EP0149219A2 - Pompe à piston - Google Patents

Pompe à piston Download PDF

Info

Publication number
EP0149219A2
EP0149219A2 EP84116156A EP84116156A EP0149219A2 EP 0149219 A2 EP0149219 A2 EP 0149219A2 EP 84116156 A EP84116156 A EP 84116156A EP 84116156 A EP84116156 A EP 84116156A EP 0149219 A2 EP0149219 A2 EP 0149219A2
Authority
EP
European Patent Office
Prior art keywords
plunger
plungers
pump according
drive
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.)
Withdrawn
Application number
EP84116156A
Other languages
German (de)
English (en)
Other versions
EP0149219A3 (fr
Inventor
Horst Wolff
Franz Hani
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.)
Speck-Kolbenpumpen-Fabrik
SPECK KOLBENPUMPEN FABRIK
Original Assignee
Speck-Kolbenpumpen-Fabrik
SPECK KOLBENPUMPEN FABRIK
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 Speck-Kolbenpumpen-Fabrik, SPECK KOLBENPUMPEN FABRIK filed Critical Speck-Kolbenpumpen-Fabrik
Publication of EP0149219A2 publication Critical patent/EP0149219A2/fr
Publication of EP0149219A3 publication Critical patent/EP0149219A3/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Withdrawn legal-status Critical Current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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • 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
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • 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
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/146—Swash plates; Actuating elements
    • 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
    • F04B53/08—Cooling; Heating; Preventing freezing

Definitions

  • the invention relates to a pump working with a plurality of plungers, the plungers being arranged centrally symmetrically with respect to the drive shaft.
  • This separation of the medium and lubricant has the advantage that pumps of this type can also be used in technical fields where special media have to be conveyed and a consequent separation of lubricating oil circuits is absolutely necessary.
  • the object of the present invention is to create a pump which works with several plungers, in particular with five plungers, and which has a particularly compact design, one provides extremely even funding, ensures smooth running and can be manufactured in a very economical manner.
  • the solution to this problem essentially consists in the fact that the plungers and the pump chambers assigned to them are arranged directly adjacent to one another and concentrically to the drive shaft and to a suction chamber provided in the center of the pump body, and that the high-pressure outlets of the pump chambers opening into a common, annular pressure chamber run essentially radially.
  • the edge of the ball bearing belonging to the swash plate on the pump side is used directly to actuate the plungers.
  • the rolling processes that occur during operation between the plungers and this ball bearing ring lead to smoothing and hardening effects, which improve the function and the service life in the desired manner.
  • Another major advantage of using a centrally and centrally located suction connection is that simple leakage return into the suction connection area is possible via short connecting bores.
  • Another peculiarity of the invention which has a beneficial effect in terms of function and in view of the desired economy of the overall construction, is that two-part plungers are used, the plunger part on the drive side having a larger diameter than the pump-side part of the plunger. In this way, on the one hand, optimal guide surfaces for the plunger on the drive side and, on the other hand, also an optimal displacement stroke on the pump side are achieved.
  • a preferred embodiment of the plungers consists in the fact that the front or pump-side plunger part consists of a solid ceramic body which is connected to the rear metallic part, in particular is glued. The gluing takes place at a temperature below the operating temperature, which is generally 80 °, while a temperature substantially corresponding to the operating temperature is selected as the adhesive curing temperature.
  • a cooling device is provided in the free space between the plungers extending into the drive space, which is designed to be self-contained and is acted upon by the medium to be conveyed in each case.
  • This cooling device preferably consists of a tube which extends from the area of the suction connection into the area of the swash plate and through which a part of the conveyed medium flows. In this way, despite the exact separation of the drive area to be lubricated and the delivery area, it is possible to use the pumped medium for heat dissipation.
  • the plungers can also be arranged radially, so that their axes do not run parallel to the drive shaft but perpendicular to the drive shaft. It is also important in this embodiment that a plurality of comparatively small plungers are used in conjunction with a high drive speed, since in all embodiments of the invention the principle must be maintained that small, optimally distributed forces are used, since only in this way the above advantages already described can be achieved and high speeds can also be driven without a disturbing increase in temperature.
  • an essentially pot-shaped drive housing 1 is provided, the bottom part 2 of which has passage openings for plungers on the one hand and forms a fastening surface for the actual pump unit 5 on the other hand.
  • the housing 1 On the side facing the respective drive motor, the housing 1 is closed with a stable end wall 3, which preferably consists of a material that conducts heat poorly, so that the engine heat is kept away from the housing 1 as far as possible.
  • Housing 1 and end wall 3 are screwed together. Furthermore, 4 holes for screw bolts are provided in the area of the flange-like housing end, by means of which the entire pump unit is fastened to a drive motor.
  • the circumferential circle of the pump preferably lies approximately on the circumferential circle of the associated motor or it has a smaller diameter. It is also advantageous to design the connections so that the pump can be attached to standard motors.
  • a pressure bearing 6 is held in the end wall 3, and a seal 8 is provided between the end wall 3 and the motor shaft 7.
  • the drive shaft 7 is wedged with a swash plate 9, which is provided in the usual way with a counterweight 10.
  • This swash plate 9, which can consist of a sintered or forged part, carries a ball bearing 11, one ring 12 of which is connected to the swash plate 9, while the other ring 13 cooperates with the plungers 14.
  • ball bearing 11 is a commercially available and therefore inexpensive ball bearing.
  • the bearing ring 13 Due to the rolling effect between the bearing ring 13 and plungers 14, the bearing ring 13 is smoothed, i.e. rougher bearing rings become smooth and hardened after a short period of operation, so that a largely wear-free pairing arises.
  • the plungers 14 are formed in two parts and consist of a section 15 made of metal in the area of the drive housing and a section 16 made of all-ceramic, which forms the actual displacement element.
  • the two plunger sections 15, 16 are preferably glued together.
  • a rigid ring is preferably inserted into a recess in the metallic plunger part, which additionally provides mechanical security in the connection of the two parts.
  • the cross section of the drive side lying metal part is larger than the cross section of the ceramic member 16. In this way, a safe and else large comparatively M guidance of the plunger member 15 can be achieved in the corresponding sleeve 17 which is preferably formed in one piece with the housing.
  • the plungers 14 are prestressed against the ball bearing ring 13 by means of a compression spring 20, ie the spring 20 ensures the return movement of the plungers 14.
  • the spring 20 is supported between the housing 1 and a support ring which is fixed to the plunger part 15 by means of a ring.
  • a low-pressure seal 18 is provided between the bottom wall 2 of the housing 1 and the respective plunger sections 15. The gap between the plunger section 15 and the guide sleeve 17 is connected to the housing interior via bores 19.
  • the housing 1 is further provided with at least one filler plug 21 and a drain plug 22, which are provided on the top and bottom of the housing 1.
  • the drain plug 22 is magnetically designed or connected to a magnetic element, so that metal particles caused by wear are held on this plug 22 and thus also a bearing wear indicator is achieved.
  • the housing 1 is very easy to manufacture, the guide bores for the plungers being able to be produced in one operation using a multi-spindle head, and overall little turning is required.
  • the actual pump part 5 is axially clamped to the drive housing via screw bolts 23.
  • a first guide and spacer sleeve 25 directly adjoins the bottom wall 2 of the housing and adjoins the transmission seal 18.
  • the larger diameter section 15 of the plunger 14 engages in this sleeve 25.
  • the annular space surrounding this plunger section is open to the outside via bores 26.
  • annular sleeve 27 which comprises an inner sleeve 28 which receives the high and low pressure seals 29, 30. Radial channels 31 are formed between these seals 29, 30, which lead into an annular space 32 between the inner sleeve 28 and the outer sleeve 27.
  • the annular space 32 is connected to the suction space 34 via bores 33.
  • a further sleeve part 35 is arranged, which delimits the pump chamber 36 on one side with its end face.
  • An inlet valve 37 and an outlet valve 38 are assigned to each pump chamber in the usual way.
  • the suction space 34 is provided in the center, so that the connecting lines to the inlet valves can be designed symmetrically and identically.
  • the suction space 34 is delimited by an end plate 39 in which the suction connection 40 is formed.
  • the plate 39 is braced against the pump body 24 by means of the screw bolts 23, which bring about the entire axial bracing of the coaxially assembled components.
  • a circumferential pressure bore 41 is connected to the high pressure outlets of the individual pumping chambers 36.
  • Figure 2 shows the symmetrical arrangement of the pumping chambers with respect to the central connection 40 and also reveals that the individual valves are easily accessible via the corresponding screw plugs.
  • a special cooling device can be used, which allows heat to be removed from the drive space, using the pumped medium as a coolant.
  • a central tube 42 is provided, which extends from the suction space 34 to the area of the ring 13 of the ball bearing 11 and is designed to be closed in this end area. Seals are provided between this tube 42 and the housing base 2 and the pump body 24.
  • the tube 42 widens somewhat in the shape of a funnel in the suction space 34, and a partial flow of the conveyed medium arises due to this configuration through the pipe 42, which results in the desired cooling effect in the area of the drive housing.
  • any other suitable cooling device can be used, which must be flowed through by a part of the conveyed medium. A flow with a proportion of about 10% of the pumped medium can in most cases bring about the desired cooling effect.
  • Pumps designed according to the invention are preferably equipped with an odd number of plungers. It is important that the pump at high speeds, e.g. 2800 revolutions per minute and more can be driven and that drive powers of 4 to 5 kW, for example, can be used without any temperature problems.
  • connection flange of the gear housing is preferably designed as a heat exchanger, for which purpose at least one copper tube can be inserted into this connection flange. This measure has the advantage that heat generated by the drive motor is prevented from the transmission.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP84116156A 1983-12-28 1984-12-21 Pompe à piston Withdrawn EP0149219A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3347307 1983-12-28
DE19833347307 DE3347307A1 (de) 1983-12-28 1983-12-28 Plungerpumpe

Publications (2)

Publication Number Publication Date
EP0149219A2 true EP0149219A2 (fr) 1985-07-24
EP0149219A3 EP0149219A3 (fr) 1987-06-16

Family

ID=6218299

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84116156A Withdrawn EP0149219A3 (fr) 1983-12-28 1984-12-21 Pompe à piston

Country Status (5)

Country Link
US (1) US4583921A (fr)
EP (1) EP0149219A3 (fr)
JP (1) JPS60156982A (fr)
DE (1) DE3347307A1 (fr)
DK (1) DK612284A (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1988005866A1 (fr) * 1987-01-28 1988-08-11 Alfred Kärcher GmbH & Co. Appareil de nettoyage a haute pression equipe d'une pompe a piston a plateau oscillant
EP0329208A3 (en) * 1988-01-25 1989-10-11 Friedrichs Pumpen Gmbh Hydraulically driven high-pressure cleaner
EP0414955A1 (fr) * 1989-09-01 1991-03-06 Alfred Kärcher GmbH & Co. Pompe à haute pression pour des disposifs à nettoyer ou appareils du même type
EP0484762A1 (fr) * 1990-11-06 1992-05-13 FAIP S.r.L. OFFICINE MECCANICHE Pompe haute pression à deux pistons et moteur à commutation pour nettoyeur hydraulique
DE4322309C1 (de) * 1993-07-05 1994-09-15 Rupert Rau Vorrichtung zum Fördern und Einsprühen von Flüssigkeit
DE19650272A1 (de) * 1996-12-04 1998-06-10 Teves Gmbh Alfred Axialkolbenpumpe
EP2369180A1 (fr) * 2010-03-13 2011-09-28 Dr. Ing. h.c. F. Porsche AG Pompe à carburant haute pression
AT519398A1 (de) * 2016-12-06 2018-06-15 Miba Sinter Austria Gmbh Verfahren zur Herstellung einer Taumelscheibe
WO2023131712A1 (fr) * 2022-01-10 2023-07-13 Alfred Kärcher SE & Co. KG Groupe motopompe, en particulier pour un appareil de nettoyage haute pression

Families Citing this family (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL8501315A (nl) * 1985-05-08 1986-12-01 Multinorm Bv Pomp.
US4734013A (en) * 1986-02-18 1988-03-29 V-Tech Industries Inc. Rotary pressure intensifier
US5074756A (en) 1988-05-17 1991-12-24 Patient Solutions, Inc. Infusion device with disposable elements
US5803712A (en) 1988-05-17 1998-09-08 Patient Solutions, Inc. Method of measuring an occlusion in an infusion device with disposable elements
US5246347A (en) 1988-05-17 1993-09-21 Patients Solutions, Inc. Infusion device with disposable elements
DE19525852B4 (de) * 1995-07-15 2004-07-15 Danfoss Analytical A/S Axialkolben-Mikropumpe
IT1287936B1 (it) * 1996-07-03 1998-08-26 Lavorwash Srl Pompa a pistoni assiali
JP3783303B2 (ja) * 1996-10-29 2006-06-07 株式会社島津製作所 プランジャ型送液ポンプ
DE19803533A1 (de) * 1998-01-30 1999-08-05 Itt Mfg Enterprises Inc Axialkolbenpumpe
US6092998A (en) * 1998-03-20 2000-07-25 Devilbiss Air Power Company Pump for a pressure washer
US5993170A (en) * 1998-04-09 1999-11-30 Applied Materials, Inc. Apparatus and method for compressing high purity gas
DE19859336C1 (de) * 1998-12-22 2000-06-29 Kaercher Gmbh & Co Alfred Hochdruckreinigungsgerät
JP4085631B2 (ja) * 2001-12-26 2008-05-14 セイコーエプソン株式会社 複合型ポンプ
DE102005009311A1 (de) * 2005-02-21 2006-08-24 Alfred Kärcher Gmbh & Co. Kg Hochdruckreinigungsgerät
US7428812B2 (en) * 2006-05-04 2008-09-30 Fci Americas Technology, Inc. Hydraulic tool with wobble plate transmission
JP4803027B2 (ja) * 2006-12-29 2011-10-26 トヨタ紡織株式会社 コンプレッサ
JP4833914B2 (ja) * 2007-04-27 2011-12-07 敏博 松本 麺紐延ばしローラ装置
US8202063B2 (en) * 2009-04-30 2012-06-19 Briggs & Stratton Corporation Base plate for power equipment configured for mounting an engine and a tool
EP2459325B1 (fr) 2009-07-27 2015-02-25 Alfred Kärcher GmbH & Co. KG Appareil de nettoyage haute pression
US8337172B2 (en) * 2009-10-05 2012-12-25 Briggs & Stratton Corporation Pressure washer pump and engine system
US8408882B2 (en) * 2009-10-05 2013-04-02 Briggs & Stratton Corporation Pressure washer pump and engine system
US8794209B2 (en) 2010-11-18 2014-08-05 Briggs & Stratton Corporation Engine mounting system
DE102011054442A1 (de) * 2011-10-12 2013-04-18 Alfred Kärcher Gmbh & Co. Kg Kolbenpumpe für ein Hochdruckreinigungsgerät
JP5687257B2 (ja) * 2012-09-04 2015-03-18 川崎重工業株式会社 燃料ポンプ
WO2020015518A1 (fr) * 2018-07-18 2020-01-23 宁波合力机泵股份有限公司 Extrémité de puissance de pompe à mouvement alternatif de type vertical reliée à une surface sphérique multiple et pompe d'injection d'eau l'utilisant
US20240102467A1 (en) * 2021-02-11 2024-03-28 Mixtron S.R.L. Axial pump with inclined plate
CN118793607B (zh) * 2024-09-12 2024-11-29 鸿鲲新能源(海南)有限公司上海分公司 一种高压柱塞泵

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US2622942A (en) * 1947-04-24 1952-12-23 Munoz Alfred Compressor
US2712829A (en) * 1951-10-30 1955-07-12 Proctor Electric Co Valve device for pressure cookers and the like
GB729811A (en) * 1952-06-18 1955-05-11 Metalurgica Joter Limitada Improvements in or relating to liquid pumps
DE1010325B (de) * 1953-08-31 1957-06-13 Bendix Aviat Corp Brennstoffzufuehrungssystem fuer Verbrennungsmotoren
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GB1067962A (en) * 1964-02-15 1967-05-10 Hydraulik Gmbh Improvements in/or relating to swash plate pumps
US3507584A (en) * 1968-03-27 1970-04-21 Us Navy Axial piston pump for nonlubricating fluids
FR1587661A (fr) * 1968-08-02 1970-03-27
US3811798A (en) * 1972-07-19 1974-05-21 Hydraulic Syst Inc Piston pump with self-lubricating pistons
US3849032A (en) * 1973-07-02 1974-11-19 Perfect Pump Co High pressure reciprocating pump
DE2413691B2 (de) * 1974-03-21 1976-04-29 Druckoelpumpe
US4140442A (en) * 1977-03-14 1979-02-20 Perfect Pump Co., Inc. High pressure pump
US4092240A (en) * 1977-06-29 1978-05-30 Texaco Inc. Refrigeration oil processing
DE3041933A1 (de) * 1980-11-06 1982-06-09 Speck-Kolbenpumpen-Fabrik Otto Speck Kg, 8192 Geretsried Hochdruckpumpe
US4956439A (en) * 1988-02-04 1990-09-11 Tong Shen Nan High performance modified polyurethanes

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1988005866A1 (fr) * 1987-01-28 1988-08-11 Alfred Kärcher GmbH & Co. Appareil de nettoyage a haute pression equipe d'une pompe a piston a plateau oscillant
US5038673A (en) * 1987-01-28 1991-08-13 Alfred Karcher Gmbh & Co. High-pressure cleaning apparatus with a wobble plate piston pump
EP0329208A3 (en) * 1988-01-25 1989-10-11 Friedrichs Pumpen Gmbh Hydraulically driven high-pressure cleaner
EP0414955A1 (fr) * 1989-09-01 1991-03-06 Alfred Kärcher GmbH & Co. Pompe à haute pression pour des disposifs à nettoyer ou appareils du même type
EP0484762A1 (fr) * 1990-11-06 1992-05-13 FAIP S.r.L. OFFICINE MECCANICHE Pompe haute pression à deux pistons et moteur à commutation pour nettoyeur hydraulique
DE4322309C1 (de) * 1993-07-05 1994-09-15 Rupert Rau Vorrichtung zum Fördern und Einsprühen von Flüssigkeit
DE19650272A1 (de) * 1996-12-04 1998-06-10 Teves Gmbh Alfred Axialkolbenpumpe
DE19650272B4 (de) * 1996-12-04 2004-08-26 Continental Teves Ag & Co. Ohg Axialkolbenpumpe
EP2369180A1 (fr) * 2010-03-13 2011-09-28 Dr. Ing. h.c. F. Porsche AG Pompe à carburant haute pression
US8720316B2 (en) 2010-03-13 2014-05-13 Dr. Ing. H.C. F. Porsche Aktiengesellschaft High-pressure fuel pump
AT519398A1 (de) * 2016-12-06 2018-06-15 Miba Sinter Austria Gmbh Verfahren zur Herstellung einer Taumelscheibe
AT519398B1 (de) * 2016-12-06 2019-05-15 Miba Sinter Austria Gmbh Verfahren zur Herstellung einer Taumelscheibe
US10792733B2 (en) 2016-12-06 2020-10-06 Miba Sinter Austria Gmbh Method for producing a swashplate
WO2023131712A1 (fr) * 2022-01-10 2023-07-13 Alfred Kärcher SE & Co. KG Groupe motopompe, en particulier pour un appareil de nettoyage haute pression

Also Published As

Publication number Publication date
DK612284D0 (da) 1984-12-19
EP0149219A3 (fr) 1987-06-16
JPS60156982A (ja) 1985-08-17
DE3347307A1 (de) 1985-07-11
US4583921A (en) 1986-04-22
DK612284A (da) 1985-06-29

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