WO2005093259A1 - Pompe volumetrique a debit volumetrique variable - Google Patents

Pompe volumetrique a debit volumetrique variable Download PDF

Info

Publication number
WO2005093259A1
WO2005093259A1 PCT/EP2005/002625 EP2005002625W WO2005093259A1 WO 2005093259 A1 WO2005093259 A1 WO 2005093259A1 EP 2005002625 W EP2005002625 W EP 2005002625W WO 2005093259 A1 WO2005093259 A1 WO 2005093259A1
Authority
WO
WIPO (PCT)
Prior art keywords
displacement pump
pump according
ring
housing
adjusting member
Prior art date
Application number
PCT/EP2005/002625
Other languages
German (de)
English (en)
Inventor
Hermann Härle
Siegfried A. Eisenmann
Original Assignee
Haerle Hermann
Eisenmann Siegfried A
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 Haerle Hermann, Eisenmann Siegfried A filed Critical Haerle Hermann
Priority to EP05729835A priority Critical patent/EP1735534A1/fr
Publication of WO2005093259A1 publication Critical patent/WO2005093259A1/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
    • F04C14/10—Control 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
    • F04C14/14—Control 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 using rotating 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-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

Definitions

  • the invention relates to positive displacement pumps, in particular internal-axis gear pumps, but also vane pumps or, for example, also pendulum slide pumps, the volume flow of which can be changed as required, ie. H. is adjustable.
  • the pumps according to the invention are preferably used as lubricating oil pumps for internal combustion engines, the internal combustion engine preferably driving the lubricating oil pump in question.
  • the internal combustion engine can in particular be the drive motor, preferably the piston engine, of a vehicle.
  • the specific volume flow i.e. H. the volume flow delivered per revolution of a pump pump wheel, continuously adjustable.
  • the positive displacement pumps can also advantageously be used as supply pumps for automatic transmissions of vehicles and are preferably also driven in this way by the drive motor of the vehicle in question.
  • a pump according to the invention can advantageously also be used in other situations in which, for example the drive speed of the pump is constant and the fluid requirement of the unit to be supplied fluctuates for other reasons.
  • Displacement pumps designed as gerotor pumps, as they also relate to the invention, are known from DE 297 03 369 UI and EP 0 846 861 B1 based on them.
  • the external rotor of the ring gear set is rotatably mounted in a control ring, which surrounds the external rotor and rolls in the pump housing through an external internal toothing without slippage, so that according to these kinematic conditions during the control process, the eccentric axis of the ring gear set is up to 90 ° with respect to the Twisted housing. This makes it possible to regulate the delivery rate from a maximum to almost zero with the smallest possible adjustment path.
  • the volume flow variable displacement pump has a housing and a chamber which is formed in the housing and which has an inlet opening on a low-pressure side and an outlet opening for a fluid on a high-pressure side having.
  • the pump can be an internal gear pump, a vane pump or a pendulum slide pump.
  • the pump further comprises an inner rotor received in the chamber, which is rotatable about an axis of rotation, and a ring received in the chamber with a central ring axis which surrounds the inner rotor.
  • the ring forms at least one delivery cell in which the fluid is required from the low-pressure side to the high-pressure side.
  • An adjusting element is arranged in such a way that it rolls on the housing in a slip-free manner during an adjusting movement.
  • the inner rotor is fastened to the adjusting member so as to be rotatable about the axis of rotation. Furthermore, the position of the axis of rotation relative to the ring axis of the ring can be adjusted by the adjusting movement of the adjusting member.
  • the sealing of the delivery space formed between the inner rotor and the outer ring can be simplified.
  • the outer ring forms an outer rotor.
  • driving the toothed ring gear set formed by the inner rotor and the outer rotor is facilitated via the outer rotor.
  • the pump speed in the case of rotary drive via the outer rotor is advantageously increased in accordance with the ratio of the number of teeth of the inner rotor and outer rotor, as a result of which the pump can be reduced in diameter.
  • the outer ring of a pendulum slide pump such as that described in FR 980 766, is also a rotor.
  • the outer ring can be fixed relative to the housing, or the housing itself can form the inner cylinder surface for an impeller that forms the inner rotor.
  • a Nerstellorgan causing the adjustment of the specific volume flow does not surround the inner rotor and the outer ring, but is arranged axially next to it. It when the arrangement of the adjusting member next to the inner rotor and or the outer ring is combined with the adjustment of the specific volume flow by adjusting the inner rotor is particularly advantageous.
  • the pivoting of the The inner rotor through the adjusting member is preferably such that the adjusting member takes the inner rotor with it in its own adjusting movement, in that the inner rotor and the adjusting member are rigidly connected to one another with respect to the adjusting movement.
  • the adjusting member can, for example, have a toothing which is in a tooth engagement with an adjusting movement with a toothing of the housing.
  • the toothing of the adjusting member is preferably a circular arc toothing. For example, a center point of a flank circle of a tooth of the toothing of the adjusting element can roughly describe a hypocycloid when it rolls on the housing.
  • Such a control pump according to the invention is therefore also suitable for small-volume internal combustion engines in which particular importance is attached to reducing the hydrostatic losses and the amount of oil circulated at high speed.
  • the compactness of a variable displacement pump according to the invention can hardly be surpassed. Since the shaft bearings are free of any hydrostatic load and are only loaded by the tension cord of a preferably used belt transmission for the drive, the diameter of the shaft can be reduced. The smaller effective barrel width also improves the suction capacity and reduces the risk of cavitation. Because of the increased speed, the volumetric efficiency is also improved. This is also because the tooth drive engagement between the outer rotor and the inner rotor now runs at the point of the deepest tooth engagement, so that the pressure side of the toothing is better sealed off from the suction side.
  • Preferred embodiments correspond when the adjustment is effected hydraulically by applying a fluid pressure to the adjusting element which is caused by the High pressure side of the pump is returned to the adjusting member.
  • the high-pressure side of the pump extends from the high-pressure side of the pump chamber to the location or locations of the aggregate or the multiple aggregates to be supplied, from which or from which the fluid is returned to a fluid reservoir in a pressure-relieved manner. It can also be advantageous to tap the fluid pressure on the high-pressure side of the pump at a location outside the positive displacement pump and to apply the pressure to the adjusting element for regulating the volume flow. For example, the pressure can be tapped from a main crankshaft gallery of the engine.
  • the fluid pressure acting on the high-pressure side in the pump chamber in combination with the fluid pressure returned to the adjusting member, generates the adjusting force for the adjustment.
  • the adjusting force can, for. B. are formed from at least one of the two hydraulic adjustment forces, which act on the adjusting member or on the inner rotor.
  • the adjusting member can be adjusted with an adjusting force against the force of an elastic component.
  • the two adjusting forces are advantageously positively superimposed on one another, preferably by generating adjusting moments in the same direction. In this way, a particularly sensitive reaction to pressure changes can be achieved.
  • the invention thus also relates to a variable-volume displacement pump with the generic features of at least one of the independent claims in combination with the return of the fluid pressure to the adjusting member and loading of the adjusting member with the returned fluid pressure in such a direction that the adjusting force generated in such a way that an adjusting force which is generated on a fluid pressure on the high pressure side of the pump chamber acting on an inner rotor and an outer ring, is positively superimposed by the sum of both forces being greater than each of the two individual forces.
  • the ease of adjustment of the control pump has the advantage that the hydraulic adjustment forces of the inner rotor via the bearing journal, on the one hand, and those between the adjustment member, which is preferably formed as an adjustment plate, and the housing, and do not subtract, as in the known adjustment pump.
  • This advantage plays a major role, especially during a cold start, where you have to quickly adjust to a zero delivery rate to protect the oil filter and the oil pipes.
  • an additional pressure relief valve had to be provided here due to the inertia of the zero adjustment.
  • this configuration is preferably combined with the adjustment of the inner rotor or the arrangement of the adjustment member axially next to the inner rotor and / or the outer ring and particularly preferably with these two features.
  • Circular arc toothing on the adjustment plate is best suited so that the internal toothing in the housing, which preferably has one tooth more than the external toothing of the adjustment plate, can be machined with a rotating cutting tool (boring bar), as is known from the known control pump with control ring in Fig 10 of EP 0 846 861 B1 is known.
  • the center of the flank circle of the tooth on the adjustment plate describes a hypocycloid when it rolls off in the housing, which, however, is not entirely free of overlap in practice. When rolling, there is therefore a radial vertical runout, so that the eccentricity of the control plate in the housing fluctuates.
  • the size and / or the angular position of an eccentricity between the axis of rotation of the inner rotor and the central ring axis of the ring can be adjusted by the adjustment movement.
  • a fluctuation in the eccentricity can, however, be undesirable in the pump runner because it leads to noise and wear on the pump teeth.
  • Guide cylinders or cylinder segments which roll against each other are therefore preferably provided on the adjustment plate and on the housing (in the drawing in this case on the pump housing) with diameters whose difference is equal to twice the eccentricity of the pump running assembly.
  • the adjustment plate does not roll in the coarse toothing caused by the system, but on the two precisely machined circular cylinders.
  • the difference in the diameters of these guide cylinders with respect to the control plate and the housing is equal to 2e, where e means the eccentricity of the pump delivery set, preferably the pump runner set, and the toothing between the control plate and the housing.
  • e means the eccentricity of the pump delivery set, preferably the pump runner set, and the toothing between the control plate and the housing.
  • Eccentric chucks are not required to machine the housing parts, since the shaft and outer rotor bearings are concentric.
  • the depth of the housing internal toothing is minimized and no longer has to be machined across the entire width of the barrel set as in the known construction.
  • This toothing can be produced on a CNC machine with a C-axis with path-controlled hsc (high speed cutting) spindle unit in one clamping together with the other machining operations with high precision. This results in a considerable reduction in the time required for machining the housing teeth.
  • the subject matter of the invention is shown using the example of a controllable internal gear pump arranged in the oil sump for a four-cylinder car engine.
  • this does not mean that the invention is limited to such an application.
  • the control pump would sit at the end of a continuous transmission input shaft, so that in this case the sprocket shown in the drawing is omitted, and instead the pump shaft is coupled in a rotationally rigid manner to the transmission input shaft.
  • FIG. 5 shows the same view as in FIG. 4, but in the position in which the pump has the minimum possible delivery rate
  • Fig. 6 is a longitudinal section through the pump along the section line D-D of Fig. 5 and
  • the direction of rotation of the running set of the pump may be to explain the function in the individual figures in the indicated arrow direction 32, so that the respective suction and pressure side is clearly given in accordance with the expanding and compressing delivery cells of the teeth.
  • the suction port 31 is arranged on the suction side of the barrel set, on which the control spring 28 can also be seen.
  • the spaces of the control spring 28, the AbroU cylinder 24 and 25 and the toothing parts shown in Figures 4, 5, 6 and 7 on the right in the picture between the control plate 13 and the housing 1 are under suction pressure, since the control plate 13 between the housing cavern floor 33 and the housing-cover parting line is axially sealed but movably fitted.
  • FIGS. 1 and 4 show the center point of the inner rotor in a position in which the pump has the greatest possible delivery rate, since the eccentric axis EE (in FIG. 1) of the gear teeth with the axis of symmetry of the suction and pressure kidneys in the housing and in the adjusting plate 13 coincides.
  • This position is always required when the pump speed is low, when the oil viscosity is relatively low, i.e. when the engine is warm and especially when it is hot idling, so that the oil consumers of the engine are supplied with a sufficient amount of oil at sufficient oil pressure.
  • the minimum pressure in the pressure chamber 35 should not drop significantly below 1 bar, even in the case of increased bearing play of the engine parts due to wear.
  • This maximum position is guaranteed by a precisely calculated preload of the control spring, which holds the adjustment plate 13 against a stop 36.
  • the instantaneous pole for the rotational mobility of the control plate lies at M1 in FIG. 4.
  • a rotation of the adjusting plate 13 by only 9 degrees in the clockwise direction produces a rotation of the eccentricity axis e of the ring gear set by 90 degrees in the counterclockwise direction.
  • the expanding and compressing delivery cells in the gear wheel set are thus opposite the housing and thus opposite the kidney-shaped suction and pressure kidneys also rotated by 90 degrees, compared to the adjustment plate 13 even by 99 degrees. This means that it is no longer possible to pump the pump. Now only a fluid exchange takes place within the suction and pressure kidneys between the converging and diverging tooth chambers.
  • the position P2 i.e. a 90 degree rotation of the center point Di of the inner rotor 4 according to FIG. 5, of course, never occurs in normal engine operation because the engine bearings always have a finite oil requirement as the speed of the overall system increases, but this is by no means proportional the speed increases in contrast to the flow rate of a non-regulated pump.
  • the oil requirement of the engine increases only approximately proportionally with the system pressure in the pressure chamber 35, adapted to the flow resistance of all oil consumers, to the viscosity of the oil and to the state of wear of the shaft bearings of the engine.
  • the floating state of the control system of the variable displacement pump according to the invention thus automatically adjusts itself so that the delivery rate of the pump exactly covers the oil requirement in the respective operating state of the overall system.
  • the designer has the option of adapting the variable pump to the motor by varying the preload and the steepness of the spring characteristic. A new pump therefore does not necessarily have to be designed for each motor size, as long as the size range is within certain limits.
  • the adjusting plate 13 does not roll on the part circles of the toothing between the adjusting plate 13 and the housing 1, but on two rolling cylinder approaches on the adjusting plate and the housing.
  • the design of the cylinder extension on the adjusting plate is shown somewhat more clearly in FIGS. 7 and 8. In FIG. 3, the cylinder extension 24 in the housing can also be seen on the left in the picture.

Landscapes

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

Abstract

La présente invention concerne une pompe volumétrique à débit volumétrique variable, comprenant: a) un boîtier (1); b) une enceinte qui est formée dans le boîtier (1) et présente d'un côté basse pression une ouverture d'entrée (8), et d'un côté haute pression une ouverture de sortie (9) destiné à un liquide; c) un rotor interne (4) qui se trouve dans l'enceinte et peut tourner autour d'un axe de rotation (DI); d) un anneau (3) qui se trouve dans l'enceinte, comprend un axe central (DA), entoure le rotor interne (4) et constitue, dans le cas d'un entraînement en rotation du rotor interne (4) et/ou de l'anneau (3), avec le rotor interne (4), au moins une cellule d'acheminement dans laquelle le liquide est acheminé du côté basse pression au côté haute pression; e) et un organe de réglage (13) qui roule sans glissement contre le boîtier (1) lors d'un mouvement de réglage. L'invention se caractérise en ce que: f) le rotor interne (4) est fixé sur l'organe de réglage (13) pour pouvoir tourner autour de l'axe de rotation (DI); et g) l'emplacement de l'axe de rotation (DI) par rapport à l'axe (DA) de l'anneau (3), est modifié grâce au mouvement de déplacement de l'organe de réglage (13).
PCT/EP2005/002625 2004-03-17 2005-03-11 Pompe volumetrique a debit volumetrique variable WO2005093259A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP05729835A EP1735534A1 (fr) 2004-03-17 2005-03-11 Pompe volumetrique a debit volumetrique variable

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202004004231U DE202004004231U1 (de) 2004-03-17 2004-03-17 Volumenstromveränderbare Verdrängerpumpe
DE202004004231.2 2004-03-17

Publications (1)

Publication Number Publication Date
WO2005093259A1 true WO2005093259A1 (fr) 2005-10-06

Family

ID=34813794

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2005/002625 WO2005093259A1 (fr) 2004-03-17 2005-03-11 Pompe volumetrique a debit volumetrique variable

Country Status (6)

Country Link
US (1) US20050214149A1 (fr)
EP (1) EP1735534A1 (fr)
CA (1) CA2501103A1 (fr)
DE (1) DE202004004231U1 (fr)
MX (1) MXPA05007799A (fr)
WO (1) WO2005093259A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007120503A2 (fr) * 2006-03-31 2007-10-25 Metaldyne Company, Llc Pompe à déplacement variable dotée d'un rotor denté
JP4760968B2 (ja) * 2009-05-12 2011-08-31 トヨタ自動車株式会社 車両用オイルポンプ
CN102563325B (zh) * 2011-12-21 2014-10-22 浙江吉利汽车研究院有限公司 一种汽车机油泵
JP6027343B2 (ja) * 2012-06-01 2016-11-16 株式会社山田製作所 オイルポンプのロータ
DE102019002949B4 (de) * 2019-04-24 2021-02-25 Bastian Voigt Innenzahnradpumpe
CN114198277B (zh) * 2021-12-14 2023-03-31 浙江工业大学 齿轮传动往复式活塞泵

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1486836A (en) * 1923-04-28 1924-03-11 Hill Compressor & Pump Company Rotary-pump pressure control
US2969021A (en) * 1958-04-16 1961-01-24 Acc Emanuel Di G E R Emanuel & Automatic device for adjusting the output of rotary hydraulic machines
EP0846861A1 (fr) * 1996-12-04 1998-06-10 Siegfried A. Dipl.-Ing. Eisenmann Pompe annulaire à engrenages continuellement variable
DE10338212A1 (de) * 2003-08-20 2005-03-10 Zahnradfabrik Friedrichshafen Volumenstromvariable Rotorpumpe

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3443378A (en) * 1967-04-04 1969-05-13 Trw Inc Hydrostatic single unit steering system
US3547565A (en) * 1967-07-21 1970-12-15 Reliance Electric Co Rotary device
US4658583A (en) * 1984-06-11 1987-04-21 Trw Inc. Double staged, internal rotary pump with flow control
US5702319A (en) * 1995-10-13 1997-12-30 Dana Corporation Hydromechanical system for limiting differential speed between differentially rotating members
CA2219062C (fr) * 1996-12-04 2001-12-25 Siegfried A. Eisenmann Pompe a engrenages a couronne infiniment variable
US6244839B1 (en) * 1997-11-14 2001-06-12 University Of Arkansas Pressure compensated variable displacement internal gear pumps
US6152717A (en) * 1998-06-11 2000-11-28 Unisia Jecs Corporation Internal gear pumps
US6195990B1 (en) * 1999-01-13 2001-03-06 Valeo Electrical Systems, Inc. Hydraulic machine comprising dual gerotors
US6481991B2 (en) * 2000-03-27 2002-11-19 Denso Corporation Trochoid gear type fuel pump
JP2002257052A (ja) * 2001-03-05 2002-09-11 Denso Corp トロコイドギヤポンプ

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1486836A (en) * 1923-04-28 1924-03-11 Hill Compressor & Pump Company Rotary-pump pressure control
US2969021A (en) * 1958-04-16 1961-01-24 Acc Emanuel Di G E R Emanuel & Automatic device for adjusting the output of rotary hydraulic machines
EP0846861A1 (fr) * 1996-12-04 1998-06-10 Siegfried A. Dipl.-Ing. Eisenmann Pompe annulaire à engrenages continuellement variable
DE10338212A1 (de) * 2003-08-20 2005-03-10 Zahnradfabrik Friedrichshafen Volumenstromvariable Rotorpumpe

Also Published As

Publication number Publication date
US20050214149A1 (en) 2005-09-29
EP1735534A1 (fr) 2006-12-27
CA2501103A1 (fr) 2005-09-17
MXPA05007799A (es) 2006-01-18
DE202004004231U1 (de) 2005-07-28

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