EP2771573A1 - Compresseur de climatisation conçu pour un véhicule automobile - Google Patents

Compresseur de climatisation conçu pour un véhicule automobile

Info

Publication number
EP2771573A1
EP2771573A1 EP12784452.0A EP12784452A EP2771573A1 EP 2771573 A1 EP2771573 A1 EP 2771573A1 EP 12784452 A EP12784452 A EP 12784452A EP 2771573 A1 EP2771573 A1 EP 2771573A1
Authority
EP
European Patent Office
Prior art keywords
pressure
spring
side port
pressure side
biasing force
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
EP12784452.0A
Other languages
German (de)
English (en)
Other versions
EP2771573B1 (fr
Inventor
Thomas Pawelski
Ulrich Fochler
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.)
Volkswagen AG
Original Assignee
Volkswagen AG
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 Volkswagen AG filed Critical Volkswagen AG
Publication of EP2771573A1 publication Critical patent/EP2771573A1/fr
Application granted granted Critical
Publication of EP2771573B1 publication Critical patent/EP2771573B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1809—Controlled pressure
    • F04B2027/1813—Crankcase pressure
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1854—External parameters

Definitions

  • the invention relates to an air conditioning compressor for a motor vehicle, whose
  • Pressure chamber with a high-pressure side port and its suction chamber with a
  • Low-pressure side port is connected, wherein between the pressure chamber and the
  • High pressure side port is arranged a check valve, the valve body is biased against the intended refrigerant flow direction and in the closing direction of the check valve by a biasing force having a first spring biasing force component which is generated by a on the valve body on the one hand and on a spring abutment on the other hand supported spring.
  • Suction chamber is sucked and pumped into the pressure chamber.
  • the suction chamber is connected to the low-pressure side port of the air conditioning compressor, which in turn in the assembled state in the motor vehicle with the low-pressure region of the air conditioning system, i. in particular connected to the outlet of the evaporator.
  • the pressure chamber is connected to the high-pressure side port of the air compressor, which in turn is connected in the assembled state in the motor vehicle with the high-pressure region of the air conditioning system, in particular via a heat exchanger to the inlet of the evaporator.
  • the term "port” should generally be understood to mean a mechanical and pneumatic / hydraulic interface between the air-conditioning compressor and its periphery.
  • a pressure control loop is established, with which the angular position of the swash plate and therefore on the piston stroke, the performance of the air compressor is adjustable.
  • An essential part of this control loop is typically a controlled by an air conditioning control valve.
  • CONFIRMATION COPY For example, it is possible that the pressure drop becomes too small to cause a sufficient initial angular position of the swash plate. Consequently, start-up difficulties of the climate system arise. It is therefore customary to install in the region between the pressure chamber and the high-pressure side port of the air conditioning compressor, a check valve, which is biased in the direction of the pressure chamber. For this purpose, a valve body is pressed in a conventional manner by means of a spring against a valve seat, wherein the orientation of the
  • Check valve is selected so that it counteracts the intended refrigerant flow from the pressure chamber to the high-pressure side port.
  • the check valve thus provides resistance to the pressure built up in the pressure chamber, so that gradually, even with low swash plate tilt an overpressure in the
  • the evaporator outlet thus the low-pressure side region of the air conditioning system, can heat up to such an extent that it leads to an overpressure in the air
  • Check valve is thus reduced in this particular case, and that by the difference of before and after the check valve pending pressures.
  • the check valve thus opens too early when starting the air conditioning compressor, so that the base pressure can not be sufficiently established.
  • an air-conditioning compressor with a check valve which additionally provides a pressure-limiting and pressure-difference protection device. These protect the compressor and the downstream air conditioning system against a harmful overpressure in the high-pressure region of the air conditioning system or against a harmful pressure difference between the pressure chamber and the high-pressure side region of the air conditioning system.
  • the above-mentioned starting problem of the air compressor ih thermally unfavorable cases is not discussed in the cited document.
  • an air compressor which in its preferred embodiment has a conventional, spring-driven check valve, but as alternatives pressure or volume flow-dependent controlled valves, in particular solenoid valves disclosed that at very low mass flows, the one-off state of
  • Compressor should comply, close sensor controlled.
  • An essential element of the invention is that the biasing force of the check valve is composed of at least two components, namely a first spring-based force component and additionally by the Vorditionserhöhungs complexion
  • imprinted force component is greater than zero in particular when, for example due to unfavorable thermal conditions, there is a pressure reversal between the high and low pressure side ports compared to the normal operation of the air conditioning compressor.
  • the additional biasing force component may be different in nature and independent of the spring-biased biasing force component.
  • the additional biasing force component is a second spring biasing force component resulting from a displacement of the spring abutment; in other words, it may be provided that the preload increasing device transmits the spring biasing force component
  • the biasing means is configured such that the additional biasing component is so large that the total biasing force of the check valve is equal to the spring biasing force component in the case of pressure equality of the high pressure and low pressure port pressures. This means that the
  • Pretension of the check valve is reduced due to the pressure reversal at the ports, with the reference situation is the case of complete pressure equalization in the overall system.
  • the spring force can thus be dimensioned in a conventional manner. Normally, i. When the pressure at the high-pressure side port is higher than the pressure at the low-pressure side port, the spring biasing component acts conventionally. This also applies in the case of complete pressure equalization. In the particularly unfavorable case of pressure reversal, which is the focus of the present invention, the weakened biasing force is just compensated, so that the piston of the compressor against the same resistance as in
  • bias voltage increase device may be different.
  • the spring is supported with its end facing away from the valve body against an electromagnetic or electromotive actuator, which is operatively connected to a dependent of the pressure difference between the high and the low pressure side port control. The position of the
  • Supporting point of the spring i. the spring abutment, and thus the amount of biasing force is thus electrically controlled, preferably regulated.
  • pressure sensitive sensors that detect the pressure and / or temperature conditions in the system and report to the controller, which in turn the adjusting device
  • the spring is supported with its valve body applied to the end against a double piston, the two successively arranged, pressure-separated cylinder chambers such that act in the individual cylinder chambers pending pressures acting antagonistically on the double piston, wherein the supported spring facing cylinder chamber with the low-pressure side and the supported spring facing away from the cylinder chamber with the high-pressure side port
  • thermostatic head containing a temperature-sensitive expansion and contraction-capable thermal material.
  • the operation of thermostatic heads is well known. They include a piston which terminates a cartridge filled with the thermal material, which may be, for example, a gas, a liquid, a gel or a solid. Expansion or contraction of the thermal material
  • Thermomaterials leads to a corresponding movement of the piston and thus to a displacement of the spring abutment.
  • the biasing spring is supported on the piston, so that in addition to the spring force, a temperature-dependent additional biasing force is generated. It is preferably provided that the piston, the spring during expansion of
  • FIG. 1 shows a schematic overview of an air conditioning compressor
  • FIG. 2 is a schematic representation of a conventional check valve
  • FIG. 3 shows a schematic representation of a first embodiment of the invention
  • FIG. 4 shows a schematic representation of a second embodiment of the invention
  • FIG. 5 a schematic representation of a third embodiment of the invention.
  • the same reference numerals in the figures indicate identical or analogous components.
  • FIG. 1 shows a schematic overview of an air conditioning compressor 10 in the installed state.
  • the elements attributed to the compressor 10 are drawn within the system boundary 12 shown in dashed lines.
  • Central part of the compressor 10 is the crankcase 14, in which the piston, not shown, run in a known manner, wherein its stroke is controlled by the inclination of a likewise driven, driven swash plate.
  • the crankcase communicates with a suction chamber 16 and a pressure chamber 18, wherein by means of a control loop comprising a control valve 20 and a throttle valve 22, the pressure differences between the crankcase 14, suction chamber 16 and pressure chamber 18 are controlled during operation so that the required
  • Tilting position of the swash plate adjusts.
  • the control valve 20 is connected to a control unit, not shown.
  • the interfaces of the compressor 10 to the rest of the air conditioning system are provided by the low-pressure side port 24 and the high-pressure side port 26.
  • the low-pressure side port 24 is connected to the output of an evaporator, not shown.
  • the high-pressure side port 26 is connected via a heat exchanger, not shown, to the inlet of the evaporator.
  • a check valve 28 is arranged, which comprises a valve seat 30 and a valve body 32, by a biasing spring 34 against the intended flow direction of the
  • Pressure chamber is biased to the high-pressure side port against the valve seat.
  • FIG. 2 shows a schematic representation of the usual construction of the check valve 28.
  • the valve body 32 With complete pressure equalization in the system, ie in the case that in particular the pressures at the high and low pressure side port and in the suction and the pressure chamber are the same, acts on the valve body 32 exclusively the force of the spring 34. Behind the valve body 32, the high-pressure side system pressure prevails; in front of the valve body 32 prevails (via the suction and the pressure chamber) of the low-pressure side system pressure, which equalize in the case of pressure equality.
  • unfavorable thermal conditions which may occur in the case of a local heating of the interior and thus of the evaporator, in particular the temperature at the evaporator outlet and thus at the low-pressure side port and in the suction and pressure chamber increases.
  • the high-pressure side system area is not affected. He is not in the interior, but under the ventilated hood of the motor vehicle between the check valve 28 and the inlet of the evaporator, so that its pressure does not increase, at least not to the same extent. As a result, it is lower than the remaining pressures in the system, so that the total force acting on the valve body 32 is smaller As the force of the spring 34. As explained above, such a constellation leads to considerable starting difficulties of the air conditioning compressor.
  • Figure 3 shows a first embodiment of the present invention.
  • the biasing spring 34 is supported against the plunger 36 of an electromagnet 38.
  • the electromagnet 38 can be compensatorily excited by appropriate energization, i. the plunger 36 is moved toward the valve body 32, so that the spring 34 undergoes additional compression and on the valve body 32 acts an increased biasing force.
  • Figure 4 shows a second embodiment of the present invention.
  • the spring 34 is supported against a double piston 40.
  • the double piston 40 passes through a low pressure chamber 42 and a high pressure chamber 44.
  • These terms do not necessarily refer to the prevailing in the chambers 42, 44 pressures, but rather on their pneumatic connection with the corresponding ports, which in Figure 4 with arrows is indicated.
  • the low-pressure pressure chamber 42 is pneumatically connected to the low-pressure side port 24, and the high-pressure pressure chamber 44 is connected to the high-pressure side port 26.
  • the position of the double piston 40 thus depends on the pressure difference between the high and the low pressure side port 24, 26 from. Accordingly, the supporting location of the spring 34, i. the spring abutment, also from this
  • FIG. 5 shows a third embodiment of the present invention.
  • the spring 34 is supported against the piston 46 of a thermostatic head 48.
  • the piston 46 terminates a thermal material cartridge 50, in particular a gas-filled chamber from pressure-tight. in the
  • Biasing force of the valve body 32 is increased. This also applies in the above-described thermally unfavorable state of a local heating of the

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)

Abstract

L'invention concerne un compresseur de climatisation conçu pour un véhicule automobile dont la chambre de compression (18) est reliée à un orifice côté haute pression (26) et dont la chambre d'aspiration (16) est reliée à un orifice côté basse pression (24). Un clapet anti-retour (28) est disposé entre la chambre de compression (18) et l'orifice haute pression (26), le corps (32) dudit clapet étant précontraint dans une direction opposée à la direction d'écoulement du fluide frigorigène selon l'invention et dans la direction de fermeture du clapet anti-retour (28) par une force de précontrainte qui comprend une première composante de force de précontrainte de ressort générée par un ressort (34) maintenu par le corps de clapet (32) d'une part et une butée de ressort d'autre part. Cette invention est caractérisée en ce que le clapet anti-retour (28) est équipé d'un dispositif d'augmentation de précontrainte qui applique une composante de force de précontrainte supplémentaire au corps (32) du clapet, lorsqu'une pression présente au niveau de l'orifice côté haute pression (26) est inférieure à une pression présente au niveau de l'orifice côté basse pression (24).
EP12784452.0A 2011-10-29 2012-10-25 Compresseur de climatisation conçu pour un véhicule automobile Active EP2771573B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110117354 DE102011117354A1 (de) 2011-10-29 2011-10-29 Klimakompressor für ein Kraftfahrzeug
PCT/EP2012/004456 WO2013060456A1 (fr) 2011-10-29 2012-10-25 Compresseur de climatisation conçu pour un véhicule automobile

Publications (2)

Publication Number Publication Date
EP2771573A1 true EP2771573A1 (fr) 2014-09-03
EP2771573B1 EP2771573B1 (fr) 2015-10-07

Family

ID=47177882

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12784452.0A Active EP2771573B1 (fr) 2011-10-29 2012-10-25 Compresseur de climatisation conçu pour un véhicule automobile

Country Status (4)

Country Link
EP (1) EP2771573B1 (fr)
CN (1) CN104105876B (fr)
DE (1) DE102011117354A1 (fr)
WO (1) WO2013060456A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014218525B4 (de) 2014-09-16 2016-10-13 Te Connectivity Germany Gmbh Elektrisches Regelventil für einen Klimakompressor mit einem Sensor zur Bestimmung der Stellung des Regelkolbens
DE102015213230B4 (de) 2015-05-29 2022-01-05 Te Connectivity Germany Gmbh Elektrisches Regelventil für einen Kältemittelverdichter mit darin enthaltenem Saugdruck- und Saugtemperatursensor
CN108473357B (zh) 2016-01-15 2022-02-08 英国热陶瓷有限公司 用于形成熔体成型无机纤维的器械和方法
DE102016203688A1 (de) 2016-03-07 2017-09-07 Te Connectivity Germany Gmbh Baugruppe für einen Kompressor, insbesondere in einem Automobil

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JP3254853B2 (ja) * 1993-11-05 2002-02-12 株式会社豊田自動織機 クラッチレス片側ピストン式可変容量圧縮機
JP2000009034A (ja) * 1998-06-25 2000-01-11 Toyota Autom Loom Works Ltd 空調システム
JP2000145629A (ja) * 1998-11-11 2000-05-26 Tgk Co Ltd 容量可変圧縮機
DE20122730U1 (de) * 2001-01-29 2007-08-02 Valeo Thermal Systems Japan Corp. Verdrängungsverdichter ohne Taumelscheibenkupplung
US7014428B2 (en) * 2002-12-23 2006-03-21 Visteon Global Technologies, Inc. Controls for variable displacement compressor
DE102004057159A1 (de) * 2004-11-26 2006-06-01 Volkswagen Ag Klimaanlage für ein Kraftfahrzeug
JP4330576B2 (ja) * 2005-10-28 2009-09-16 サンデン株式会社 圧縮機
EP1948927B1 (fr) 2005-11-09 2009-08-05 ixetic MAC GmbH Compresseur de climatisation a systeme de limitation de la pression differentielle
DE102006048380A1 (de) 2006-10-12 2008-04-17 Valeo Compressor Europe Gmbh Verdichter
US8277200B2 (en) * 2008-06-17 2012-10-02 Delphi Technologies, Inc. Variable displacement compressor with a discharge pressure compensated suction shutoff valve
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Also Published As

Publication number Publication date
DE102011117354A1 (de) 2013-05-02
WO2013060456A8 (fr) 2014-05-01
WO2013060456A1 (fr) 2013-05-02
EP2771573B1 (fr) 2015-10-07
CN104105876B (zh) 2016-10-05
CN104105876A (zh) 2014-10-15

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