EP0893601A2 - Pompe à piston combinée avec une pompe de surpression - Google Patents

Pompe à piston combinée avec une pompe de surpression Download PDF

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Publication number
EP0893601A2
EP0893601A2 EP98111868A EP98111868A EP0893601A2 EP 0893601 A2 EP0893601 A2 EP 0893601A2 EP 98111868 A EP98111868 A EP 98111868A EP 98111868 A EP98111868 A EP 98111868A EP 0893601 A2 EP0893601 A2 EP 0893601A2
Authority
EP
European Patent Office
Prior art keywords
pump
arrangement according
booster
piston
pump housing
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.)
Granted
Application number
EP98111868A
Other languages
German (de)
English (en)
Other versions
EP0893601B1 (fr
EP0893601A3 (fr
Inventor
Roland Nuber
Hans Götz
Verena Dettinger-Müller
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.)
Uraca Pumpenfabrik GmbH and Co KG
Original Assignee
Uraca Pumpenfabrik GmbH and Co KG
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 Uraca Pumpenfabrik GmbH and Co KG filed Critical Uraca Pumpenfabrik GmbH and Co KG
Publication of EP0893601A2 publication Critical patent/EP0893601A2/fr
Publication of EP0893601A3 publication Critical patent/EP0893601A3/fr
Application granted granted Critical
Publication of EP0893601B1 publication Critical patent/EP0893601B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/12—Combinations of two or more pumps
    • 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
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
    • 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
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/14—Combinations of two or more pumps the pumps being of different types at least one pump being of the non-positive-displacement type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/48—Fluid-guiding means, e.g. diffusers adjustable for unidirectional fluid flow in reversible pumps
    • F04D29/486—Fluid-guiding means, e.g. diffusers adjustable for unidirectional fluid flow in reversible pumps especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/628—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for liquid pumps

Definitions

  • the invention relates to a pump arrangement with a plunger or piston pump and with a charge or booster pump, which can be driven via a common drive shaft, wherein a piston pump housing and a booster pump housing form a structural unit.
  • Piston pumps are usually used for pumping of liquids, especially hydraulic liquids, used, with this type of pump particularly high Pressures are achievable.
  • Piston pumps are known, the Housing are designed so that they are in different Installation positions can be installed in a functional manner. Also are Piston pumps are known in which the drive mechanism of the Piston or the plunger formed so far symmetrical is that the piston pump in both directions of rotation of its drive shaft works fully functional.
  • a charge or booster pump for the piston pump which the suction-side liquid of the piston pump with Pressurized so that the suction-side valves of the piston pump are preloaded in their open position and the Liquid of the suction movement of the plunger or the piston can follow without risk of cavitation.
  • the piston pump works hydrostatically to achieve a high final pressure
  • the booster pump can work hydrodynamically, which results in although a significantly lower one to avoid the Cavitation can achieve sufficient pre-pressure. Doing so a flow pump is usually used as a booster pump, where the conveying capacity by rotating a profiled blades provided impeller is achieved.
  • the present invention addresses the problem a pump arrangement of the type mentioned with simple constructive measures to the effect that when installing or connecting the drive shaft has an increased variability.
  • the invention is based on the general idea for the pump arrangement one in both directions of rotation of the drive shaft functional piston pump with a booster pump to combine, which are also generally suitable is in both directions of rotation of the drive shaft in to be sufficiently functional. Since it is one Pump used as a booster pump is not achieving a high pressure difference arrives and generally on the drive side a high excess of power is available stands, such a booster pump does not need an efficient To show efficiency. In view of this finding can therefore in the pump arrangement according to the invention Pumps are also used as booster pumps that for common applications, e.g. because of their poor efficiency, not acceptable.
  • a preferred embodiment of the pump arrangement according to the invention has the features of claim 2.
  • the redirection section becomes the liquid conveyed by the impeller on the pressure side of the booster pump to an outlet opening deflected, which communicates with the suction side of the piston pump.
  • the pump wheel, the The shaft and the deflection section must be accessible so that maintenance and assembly work can be carried out.
  • a pump wheel which has straight, radial blades.
  • Such an impeller conveys in both directions of rotation its shaft or the drive shaft driving it the pump medium is radial with the same efficiency outward.
  • the pump arrangement can be disadvantageous compared to the advantage that the pump arrangement is independent of the respective direction of rotation of the drive axis immediately is fully functional, negligible.
  • a preferred embodiment has the features of Claim 7 on.
  • Such a shape for the deflection section is to the working of a radially promoting Adjusted pump wheel and enables a particularly cheap Efficiency.
  • Pump arrangement can do this with the features of claim 10 be equipped.
  • Such a timing belt is characterized by a long service life and a short one Need for maintenance.
  • Another advantageous embodiment has the features of claim 11. This measure causes when the Booster pump housing a centering or positioning of the booster pump housing compared to the piston pump housing and enables a defined position of the shaft for the pump wheel and this e.g. driving over the timing belt common drive shaft for the pumps, which are usually is also mounted on the piston pump housing. So less need Tolerances in the manufacture of the individual parts adhered to become.
  • the piston pump 1 has a pump arrangement according to the invention a plunger or piston pump 1 with a piston pump housing 2 on.
  • the piston pump 1 of the embodiment is intended for horizontal installation, i.e. you not Piston or plunger shown works in a horizontal trending level.
  • connection flanges 3 and 4 are provided for fastening the pump arrangement are on the lower side of the piston pump housing corresponding to FIG. 1 2 connection flanges 3 and 4 are provided.
  • the Pump arrangement or the piston pump housing 2 is in the embodiment designed so that the pump assembly without more effort both on their back and on her belly side is mountable.
  • the connecting flange 4 at the location of the piston pump housing 2 mounted, on the in Fig. 1 still a lifting eye 5 is attached.
  • the remaining connection and fastening means the piston pump housing 2 or the pump arrangement are in a corresponding manner on the opposite Side attachable or already exist twice.
  • a charging or booster pump 6 with a booster pump housing 7 arranged on the side of the piston pump housing shown in Fig. 1 2 is a charging or booster pump 6 with a booster pump housing 7 arranged.
  • the booster pump housing 7 is closed with a disc-shaped cover 8, the with Screws 9 is attached to the booster pump housing 7.
  • a suction opening 10 of the booster pump in the middle 6 provided with a feed line, not shown for the liquid to be pumped by the pump arrangement communicates.
  • the pump wheel 11 is a radial pump wheel trained and has rectilinear, radially extending Paddles 13, which increases the delivery rate of the pump wheel 11 is the same size in both directions of rotation of the shaft 12.
  • the pump wheel 11 or its blades 13 rotate in one Interior 14, which is referred to as a deflection section Section 15 of the booster pump housing 7 is formed.
  • the interior 14 is in the deflection section 15 designed so that the radial distance between the Outer circumference of the pump wheel 11 and the inside of the deflection section 15 spirally expanded to one on the pressure side Outlet opening 16 of the booster pump 6.
  • This outlet opening 16 in turn communicates with the suction side connected to the piston pump 1.
  • This special shape of the interior 14 in which the impeller 11 with its Blades 13 rotates, causing the delivery rate of the Pump wheel 11 is optimized in one direction of rotation. This preferred direction of rotation corresponds to the direction in which the Distance between the circumference of the impeller 11 and the inside of the deflection section 15 increases.
  • the deflection section 15 is designed as a separate component, that can be removed and reassembled.
  • the deflection section 15 is in which the deflection section in Fig. 3 cut at least with regard to the contour of its interior 14 mirror-symmetrical. This configuration causes that when turning the deflection section 15 by 180 ° with respect a mirror axis 17 lying in the plane of symmetry an inner contour mirrored on this mirror axis 17 results.
  • the radial Gap between the outer circumference of the impeller 11 and the Inner contour of the deflection section 15 smaller clockwise is, he takes the turned deflection section 15 in Clockwise to.
  • the deflection section 15 is corresponding 2 through the cover 8 on the booster pump housing 7 attached.
  • the deflection section 15 is between one Base plate 19 and the cover 8 using the screws 9 tense.
  • the seal between the deflection section 15 and the base plate 19 and the cover 8 are each with an axially acting seal 20 causes, for example consists of a sealing ring or a sealing cord that is inserted into a corresponding groove.
  • the shaft 12, on which the pump wheel 11 is attached, has on its area facing away from the pump wheel 11, two bearings 21 and 22 on. While the bearing 21 is completely in the booster pump housing 7 is positioned, the other is at the end of the shaft 12 mounted bearings 22 partially in the booster pump housing 7 and partly in the piston pump housing 2 kept positioned. For this purpose is in the piston pump housing 2 a corresponding recess 23 is provided.
  • This special mounting of the shaft 12 causes a defined position the shaft 12 with respect to a drive shaft driving this 24, which is also positioned on the piston pump housing 2 is stored.
  • the shaft 12 is driven via a toothed belt 25, which is attached to the shaft 12 Gear and a gear attached to the drive shaft 24 connects power-transmitting with each other.
  • the positioning of the bearing 22 in the piston pump housing 2 also causes the booster pump housing to be centered 7, while it is attached to the piston pump housing 2. Also is the booster pump housing 7 via the bearing 22 in addition supported on the piston pump housing 2. At the same time can the booster pump housing 7 by this measure on this Side be open, it is only at his Assembly on the piston pump housing 2 is closed.
  • a piston pump 1 discontinuously the liquid to be pumped promotes, it can on the suction side of the piston pump 1 come to the formation of vibrations. Such vibrations lead to considerable loads on the lines and other pump parts on the suction side of piston pump 1 and thus also loads on the booster pump 6. In addition this also increases the risk of cavitation.
  • a vibration damping device can in the pump arrangement according to the invention between the suction side of the piston pump 1 and the pressure side of the Booster pump 6 arranged a vibration damping device become.
  • a vibration or pulsation damping device is for example in DE 42 40 590 A1 described. This damping device is preferably in the Piston pump housing 2 integrated, so that no additional Components are to be assembled.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP98111868A 1997-07-25 1998-06-26 Pompe à piston combinée avec une pompe de surpression Expired - Lifetime EP0893601B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19732062 1997-07-25
DE19732062A DE19732062A1 (de) 1997-07-25 1997-07-25 Pumpenanordnung mit einer Kolbenpumpe und einer Boosterpumpe

Publications (3)

Publication Number Publication Date
EP0893601A2 true EP0893601A2 (fr) 1999-01-27
EP0893601A3 EP0893601A3 (fr) 2000-03-01
EP0893601B1 EP0893601B1 (fr) 2004-05-12

Family

ID=7836891

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98111868A Expired - Lifetime EP0893601B1 (fr) 1997-07-25 1998-06-26 Pompe à piston combinée avec une pompe de surpression

Country Status (2)

Country Link
EP (1) EP0893601B1 (fr)
DE (2) DE19732062A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10352029A1 (de) * 2003-11-07 2005-06-16 SCHWäBISCHE HüTTENWERKE GMBH Verdrängerpumpe mit Vorladeeinrichtung
WO2013053794A1 (fr) * 2011-10-14 2013-04-18 Continental Automotive Gmbh Ensemble de pompes

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4026717A1 (de) 1990-08-24 1992-02-27 Uraca Pumpen Verdraenger- bzw. kolbenpumpe

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB590199A (en) * 1944-12-19 1947-07-10 Fawcett Preston & Co Ltd Improvements in swash plate pumps for liquids
FR2439312A1 (fr) * 1978-10-16 1980-05-16 Messier Hispano Sa Perfectionnements aux pompes hydrauliques comportant un etage de suralimentation
EP0061159A3 (fr) * 1981-03-20 1983-04-20 Houdaille Industries, Inc. Pompe centrifuge reversible ayant les mêmes performances dans les deux sens
DE3741977A1 (de) * 1987-12-11 1989-06-22 Philips Patentverwaltung Pumpvorrichtung fuer leicht viskose fluessigkeiten
US5220225A (en) * 1992-06-17 1993-06-15 Vickers, Incorporated Integrated electric motor driven inline hydraulic apparatus

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4026717A1 (de) 1990-08-24 1992-02-27 Uraca Pumpen Verdraenger- bzw. kolbenpumpe

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10352029A1 (de) * 2003-11-07 2005-06-16 SCHWäBISCHE HüTTENWERKE GMBH Verdrängerpumpe mit Vorladeeinrichtung
WO2013053794A1 (fr) * 2011-10-14 2013-04-18 Continental Automotive Gmbh Ensemble de pompes

Also Published As

Publication number Publication date
DE59811361D1 (de) 2004-06-17
EP0893601B1 (fr) 2004-05-12
DE19732062A1 (de) 1999-01-28
EP0893601A3 (fr) 2000-03-01

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