EP1559970A2 - Procédé et dispositif pour la régulation de la pression dans un circuit de frigorigène - Google Patents

Procédé et dispositif pour la régulation de la pression dans un circuit de frigorigène Download PDF

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Publication number
EP1559970A2
EP1559970A2 EP20050001630 EP05001630A EP1559970A2 EP 1559970 A2 EP1559970 A2 EP 1559970A2 EP 20050001630 EP20050001630 EP 20050001630 EP 05001630 A EP05001630 A EP 05001630A EP 1559970 A2 EP1559970 A2 EP 1559970A2
Authority
EP
European Patent Office
Prior art keywords
high pressure
pressure
control
manipulated variable
value
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Withdrawn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
EP20050001630
Other languages
German (de)
English (en)
Inventor
Wilhelm Dipl.-Ing. Baruschke
Armin Britsch-Laudwein
Karl Dipl.-Ing. Lochmahr (Fh)
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.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr 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 Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP1559970A2 publication Critical patent/EP1559970A2/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/005—Arrangement or mounting of control or safety devices of safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/07—Exceeding a certain pressure value in a refrigeration component or cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/023—Compressor control controlling swash plate angles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/17—Control issues by controlling the pressure of the condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • the invention relates to a method and a device for pressure control in a refrigerant circuit of an air conditioner for a vehicle.
  • an air conditioning system also called air conditioning
  • a heating and Refrigerant circuit z. B.
  • CO2 refrigerant circuit
  • CO2 so-called R744 refrigerant circuit
  • the object of the invention is therefore a method and a device to specify for pressure control in a refrigerant circuit, which without additional components provide comprehensive protection against impermissibly high Offers pressure peaks.
  • a basic control loop also superordinate Called a setpoint for an evaporator temperature
  • the one evaporator temperature controller for forming a manipulated variable is supplied.
  • a high-pressure setpoint is determined for a high-pressure regulator, whereby the Prevention of pressure peaks by means of the high-pressure regulator on the basis of High pressure setpoint a primary and in addition by means of a high pressure limitation a secondary control variable to a regulation of the high pressure be determined.
  • Pulse width modulated control signal which is a control valve for Controlling the stroke volume of a compressor, in particular a refrigerant compressor, is supplied.
  • the high pressure set point is increased by one pressure value. Subsequently the difference between the high pressure limitation as an input variable of the pressure value modified high pressure setpoint and the high pressure actual value fed.
  • High pressure limitation is a by a predetermined pressure value, eg. B. 10 bar to 15 bar, raised high pressure setpoint supplied.
  • the common manipulated variable which is the result of this linkage is (also called resulting manipulated variable), is determined by a transfer characteristic in the pulse width modulated control signal for controlling the Compressor stroke volume implemented.
  • the high-pressure limitation as a comparator this is fed to the high pressure actual value.
  • the comparator can both in terms of software and in time-critical cases in terms of hardware, z. B. in analog circuit technology, be formed.
  • the secondary manipulated variable is determined.
  • the primary control value with a transfer characteristic in implemented a pulse width modulated primary manipulated variable.
  • the limiting function of the comparator acts statically and not continuously, but as a pure ON / OFF function. A The resulting system unrest can occur in some air conditioning systems be acceptable.
  • this comprises a basic control loop to determine a set point for the evaporator temperature and a downstream evaporator temperature controller, via whose Control value is a high pressure setpoint is determined, the Evaporator temperature controller a high-pressure regulator to determine the primary command value for the high pressure and a high pressure limit to Determination of the secondary control value for the high pressure downstream are.
  • the high-pressure limitation is preferably parallel to the high-pressure regulator connected.
  • Fig. 1 is a device 1 for pressure control in a refrigerant circuit 2 of an air conditioning system 4 (also called air conditioning) for a Vehicle shown.
  • the air conditioning system 4 can also be used as a combined Device for cooling or heating in a closed Space, z. B. in the vehicle interior, to be formed leading air.
  • the air conditioning system 4 comprises a gas cooler 6, an evaporator 8 and an interposed inner heat exchanger 10, in which a cycle process underlying air conditioning or cooling to run the air conditioning system 4 and vice versa can, so that the air conditioning system 4 also acts as a heat pump.
  • the heat pump operation is not the subject of the application. following the air conditioning system 4 for the refrigerant circuit 2 is closer described.
  • the refrigerant circuit 2 represents a closed system in which a refrigerant KM, z.
  • a refrigerant KM As carbon dioxide, R134a, R177, from the gas cooler 6 via the inner heat exchanger 10 is led to the evaporator 8 in the circuit.
  • the refrigerant KM takes heat from one into the vehicle flowing air and releases it to the ambient air again.
  • the cooling of the refrigerant takes place KM arranged by pressure loss at one in the refrigerant circuit 2 Expansion organ 12; the cooling of the inside of the vehicle flowing air takes place by heat absorption of the refrigerant KM in the evaporator 8th.
  • the refrigerant circuit 2 includes, for example, the engine the vehicle driven compressor 14 or compressor with a variable Stroke volume H for compression of a gaseous refrigerant KM, z. B. carbon dioxide.
  • the compressor 14 sucks the gaseous refrigerant KM from the evaporator 8 via the expansion device 12 coming on.
  • the sucked gaseous refrigerant KM has a low temperature and a low pressure.
  • the refrigerant KM is under the compressor 14 under Heating compresses and changes its state of aggregation from gaseous after liquid with simultaneous heating.
  • the gaseous and hot Refrigerant KM is the heat exchanger 6, z. B. a gas cooler or Capacitor, guided. Due to the air flowing into the gas cooler 6 air the refrigerant KM is cooled.
  • the cooled in the gas cooler 6 refrigerant KM becomes the subsequent suction pressure side supply of the compressor 14 via the inner heat exchanger 10 and passed over the expansion member 12, which as throttle is working. It comes here to a relaxation of the refrigerant KM, so that the coolant KM cools down considerably.
  • the expansion organ 12 the cooled refrigerant KM is injected into the evaporator 8, where the Refrigerant KM of the incoming air, z. B. fresh air, the required heat of evaporation withdraws. This cools the air.
  • the cooled air is via a fan not shown in detail and air ducts in led the vehicle interior.
  • the refrigerant KM is after the evaporator 8 on the inner heat exchanger 10 suction pressure side of the compressor 14 fed again.
  • the evaporator temperature control includes a modified subordinate one Refrigerant high pressure control, in addition to the well-known refrigerant high pressure control According to the prior art, a highly dynamic Protection mechanism to avoid pressure peaks in the form of a Has additional control loop.
  • the actual value IW (VT) for the evaporator temperature VT at the evaporator 8 determined.
  • the difference from the setpoint SW (VT) and the actual value IW (VT) for the evaporator temperature VT is a evaporator temperature controller 18, for example a PI controller supplied.
  • U of Evaporator temperature controller 18 is by means of a base characteristic 20 a Setpoint SW (HD) for the high pressure HP of the refrigerant KM in Refrigerant circuit 2 derived after the gas cooler 6.
  • R744 may require an additional correction characteristic 22, with the setpoint value SW (HD) obtained from the basic characteristic curve for the High pressure HD is modified to be a corrected or modified one High pressure setpoint SW (HDm) to obtain.
  • inputs E1 to En for the correction of the set value SW (HD) for the high pressure HD on the basis of Correction characteristic curve 22 serve, for example, the air inlet temperature, the Air inlet moisture, the amount of air and / or the speed of the compressor 14th
  • the high pressure HD in the refrigerant circuit 2 after the gas cooler 6 determined.
  • the difference from the modified high pressure setpoint SW (HDm) and the high pressure actual value IW (HD) becomes one High pressure regulator 24 supplied as a pressure difference value ⁇ p.
  • the Pressure difference value .DELTA.p is a primary by means of the high-pressure regulator 24 Control value Up for the high pressure HD for controlling the stroke volume H of the Compressor 14 determined by means of a control valve 26.
  • the high-pressure regulator 24 is a high pressure limitation as an additional control loop 28 assigned.
  • the high-pressure limitation 28 is for adjustment the high pressure HD after the gas cooler 6 in addition to the primary control variable Up a secondary control variable Us for the control valve 26 of the compressor 14 determined.
  • the high-pressure limitation 28 (also additional high-pressure refrigerant control called) acts as a protective mechanism for Avoiding unwanted high pressure peaks. This is the high pressure limit 28 parallel to the regular high pressure control - to the high pressure regulator 24 - switched.
  • the high-pressure limitation 28 becomes a pressure difference value ⁇ p from modified High pressure setpoint SW (HDm) and high pressure actual value IW (HD) fed.
  • the modified high pressure set point SW (HDm) by a pressure value p, for example 10 bar to 15 bar, raised so that possibly no premature high-pressure limiting measure is triggered.
  • the high-pressure limitation 28 is, for example, as a PD or PID controller R formed.
  • a PID controller at any high-pressure peaks high dynamic the stroke volume H of the Compressor 14 can be reduced.
  • the result of the link is a Resulting manipulated variable Ug, which avoids highly dynamic pressure peaks.
  • the common manipulated variable Ug is by means of a pulse width modulator 32nd based on a transfer characteristic in a pulse width modulated control signal S implemented. Subsequently, the pulse width modulated actuating signal S is the Control valve 26 of the compressor 14 for controlling the stroke volume H. fed.
  • Fig. 2 is another alternative, in particular simple embodiment for the device 1 for pressure control with a static secondary Pressure peak limitation by an extended evaporator temperature control shown.
  • a high-pressure limiting 28 for determining the secondary control variable Us a comparator K provided.
  • This is the high pressure limit 28, the high pressure actual value IW (HD) supplied.
  • the comparator K points a hysteresis two-point behavior with a fixed predetermined Maximum value for the high pressure setpoint SW (HD) to.
  • the steady Function of dynamic as PD or PID controller R working High pressure limitation 28 of FIG. 1 are in the as comparator K.
  • only working high-pressure static limitation 28 in Fig. 2 two switching states for the secondary manipulated variable Us set.
  • the effect Limiting function in this embodiment shown in FIG. 2 not continuous, but as a pure ON / OFF circuit that only is activated for unauthorized high pressure values. This results in an increased System unrest, which can be accepted under certain circumstances.
  • the comparator K can be used both as a software module and in time-critical Cases hardware, z. B. in analog circuit technology be.
  • FIG. 3 shows a further alternative embodiment for the device 1 for pressure control with a dynamic pressure peak limitation by an expanded evaporator temperature control shown.
  • the high pressure limitation 28 takes place to determine the secondary manipulated variable Us continuously over the exemplary characteristic of FIG. 4.
  • the resulting manipulated variable Ug is determined by means of a Pulse width modulator 32 based on a transfer characteristic in a pulse width modulated control signal S implemented. Subsequently, the Control signal S the control valve 26 of the compressor 14 for controlling the Stroke volume H supplied.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
EP20050001630 2004-02-02 2005-01-27 Procédé et dispositif pour la régulation de la pression dans un circuit de frigorigène Withdrawn EP1559970A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004005175 2004-02-02
DE200410005175 DE102004005175A1 (de) 2004-02-02 2004-02-02 Verfahren und Vorrichtung zur Druckregelung in einem Kältemittelkreislauf

Publications (1)

Publication Number Publication Date
EP1559970A2 true EP1559970A2 (fr) 2005-08-03

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Application Number Title Priority Date Filing Date
EP20050001630 Withdrawn EP1559970A2 (fr) 2004-02-02 2005-01-27 Procédé et dispositif pour la régulation de la pression dans un circuit de frigorigène

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EP (1) EP1559970A2 (fr)
DE (1) DE102004005175A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011056371A3 (fr) * 2009-11-03 2011-08-18 Carrier Corporation Réduction des pointes de pression pour systèmes de réfrigérant comprenant un échangeur de chaleur à microcanaux
EP2634508A4 (fr) * 2010-10-29 2016-11-16 Mitsubishi Electric Corp Dispositif à cycle de réfrigération et procédé de commande d'un cycle de réfrigération

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006008238A1 (de) 2006-02-22 2007-08-23 Volkswagen Ag Verfahren zum Betrieb einer Klimaanlage eines Kraftfahrzeuges
JP4715650B2 (ja) * 2006-06-26 2011-07-06 株式会社デンソー 冷凍サイクル装置
DE102014200227B4 (de) * 2014-01-09 2022-10-20 Bayerische Motoren Werke Aktiengesellschaft Verfahren zur Steuerung einer Heiz-Klimaanlage in einem Kraftfahrzeug
DE102016001096B4 (de) 2016-02-01 2023-07-27 Audi Ag Verfahren zum Betreiben einer Fahrzeug-Kälteanlage, Fahrzeug-Kälteanlage zur Durchführung des Verfahrens und Fahrzeug mit einer solchen Fahrzeug-Kälteanlage

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6588222B1 (en) * 2002-05-08 2003-07-08 Delphi Technologies, Inc. Low-cost energy-efficient vehicle air conditioning system

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011056371A3 (fr) * 2009-11-03 2011-08-18 Carrier Corporation Réduction des pointes de pression pour systèmes de réfrigérant comprenant un échangeur de chaleur à microcanaux
US20120167602A1 (en) * 2009-11-03 2012-07-05 Taras Michael F Pressure spike reduction for refrigerant systems incorporating a microchannel heat exchanger
US10107535B2 (en) * 2009-11-03 2018-10-23 Carrier Corporation Pressure spike reduction for refrigerant systems incorporating a microchannel heat exchanger
EP2634508A4 (fr) * 2010-10-29 2016-11-16 Mitsubishi Electric Corp Dispositif à cycle de réfrigération et procédé de commande d'un cycle de réfrigération

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Publication number Publication date
DE102004005175A1 (de) 2005-08-18

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