EP1445485B1 - Pompe de dosage pour dispositif de chauffage pour véhicule - Google Patents

Pompe de dosage pour dispositif de chauffage pour véhicule Download PDF

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Publication number
EP1445485B1
EP1445485B1 EP04000552A EP04000552A EP1445485B1 EP 1445485 B1 EP1445485 B1 EP 1445485B1 EP 04000552 A EP04000552 A EP 04000552A EP 04000552 A EP04000552 A EP 04000552A EP 1445485 B1 EP1445485 B1 EP 1445485B1
Authority
EP
European Patent Office
Prior art keywords
piston
displacement
chamber
inlet chamber
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.)
Expired - Fee Related
Application number
EP04000552A
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German (de)
English (en)
Other versions
EP1445485A2 (fr
EP1445485A3 (fr
Inventor
Michael Humburg
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.)
Eberspaecher Climate Control Systems GmbH and Co KG
Original Assignee
J Eberspaecher 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 J Eberspaecher GmbH and Co KG filed Critical J Eberspaecher GmbH and Co KG
Publication of EP1445485A2 publication Critical patent/EP1445485A2/fr
Publication of EP1445485A3 publication Critical patent/EP1445485A3/fr
Application granted granted Critical
Publication of EP1445485B1 publication Critical patent/EP1445485B1/fr
Anticipated expiration legal-status Critical
Expired - Fee Related 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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • F04B17/046—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the fluid flowing through the moving part of the motor
    • 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
    • F04B13/00—Pumps specially modified to deliver fixed or variable measured quantities

Definitions

  • the present invention relates to a metering pump device for a vehicle heater, as defined in the preamble of claim 1.
  • Heaters used in motor vehicles which may be effective, for example, as a heater or as a heater, are generally operated with the same fuel as a drive unit provided in such a vehicle. It is therefore necessary to supply such a heater, depending on the required heat output, a correspondingly adapted amount of fuel or fuel quantity.
  • metering pumping devices are generally used which must be able to deliver comparatively small amounts of fuel in precisely metered manner to the heater in order to minimize combustion in the required manner, e.g. especially with minimal pollutant emissions to run off.
  • a Dosierpumpan extract in which a pump piston in a pump chamber is movable back and forth.
  • this pumping chamber is connected to either a fuel supply region or a fuel discharge region, so that fuel is introduced into the pump chamber, for example when the pump chamber is connected to the fuel supply region and when the pump piston is retracted by enlarging the pump chamber volume, and in a subsequent power stroke after connecting the pump chamber the Kraftstoffableit Scheme and pushing back the pump piston into the pump chamber by reducing the volume of the same fuel is discharged.
  • This effect has the consequence that, for example, only at every second stroke of the pump piston for receiving or sucking fluid to be funded in the pump chamber is effective and in a corresponding manner only at every second stroke for dispensing previously recorded fluids is effective.
  • an electromagnetically operated pump in which a displacement piston element is periodically movable back and forth between a position in which the volume of an inlet chamber is minimal and a position in which the volume of an outlet chamber is minimal ,
  • the change in volume of the inlet chamber or outlet chamber is achieved in that a piston portion of the displacement piston element is guided in a cylinder housing and more or less immersed in this. Since the piston portion displaceable in the cylinder housing and more or less immersed in this piston portion has a constant outer cross-section over its length, a displacement of the displacement piston member causes the volume of the inlet chamber and the volume of the outlet chamber to vary to the same extent.
  • the first valve arrangement is provided in the interior of the piston section and thus movable with this back and forth.
  • the fluid displaced from the displaced fluid during movement in order to minimize the volume of the inlet chamber initially enters an interior area of the piston section and leaves it through passage openings in the direction of the remaining volume area of the outlet chamber.
  • a pump according to the preamble of claim 1 is known from US 6,186,118 B1.
  • This known pumping device serves to generate the high fuel pressure required for the supply of the various cylinders of a diesel internal combustion engine in so-called common rail systems.
  • a piston to be driven via a piston rod of this pump is reciprocable in a cylinder.
  • the piston rod is guided through an opening formed with the cylinder end cap.
  • GB 2 180 302 A discloses a pumping device designed for dispensing beer.
  • a piston member driven by a piston rod, reciprocates in a cylinder.
  • the piston rod is guided through an open end of the cylinder for interaction with a drive.
  • US 3,809,507 discloses telescopically nested piston elements which are interconnected by openings extending along their longitudinal axis.
  • US Pat. No. 6,193,477 B1 discloses an electromagnetic pump in which, by exciting a coil arrangement, a piston element is moved in order to achieve a pumping effect in this way with low energy consumption.
  • a metering pump device for a vehicle heater according to claim 1.
  • This comprises an inlet chamber, an outlet chamber, a first valve arrangement between the inlet chamber and the outlet chamber, which allows a fluid exchange substantially only from the inlet chamber to the outlet chamber Displacement piston element, which between a first piston position, in which it minimizes the volume of the inlet chamber, and in a second piston position, in which it minimizes the volume of the outlet chamber, is movable, wherein upon movement of the displacement piston member from the second piston position to the first piston position, a volume decrease of the inlet chamber is greater than an increase in volume of the outlet chamber.
  • An essential feature of the metering pump device is that it has two chambers separated by a first valve arrangement, and that either the volume of the inlet chamber or the volume of the outlet chamber is minimized by the displacement piston element, depending on the direction of movement or movement stroke. It follows, however, that whenever, for example, when the displacement piston element enters the second piston position, ie moves in a certain direction of movement or a certain movement mode, this volume of the outlet chamber is minimized and fluid to be delivered thereby is expelled from this outlet chamber.
  • the delivery cycle or the delivery frequency of the metering pump device according to the invention is increased, so that a significantly higher-frequency delivery of fluid to be conveyed to the vehicle heater takes place, which results in improved adaptation to a quasi-continuous fluid flow entails.
  • the opening is stepped with a smaller diameter section and a larger diameter section, in that the displacement piston element has a portion of lesser diameter, the dimension of which is adapted to the smaller diameter portion of the opening and which is guided in the portion of lesser diameter of the opening, in that the displacement piston element has a section with a larger diameter, its dimension at the section is adapted with larger diameter of the opening and which is guided in the section of larger diameter of the opening, the piston housing is formed in the region in which the smaller diameter portion of the opening is formed, surrounded by a coil of an electromagnetic drive, that the displacement piston element with its portion of smaller diameter dips into the coil and forms an armature (36) of the electromagnetic drive, in that there is provided in the displacement piston element a fluid supply line which is open at the smaller diameter portion of the displacement piston element to the smaller diameter portion of the opening which has a mouth to the inlet chamber at the larger diameter portion of the displacement piston element and which is closable by a second valve arrangement which permits a fluid exchange
  • the construction of the metering pump device according to the invention can be, for example, such that in the first piston position, the displacement piston element dips into the inlet chamber with a first piston area and, in the second piston position, the displacement piston element dips into the outlet chamber with a second piston area.
  • the different changing of the volume of the inlet chamber and the volume of the outlet chamber upon movement of the displacement piston element which ultimately induces both volume changes by its movement, can be achieved, for example, in that the displacement piston element in a first piston area effective during movement of the displacement piston element in the direction of the first piston position has a first displacement surface and in a second piston region has a second displacement surface effective on movement of the displacement piston element in the direction of the second piston position and in that the first displacement surface is greater than the second displacement surface.
  • a homogenization of the outwardly ejected fluid flow in the direction of a continuous or quasi-continuous fluid flow can be further assisted by the fact that the first displacement surface and the second displacement surface have an area ratio of 2: 1 to each other.
  • the displacement piston member has a piston portion providing the first piston portion and the second piston portion and a displacement portion which dips when moving the displacement piston member from the first piston position to the second piston position in the outlet chamber.
  • a particularly simple design can provide that the displacement piston element between the first piston position and the second piston position is displaceable.
  • the region of the inlet chamber, in which the first piston region dips in the first piston position, and the region of the outlet chamber, in which the second piston region dips in the second piston position, are at least partially formed.
  • the piston housing is at least partially surrounded by a chamber housing and that the inlet chamber and / or the outlet chamber at least partially formed between the piston housing and the chamber housing is.
  • the first valve arrangement and / or the second valve arrangement is designed as a check valve.
  • the first valve arrangement and / or the second valve arrangement has a spring-biased valve member.
  • the first valve arrangement comprises a valve seat and a valve member which can be pressed against the valve seat, wherein the valve seat of the first valve arrangement is provided on a housing accommodating the displacement piston element.
  • FIG. 1 shows a dosing pump device 10 according to the invention in longitudinal section, cut along a longitudinal center line of a displacement piston element, generally designated 12.
  • the metering pump device 10 comprises a piston housing 14, in which a stepped, in the direction of the longitudinal axis L is provided substantially cylindrically extending opening 16 is provided.
  • an inlet nozzle member 22 having an inlet port 24 positioned and secured thereto in the opening 16 and the smaller diameter portion 20 thereof is formed.
  • This inlet connection element 22 can be connected, for example via a hose line or the like, to a fuel reservoir.
  • the displacement piston member 12 is formed correspondingly stepped and has a portion 28 with a lesser Diameter up, as well as a section 30 with a larger diameter.
  • the portion 28 of smaller diameter is adapted to the portion 20 of the opening 16, and in a corresponding manner, the portion 30 of the displacement piston member 12 is adapted to the portion 26 of the opening 16, so that in the two opening portions 20, 26 the Displacement piston element 12 is guided with very accurate fit.
  • sealing elements such as sealing rings or the like, on the outer periphery of the portion 30 of the displacement piston element 12.
  • the displacement piston member 12 In the region of the piston housing 14, in which the portion 20 of the opening 16 is formed, this is surrounded by a coil 32.
  • the coil 32 forms part of an electromagnetic drive 34.
  • the displacement piston member 12 forms with its portion 28, the partially in When the coil 32 is energized, the displacement piston element 12 is displaced upward against the action of a biasing spring 34 from the piston position shown in FIG.
  • the biasing spring 34 which may be formed for example as a helical compression spring, supported on the step-like transition between the sections 20, 26 of the opening 16 on the one hand and on the step-like transition between the sections 28 and 30 of the displacement piston member 12 on the other hand. If the excitation of the coil 32 terminated or reduced, so the displacement piston member 12 is moved back into the piston position shown in Fig. 1 under the biasing action of this biasing spring 34.
  • an inlet chamber 40 which can be seen above all in FIG. 2, is formed.
  • This inlet chamber 40 includes a first inlet chamber portion 42 which is provided substantially at the axial end portion 44 of the piston housing 14 and provided there through the portion 26 of the opening 16.
  • a second inlet chamber region 46 comprises at least one, preferably a plurality of radially outwardly leading openings 48 in the end region 44 of the piston housing 14.
  • a third inlet chamber region 50 comprises a substantially cylindrical, annular volume region 52 between the piston housing 14 and the chamber housing 38.
  • a generally designated 54 outlet chamber is formed.
  • This comprises an annular outlet chamber region 56 adjoining the inlet chamber region 50 and an outlet chamber region 58 leading radially inwards from the latter and comprising at least one opening 60 in the piston housing 14.
  • This opening or openings 60 and the Auslasshunt Scheme 58 are open radially inward to the portion 26 of the opening 14 in the piston housing 14, in a formed at the step-like transition between the sections 20 and 26 portion thereof, in which also the biasing spring 34 is received is.
  • This volume region of the opening section 26 forms a further outlet chamber region 62.
  • the metering pump device 10 can be connected to a device to be supplied, that is, for example, a vehicle heater, via an outlet connection 64 provided or integrally formed on the chamber housing 38.
  • a first valve arrangement 66 comprises a ring-like valve member 68, which under the biasing action of another biasing spring 70 rests against a stepped transition formed between the outlet chamber area 56 and the inlet chamber area 50, both on the piston housing 14 and the chamber housing 38.
  • this first valve assembly 66 which is in the form of a check valve, ensures that fluid flow can take place substantially only from the inlet chamber region 50 to the outlet chamber region 56, and not vice versa.
  • a supply line 72 extending in the longitudinal direction thereof is formed.
  • this supply line 72 is open to the opening section 20 of the opening 16 in the piston housing 14 and thus also to the inlet opening 24 of the inlet connection element 22.
  • this supply line 72 opens to the inlet chamber 40. Furthermore, the supply line 72 can be closed off at this mouth region 74 by a second valve arrangement 76.
  • This second valve arrangement 76 comprises a disk-like valve member 78, which is biased under the biasing action of another biasing spring 80 against a formed at a step-like extension transition of the feed line 72 providing opening in the displacement piston member 12 valve seat 82, wherein the spring 80 is thereby at one with the Displacement piston member 12 connected support member 84 is supported.
  • This second valve arrangement 76 thus ensures that a fluid flow from the fluid supply line 72 in the direction of the inlet chamber 40 is possible, while a fluid flow in the opposite direction is not possible.
  • the displacement piston member 12 is in a first piston position in which it is held by the biasing action of the biasing spring 34.
  • the displacement piston member 12 with a piston portion 86 dips into the inlet chamber 40 to the maximum extent, so that the inlet chamber portion 42 is substantially completely filled by the piston portion 86 of the displacement piston member 12 and thus the total volume of the inlet chamber 40 is minimized.
  • the total volume of the outlet chamber 54 which is not occupied by the displacement piston member 12 and can be arranged in the thus to be conveyed fluid, is reduced, until in the recognizable in Fig. 3 state in which the displacement piston member 12 in a second Piston position is, this volume is minimized.
  • the displacement piston element 12 displaces fluid from the outlet chamber region 62 with an axial end face of the section 30 which acts as a displacement surface 89.
  • the inlet nozzle element 22 can form a movement stop for the displacement piston element 12, preferably even before the biasing spring 34 is completely compressed and thus set to block.
  • the volume which is ready for fluid absorption becomes Inlet chamber 40 is increased, while the available for the fluid intake volume of the outlet chamber 54 is reduced.
  • the displacement piston element 12 returns again in the direction of its first piston position. That is, the first piston portion 86 again progressively plunges into the inlet chamber portion 42, while the second piston portion 88 is increasingly pulled out of the discharge chamber portion 58.
  • a reduction in the volume of the inlet chamber 40 available for fluid intake occurs, while at the same time the volume of the outlet chamber 54 available for fluid intake increases.
  • the displacement piston element 12, with its section 30 or a displacement surface 87 thereon initially displaces the fluid still contained in the inlet chamber region 42.
  • the displacement piston element 12 is designed to be substantially cylindrical, in particular in its section 30, and since the section 28 of smaller diameter always dips at least partially into the opening section 20, the volume change in the region of the outlet chamber is defined multiplied by the size of the displacement surface 89 configured in a substantially ring-like manner with the stroke of the displacement piston member 12, while at the same stroke the piston portion 86 with a substantially the entire cross section of the portion 30 of the piston member comprising the displacement surface 87 is effective.
  • the ratio of the volume change of the inlet chamber 40 to the volume change of the outlet chamber 54 is defined by the ratio of the size of the displacement surface 87 to the size of the displacement surface 89, ie the displacement surface effective during the respective movement.
  • each stroke movement of the displacement piston element leads to an exhaust stroke. This means at a given frequency of movement of the displacement piston element, a doubling of the delivery frequency in comparison to the known from the prior art metering pump assembly with a corresponding much more uniform flow characteristics of the fuel delivered to a heater.
  • the metering pump according to the invention has only a single to be moved by appropriate control organ, which simplifies the structure and reduces the number of required components. Furthermore, a very compact construction is provided in particular by the passage of the fluid supply through the displacement piston element 12, and there is no movable component to seal to the outside.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Reciprocating Pumps (AREA)
  • Loading And Unloading Of Fuel Tanks Or Ships (AREA)
  • Air-Conditioning For Vehicles (AREA)

Claims (11)

  1. Pompe de dosage pour un dispositif de chauffage de véhicule, comprenant une chambre d'admission (40), une chambre de sortie (54), un premier dispositif de soupape (66) entre la chambre d'admission (40) et la chambre de sortie (54), qui permet un échange de fluide essentiellement uniquement depuis la chambre d'admission (40) vers la chambre de sortie (54), un élément de piston de refoulement (12) qui, entre une première position de piston, dans laquelle il réduit le volume de la chambre d'admission (40), et dans une deuxième position de piston, dans laquelle il réduit le volume de la chambre de sortie (54), se déplace en mouvement de va-et-vient dans une ouverture (16) formée dans un logement de piston (14), lors du mouvement de l'élément de piston de refoulement (12) depuis la deuxième position de piston vers une première position de piston, une réduction de volume (V1) de la chambre d'admission (40) est supérieure à une augmentation de volume (V2) de la chambre de sortie (54),
    caractérisée
    en ce que l'ouverture (16) est formée de façon graduée avec une section (20) de plus petit diamètre et une section (26) de plus grand diamètre,
    en ce que l'élément de piston de refoulement (12) présente une section (28) de plus petit diamètre dont la dimension est adaptée à la section (20) de plus petit diamètre de l'ouverture (16) et qui est guidée dans la section (20) de plus petit diamètre de l'ouverture (16),
    en ce que l'élément de piston de refoulement (12) présente une section (30) de plus grand diamètre dont la dimension est adaptée à la section (26) de plus grand diamètre de l'ouverture (16) et qui est guidée dans la section (26) de plus grand diamètre de l'ouverture (16),
    en ce que le logement de piston (14), dans la zone
    où est formée la section (20) de plus grand diamètre de l'ouverture (16), est entouré d'une bobine (32) d'un système d'entraînement électromagnétique (34),
    en ce que l'élément de piston de refoulement (12) avec sa section (28) de plus petit diamètre plonge dans la bobine (32) et forme un induit (36) du système d'entraînement électromagnétique (34),
    en ce que, dans l'élément de piston de refoulement (12), est prévue une conduite d'amenée de fluide qui, dans la section (28) de plus petit diamètre de l'élément de piston de refoulement (12), est ouverte vers la section (20) de plus petit diamètre de l'ouverture (16) qui présente, au niveau de la section (30) de plus grand diamètre de l'élément de piston de refoulement (12), une embouchure vers la chambre d'admission (40) et qui peut être obturée par un deuxième dispositif de soupape (76), lequel permet l'échange de fluide sensiblement uniquement à partir de la conduite d'amenée de fluide (12) vers la chambre d'admission (40).
  2. Pompe de dosage selon la revendication 1,
    caractérisée en ce que, dans la première position de piston, l'élément de piston de refoulement (12) plonge, avec une première zone de piston (86), dans la chambre d'admission (40) et, dans la deuxième position de piston, l'élément de piston de refoulement (12 ; 12a) plonge avec une deuxième zone de piston (88) dans la chambre de sortie (54 ; 54a).
  3. Pompe de dosage selon la revendication 1 ou 2,
    caractérisée en ce que l'élément de piston de refoulement (12) présente, dans une première zone de piston (86), une première surface de refoulement efficace lors du mouvement de l'élément de piston de refoulement (12) dans la direction de la première position de piston et, dans une deuxième zone de piston (88), présente une deuxième surface de refoulement efficace (89) lors du mouvement de l'élément de piston de refoulement (12) dans la direction de la deuxième position de piston, et en ce que la première surface de refoulement (87) est plus grande que la deuxième surface de refoulement (89).
  4. Pompe de dosage selon la revendication 6,
    caractérisée en ce que la première surface de refoulement (87) et la deuxième surface de refoulement (89) présentent un rapport de surfaces entre elles de 2:1.
  5. Pompe de dosage selon l'une des revendications 2 à 4,
    caractérisée en ce que l'élément de piston de refoulement (12) présente une section de piston (30) rassemblant la première zone de piston (86) et la deuxième zone de piston, ainsi qu'une section de refoulement (28) qui, lors du mouvement de l'élément de piston de refoulement (12), plonge depuis la première position de piston vers la deuxième position de piston dans la chambre de sortie (54).
  6. Pompe de dosage selon l'une des revendications 1 à 5,
    caractérisée en ce que l'élément de piston de refoulement (12) est déplaçable entre la première position de piston et la deuxième position de piston.
  7. Pompe de dosage selon l'une des revendications 1 à 6,
    caractérisée en ce que la zone (42) de la chambre d'admission (40), dans laquelle plonge la première zone de piston (86) dans la première position de piston, et la zone (62) de la chambre de sortie (54), dans laquelle la deuxième zone de piston (88) plonge dans la deuxième position de piston, sont formées au moins en partie dans le logement de piston (14).
  8. Pompe de dosage selon la revendication 7,
    caractérisée en ce que le logement de piston (14) est entouré au moins partiellement par un logement de chambre (38), et en ce que la chambre d'admission (40) ou/et la chambre de sortie (54) sont au moins formées partiellement entre le logement de piston (14) et le logement de chambre (38).
  9. Pompe de dosage selon l'une des revendications 1 à 8,
    caractérisée en ce que le premier dispositif de soupape (66) ou/et le deuxième dispositif de soupape (76) sont formés en tant que soupape anti-retour.
  10. Pompe de dosage selon la revendication 9,
    caractérisée en ce que le premier dispositif de soupape (66) ou/et le deuxième dispositif de soupape (76) présentent un organe de soupape précontraint par ressort (68, 78).
  11. Pompe de dosage selon l'une des revendications 1 à 10,
    caractérisée en ce que le premier dispositif de soupape (66) comprend un siège de soupape (90) et un organe de soupape (68) pouvant être comprimé contre le siège de soupape, le siège de soupape (90) du premier dispositif de soupape (66) étant prévu sur un logement (14, 38) recevant l'élément de piston de refoulement.
EP04000552A 2003-01-14 2004-01-13 Pompe de dosage pour dispositif de chauffage pour véhicule Expired - Fee Related EP1445485B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10301093 2003-01-14
DE10301093A DE10301093A1 (de) 2003-01-14 2003-01-14 Dosierpumpeinrichtung für ein Fahrzeugheizgerät

Publications (3)

Publication Number Publication Date
EP1445485A2 EP1445485A2 (fr) 2004-08-11
EP1445485A3 EP1445485A3 (fr) 2005-09-07
EP1445485B1 true EP1445485B1 (fr) 2007-06-06

Family

ID=32519943

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04000552A Expired - Fee Related EP1445485B1 (fr) 2003-01-14 2004-01-13 Pompe de dosage pour dispositif de chauffage pour véhicule

Country Status (3)

Country Link
US (1) US7322804B2 (fr)
EP (1) EP1445485B1 (fr)
DE (2) DE10301093A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102005044904B4 (de) * 2005-09-14 2009-12-03 Hirschmann, Karl-Heinz, Prof.Dr. Elektromagnetisch betreibbare Dosierpumpe
JP5034705B2 (ja) * 2007-06-18 2012-09-26 株式会社アドヴィックス ピストンポンプ
US8550794B2 (en) * 2010-08-09 2013-10-08 Foothill Land, Llc Double acting fluid pump
DE102011008086A1 (de) * 2011-01-07 2012-07-12 Inficon Gmbh Doppeltwirkender Kältemittelkompressor
US9528505B2 (en) * 2014-02-10 2016-12-27 Haier Us Appliance Solutions, Inc. Linear compressor
US9562525B2 (en) * 2014-02-10 2017-02-07 Haier Us Appliance Solutions, Inc. Linear compressor
JP6253623B2 (ja) * 2015-09-14 2017-12-27 本田技研工業株式会社 燃料遮断弁
DE102015116783A1 (de) * 2015-10-02 2017-04-06 Eberspächer Climate Control Systems GmbH & Co. KG Dosierpumpe, insbesondere Brennstoffdosierpumpe für ein Fahrzeugheizgerät
EP3910261A1 (fr) 2016-03-30 2021-11-17 Marine Canada Acquisition Inc. Appareil de chauffage de véhicule et commandes associées
JP7051412B2 (ja) * 2017-12-13 2022-04-11 Ｎｉｔｔｏｋｕ株式会社 プランジャポンプ

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US4349130A (en) * 1980-03-03 1982-09-14 Woolfolk Chemical Works, Inc. Liquid metering pump
GB2132284B (en) * 1982-12-17 1986-04-03 Commw Scient Ind Res Org Porting and ducting arrangement
GB8522466D0 (en) * 1985-09-11 1985-10-16 British Syphon Ind Plc Liquid dispence system
GB2180301B (en) 1985-09-12 1989-09-20 Crown Technology Corp Variable proportioner
DE4205290A1 (de) * 1992-02-21 1993-08-26 Thomas Technik Kg Ges Fuer Mag Elektromagnetisch betriebene pumpe
WO1995025223A1 (fr) 1994-03-11 1995-09-21 Wilson Greatbatch Ltd. Pompe electromagnetique de faible puissance
JP3058412B2 (ja) * 1997-12-30 2000-07-04 エルジー電子株式会社 リニア圧縮機の吐出バルブ装置
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US6796777B2 (en) * 2001-11-08 2004-09-28 Wilson Greatbatch Technologies, Inc. Low power electromagnetic pump

Also Published As

Publication number Publication date
US20050047941A1 (en) 2005-03-03
DE502004004001D1 (de) 2007-07-19
EP1445485A2 (fr) 2004-08-11
US7322804B2 (en) 2008-01-29
EP1445485A3 (fr) 2005-09-07
DE10301093A1 (de) 2004-07-22

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