EP0600168A1 - Pompe à déplacement positif - Google Patents

Pompe à déplacement positif Download PDF

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Publication number
EP0600168A1
EP0600168A1 EP93114457A EP93114457A EP0600168A1 EP 0600168 A1 EP0600168 A1 EP 0600168A1 EP 93114457 A EP93114457 A EP 93114457A EP 93114457 A EP93114457 A EP 93114457A EP 0600168 A1 EP0600168 A1 EP 0600168A1
Authority
EP
European Patent Office
Prior art keywords
suction
pump
displacement pump
space
pump according
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
EP93114457A
Other languages
German (de)
English (en)
Other versions
EP0600168B1 (fr
Inventor
Willi W. Professor Dr.-Ing. Dettinger
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 EP0600168A1 publication Critical patent/EP0600168A1/fr
Application granted granted Critical
Publication of EP0600168B1 publication Critical patent/EP0600168B1/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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0008—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
    • F04B11/0016—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators with a fluid spring
    • F04B11/0025—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators with a fluid spring the spring fluid being in direct contact with the pumped fluid

Definitions

  • the invention relates to a positive displacement pump, in particular a piston or plunger pump, with at least one displacement work space closed by a suction and a pressure valve and a pump body comprising at least one suction valve and a suction line part, e.g. B. valve head or displacement housing block, and a suction-side vibration damper designed in the manner of a wind boiler.
  • a positive displacement pump in particular a piston or plunger pump
  • a suction line part e.g. B. valve head or displacement housing block
  • a suction-side vibration damper designed in the manner of a wind boiler.
  • the risk of cavitation in the area of the suction valves during the suction stroke of the respective displacer is also significantly increased. Because under unfavorable Operating conditions, the vacuum occurring at the suction valve during the suction stroke can coincide with a pressure minimum of the aforementioned vibrations in the pump medium. The cavitation that occurs causes premature wear of the suction valves. In addition, the efficiency of the pump can be considerably reduced because the respective displacement work space in the case of cavitation is only incompletely filled with pump medium during the suction stroke.
  • Vibration dampers of this type typically consist of a relatively large pressure vessel, which is connected to the suction line of the pump at a large distance from the pump and is partially filled with gas, which, due to its elasticity, makes it possible to compensate for the vibrations that otherwise occur in the pump medium on the suction side of the pumps.
  • the damping effect is relatively low even in the case of large wind boilers compared to the design effort.
  • the object of the invention is now to significantly reduce the design effort for the vibration damper in a positive displacement pump of the type specified.
  • a sack space forming the wind boiler is arranged directly on the pump body, at least partially above a suction line part of the pump body connected to it, or is formed as part of the pump body.
  • the invention is based on the general idea of arranging the vibration damper on the suction side directly on or integrated in housing parts of the pump, so that the wind boiler practically forms part of the pump and is accordingly produced together with the pump. This eliminates a significant part of the effort that would otherwise be required to install a vibration damper. In essence, the wind boiler in the invention Design only to be taken into account when designing the housing parts of the pump body once.
  • the cylinders assigned to the pistons or plungers can be arranged in series in a generally known manner within a cylinder block and each communicate with bores extending transversely to the plane of the cylinder which the suction and pressure valves are arranged, these bores then communicating at their suction valve-side ends with a suction manifold in the cylinder block, and the sack space forming the wind boiler is arranged or formed next to the suction manifold on the cylinder block or a part thereof.
  • the level of the pump medium in the sack space forming the air chamber is expediently regulated in order to ensure the optimal vibration-damping effect at all times.
  • an air supply line on the bag space, via which air can then be supplied, which has a certain excess pressure compared to the suction pressure of the pump.
  • a suction line is arranged in the bag room, the inlet opening of which is approximately at the level of the desired level of the pump medium in the bag room.
  • the outlet of this suction line is connected on the suction side of the pump to an area with particularly low pressure, for example to a constriction in the suction line designed in the manner of a Venturi nozzle, so that the dynamic pressure reduction occurring in the flowing pump medium within the constriction can be exploited.
  • the invention is also particularly advantageous for so-called booster pumps because the vibration damping on the suction side of the piston or plunger pump avoids transmission of these vibrations to the pressure side of the charge pump arranged on the suction side of the piston or plunger pump. Accordingly, the charge pump can easily be designed in the manner of a centrifugal pump, the turbine wheel of which serves to convey the pump medium is typically very sensitive to vibrations on the pressure side.
  • the aforementioned suction line is connected with its outlet on the suction side of the charge pump, while the air supply line is connected to a compressed air source due to the relatively high pressure generated by the charge pump on the suction side of the piston or plunger pump.
  • the pump shown in Fig. 1 has a cylinder block 1 with lying horizontally arranged cylinder bores, in each of which a plunger 2 operates.
  • the cylinder bores open into vertical bores 3, which are connected at their lower ends to a suction manifold 4 and in the area of their upper sections are penetrated by a pressure manifold 4, which is not visible in FIG. 1 and is parallel to the suction manifold 4.
  • a suction and a pressure valve 5 and 6 are housed in a generally known manner, so that during the suction stroke of the respective plunger 2 from the suction manifold 4, pump medium flows into the cylinder bore 1 assigned to the respective plunger 2 and during the subsequent pressure stroke into the Pressure manifold is displaced.
  • the suction manifold 4 is connected via an opening 7 arranged in the cylinder block 1 to a sack space 8 arranged on or in the cylinder block 1, the interior of which is at least partially vertically above the Levels of the suction manifold 4 is.
  • said opening 7 is preferably designed as an elongated hole which extends in the direction of the axis of the suction manifold 4 and which, according to FIG. 1, is preferably arranged in the region of the lower cross-sectional half of the suction manifold 4.
  • this sack space is filled with pump medium in a lower region and with air in the upper region, so that vibrations in the pump medium are formed on the suction side of the pump-damping wind chamber.
  • the level of the liquid is expediently regulated.
  • a supply air line 10 covered on the outside by a filter cap 9, which is provided at its lower end projecting into the bag space 8 with a float valve 11 and a throttle 13, which is however also at a greater distance from the float valve 11. ie can be arranged further up on the supply air line 10.
  • the float valve 11 is automatically closed by the pump medium as soon as its level in the bag space 8 exceeds a target level below the lower end of the supply air line 10.
  • a suction line 12 is arranged in the lower part of the bag space 8, the inlet opening of which is arranged somewhat lower than the lower end of the supply air line 10 or the float valve 11.
  • the suction line 12 opens into a constriction 14 designed in the manner of a Venturi nozzle within a suction line 15 connected to the suction manifold 4, via which the pump medium is led to the suction manifold 4.
  • suction line 12 opens into the constriction 14 from above.
  • the suction line 15 or the suction manifold 4 In front of and behind the constriction 14, the suction line 15 or the suction manifold 4 have a comparatively large cross section, so that during pumping operation, when the pumping medium flows through the constriction 14, in the region of the constriction 14 there is a clear dynamic pressure drop compared to the pressure in the pumping medium occurs behind the constriction 14, d. H. the pressure of the pump medium in the constriction 14 is constantly lower than the pressure of the pump medium in the suction manifold 4 during pump operation.
  • the supply air line 10 and the suction line 12 interact in the following manner to regulate the level of the pump medium in the bag room 8: First of all, it is assumed that a certain negative pressure in relation to the pressure of the atmosphere occurs in the suction manifold 4 during pump operation.
  • the suction line 12 opens into the constriction 14 from above, the air bubbles entrained by the suction flow of the pump medium predominantly remain in the upper cross-sectional area of the suction line 15 or the suction manifold 4, so that these air bubbles due to the relatively deep opening 7 between the suction manifold 4 and the bag space 8 only enter bag space 8 in exceptional cases and are mainly conveyed by the pump together with the pump medium to the pressure side of the pump.
  • a level of the pump medium which is approximately at the level of the inlet opening of the suction line 12 is set within the bag space 8 within a very short time.
  • the pump medium of the suction manifold 4 is supplied with a certain excess pressure (suction pressure), so that while pump operation in the suction manifold due to dynamic effects compared to this suction pressure, a drop in pressure may occur, the pressure in the suction manifold 4 remains above the pressure of the atmosphere .
  • the supply air line 10 must be connected to a pneumatic pressure source, with which air can be supplied under a pressure which is above the pressure of the pump medium in the suction manifold 4.
  • the supply air line 10 and the suction line 12 can then interact to regulate the level of the pump medium in the bag space 8 in the manner described above.
  • the increased suction pressure can be generated, for example, by the pump medium flowing to the pump from a reservoir which is arranged higher than the pump. Instead, it can also be provided that the reservoir is under a certain excess pressure.
  • the invention can also be implemented in a so-called booster pump, in which a charge pump 16 is arranged on the inlet side of the suction manifold 4 of a piston pump, or the like, for example, in the manner of a centrifugal pump. is working.
  • a corresponding arrangement is shown schematically in FIG. 4.
  • the suction line 12 opens on the inlet side of the charge pump 16 into the suction line 15.
  • Compressed air is supplied via the supply air line 10, the pressure of which is slightly above the charge pressure of the charge pump 16 or above the pressure in the suction line 4.
  • the level of the pump medium in the bag space 8 is thus regulated again in the manner described above. If this level is above the inlet opening of the suction line 12, it is lowered by the compressed air during pump operation until it has dropped so far that the compressed air enters the suction line 12 and can be sucked off by means of the charging pump 16.
  • the throttle 13 or another limitation of the inflow of compressed air via the supply air line 10 in turn ensures that only comparatively small amounts of air can flow in, which can be easily extracted via the suction line 12 and overall the efficiency do not or only negligibly impair the pump.
  • the wind chamber formed by the bag space 8 serves primarily to protect the charge pump 16 from vibrations of the piston pump generated on the suction side.
  • charge pumps, or the like, for example, with a turbine wheel. promote, namely the conveyor is extremely sensitive to vibrations on the pressure side of the charge pump 16.
  • the vibration damping provided according to the invention, the charge pump 16 is effectively protected and can accordingly achieve a long life.
  • the compressor for the compressed air-operated vehicle brakes is typically a suitable compressed air source available, to which the supply air line 10 can be connected if necessary.
  • Basically known priority control valves then ensure that the vehicle brakes are preferably supplied with compressed air and that only excess compressed air can reach the supply air line 10.
  • the compressed air supply to the supply air line 10 is practically always unproblematic.
  • the compressed air can also be used for pneumatically operated control elements of the pump, for example pneumatically operated feed or circulation valves and the like. It is expedient to design these control elements in such a way that the supply air line receives compressed air only during pump operation.
  • the float valve 11 on the supply air line 10 can optionally be omitted. However, the arrangement of the float valve 11 is expedient in order to prevent pump medium from kicking back into the supply air line 10.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP93114457A 1992-12-03 1993-09-09 Pompe à déplacement positif Expired - Lifetime EP0600168B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4240590A DE4240590A1 (de) 1992-12-03 1992-12-03 Verdrängerpumpe
DE4240590 1992-12-03

Publications (2)

Publication Number Publication Date
EP0600168A1 true EP0600168A1 (fr) 1994-06-08
EP0600168B1 EP0600168B1 (fr) 1996-10-16

Family

ID=6474243

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93114457A Expired - Lifetime EP0600168B1 (fr) 1992-12-03 1993-09-09 Pompe à déplacement positif

Country Status (3)

Country Link
EP (1) EP0600168B1 (fr)
DE (2) DE4240590A1 (fr)
ES (1) ES2094438T3 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19543780B4 (de) * 1995-11-24 2005-09-08 Zf Friedrichshafen Ag Radialkolbenpumpe
DE19604132C2 (de) * 1996-02-06 2000-04-13 Hammelmann Paul Maschf Hochdruckplungerpumpe, vorzugsweise für Arbeitsdrücke oberhalb 2.000 bar
DE102004015263A1 (de) * 2004-03-29 2005-10-20 Siemens Ag Radialkolbenpumpe
DE102004015266A1 (de) * 2004-03-29 2005-10-20 Siemens Ag Hochdruckpumpe mit integriertem Hochdruckspeicher
DE102012219621A1 (de) * 2012-10-26 2014-04-30 Robert Bosch Gmbh Kolbenpumpe

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE63438C (de) * haniel & lueg in Düsseldorf-Grafenberg Einrichtung zur hydraulischen Ausgleichung von Druckschwankungen in Pumpen und Rohrleitungen
CH118293A (de) * 1926-04-19 1927-05-16 Bucher Guyer Ag Masch Kolbenpumpe.
FR723328A (fr) * 1930-12-08 1932-04-07 Perfectionnements aux pompes à piston
DE893889C (de) * 1951-10-19 1953-10-19 Knorr Bremse Gmbh Saugwindkessel mit Wasserstandsregelung fuer Kolbenpumpen
DE956019C (de) * 1954-03-28 1957-01-10 Gotthard Allweiler Pumpenfabri Doppelt wirkende Kolbenpumpe, insbesondere fuer Hauswasserversorgungsanlagen
US3329155A (en) * 1963-12-19 1967-07-04 Commissariat Energie Atomique Anti-hammer apparatus

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE63438C (de) * haniel & lueg in Düsseldorf-Grafenberg Einrichtung zur hydraulischen Ausgleichung von Druckschwankungen in Pumpen und Rohrleitungen
CH118293A (de) * 1926-04-19 1927-05-16 Bucher Guyer Ag Masch Kolbenpumpe.
FR723328A (fr) * 1930-12-08 1932-04-07 Perfectionnements aux pompes à piston
DE893889C (de) * 1951-10-19 1953-10-19 Knorr Bremse Gmbh Saugwindkessel mit Wasserstandsregelung fuer Kolbenpumpen
DE956019C (de) * 1954-03-28 1957-01-10 Gotthard Allweiler Pumpenfabri Doppelt wirkende Kolbenpumpe, insbesondere fuer Hauswasserversorgungsanlagen
US3329155A (en) * 1963-12-19 1967-07-04 Commissariat Energie Atomique Anti-hammer apparatus

Also Published As

Publication number Publication date
ES2094438T3 (es) 1997-01-16
DE4240590A1 (de) 1994-06-09
DE59304188D1 (de) 1996-11-21
EP0600168B1 (fr) 1996-10-16

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