EP1944512A1 - Pompe volumétrique avec un amortisseur de pulsations - Google Patents

Pompe volumétrique avec un amortisseur de pulsations Download PDF

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Publication number
EP1944512A1
EP1944512A1 EP08100144A EP08100144A EP1944512A1 EP 1944512 A1 EP1944512 A1 EP 1944512A1 EP 08100144 A EP08100144 A EP 08100144A EP 08100144 A EP08100144 A EP 08100144A EP 1944512 A1 EP1944512 A1 EP 1944512A1
Authority
EP
European Patent Office
Prior art keywords
pulsation damper
positive displacement
displacement pump
pump according
pulsation
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.)
Withdrawn
Application number
EP08100144A
Other languages
German (de)
English (en)
Inventor
Reiner Mayer
Johann Merz
Edgar Motzer
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.)
Robert Bosch Automotive Steering GmbH
Original Assignee
ZF Lenksysteme 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 ZF Lenksysteme GmbH filed Critical ZF Lenksysteme GmbH
Publication of EP1944512A1 publication Critical patent/EP1944512A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0049—Equalization of pressure pulses
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/086—Carter

Definitions

  • the invention relates to a displacement pump, in particular for motor vehicles, with a pump suction side and a pump pressure side, wherein a pulsation damper is arranged in at least one fluid-flow element of the pump pressure side.
  • a generic positive displacement pump is from the DE 41 12 476 A1 known.
  • Displacement pumps in particular in one embodiment as a single-stroke, adjustable vane pumps whose delivery volume is adjustable, are used regularly in power steering devices of motor vehicles. This is only on the example DE 199 42 466 A1 directed.
  • the from the DE 199 42 466 A1 known vane pump has a housing in which a set of rotors, consisting essentially of a rotor, rotor elements and a cam ring is mounted.
  • a set of rotors consisting essentially of a rotor, rotor elements and a cam ring is mounted.
  • an outer ring is inserted between the inner wall of the housing and the rotor set.
  • the rotor is enclosed by the cam ring.
  • a working space is formed, which is divided by the rotor elements in working cells.
  • the volume of the working cells can be adjusted by changing the eccentricity between the rotor and the cam ring.
  • the term "geometric delivery volume” refers to the volume of the positive displacement pump delivered per revolution.
  • the working space is laterally or at its end sides by two side plates (also referred to as control plates or end plates) or alternatively directly through the housing or a housing cover limited.
  • the side plates, the housing and the housing cover can have in a known manner a pump suction and a pump pressure opening, which serve to suck fluid into the working space or to discharge from the working space.
  • the area of the working space which faces the pump suction opening is called the suction chamber.
  • the area of the working space associated with the pump pressure opening is called the pressure chamber.
  • Between the suction and the pressure chamber is the so-called delivery chamber, in which the pressure medium is promoted.
  • a disadvantage of the transition from the delivery chamber into the pressure chamber or the pump pressure side are the pressure pulsations occurring and the resulting noise.
  • Displacement pumps in particular single-stroke vane pumps, have a relatively high pressure pulsation due to their function.
  • the respective work cell is brought abruptly at the transition to the pressure range to the pressure level that prevails in this area.
  • the DE 199 17 506 B4 it is known to provide the pump pressure opening with at least one notch.
  • the notch extends against the direction of rotation of the rotor in the direction of the pump suction.
  • the notch makes it possible that the pressure level in the corresponding work cell is slowly brought to the pressure level of the pressure chamber.
  • the notch thus reduces the pressure pulsations.
  • a further improvement or reduction of the pressure pulsations is desirable.
  • a pulsation damper in the form of a closed Insert the chamber into the pump so that it is exposed to the flow in the pump outlet.
  • the closed chamber has thin, flexible walls and an internal pressure greater than the atmospheric pressure to reduce the pulses in the outlet and the resulting pump noise.
  • the closed chamber can be formed from a flexible plastic.
  • the material may be formed into a sealed chamber by a blowing process, the internal pressure being controlled to be greater than the atmospheric pressure.
  • the pressurized chamber may also be formed as a thin-walled hose. In this case, one end of the tube is closed and the tube is compressed between rollers in the direction of the closed end in order to increase the pressure exerted on the closed end.
  • the from the DE 41 12 476 A1 known fuel pump has several disadvantages. On the one hand, it has proven in practice to be less effective to damp pulsations by being absorbed by a pressurized gas. On the other hand, there is the disadvantage that the pulsation damper only responds when the pulsations reach a pressure which is higher than the pressure of the gas, otherwise the shell is not pressed against the gas pressure. Furthermore, such a pulsation damper is effective only when the internal pressure is higher than the ambient atmospheric pressure. It must therefore be generated during manufacture of the Pulsationsdämpfers an increased internal pressure. However, during operation of the pump, it is unavoidable that the gas will diffuse through the flexible walls, thus reducing the internal pressure over time and equalizing it to the atmospheric pressure. The function of the pulsation damper, which is based on the fact that an increased internal pressure is present, which is to enable the gas to absorb pulsations, thus deteriorates.
  • the present invention is therefore based on the object to provide a positive displacement pump, are largely attenuated in the pressure pulsations.
  • the pulsations which occur are essentially damped or lowered by an elastic deformation or a resilient and / or damping property of the material of the pulsation damper.
  • the damping takes place in that the material of the pulsation damper is displaced, with part of the pulsations or the energy in the material being converted into heat.
  • the heat-converted part of the energy is not reversible - it is therefore not returned as a phase-shifted pulse - resulting in a particularly suitable attenuation of the pulsations.
  • Another part of the energy is resiliently absorbed by the material by the deformation and discharged again by the recovery.
  • the Pulsationsdämpfer can be compressed.
  • the cavity thus forms an escape surface for the material.
  • the elastically deformable material penetrates into the cavity. The pulsations or their energy are absorbed by the material itself and thereby damped.
  • pulsations can be much better absorbed by an elastically deformable material, so by a resilient action of a gas (as in the DE 41 12 476 A1 ), since an elastically deformable material, for. As rubber, can store more energy than a gas, eg. For example, air.
  • a gas eg. For example, air.
  • the absorption of the pulsations by an elastic deformation of the material has the advantage that the pulsations do not first have to have a certain size, but that the material is already immediately deformed by small pulsations or shrinks back into the cavity.
  • the solution according to the invention is independent of a pressure within a cavity, so that there are no disadvantages due to diffusion to adjust. With regard to the most cost-effective production of the pulsation damper according to the invention, provision is made for the atmospheric pressure to be present in the cavity.
  • the solution according to the invention provides to absorb and damp the pulsations by an elastic deformation of the material, while according to the DE 41 12 476 A1 is provided to absorb the pulsations by a sheath is compressed against a gas under high pressure.
  • the flexible walls according to the DE 41 12 476 A1 have only the function to spring against the gas and to keep the gas in the interior with an increased pressure together. A recording of pulsations or energy through the wall itself is neither provided nor possible, the energy is absorbed exclusively by the gas. As soon as the increased internal pressure has escaped by diffusion, the pulsation damper loses according to the DE 41 12 476 A1 its effect and can no longer absorb the pulsations in the desired manner.
  • the solution according to the invention absorbs the pulsations by the deformable material, from which the pulsation damper is formed substantially, preferably completely.
  • the material itself for example in a rubber embodiment, is not compressible itself, the inventor has created a cavity or space in the interior of the material into which the material can retreat or penetrate, if a corresponding load (eg. Pulsation) from the outside acts on the pulsation damper.
  • a corresponding load eg. Pulsation
  • the pulsations act on all sides of the pulsation damper.
  • the pulsation damper can thus not be bulged laterally outward like a conventional rubber mount, for example in bridge construction, when a force acts from above. For this reason, the inventors have created in the interior of the material a cavity through which it is possible that the material shrinks inwards and is thus compressed.
  • the pulsation damper can thus due to an external action according to energy (Pulsations) record and return to its original position, when the external impact decreases.
  • a recording of pulsations by a deformable material was hitherto known only through the expansion tubes, which have expanded with an increase in pressure or the occurrence of pulsations to the outside, so that the inner diameter has increased.
  • the inventors instead of a retreat area in the outer area (as in the expansion hoses), the inventors have now created a retreat space in the interior of the material.
  • the volume of the pulsation damper is at least 50%, preferably at least 80%, formed from the elastically deformable material.
  • the envelope formed by the elastically deformable material is thus relatively thick in relation to the cavity. Since the recording of pulsations based on the deformation of the material and this is a relatively small cavity in the interior is sufficient, the pulsation damper in contrast to the DE 41 12 476 A1 Considered in volume to be formed essentially by the deformable material.
  • rubber as a deformable material for the pulsation damper has proven to be particularly suitable because rubber is oil-resistant, has resilient properties and is suitable for energy absorption.
  • the preferably used rubber compound can be tuned to the frequency of the pulsations to be damped.
  • a rubber compound that is stiff and hard is preferable because the rubber compound is to absorb the energy of the pulsations.
  • the pulsation damper can in principle be arranged or introduced in any fluid-flow element of the pump pressure side. Also conceivable is the arrangement of several pulsation dampers.
  • a substantially elongated shape of the pulsation damper has been found suitable for placement in most fluid flow elements.
  • the pulsation damper may be a substantially circular one Have cross-section. This has been found to be particularly suitable with regard to the conditions, namely that the pressure acts on the pulsation damper essentially uniformly from the outside and deforms it.
  • the cavity extends as possible in the center or centrally within the Pulsationsdämpfers.
  • the at least one cavity extends substantially in the longitudinal direction of the pulsation damper.
  • the thickness of the material and the at least one cavity can be tuned to the frequency of the pulsations to be damped.
  • the deformable material is provided on its outside for fixing in the respective fluid-flow element with fixing elements or spacer elements, by which a distance between the outside of the deformable material and the inner wall of the element is definable ,
  • the pulsation damper can be positioned in a particularly simple and reliable manner at the desired location in the fluid-flow element.
  • the fixing elements are designed as knobs or ribs.
  • the pulsation damper has only one coherent and outwardly closed cavity.
  • the cavity thus represents a continuous inner bore.
  • the easiest way to produce such a pulsation damper is that the deformable material is vulcanized.
  • Fig. 1 an exploded view of a positive displacement pump according to the invention
  • Fig. 2 an end view of a pressure accumulation chamber of a positive displacement pump, in which the pulsation damper according to the invention is introduced;
  • Fig. 3 a section along the line III-III of Fig. 2 ;
  • Fig. 4 a longitudinal section through a pulsation damper according to the invention
  • Fig. 5 a cross section through a pulsation damper according to the line VV of Fig. 4 ;
  • Fig. 6 a longitudinal section through a second pulsation damper according to the invention.
  • Fig. 7 a longitudinal section through a third pulsation damper according to the invention.
  • Positive displacement pumps are well known from the general state of the art, for which reason only the features essential to the invention will be described in more detail below. This is done in the embodiment using a single-stroke vane pump with variable displacement. Such a vane pump results z. B. from the DE 199 42 466 A1 , which is hereby incorporated by reference.
  • the in the Fig. 1 illustrated positive displacement pump is designed as a vane pump and has a housing 1 with a set of rotors 2, which consists essentially of a rotor 3, rotor elements 4 and a cam ring 5.
  • an outer ring 6 is used for receiving the rotor set 2 in a bore of the housing 1. The outer ring 6 ensures the free movement of the cam ring 5 and transmits lateral forces from the cam ring 5 in the housing first
  • a working space 7 is formed, which is divided by the rotor elements 4 in working cells 8.
  • the volume of the working cells 8 by a change in the eccentricity between the rotor 3 and cam ring. 5 be set.
  • the rotor elements are formed in the embodiment as a wing 4.
  • positive displacement pumps including the vane pump shown, have a pump suction side 9 and a pump pressure side 10.
  • the pump suction side 9 and the pump pressure side 10 are each assigned a plurality of fluid-flow elements 11, at which, according to their assignment, the pressure of the pump suction side 9 or the pressure of the pump pressure side 10 is applied.
  • the vane pump shown in the embodiment further comprises two side plates 12a, 12b, which limit the rotor set 2 laterally in a known manner and the one (in Fig. 1 not shown) Pumpensaugö réelle (suction kidney) and a pump pressure port (Druckniere) have.
  • One of the side plates 12a, 12b can also be omitted as a separate part, in which case the housing wall of the housing 1 adjoining the set of rotors 2 or a wall of a housing cover 13 are correspondingly formed.
  • Fig. 2 shows a possible, advantageous arrangement of a pulsation damper 14 according to the invention in the vane pump.
  • the pulsation damper 14 is arranged in a fluid-flow element 11 designed as a pressure collecting space.
  • the pressure accumulator 11 is located on the pump pressure side and is therefore subjected to the pressure of the pump pressure side.
  • the pulsation damper 14 is adapted to the contour of the interior of the pressure accumulation chamber 11.
  • the pulsation damper 14 has for this purpose a substantially elongated, arcuate shape.
  • the pulsation damper 14 is, as is apparent 4 and FIG. 5 results, provided with a cavity 15 in the embodiment of an inner bore.
  • the cavity 15 extends substantially in the longitudinal direction of the pulsation damper 14 and has a substantially circular cross-section.
  • the pulsation damper 14 is formed in the embodiment of a deformable material under pressure 16. In the embodiment is this is rubber or a suitable rubber compound. The formed in the interior of the pulsation damper 14 and the material 16 cavity 15 is closed to the outside. Pulsation of the fluid pumped by the positive displacement pump is damped or absorbed by the material 16 by elastic deformation of the material 16, with the material 16 penetrating into the cavity 15.
  • the volume of the pulsation damper 14 is due to the material 16 and the cavity 15.
  • the pulsation of the fluid is thereby damped in that the deformable material has a suitable thickness and the cavity 15 has a suitable volume to deform by a deformation of the material 16 to dampen the pulsation.
  • the material already occupies over 80% of the volume of the pulsation damper in the unloaded state.
  • Fig. 6 shows one to the FIGS. 2 to 5 alternative representation of a Pulsationsdämpfers 14, which has an unbent, elongated shape.
  • Fig. 7 shows a likewise elongated design of a Pulsationsdämpfers 14, wherein a plurality of cavities 15 is provided.
  • the cavities 15 may have a spherical shape.
  • the pulsation damper 14 has, as out 4 and FIG. 5 it can be seen on its outer side for fixing in the pressure accumulation chamber 11 fixing elements 17, through which a distance between the outside of the pulsation damper 14 and the inner wall of the pressure accumulation chamber 11 can be defined.
  • the fixing elements 17 are formed as knobs.
  • the solution according to the invention is particularly suitable for positive displacement pumps which are used in power steering devices of vehicles, in particular passenger cars and commercial vehicles.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP08100144A 2007-01-10 2008-01-07 Pompe volumétrique avec un amortisseur de pulsations Withdrawn EP1944512A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200710001485 DE102007001485A1 (de) 2007-01-10 2007-01-10 Verdrängerpumpe

Publications (1)

Publication Number Publication Date
EP1944512A1 true EP1944512A1 (fr) 2008-07-16

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EP08100144A Withdrawn EP1944512A1 (fr) 2007-01-10 2008-01-07 Pompe volumétrique avec un amortisseur de pulsations

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EP (1) EP1944512A1 (fr)
DE (1) DE102007001485A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2385241A1 (fr) * 2010-05-04 2011-11-09 Continental Automotive GmbH Amortisseur de pulsation
WO2014079888A3 (fr) * 2012-11-20 2014-08-14 Safran Power Uk Ltd. Pompe à haute pression
US9121397B2 (en) 2010-12-17 2015-09-01 National Oilwell Varco, L.P. Pulsation dampening system for a reciprocating pump

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020214277B3 (de) 2020-11-13 2022-03-17 Zf Friedrichshafen Ag Schwingungsdämpfer mit einer Pumpenanordnung

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4181473A (en) * 1976-07-01 1980-01-01 Nippondenso Co., Ltd. Motor pump
DE4113373A1 (de) * 1990-05-29 1991-12-05 Walbro Corp Elektrisch angetriebene kraftstoffpumpe
DE4112476A1 (de) 1990-06-06 1991-12-12 Walbro Corp Kraftstoffpumpe
EP0496591A1 (fr) * 1991-01-23 1992-07-29 IMO INDUSTRIES Inc. Structure de pompe hydraulique réduisant le bruit
DE4306921A1 (de) * 1993-03-05 1994-09-08 Bosch Gmbh Robert Förderpumpe für ein hydraulisches System
DE4441746A1 (de) * 1993-11-23 1995-05-24 Walbro Corp Kraftstoffpumpe mit Impulsdämpfer
DE19942466A1 (de) 1998-09-10 2000-03-16 Jidosha Kiki Co Variable Displacement Pump
DE19917506B4 (de) 1998-04-23 2004-02-12 Unisia JKC Steering Systems Co., Ltd., Atsugi Verstellbare Flügelzellenpumpe

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4181473A (en) * 1976-07-01 1980-01-01 Nippondenso Co., Ltd. Motor pump
DE4113373A1 (de) * 1990-05-29 1991-12-05 Walbro Corp Elektrisch angetriebene kraftstoffpumpe
DE4112476A1 (de) 1990-06-06 1991-12-12 Walbro Corp Kraftstoffpumpe
EP0496591A1 (fr) * 1991-01-23 1992-07-29 IMO INDUSTRIES Inc. Structure de pompe hydraulique réduisant le bruit
DE4306921A1 (de) * 1993-03-05 1994-09-08 Bosch Gmbh Robert Förderpumpe für ein hydraulisches System
DE4441746A1 (de) * 1993-11-23 1995-05-24 Walbro Corp Kraftstoffpumpe mit Impulsdämpfer
DE19917506B4 (de) 1998-04-23 2004-02-12 Unisia JKC Steering Systems Co., Ltd., Atsugi Verstellbare Flügelzellenpumpe
DE19942466A1 (de) 1998-09-10 2000-03-16 Jidosha Kiki Co Variable Displacement Pump

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2385241A1 (fr) * 2010-05-04 2011-11-09 Continental Automotive GmbH Amortisseur de pulsation
US9121397B2 (en) 2010-12-17 2015-09-01 National Oilwell Varco, L.P. Pulsation dampening system for a reciprocating pump
WO2014079888A3 (fr) * 2012-11-20 2014-08-14 Safran Power Uk Ltd. Pompe à haute pression
CN104903581A (zh) * 2012-11-20 2015-09-09 英国赛峰动力有限公司 具有在连接到泵出口的槽道中的填充件的高压泵
JP2015535054A (ja) * 2012-11-20 2015-12-07 サフラン・パワー・ユー・ケイ・リミテッド ポンプ出口に接続されたギャラリ内にフィラーを有する高圧ポンプ

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