EP2136163A1 - Collecteur de moyen de refroidissement doté d'un séparateur de liquide - Google Patents

Collecteur de moyen de refroidissement doté d'un séparateur de liquide Download PDF

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Publication number
EP2136163A1
EP2136163A1 EP09007514A EP09007514A EP2136163A1 EP 2136163 A1 EP2136163 A1 EP 2136163A1 EP 09007514 A EP09007514 A EP 09007514A EP 09007514 A EP09007514 A EP 09007514A EP 2136163 A1 EP2136163 A1 EP 2136163A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
collector according
guide surfaces
range
annular gap
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
EP09007514A
Other languages
German (de)
English (en)
Other versions
EP2136163B1 (fr
Inventor
Ulrich Vedder
Karl-Heinz Staffa
Alexander Satrapa
Christoph Walter
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 EP2136163A1 publication Critical patent/EP2136163A1/fr
Application granted granted Critical
Publication of EP2136163B1 publication Critical patent/EP2136163B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • 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
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/02—Centrifugal separation of gas, liquid or oil
    • 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
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/03—Suction accumulators with deflectors
    • 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
    • F25B2500/01—Geometry problems, e.g. for reducing size

Definitions

  • the invention relates to a refrigerant collector with liquid separator according to the preamble of claim 1.
  • Refrigerant collectors also called refrigerant accumulators, for refrigerant circuits are known:
  • the refrigerant collector hereinafter also referred to collectors, is arranged behind an evaporator of the refrigerant circuit and has the task of separating the gaseous and the liquid phase of the incoming refrigerant from each other and the liquid refrigerant to save.
  • the collector thus also serves as a volume buffer.
  • the refrigerant extracted from the collector which is supplied to a downstream compressor of the refrigerant circuit, is intended to have the highest possible vapor capacity, ie. H. have a high proportion of gaseous phase.
  • the collector has the task of compressor introduced into the refrigerant circuit from the compressor or refrigerant oil, which is inevitably separated together with the refrigerant, due to the compressor.
  • a refrigerant collector with a liquid separator which is formed as a bell-shaped baffle plate and is arranged above the inlet of a suction tube.
  • the baffle thus shields the inlet of the suction pipe from the refrigerant flowing into the collector and prevents a "short-circuit flow" to the outlet of the collector.
  • a refrigerant collector has been known with a liquid separator, which has on its upper side a spiral-shaped channel through which the incoming refrigerant flow is given a tangential flow direction. After emerging from the spiral channel, the refrigerant flow hits the container inner wall and flows through an annular gap in the lower region of the container, where the liquid phase of the refrigerant collects.
  • the liquid separator adjacent to a chaff surface, has a jacket surface on which helically extending guide surfaces are arranged.
  • the guide surfaces are at least two-speed, preferably free-moving - arranged on the lateral surface - in the manner of a movement thread.
  • the refrigerant impinges on the helical vanes, thereby imparting a swirling flow to the refrigerant, with the result that the liquid particles in the refrigerant are forced outwards due to centrifugal forces, ie, to the inner wall of the container.
  • an annular gap is left between the lateral surface with guide surfaces and the inner wall of the container, d. H. the outer edges of the helically extending baffles do not abut the inner wall of the container, rather the overall passage cross-sectional area is widened, thereby reducing the flow velocity, thereby calming the flow, i. H. there is less turbulence.
  • a bypass flow is formed, which is oriented predominantly vertically or in the axial direction of the container.
  • the bypass flow thus forms a "liquid curtain" between the baffles and the container inner wall, which has the advantage that the liquid particles conveyed outwards due to the swirl flow are immediately entrained by the downward bypass flow. This decisively improves the separation of the liquid phase of the refrigerant.
  • the annular gap has a gap width of 0.5 to 3 mm. It is also advantageous if the annular gap has a cross-sectional or passage area in the range of 100 to 400 mm 2 , preferably in the range of 200 to 300 mm 2 .
  • the mode of operation of the liquid separator according to the invention if a defined ratio between the bypass cross-section, i. H. the annular gap cross-sectional area and the total channel cross section, which is composed of the sum of the individual channel cross sections, is maintained.
  • This ratio is in the range of 2 to 4 and is preferably 3, d. H. the annular gap area in the preferred case is three times the total channel cross-sectional area of the separator.
  • a suction tube is arranged in the container, which is preferably U-shaped and the output side is guided by the baffle of the liquid separator, while the input of the suction tube is shielded by the baffle surface relative to the container inlet. This prevents a short-circuit flow between the refrigerant inlet and outlet.
  • the refrigerant collector with inventive liquid separator with an internal heat exchanger of the refrigerant circuit is integrated into a structural unit, a so-called combination unit. This results in a compact design of two components of the refrigerant circuit, associated with a thermal coupling between the low pressure side and the high pressure side of the refrigerant circuit.
  • Fig. 1 shows a refrigerant collector 1, also called refrigerant accumulator or short collector, for a refrigerant circuit, not shown, preferably operated with CO 2 or R744 Käfteschniklauf for a motor vehicle air conditioning.
  • the collector 1 has a circular cylindrical container 2, which is closed by a lid 3 refrigerant tight and flameproof.
  • the cover 3 is formed as a refrigerant connection flange and has an input port 4, which is arranged downstream of an evaporator of the refrigerant circuit, not shown, and an output port 5, which is arranged upstream in the direction of a compressor, not shown.
  • a U-shaped suction tube 6 is arranged, which has an input-side end 6a, an output-side end 6b and an arcuate portion 6c.
  • a liquid separator 7 is arranged, which is approximately pot-shaped and has helically shaped guide surfaces 8 on its periphery. Between the liquid separator 7, also referred to below as a short spin separator 7, an annular gap 9 is left, which will be discussed in more detail below.
  • the input-side end 6a is arranged inside the cup-shaped swirl separator 7 and is enclosed by a gas filter 10.
  • the input-side end 6a of the suction pipe 6 is thus shielded by the swirl separator 7 with respect to the refrigerant flowing in through the inlet opening 4.
  • the output-side end 6b is pressure and refrigerant tightly connected to the lid 3 in the region of the outlet opening 5, preferably by rolling into the wall of the bore 5.
  • an oil filter 11 is arranged, via which separated from the refrigerant Suction of compressor lubricant and retention of dirt particles.
  • Fig. 2 shows the cut-open collector 1 in a perspective view with an outside view of the swirl body 7, which has a flat swirl surface 7a and a cylindrical surface 7b, from which protrude three helically shaped guide surfaces 8a, 8b, 8c.
  • the guide surfaces 3a form quasi a three-speed movement thread, wherein the arrangement of the guide surfaces can also be formed two or four-way.
  • Fig. 3 shows an enlarged partial section of the swirl separator 7 and its arrangement in the container 2, which has a cylindrical inner wall 2a and a cylinder axis a.
  • the outer edges of the guide surfaces 8a, 8b, 8c have no contact with the inner wall 2a, but between them an annular gap 9 is left, which in Fig.
  • baffles 8 may have a circumferential or coverage angle in the range of 180 ° to 400 °, preferably 270 ° to 360 °.
  • the choice of this ratio V is decisive for the formation of the flow at the swirl separator 7 and thus for the separation of gaseous and liquid phase of the refrigerant, ie ultimately for the steam quality of the exiting refrigerant.
  • the function of the liquid separator 7 according to the invention or of the so-called swirl separator 7 is described below:
  • the refrigerant which is in the vaporous and liquid phase, enters the collector 1 through the inlet 4 and then strikes the impact surface 7a of the swirl separator 7, where liquid portions adhere to the baffle surface 7a and flow outward in a radially directed flow until they strike the baffles 8a, 8b, 8c.
  • the helically arranged guide surfaces 8a, 8b, 8c impose a swirling flow on the refrigerant flow, which exerts a centrifugal force effect on the liquid portions and urges them outward into the annular gap 9.
  • a bypass flow of the refrigerant which is oriented essentially in the direction of the cylinder axis a, is formed, which receives the liquid portions thrown outward from the guide surfaces 8a, 8b, 8c and transports them to the lower region of the container.
  • the characteristic of the swirl separator 7 is that on the one hand a swirl flow in the channel cross-sections between the guide surfaces 8a, 8b, 8c and on the other hand form a bypass flow in the annular gap 9.
  • the centrifugal force is used for the separation of liquid components of the refrigerant and, on the other hand, the bypass flow achieves a faster effective removal with a low pressure drop.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Cyclones (AREA)
EP20090007514 2008-06-19 2009-06-08 Collecteur de moyen de refroidissement doté d'un séparateur de liquide Active EP2136163B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008028852A DE102008028852A1 (de) 2008-06-19 2008-06-19 Kältemittelsammler mit Flüssigkeitsabscheider

Publications (2)

Publication Number Publication Date
EP2136163A1 true EP2136163A1 (fr) 2009-12-23
EP2136163B1 EP2136163B1 (fr) 2012-08-15

Family

ID=41055238

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20090007514 Active EP2136163B1 (fr) 2008-06-19 2009-06-08 Collecteur de moyen de refroidissement doté d'un séparateur de liquide

Country Status (2)

Country Link
EP (1) EP2136163B1 (fr)
DE (1) DE102008028852A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012132608A (ja) * 2010-12-21 2012-07-12 Calsonic Kansei Corp アキュムレータ
JP2012233664A (ja) * 2011-05-09 2012-11-29 Calsonic Kansei Corp アキュムレータ
CN108759203A (zh) * 2018-08-03 2018-11-06 蚌埠市昊源压缩机制造有限公司 一种用于压缩机的气液分离器
WO2019107011A1 (fr) * 2017-12-01 2019-06-06 株式会社不二工機 Accumulateur
CN111442581A (zh) * 2020-05-14 2020-07-24 和龙双昊高新技术有限公司 一种带余热回收功能的汽车空调用气液分离器

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015207808A1 (de) 2014-04-29 2015-10-29 Mahle International Gmbh Volumenausgleichsvorrichtung
DE102014220401A1 (de) 2014-10-08 2016-04-14 Mahle International Gmbh Kältemittelbehälter für eine Kälteanlage
IT201900003469A1 (it) * 2019-03-12 2020-09-12 Techinvest S R L Ciclocondensatore
WO2023128458A1 (fr) * 2021-12-31 2023-07-06 한온시스템 주식회사 Accumulateur de véhicule

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4182136A (en) * 1977-12-22 1980-01-08 Tecumseh Products Company Suction accumulator
US4651540A (en) 1986-03-21 1987-03-24 Tecumseh Products Company Suction accumulator including an entrance baffle
JPH04366377A (ja) * 1991-06-11 1992-12-18 Daikin Ind Ltd 気液分離器
US6167720B1 (en) * 1999-10-19 2001-01-02 Automotive Fluid Systems, Inc. Accumulator baffle molded from desiccant
US20020095948A1 (en) * 2001-01-22 2002-07-25 Corrigan Daniel Leonard Suction accumulator for air conditioning systems
DE10300801B3 (de) 2003-01-13 2004-06-24 Hansa Metallwerke Ag Akkumulator für eine Klimaanlage, insbesondere Fahrzeugklimaanlage
DE102005059482A1 (de) 2005-12-07 2007-06-14 Visteon Global Technologies, Inc., Van Buren Kältemittelakkumulator mit Flüssigkeitsabscheider
US20080000261A1 (en) * 2006-07-03 2008-01-03 Thomas Klotten Internal heat exchanger

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5746065A (en) * 1996-08-21 1998-05-05 Automotive Fluid Systems, Inc. Accumulator deflector connection and method
DE19808893A1 (de) * 1998-03-03 1999-09-09 Behr Gmbh & Co Wärmeübertragereinheit und diese enthaltende Sammler-Wärmeübertrager-Baueinheit
IT1312193B1 (it) * 1999-04-20 2002-04-09 Bundy Kmp S R L Accumulatore disidratatore per circuiti di refrigerazione e suoprocedimento di assiemaggio
US6523365B2 (en) * 2000-12-29 2003-02-25 Visteon Global Technologies, Inc. Accumulator with internal heat exchanger

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4182136A (en) * 1977-12-22 1980-01-08 Tecumseh Products Company Suction accumulator
US4651540A (en) 1986-03-21 1987-03-24 Tecumseh Products Company Suction accumulator including an entrance baffle
JPH04366377A (ja) * 1991-06-11 1992-12-18 Daikin Ind Ltd 気液分離器
US6167720B1 (en) * 1999-10-19 2001-01-02 Automotive Fluid Systems, Inc. Accumulator baffle molded from desiccant
US20020095948A1 (en) * 2001-01-22 2002-07-25 Corrigan Daniel Leonard Suction accumulator for air conditioning systems
DE10300801B3 (de) 2003-01-13 2004-06-24 Hansa Metallwerke Ag Akkumulator für eine Klimaanlage, insbesondere Fahrzeugklimaanlage
EP1437563A2 (fr) * 2003-01-13 2004-07-14 Hansa Metallwerke Ag Accumulateur pour un appareil de climatisation, en particulier pour un appareil de climatisation de véhicule
DE102005059482A1 (de) 2005-12-07 2007-06-14 Visteon Global Technologies, Inc., Van Buren Kältemittelakkumulator mit Flüssigkeitsabscheider
US20080000261A1 (en) * 2006-07-03 2008-01-03 Thomas Klotten Internal heat exchanger
DE102006031197A1 (de) 2006-07-03 2008-01-10 Visteon Global Technologies Inc., Van Buren Innerer Wärmeübertrager mit Akkumulator

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012132608A (ja) * 2010-12-21 2012-07-12 Calsonic Kansei Corp アキュムレータ
JP2012233664A (ja) * 2011-05-09 2012-11-29 Calsonic Kansei Corp アキュムレータ
WO2019107011A1 (fr) * 2017-12-01 2019-06-06 株式会社不二工機 Accumulateur
JP2019100624A (ja) * 2017-12-01 2019-06-24 株式会社不二工機 アキュームレータ
CN108759203A (zh) * 2018-08-03 2018-11-06 蚌埠市昊源压缩机制造有限公司 一种用于压缩机的气液分离器
CN111442581A (zh) * 2020-05-14 2020-07-24 和龙双昊高新技术有限公司 一种带余热回收功能的汽车空调用气液分离器

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Publication number Publication date
DE102008028852A1 (de) 2009-12-24
EP2136163B1 (fr) 2012-08-15

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