US20080310979A1 - Piston Pump With Improved Efficiency - Google Patents

Piston Pump With Improved Efficiency Download PDF

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Publication number
US20080310979A1
US20080310979A1 US11/658,267 US65826705A US2008310979A1 US 20080310979 A1 US20080310979 A1 US 20080310979A1 US 65826705 A US65826705 A US 65826705A US 2008310979 A1 US2008310979 A1 US 2008310979A1
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US
United States
Prior art keywords
piston
piston pump
pump according
sealing element
region
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.)
Abandoned
Application number
US11/658,267
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English (en)
Inventor
Rene Schepp
Harald Hermann
Georg Blosch
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 GmbH
Original Assignee
Individual
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 Individual filed Critical Individual
Assigned to ROBERT BOSCH GMBH reassignment ROBERT BOSCH GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HERMANN, HARALD, SCHEPP, RENE, BLOSCH, GEORG
Publication of US20080310979A1 publication Critical patent/US20080310979A1/en
Abandoned 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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/12—Valves; Arrangement of valves arranged in or on pistons
    • F04B53/121—Valves; Arrangement of valves arranged in or on pistons the valve being an annular ring surrounding the piston, e.g. an O-ring
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
    • B60T8/4031—Pump units characterised by their construction or mounting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0408—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F04B39/0016—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons with valve arranged in the piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/12—Valves; Arrangement of valves arranged in or on pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/11—Kind or type liquid, i.e. incompressible
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Definitions

  • the present invention relates to a piston pump for delivering hydraulic fluid with improved efficiency in which the piston pump is particularly inexpensive to manufacture.
  • Piston pumps for vehicle brake systems are frequently embodied in the form of radial piston pumps, in which at least one piston can be set into a reciprocating motion by means of a cam.
  • Piston pumps of this kind are frequently used in connection with electronic stability systems (ESP) or electrohydraulic brake systems (EHB). Since the use of such systems is on the rise, even in smaller vehicles, it is necessary for the piston pumps to be very inexpensive to manufacture.
  • ESP electronic stability systems
  • EHB electrohydraulic brake systems
  • Another requirement for such piston pumps is that they be as small and lightweight as possible. Since future brake systems will operate with higher pressures, the piston pump must also be able to generate these desired pressure levels.
  • the known piston pumps are usually equipped with a pressure chamber situated between an inlet valve and an outlet valve; the movement of the piston builds up an operating pressure in this pressure chamber. At its end oriented toward the piston, this pressure chamber must be sealed in relation to a low-pressure region of the piston pump. This is frequently accomplished by means of piston rings or sealing elements situated inside the cylinder.
  • the inlet valve is situated in the pressure chamber and a supply line of hydraulic fluid can be provided by means of conduits integrated into the piston.
  • the pressure chamber also contains a spring for returning the piston to its initial position; this placement of the spring can result in unfavorable flow conditions in the pressure chamber and in particular, can lead to problems due to gas evolution from the gases combined in the hydraulic fluid, and can also lead to noise problems.
  • the piston pump for delivering hydraulic fluid according to the present invention has the advantage over the prior art that it is particularly compact and requires fewer parts. This enables a particularly inexpensive production of the piston pump according to the invention. According to the invention, this is achieved by the fact that a sealing element situated on the piston simultaneously also performs the function of the inlet valve. This makes it possible to reduce the number of parts and to achieve a particularly compact design of the piston pump.
  • the sealing element is embodied in such a way that during a compression phase, its seals the pressure chamber in relation to a low-pressure region of the piston pump and during an intake phase, it produces a connection to the low-pressure region in order to draw hydraulic fluid into the pressure chamber.
  • the sealing element is situated on the piston so that it has an axial play.
  • the position of the sealing element in relation to the piston can be changed in the axial direction of the piston by the amount of the axial play.
  • the sealing element can consequently assume two positions in relation to the piston, namely a first position for the intake phase and a second position for the compression phase.
  • the sealing element on the piston is situated in a stepped region provided at the pressure chamber end region of the piston.
  • the sealing element is embodied in such a way that its inner circumference has at least one raised region and one recessed region. During the intake phase, this permits an overflow of the sealing element along the recessed region between the sealing element and the piston.
  • the inner circumference of the sealing element is provided with a number of plane-like raised regions and a number of plane-like recessed regions situated between the raised regions. It is particularly preferable in this case for the arrangement of the raised and recessed regions to be symmetrical. This makes it possible to assure symmetrical pressure conditions against the sealing element.
  • the size and depth of the recessed regions depends on the one hand on the inner diameter of the sealing element and on the other hand, also depends on the desired intake volume and stroke length of the piston.
  • the inner circumference of the sealing element has a bevel on the edge oriented toward the low-pressure region of the piston pump.
  • This bevel facilitates the opening of the sealing element for the intake phase, thus permitting a very short reaction time for the inlet function of the sealing element.
  • the spring element is preferably embodied in the form of a leaf spring with one or more spring tabs. Affixing the spring element to the piston in a preferable fashion achieves a particularly compact design.
  • the spring element can, for example, be affixed to the piston by means of a plate-shaped retaining element; the retaining element is affixed to the pressure chamber end of the piston and protrudes beyond the stepped region of the piston in order to support the spring element.
  • the piston has at least one flattened region on the circumference in order to supply hydraulic fluid from the low-pressure region to the sealing element.
  • three flattened regions are provided on the piston, each spaced equidistantly apart from adjacent flattened regions along the circumference of the piston.
  • a return spring for returning the piston to its initial position is situated outside the pressure chamber. Since the sealing element that performs the function of the inlet valve is also not situated in the pressure chamber, it is thus possible to obtain a clearance-optimized pressure chamber. Consequently, the pressure chamber can be easily designed for the desired pressure conditions and can have a simple geometry.
  • a cylinder element is preferably provided for this, against the inside of which the sealing element is guided and against the outside of which the return spring for the piston is guided.
  • the return spring in this case can be supported on the piston against an additional stepped region or against protruding projections.
  • the return spring is embodied in the form of a tapering, in particular conical spiral spring, which rests against a circumferential groove provided on the piston.
  • the return spring for the piston is situated in a cam chamber of the piston pump. This, too, makes it possible to situate the return spring outside the pressure chamber of the piston pump.
  • the return spring in the cam chamber is preferably fastened to the piston and particularly preferably, is embodied in the form of a leaf spring, which is supported against the walls of the cam chamber.
  • the piston pump according to the present invention is particularly preferable to use in brake systems of motor vehicles, for example to control and regulate a pressure in a wheel brake cylinder. It is particularly preferable for the piston pump according to the present invention to be used in connection with electronic control and regulating systems of the brake system, e.g. ESB, EHB, TCS, etc. Since the piston pump according to the present invention is particularly inexpensive to produce, it is possible to significantly reduce the costs for equipping even small vehicles with such brake systems.
  • FIG. 1 is a schematic sectional view of a piston pump according to a first exemplary embodiment of the present invention
  • FIG. 2 is a perspective view of several individual parts of the piston pump shown in FIG. 1 ,
  • FIGS. 3 a to 3 c show various views of a sealing ring according to the first exemplary embodiment of the present invention
  • FIGS. 4 a and 4 b show schematic views of a spring element for exerting a spring force on the sealing element
  • FIG. 5 shows an enlarged partial cross section through the piston pump of the first exemplary embodiment during the intake phase
  • FIG. 6 is an enlarged, partial cross-sectional view of the piston pump of the first exemplary embodiment during the compression phase
  • FIG. 7 is a schematic sectional view of a piston pump according to a second exemplary embodiment of the present invention.
  • FIG. 8 is a schematic sectional view of a piston pump according to a third exemplary embodiment of the present invention.
  • a piston pump 1 according to a first exemplary embodiment of the present invention will be described below in conjunction with FIGS. 1 through 6 .
  • the piston pump 1 has a piston 3 contained in a housing 2 .
  • the housing 2 has a stepped bore 2 a to accommodate the piston 3 .
  • the piston 3 is driven by means of a cam 22 that is situated in the cam chamber 21 and whose rotation direction is indicated by the arrow D.
  • the piston 3 is depicted in detail in the perspective view in FIG. 2 .
  • the end of the piston 3 oriented toward the pressure chamber has a stepped region 3 a and three flattened regions 3 b situated along the circumference of the piston.
  • a sealing element 4 is situated on the stepped region 3 a .
  • the sealing element 4 is affixed to the stepped region 3 a of the piston 3 by means of a spring element 7 and a plate-shaped retaining element 8 .
  • the plate-shaped retaining element 8 is fastened by being press-fit in a recess 3 d of the piston by means of an annular fastening region.
  • the piston pump 1 also includes a pressure chamber 9 , which is situated between the sealing element 4 and an outlet valve 11 .
  • the sealing element 4 is provided as an inlet valve element for supplying hydraulic fluid, as will be described later.
  • the outlet valve 11 has ball 12 and a return spring 13 .
  • the return spring 13 is supported in a stopper element 14 ; the stopper element 14 seals the stepped bore 2 a of the housing 2 in a fluid-tight fashion. Downstream of the outlet valve 11 , there are two pressure lines 15 to which the pressurized fluid from the pressure chamber 9 is supplied.
  • a cylinder element 10 is situated between the outlet valve 11 and the pressure chamber 9 .
  • the cylinder element 10 includes a plate-shaped base region 10 a with a flange-like cylinder ring 10 b integrally joined to it.
  • the cylinder ring 10 b has an inner circumference surface 10 c and an outer circumference surface 10 d .
  • the cylinder element 10 also has a central through opening 10 e that is opened and closed by means of the outlet valve 11 .
  • a return spring 16 is provided, which is supported against the cylinder element 10 at one end and is supported against a raised region 3 c on the piston 3 at the other (see FIG. 1 ).
  • the housing 2 also contains supply lines 17 , which supply hydraulic fluid to a low-pressure region 18 .
  • the return spring 16 for the piston 3 is likewise situated in the low-pressure region 18 of the piston pump.
  • the piston 3 is also provided with a sealing ring 19 and a guide ring 20 , which are situated in a groove-shaped recess in the piston.
  • FIG. 3 a is a top view of the sealing ring 4 .
  • the sealing ring 4 is embodied in the form of a closed ring and on its inner circumference, has four raised regions 5 and four recessed regions 6 .
  • the raised regions 5 and recessed regions 6 are each embodied as plane-like.
  • FIG. 3 b is a sectional view of the sealing element 4 , cut along the line IV-IV. As is clear from FIG.
  • relatively wide bevels 5 a are provided in the region of the sealing element 4 oriented toward the low-pressure side and relatively wide bevels 5 b are provided in the region of the sealing element 4 oriented toward the pressure chamber.
  • the bevels 5 a on the low-pressure side permit the sealing element 4 to rapidly react when it is to perform the function of an inlet valve.
  • the sealing element 4 is situated on the stepped region 3 a of the piston 3 in such a way that it is able to move in the axial direction X-X of the piston with a predetermined amount of play S.
  • the movement of the sealing element 4 is limited on the one hand by the stepped region 3 a and on the other hand by the retaining element 8 , which is affixed to the piston 3 and has a larger diameter than the stepped end of the piston 3 oriented toward the pressure chamber.
  • the spring element 7 is also situated between the retaining element 8 and the sealing element 4 . The spring element 7 is shown in the detailed views in FIGS.
  • the spring element 7 exerts a spring force on the sealing element 4 in the axial direction X-X.
  • the sealing element 4 is preferably manufactured of a plastic material, in particular PA66 or PEEK, or of a ceramic material.
  • FIG. 5 shows the beginning of the intake phase of the piston pump, in which the piston 3 moves in the direction of the arrow A.
  • the sealing element 4 is situated in the first position shown in FIG. 5 so that hydraulic fluid in the low-pressure region 18 can overflow the sealing element 4 . This is indicated by the arrows in FIG. 5 .
  • the outlet valve 11 is in its closed position.
  • the hydraulic fluid from the low-pressure region 18 overflows the sealing element 4 along the recessed regions 6 on the inner circumference of the sealing element 4 and then travels through the interstices between the spring tabs 7 b of the spring element 7 and into the pressure chamber 9 .
  • the spring tabs 7 b thus serve as a stop for the sealing element 4 so that between the plate-shaped retaining element 8 and the sealing element 4 , an intermediate space remains open, through which the hydraulic fluid can flow into the pressure chamber 9 .
  • the spring element 7 does in fact exert a spring force F F on the sealing element in the movement direction A of the piston, but this spring force is less than the friction force F K between the sealing element 4 and the inner circumference 10 c of the cylinder element 10 , which acts in opposition to the spring force. Consequently, the sealing element 4 is situated in the position shown in FIG. 5 during the intake phase of the piston pump in order to draw in hydraulic fluid.
  • the sealing element 4 makes it possible that, after the piston 3 reverses direction once it reaches its bottom dead center, the connection between the pressure chamber 9 and the low-pressure region 18 is closed since the sealing element 4 produces a seal against both the inner circumference 10 c of the cylinder element 10 and the stepped region 3 a of the piston 3 .
  • a continuously increasing pressure builds up in the pressure chamber 9 .
  • the outlet valve 11 remains closed until the pressure in the pressure chamber 9 is greater than the pressure in the pressure lines 15 .
  • FIG. 6 shows this open state.
  • the spring force F F of the spring element 7 in the axial direction X-X of the piston 3 consequently acts on the sealing element 4 in addition to an axial force F A exerted by the pressurized hydraulic fluid in the pressure chamber 9 .
  • the hydraulic fluid in the pressure chamber 9 also acts against the recessed regions 6 on the inner circumference of the sealing element 4 , thus also exerting a radial force FR on the sealing element 4 during the compression phase. It is consequently possible to achieve an improved sealing by making use of the compression forces of the hydraulic fluid present in the pressure chamber 9 .
  • the sealing element 4 provides the axial play S of the sealing element 4 in relation to the piston 3 makes it possible for the sealing element 4 to perform both the sealing function between the pressure chamber 9 and the downstream pressure region 18 during the compression phase of the piston pump and the inlet valve function during the intake phase. As a result, it is no longer necessary to provide a separate inlet valve for the pressure chamber 9 ; instead, a single component performs both functions.
  • the overflow of the sealing element 4 during the intake phase occurs along the inner circumference. It should be noted that for a uniform pressure distribution on the sealing element 4 , the raised regions 5 and the recessed regions 6 are preferably situated symmetrically in relation to the central axis of the sealing element.
  • the piston pump according to the invention is very easy to assemble since on the one hand, the number of parts can be reduced and on the other hand, for example, the sealing element 4 can be premounted onto the piston 3 along with the spring element 7 and the retaining element 8 .
  • the retaining element 8 can be fastened into the recess 3 d of the piston 3 by means of a press fit or by means of caulking.
  • a piston pump 1 according to a second exemplary embodiment of the invention will be described below in conjunction with FIG. 7 . Parts that are the same or are functionally equivalent have been provided with the same reference numerals as in the first exemplary embodiment.
  • the piston pump 1 of the second exemplary embodiment corresponds essentially to that of the first exemplary embodiment; instead of a cylindrical return spring 16 , in the second exemplary embodiment, a tapering return spring 16 is used.
  • the end of the reliably tapering return spring 16 oriented toward the pressure chamber once again rests against the cylinder element 10 while the end of the tapering return spring 16 oriented toward the cam rests against a circumferential groove 23 provided in the piston 3 .
  • It is particularly preferable for the tapering return spring 16 of the second exemplary embodiment to be wound directly onto the piston 3 so that the installation of the return spring 16 onto the piston 3 can be automated.
  • the piston pump 1 from FIG. 7 is depicted in the compression phase; the outlet valve 11 is still closed and the pressure in the pressure chamber 9 continuously increases as the movement of the piston 3 continues toward its top dead center.
  • this exemplary embodiment corresponds to the first exemplary embodiment so that reference can be made to the description given in conjunction therewith.
  • FIG. 8 shows a piston pump 1 according to third exemplary embodiment of the present invention. Parts that are the same or are functionally equivalent have once again been provided with the same reference numerals as in the first exemplary embodiment.
  • the sealing element 4 is likewise embodied in the form of an inlet valve.
  • FIG. 8 shows the piston pump 1 during its intake phase.
  • the return spring for the piston 3 is embodied in the form of a leaf spring, which is situated in the cam chamber 21 of the piston pump 1 .
  • the leaf spring 24 is fastened in a groove 26 in the piston 3 situated at the cam end of the piston 3 and is supported against the wall of the cam chamber 21 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
US11/658,267 2004-07-30 2005-07-14 Piston Pump With Improved Efficiency Abandoned US20080310979A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102004037140.7 2004-07-30
DE200410037140 DE102004037140A1 (de) 2004-07-30 2004-07-30 Kolbenpumpe mit verbessertem Wirkungsgrad
PCT/EP2005/053377 WO2006013143A1 (de) 2004-07-30 2005-07-14 Kolbenpumpe mit verbessertem wirkungsgrad

Publications (1)

Publication Number Publication Date
US20080310979A1 true US20080310979A1 (en) 2008-12-18

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ID=34972876

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/658,267 Abandoned US20080310979A1 (en) 2004-07-30 2005-07-14 Piston Pump With Improved Efficiency

Country Status (7)

Country Link
US (1) US20080310979A1 (ja)
EP (1) EP1774177B1 (ja)
JP (1) JP4651049B2 (ja)
KR (1) KR101077506B1 (ja)
CN (1) CN100460679C (ja)
DE (2) DE102004037140A1 (ja)
WO (1) WO2006013143A1 (ja)

Cited By (2)

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US20140308143A1 (en) * 2011-11-17 2014-10-16 Nissin Kogyo Co., Ltd. Plunger pump
CN104471243A (zh) * 2012-01-19 2015-03-25 通用电气石油和天然气压缩系统有限责任公司 无阀往复式压缩机

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DE102007049152A1 (de) * 2007-10-12 2009-04-16 Robert Bosch Gmbh Hydraulische Kolbenpumpe
CN102575655A (zh) * 2009-10-05 2012-07-11 舍弗勒技术股份两合公司 液压的泵装置
DE102009047217A1 (de) * 2009-11-27 2011-06-01 Robert Bosch Gmbh Kolbenplumpe
DE102010001237A1 (de) * 2009-12-01 2011-06-09 Continental Teves Ag & Co. Ohg Kolbenpumpe
DE102009054520A1 (de) * 2009-12-10 2011-06-16 Robert Bosch Gmbh Kolbenpumpe
DE102010040889A1 (de) * 2010-09-16 2012-03-22 Robert Bosch Gmbh Pumpenaggregat
FI20125250L (fi) * 2012-03-09 2013-09-10 Waertsilae Finland Oy Kaasunvaihtoventtiilijärjestely ja kaasunvaihtoventtiili
EP2746566A1 (en) * 2012-12-18 2014-06-25 Delphi International Operations Luxembourg S.à r.l. Pump Unit
JP5915601B2 (ja) 2013-07-24 2016-05-11 株式会社アドヴィックス ピストンポンプ
DE102013226052B4 (de) 2013-12-16 2024-05-02 Robert Bosch Gmbh Kolbenpumpe für eine hydraulische Fahrzeugbremsanlage
KR102413429B1 (ko) 2017-08-08 2022-06-28 주식회사 만도 브레이크 시스템용 피스톤 펌프

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US10359030B2 (en) * 2011-11-17 2019-07-23 Nissin Kogyo Co., Ltd. Plunger pump
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EP1774177A1 (de) 2007-04-18
CN100460679C (zh) 2009-02-11
EP1774177B1 (de) 2010-02-17
JP2008507661A (ja) 2008-03-13
JP4651049B2 (ja) 2011-03-16
CN1993550A (zh) 2007-07-04
WO2006013143A1 (de) 2006-02-09
KR101077506B1 (ko) 2011-10-28
KR20070038535A (ko) 2007-04-10
DE502005009044D1 (ja) 2010-04-01
DE102004037140A1 (de) 2006-03-23

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