pump is thus regulated from reaching the limit speed for compliance with the limit value of the fluid control pressure P R. By regulating a pressure limit and thus a delivery volume limit of the pump is obtained. The fluid pressure of the high pressure side increases in the lower speed range of the driven first impeller 1 up to the limit speed substantially proportional to the speed and buckles at the limit speed in a horizontal, ie the fluid pressure of the high pressure side remains constant in the speed range above the limit speed.
  • By replacement of the control valve 15 by another control valve with more than two switching positions and other pressure curves can be realized. Thus, it may be advantageous, for example, if the described pressure curve is set in the lower speed range and an adjoining middle speed range, but the fluid pressure of the high pressure side returns to the speed of the driven first drive wheel in a high speed range following the middle speed range 1 increases. For the realization of such a pressure curve could be the control valve 15 of the embodiment are replaced by a control valve with three switching positions and the second pressure chamber 10 in the upper speed range via a pressure reducing element, such as a diaphragm, connect to the high pressure side to the spring element 13 to support.
  • LIST OF REFERENCE NUMBERS
  • 1
    conveyor wheel
    1a
    gearing
    2
    conveyor wheel
    2a, 2i
    gearing
    3
    casing
    4
    delivery chamber
    5
    inlet
    6
    outlet
    7
    piston body
    8th
    piston body
    9
    pressure chamber
    10
    pressure chamber
    11
    fluid communication
    12
    fluid communication
    13
    spring element
    14
    15
    Regulator, control valve
    16
    Return element
    17
    18
    19
    20
    fluid sump
    D 1
    axis of rotation
    D 2
    axis of rotation
    P 9
    fluid pressure
    P 10
    fluid pressure
    P R
    Fluid control pressure

Claims (4)

  1. External gear pump with adjustable specific delivery volume, comprising: a) a housing ( 3 ), which is a delivery chamber ( 4 ) into which at least one inlet (on a low-pressure side of the pump) 5 ) for fluid and at a high pressure side of the pump at least one outlet ( 6 ) for fluid, b) at least two in the delivery chamber ( 4 ), rotatably driven, externally toothed spur gears ( 1 . 2 ) which are in meshing engagement with each other, namely, meshing tooth engagement to remove the fluid from the inlet (10). 5 ) to the outlet ( 6 ), the conveyor wheels ( 1 . 2 ) are adjustable so that by an adjustment of the conveyor wheels ( 1 . 2 ) relative to each other, the specific delivery volume of the pump is adjusted, c) a piston ( 7 / 8th ), for the adjustment of the conveyor wheels ( 1 . 2 ) with at least one of the conveyor wheels ( 1 . 2 ) is coupled and forms a pivot bearing for this at least one of the conveyor wheels, d) wherein by an axial displacement of the piston ( 7 / 8th ) an axial engagement length of the conveyor wheels ( 1 . 2 ) and thereby the specific delivery volume of the pump is adjusted, e) a first pressure chamber ( 9 ) and a second pressure chamber ( 10 ) for loading the piston ( 7 / 8th ) each with high-pressure fluid, with one on the piston ( 7 / 8th ) acting fluid pressure (P 9 ) of the first pressure chamber ( 9 ) one on the piston ( 7 / 8th ) acting fluid pressure (P 10 ) of the second pressure chamber ( 10 ), f) a first fluid connection ( 11 ), the first pressure chamber ( 9 ) connects to the high pressure side, and a second fluid connection ( 12 ), the second pressure chamber ( 10 ) connects to the high pressure side, g) a spring element ( 13 ) that in the first pressure chamber ( 9 ) on the piston ( 7 / 8th ) counteracts acting fluid pressure (P 9 ), h) and a controller ( 15 ), the fluid pressure (P 10 ) of the second pressure chamber ( 10 ) as a function of a control variable (P R ) which is decisive for the fluid delivery of the pump, namely a fluid control pressure (P R ) of the high-pressure side, i) the regulator ( 15 ) in a first controller state, the second pressure chamber ( 10 ) connects to the high-pressure side of the pump and in a second controller state, the second fluid connection ( 12 ) and the second pressure chamber ( 10 ) connects to the low pressure side of the pump when the controlled variable (P R ) exceeds a predetermined value, j) and wherein the controller ( 15 ) a connecting line is connected, by the under the fluid control pressure (P R ) standing high-pressure fluid from outside the housing ( 3 ) of the pump to the regulator ( 15 ) can be fed.
  2. External gear pump according to the preceding claim, characterized in that the regulator ( 15 ) is or comprises a control valve, wherein the fluid control pressure (P R ) is a restoring force of a return element ( 16 ) counteracts.
  3. External gear pump according to one of the preceding claims, characterized in that the regulator ( 15 ) is a control valve with at least two discrete switch positions (controller states), which are switched in response to the controlled variable (P R ).
  4. External gear pump according to one of the preceding claims, characterized in that the regulator ( 15 ) in the first controller state, the second pressure chamber ( 10 ) with the first pressure chamber ( 9 ) connects.
DE2002122131 2002-05-17 2002-05-17 Positive displacement pump with delivery volume adjustment Expired - Fee Related DE10222131C5 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE2002122131 DE10222131C5 (en) 2002-05-17 2002-05-17 Positive displacement pump with delivery volume adjustment

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE2002122131 DE10222131C5 (en) 2002-05-17 2002-05-17 Positive displacement pump with delivery volume adjustment
ES03011033T ES2367969T3 (en) 2002-05-17 2003-05-19 Volumetric pump with displaced volume adjustment.
AT03011033T AT515636T (en) 2002-05-17 2003-05-19 Displacement pump with conveyor volume adjustment
EP20030011033 EP1363025B1 (en) 2002-05-17 2003-05-19 Variable capacity pump

Publications (3)

Publication Number Publication Date
DE10222131A1 DE10222131A1 (en) 2003-12-04
DE10222131B4 DE10222131B4 (en) 2005-05-12
DE10222131C5 true DE10222131C5 (en) 2011-08-11

Family

ID=29265354

Family Applications (1)

Application Number Title Priority Date Filing Date
DE2002122131 Expired - Fee Related DE10222131C5 (en) 2002-05-17 2002-05-17 Positive displacement pump with delivery volume adjustment

Country Status (4)

Country Link
EP (1) EP1363025B1 (en)
AT (1) AT515636T (en)
DE (1) DE10222131C5 (en)
ES (1) ES2367969T3 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009060188B4 (en) * 2009-12-23 2016-07-07 Schwäbische Hüttenwerke Automotive GmbH Adjustment valve for adjusting the delivery volume of a positive displacement pump with cold start function

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004002062A1 (en) * 2004-01-15 2005-08-04 Volkswagen Ag Gear pump with flow control
AT500629B8 (en) * 2004-05-27 2007-02-15 Tcg Unitech Ag Gear pump
DE102004028830A1 (en) * 2004-06-15 2005-12-29 Zf Friedrichshafen Ag Hydraulic pump has two intermeshing gear wheels each adjacent to a chamber
DE102006011200B4 (en) 2006-03-10 2014-11-13 Schwäbische Hüttenwerke Automotive GmbH & Co. KG External gear pump with discharge pocket
GB2436594A (en) * 2006-03-28 2007-10-03 Concentric Vfp Ltd A variable output pump assembly
DE102006018124A1 (en) * 2006-04-19 2007-10-25 Schwäbische Hüttenwerke Automotive GmbH & Co. KG Adjustable rotary pump with wear reduction
DE102006044810A1 (en) * 2006-09-22 2008-03-27 Bayerische Motoren Werke Ag Fluid pump i.e. external gear pump, has secondary pump wheel rotatably supported on adjustment piston relative to adjustment piston in axially immovable manner, where adjustment piston is pre-stressed in direction of rotation around axle
WO2010008575A1 (en) * 2008-07-18 2010-01-21 Becton, Dickinson And Company Dual chamber and gear pump assembly for a high pressure delivery system
DE102009019419B4 (en) 2009-04-29 2016-01-14 Schwäbische Hüttenwerke Automotive GmbH Rotary displacement machine with simplified bearing axle or shaft
DE102009019418B4 (en) 2009-04-29 2013-05-16 Schwäbische Hüttenwerke Automotive GmbH Circulating positive displacement pump with improved bearing lubrication
DE102009060189B4 (en) 2009-12-23 2017-07-13 Schwäbische Hüttenwerke Automotive GmbH Regulating device for adjusting the delivery volume of a pump
DE102010003574B4 (en) 2010-03-31 2012-02-09 Schwäbische Hüttenwerke Automotive GmbH Press assembly and method for producing a press composite
DE102010020299B4 (en) 2010-05-12 2013-05-16 Schwäbische Hüttenwerke Automotive GmbH Pump with friction clutch speed control
DE102010038430B4 (en) * 2010-07-26 2012-12-06 Schwäbische Hüttenwerke Automotive GmbH Positive displacement pump with suction groove
DE102010051141B3 (en) * 2010-11-11 2011-12-29 Dieter Voigt External gear-oil pump for combustion engine, has two gear wheels arranged in housing, and control piston arranged in stepped bore, where bore is formed as through-hole of housing and closed at side by cover
DE102011005408B4 (en) 2011-03-11 2014-02-13 Schwäbische Hüttenwerke Automotive GmbH Method for producing a joint in a pump or a camshaft phaser
DE102011013756A1 (en) * 2011-03-12 2012-09-13 Volkswagen Aktiengesellschaft Gear pump, particularly oil pump for internal combustion engine, has control valve, which is additionally connected with outlet over throttle in position of piston for connecting control fluid in fluid conducting manner
DE102012214503B4 (en) 2012-08-14 2017-10-12 Schwäbische Hüttenwerke Automotive GmbH Rotary pump with adjustable delivery volume, in particular for adjusting a coolant pump
JP6021623B2 (en) 2012-12-11 2016-11-09 三菱重工業株式会社 Inverter-integrated electric compressor
DE102014207070B4 (en) 2014-04-11 2016-11-24 Volkswagen Aktiengesellschaft Pump
CN105041639A (en) * 2015-08-27 2015-11-11 刘凡 External gearing variable gear pump
DE102015015481A1 (en) 2015-11-28 2016-07-21 Daimler Ag Positive displacement pump for a motor vehicle
DE102017117787A1 (en) 2017-08-04 2019-02-07 Schwäbische Hüttenwerke Automotive GmbH Adjustable external gear pump
DE102018211125B4 (en) * 2018-07-05 2020-03-26 Continental Automotive Gmbh Gear pump and heat engine with a gear pump

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2008952A1 (en) * 1970-02-26 1971-09-09
DE2218391A1 (en) * 1971-04-16 1972-10-26 Lucas Industries Ltd
US4259039A (en) * 1979-03-20 1981-03-31 Integral Hydraulic & Co. Adjustable volume vane-type pump
DE3446603A1 (en) * 1983-12-23 1985-07-11 Atos Oleodinamica Spa Adjustable lobed positive displacement pump for hydraulic drives
DE3528651A1 (en) * 1985-08-09 1987-02-19 Rohs Hans Guenther Prof Dr Ing Gear pump
DE4121074A1 (en) * 1991-06-26 1993-01-07 Pierburg Gmbh External gear pump - has main drive gear fixed inside housing and driven gear adjusted by pressure differential piston action
DE19736846A1 (en) * 1997-08-23 1999-03-04 Mannesmann Vdo Ag Pressure control arrangement
DE19847132C2 (en) * 1998-10-13 2001-05-31 Schwaebische Huettenwerke Gmbh External gear pump with delivery volume limitation
DE10043842A1 (en) * 2000-03-02 2001-09-06 Volkswagen Ag Gear pump with a displacement unit that changes the delivery rate
EP1182351A1 (en) * 2000-08-03 2002-02-27 Schwäbische Hüttenwerke GmbH Ring gear pump with eccentricity adjustment
DE10207350A1 (en) * 2001-02-23 2002-09-12 Joma Hydromechanic Gmbh Volume flow variable rotor pump
DE10127478A1 (en) * 2001-06-07 2002-12-12 Iav Gmbh Lubrication device, for internal combustion engine, has return valve response pressure corresponding to feed pressure ensuring lubricant pressure for permitted filter pressure drop

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3327978A1 (en) 1983-08-03 1985-02-21 Rexroth Mannesmann Gmbh Arrangement for loading a pressure-medium accumulator
DE3503491C2 (en) 1985-02-01 1988-04-21 Mannesmann Rexroth Gmbh, 8770 Lohr, De
GB8706630D0 (en) 1987-03-20 1987-04-23 Concentric Pumps Ltd Variable output oil pump
GB2265946B (en) * 1992-04-08 1995-01-18 Concentric Pumps Ltd Improvements relating to pumps
US6244839B1 (en) * 1997-11-14 2001-06-12 University Of Arkansas Pressure compensated variable displacement internal gear pumps

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2008952A1 (en) * 1970-02-26 1971-09-09
DE2218391A1 (en) * 1971-04-16 1972-10-26 Lucas Industries Ltd
US4259039A (en) * 1979-03-20 1981-03-31 Integral Hydraulic & Co. Adjustable volume vane-type pump
DE3446603A1 (en) * 1983-12-23 1985-07-11 Atos Oleodinamica Spa Adjustable lobed positive displacement pump for hydraulic drives
DE3528651A1 (en) * 1985-08-09 1987-02-19 Rohs Hans Guenther Prof Dr Ing Gear pump
US4740142A (en) * 1985-08-09 1988-04-26 Rohs Hans Gunther Variable capacity gear pump with pressure balance for transverse forces
DE4121074A1 (en) * 1991-06-26 1993-01-07 Pierburg Gmbh External gear pump - has main drive gear fixed inside housing and driven gear adjusted by pressure differential piston action
DE19736846A1 (en) * 1997-08-23 1999-03-04 Mannesmann Vdo Ag Pressure control arrangement
DE19847132C2 (en) * 1998-10-13 2001-05-31 Schwaebische Huettenwerke Gmbh External gear pump with delivery volume limitation
DE10043842A1 (en) * 2000-03-02 2001-09-06 Volkswagen Ag Gear pump with a displacement unit that changes the delivery rate
EP1182351A1 (en) * 2000-08-03 2002-02-27 Schwäbische Hüttenwerke GmbH Ring gear pump with eccentricity adjustment
DE10207350A1 (en) * 2001-02-23 2002-09-12 Joma Hydromechanic Gmbh Volume flow variable rotor pump
DE10127478A1 (en) * 2001-06-07 2002-12-12 Iav Gmbh Lubrication device, for internal combustion engine, has return valve response pressure corresponding to feed pressure ensuring lubricant pressure for permitted filter pressure drop

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009060188B4 (en) * 2009-12-23 2016-07-07 Schwäbische Hüttenwerke Automotive GmbH Adjustment valve for adjusting the delivery volume of a positive displacement pump with cold start function

Also Published As

Publication number Publication date
EP1363025A3 (en) 2006-04-19
EP1363025B1 (en) 2011-07-06
DE10222131B4 (en) 2005-05-12
DE10222131A1 (en) 2003-12-04
AT515636T (en) 2011-07-15
EP1363025A2 (en) 2003-11-19
ES2367969T3 (en) 2011-11-11

Similar Documents

Publication Publication Date Title
JP5815625B2 (en) Variable displacement vane pump with multiple control chambers
KR101454040B1 (en) Pump system
US8360745B2 (en) Air driven pump with performance control
US8444395B2 (en) Variable displacement variable pressure vane pump system
US6763797B1 (en) Engine oil system with variable displacement pump
EP0702755B1 (en) Multi-stage regulator for lubricant pumps with continuously variable feed rate
US4798561A (en) Hydraulic control apparatus for stepless transmission
US7210396B2 (en) Valve having a hysteretic filtered actuation command
JP5589068B2 (en) Lubricating oil pump system and lubricating oil pump
US5722815A (en) Three stage self regulating gerotor pump
US7946402B2 (en) Motor vehicle hydraulic pump
JP5873109B2 (en) Oil pump with selectable outlet pressure
US7588431B2 (en) Variable capacity pump/motor
US7018178B2 (en) Variable displacement pump and control therefore for supplying lubricant to an engine
CN101454177B (en) Mixer drum driving device
JP2005337502A (en) Hydraulic circuit for oil supply to automatic transmission for automobile
US5167493A (en) Positive-displacement type pump system
AU2008259733B2 (en) Hydroelectric device for closed-loop driving the control jack of a variable compression rate engine
US7179070B2 (en) Variable capacity pump/motor
US7549848B2 (en) Device for adjusting the pumping capacity of a lubricant pump for an internal combustion engine
US20030089107A1 (en) Power unit
US6739853B1 (en) Compact control mechanism for axial motion control valves in helical screw compressors
EP1463888B1 (en) Device for pressure regulation of hydraulic pumps
US4712377A (en) Control apparatus for hydraulic motor
US20040138025A1 (en) Pressure regulating valve

Legal Events

Date Code Title Description
OP8 Request for examination as to paragraph 44 patent law
8363 Opposition against the patent
8327 Change in the person/name/address of the patent owner

Owner name: SCHWäBISCHE HüTTENWERKE AUTOMOTIVE GMBH & CO. , DE

R034 Decision of examining division/fpc maintaining patent in limited form now final

Effective date: 20110405

R206 Amended patent specification

Effective date: 20110811

R119 Application deemed withdrawn, or ip right lapsed, due to non-payment of renewal fee

Effective date: 20131203