EP0132620A2 - Evaporateur - Google Patents

Evaporateur Download PDF

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Publication number
EP0132620A2
EP0132620A2 EP84107488A EP84107488A EP0132620A2 EP 0132620 A2 EP0132620 A2 EP 0132620A2 EP 84107488 A EP84107488 A EP 84107488A EP 84107488 A EP84107488 A EP 84107488A EP 0132620 A2 EP0132620 A2 EP 0132620A2
Authority
EP
European Patent Office
Prior art keywords
evaporator
flow
refrigerant
tubes
evaporator according
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
EP84107488A
Other languages
German (de)
English (en)
Other versions
EP0132620B1 (fr
EP0132620A3 (en
Inventor
Hans Dipl.-Ing. Kampf
Hans-Joachim Ing.-Grad. Ingelmann
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 EP0132620A2 publication Critical patent/EP0132620A2/fr
Publication of EP0132620A3 publication Critical patent/EP0132620A3/de
Application granted granted Critical
Publication of EP0132620B1 publication Critical patent/EP0132620B1/fr
Expired 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • F25B41/45—Arrangements for diverging or converging flows, e.g. branch lines or junctions for flow control on the upstream side of the diverging point, e.g. with spiral structure for generating turbulence
    • 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 an evaporator, in particular for air conditioning systems of motor vehicles, with an evaporator block with a plurality of evaporator tubes and a supply device for the refrigerant, which consists of an expansion valve and a flow distributor dividing the refrigerant flow, the connecting line between the expansion valve and the flow distributor being at least partially bent or is winding.
  • Such evaporators are known in principle. They include a thermostatically controlled expansion valve, to which the refrigerant is fed. A flow distributor is arranged behind the expansion valve, which distributes the refrigerant flow evenly over different evaporator tube strings. The actual evaporation then takes place in the evaporator block.
  • the flow distributor is designed in such a way that it distributes the refrigerant flow evenly over the various evaporator tube strands.
  • a venturi distributor is used, which divides the refrigerant flow into circular segments accordingly (US Pat. No. 28 03 116).
  • US Pat. No. 28 03 116 In order to ensure a uniform supply of refrigerant to the various evaporator tube strands, it is therefore necessary for there to be a homogeneous wet steam flow in front of the flow distributor.
  • the evaporator tube strands are charged with refrigerant to different extents, which worsens the efficiency of the evaporator and, under certain circumstances, also leads to unsatisfactory charge regulation by the thermostatic expansion valves.
  • Calming sections designed to rise or fall vertically have proven to be particularly favorable.
  • the object of the invention is to design an evaporator of the type mentioned in such a way that the connecting line between the expansion valve and the flow distributor can be at least partially bent or wound and that a homogeneous wet steam flow is nevertheless present in front of the flow distributor.
  • a swirl member is at an evaporator of the type mentioned immediately before the Strömun g sver- divider in the coolant flow arranged, whose flow cross section abruptly expanded in the direction of refrigerant flow.
  • the expansion of the flow cross-section causes the two-phase flow consisting of refrigerant vapor and refrigerant liquid to burst, so that these two phases are swirled. This becomes a homogeneous mixture and therefore a homogeneous wet steam flow. If the flow distributor now divides this homogeneous wet steam flow into different circular segments, it is ensured that each evaporator tube string is subjected to a mixture with the same properties. The efficiency and the control of the V improved ER steamer.
  • the swirling element is advantageous to design as a cylindrical swirl cell, the diameter d w of which is greater than the diameter d of the inlet opening for the refrigerant flow.
  • Such a vortex cell can be manufactured with little component and assembly effort. It has proven to be advantageous here if the ratio of the diameters d E / d W is at least 1/2 and at most 2/3.
  • the inlet opening for the refrigerant flow can advantageously be arranged on the cylinder jacket of the vortex cell.
  • the bursting of the two-phase flow or the swirling of refrigerant vapor and refrigerant liquid is additionally supported by the impact of the liquid particles on the cylinder wall opposite the inlet opening.
  • the flow distributor can be placed directly on an opening of the vortex cell. As a result, no additional connecting line between the vortex cell and the flow distributor is necessary.
  • the opening for the flow distributor is also expediently arranged on the cylinder jacket of the swirl cell.
  • the swirling element can also be constructed differently. It is possible, for example, if it consists of a component with a cross section that initially tapers in the direction of flow. After this tapering, it can expand again in the direction of flow, as a result of which the swirling already mentioned and thus a homogeneous wet steam flow is achieved. Since a taper is made first, this component can be built into a tube or between two tubes, which can have constant diameters throughout. It is therefore not necessary to change the cross-section of these pipes.
  • a component which tapers in cross-section exclusively in the flow direction inside one or more tubes, the expansion of the flow cross-section being formed by the tapered point of this component opening into the tube.
  • the component is structurally very simple and can still be installed in pipes of constant cross-section. It is particularly expedient to provide this component with a collar running on its circumference, which abuts the end pieces of two pipes. For further sealing, one of these pipes can moreover be provided with an apron which overlaps the collar.
  • the swirling element can also simply consist of an aperture.
  • This diaphragm can be fastened between the ends of two pipes in a manner similar to the collar of the mentioned component.
  • Another possible application of the invention is in evaporators, in which the refrigerant connections have to be on a specific evaporator side. Since the suction lines, that is, the lines for discharging the refrigerant vapor, are on the other side of the evaporator, it follows that an odd number of tubes is always omitted on each evaporator branch. It often happens that the number of evaporator strands, i.e. the number of refrigerant injections, is even, which means that an even number of tubes in the evaporator block is required, since the even number of evaporator strands multiplied by the odd number of tubes per strand in turn is even Number results. However, the evaporator blocks are often designed so that they contain an odd number of tubes. In this case, an empty pipe remains.
  • An evaporator block comprises 9 tubes in width and 5 tubes in depth, for a total of 45 tubes.
  • the 45th pipe remains as an empty pipe.
  • the suction line to the compressor which removes the refrigerant vapor again, cannot be led through the empty pipe in the evaporator to the connection side of the evaporator.
  • this empty pipe is therefore located on the side of the evaporator block facing away from the connection side, the empty pipe connecting this expansion valve to the connection side.
  • a swirling element according to the invention is then arranged on the connection side, which ensures a homogeneous wet steam flow in front of the flow distributor. This does not reduce the evaporator output.
  • Fig. 1 denotes an expansion valve.
  • the refrigerant enters this expansion valve in the direction of arrow A. stream on.
  • the expansion valve is a thermostatic expansion valve in which the superheating of the refrigerant vapor in the evaporator tubes is used as a control variable for the charge control.
  • Via a calming section 2 this expansion valve is connected to a flow distributor 3, which divides the refrigerant flow symmetrically.
  • a flow distributor is used here, which divides the coolant flow into circular segments.
  • a flow distributor is, for example, the Venturi distributor known from US-PS 28 03 116.
  • the calming section 2 fulfills the task of ensuring a homogeneous wet steam flow or a central ring flow upstream of the flow distributor 3, so that each of the evaporator lines from the flow distributor 3 is assigned a refrigerant flow with the same properties.
  • the outputs of the flow distributor 3 are connected to the evaporator block 4.
  • This evaporator block has a number of evaporator tubes. In each case several of these evaporator tubes are combined to form an evaporator tube string, so that each of the refrigerant partial streams originating from the flow distributor 3 flows through the evaporator block 4 several times.
  • the aim is for the refrigerant to evaporate completely at the end of all evaporator lines and to be overheated by an amount that is the same in all lines. This overheating is then used again as a controlled variable for the filling control by the expansion valve 1.
  • the refrigerant vapor then leaves the evaporator block in the direction of arrow B and is fed to the compressor in a manner not shown here via a suction line.
  • FIG. 2 A similar arrangement to that Fig. 1 shows the Fig. 2.
  • the expansion valve 1 is also an at least approximately homogeneous Nöndampfströmun prevails g, dispense with a calming section.
  • such an arrangement is also not possible due to sealing problems on the evaporator housings in practical use.
  • FIG. 3 A prior art arrangement of the evaporator in confined spaces shows the F ig. 3.
  • the refrigerant enters the expansion valve 1 in the direction of arrow A and is fed from there to the flow distributor 3 via a multiply bent or winding line 5.
  • the line 5 can no longer take on the function of a calming section, as shown in FIGS. 4 to 6, which show cross sections in the direction of the reference line IV-IV, VV and VI-VI of FIG. 3.
  • FIGS. 4 to 6 show cross sections in the direction of the reference line IV-IV, VV and VI-VI of FIG. 3.
  • the invention therefore proposes to arrange a swirling element with an expanding flow cross-section directly in front of the flow distributor.
  • An aera-like arrangement is shown in principle in FIG. 7.
  • the reference numbers of the previous figures have been retained.
  • the cross-sectional expansion of the swirling element 8 arranged in front of the flow distributor 3 leads to a violent swirling of the refrigerant vapor and refrigerant liquid and therefore to a homogeneous mixture.
  • the flow distributor can now divide the refrigerant flow into similar partial refrigerant flows that are fed to the individual evaporator tube strands. Evaporation and overheating therefore occur evenly in all evaporator tube strands, which results in an increased efficiency of the evaporator and at the same time better regulation of the expansion valve.
  • FIG. 8 An exemplary embodiment of the swirling element 8, which is only indicated schematically in FIG. 7, is shown in FIG. 8.
  • the swirling element is designed as a cylindrical swirl cell 9.
  • An inlet opening 11 for the refrigerant flow is arranged on the cylinder jacket 10 of this vortex cell 9.
  • the diameter dp of this inlet opening 11 is selected to be smaller than the diameter d of the vertebral cell 9, the ratio d E / d W preferably being between 1/2 and 2/3. This results in an expansion of the flow cross-section, which leads to a bursting of the two-phase flow consisting of refrigerant vapor and refrigerant liquid and therefore to a violent swirling or to the formation of a homogeneous mixture.
  • the outlet opening is also arranged on the cylinder jacket 1 0 12.
  • the opening 11 between the inlet and the outlet opening 12 effective distance L is preferably 25 mm to 35th.
  • the flow distributor 13 shown here as a component is inserted directly into the outlet opening 12. The component and assembly effort is thereby further reduced and cheaper the manufacture of an evaporator according to the invention.
  • FIG. 8 shows the cross section in the direction of the reference line IX-IX in FIG. 9.
  • the inlet connector 14 placed on the inlet opening 11 can be seen.
  • This inlet port 14 can be arranged as desired on the cylinder jacket 10, as indicated by the angle ⁇ , which can be between 0 and 360 °.
  • the inlet opening can thus be adapted to the respective installation conditions.
  • FIG. 10 Another embodiment of a swirling element according to the invention is shown in FIG. 10.
  • a component 15 provided with a cross section that tapers in the flow direction is provided here. With this configuration, it is achieved that the V erwirbelungselement in the interior of tubes 16 and 17 can be arranged without changing the cross-section must change these tubes.
  • the component 15 to the tubes 16 and 17, the latter is provided with a collar 18 which runs on its circumference and which bears against the end pieces of the tubes 16 and 17. This enables easy attachment.
  • the tube 16 also has an apron 19 which engages over the collar 18 and thus ensures a simple and reliable seal.
  • FIG. 10 can be simplified even further.
  • the swirling element consists only of an aperture 20, which is fastened to the tubes 16 and 17 in a manner similar to that of the component 15 according to FIG. 10.
  • FIG. 12 A special application of the invention is finally shown in FIG. 12.
  • the case occurs frequently that an evaporator block is equipped with an odd number of tubes, while the number of evaporator tube strings and so that the number of pipes required is even.
  • an empty pipe remains in the evaporator block.
  • This empty pipe cannot be used as a suction line to the compressor because of the high gas speeds and the associated high pressure losses.
  • the invention makes it possible to use this empty pipe as a connecting line between the expansion valve and the flow distributor. A separate and sometimes difficult or impossible to accommodate evaporator connection line around the evaporator block is not necessary.
  • the refrigerant flows in the direction of arrow A through the expansion valve 1 and is fed via a connecting line 21 to the empty pipe 22, which is only shown in broken lines.
  • this empty tube 22 opens into the swirling element, which is designed here as a swirl cell 24, as a result of which a homogeneous wet steam flow is produced again.
  • the refrigerant partial flows 26abis 26d which are only shown schematically, are then fed to the evaporator tube strands. After passing through these strands, the refrigerant vapor passes through the suction line 27 in the direction of arrow B to the compressor, not shown here.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP84107488A 1983-07-28 1984-06-28 Evaporateur Expired EP0132620B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3327179 1983-07-28
DE19833327179 DE3327179A1 (de) 1983-07-28 1983-07-28 Verdampfer

Publications (3)

Publication Number Publication Date
EP0132620A2 true EP0132620A2 (fr) 1985-02-13
EP0132620A3 EP0132620A3 (en) 1985-12-18
EP0132620B1 EP0132620B1 (fr) 1987-09-16

Family

ID=6205108

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84107488A Expired EP0132620B1 (fr) 1983-07-28 1984-06-28 Evaporateur

Country Status (4)

Country Link
US (1) US4543802A (fr)
EP (1) EP0132620B1 (fr)
DE (2) DE3327179A1 (fr)
ES (1) ES279746Y (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0566899A1 (fr) * 1992-04-16 1993-10-27 Behr GmbH & Co. Echangeur de chaleur, notamment évaporateur
AT396834B (de) * 1992-05-04 1993-12-27 Friedmann Kg Alex Kältemaschine
DE19515527A1 (de) * 1995-04-27 1996-10-31 Thermal Werke Beteiligungen Gm Verdampfer in Flachrohr- oder Plattenbauweise für den Kältemittelkreislauf einer Kraftfahrzeugklimaanlage
DE19824881A1 (de) * 1998-06-04 1999-12-16 Reisner Gmbh Kaeltetechnischer Kältemittelverdampfer zur Kühlung eines fluiden Mediums, insbesondere Wasser

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4922732A (en) * 1989-11-20 1990-05-08 Dyna-Manufacturing, Ltd. Evaporator system for refrigeration systems
US5479784A (en) * 1994-05-09 1996-01-02 Carrier Corporation Refrigerant distribution device
US5842351A (en) * 1997-10-24 1998-12-01 American Standard Inc. Mixing device for improved distribution of refrigerant to evaporator
US6023940A (en) * 1998-07-06 2000-02-15 Carrier Corporation Flow distributor for air conditioning unit
JP2002535590A (ja) 1999-01-12 2002-10-22 エックスディーエックス・インコーポレーテッド ベーパ圧縮装置及び方法
US6185958B1 (en) 1999-11-02 2001-02-13 Xdx, Llc Vapor compression system and method
US6314747B1 (en) 1999-01-12 2001-11-13 Xdx, Llc Vapor compression system and method
CN1343296A (zh) 1999-01-12 2002-04-03 Xdx有限公司 蒸汽压缩系统及其方法
ATE343770T1 (de) 1999-11-02 2006-11-15 Xdx Technology Llc Dampfkompressionssystem und verfahren zur steuerung der umgebungsverhältnisse
EP1122503A1 (fr) * 2000-01-31 2001-08-08 Eaton Aeroquip Inc. Dispositif introduisant une turbulence dans des systèmes réfrigérants
US6393851B1 (en) 2000-09-14 2002-05-28 Xdx, Llc Vapor compression system
US6915648B2 (en) 2000-09-14 2005-07-12 Xdx Inc. Vapor compression systems, expansion devices, flow-regulating members, and vehicles, and methods for using vapor compression systems
US6857281B2 (en) 2000-09-14 2005-02-22 Xdx, Llc Expansion device for vapor compression system
US6389825B1 (en) 2000-09-14 2002-05-21 Xdx, Llc Evaporator coil with multiple orifices
US6401470B1 (en) 2000-09-14 2002-06-11 Xdx, Llc Expansion device for vapor compression system
SE0101636D0 (sv) * 2001-05-10 2001-05-10 Emerson Energy Systems Ab Apparatus and method for improving the performance of an evaporator
US6898945B1 (en) * 2003-12-18 2005-05-31 Heatcraft Refrigeration Products, Llc Modular adjustable nozzle and distributor assembly for a refrigeration system
US20060064997A1 (en) * 2004-09-29 2006-03-30 Grabon Michal K Cooling systems
US9506701B2 (en) * 2006-05-29 2016-11-29 Webasto Ag Cold and/or heat accumulator
US7597137B2 (en) * 2007-02-28 2009-10-06 Colmac Coil Manufacturing, Inc. Heat exchanger system
WO2009140584A2 (fr) * 2008-05-15 2009-11-19 Xdx Innovative Refrigeration, Llc Système de transfert de chaleur à compression de vapeur pompée avec dégivrage réduit
US20100024440A1 (en) * 2008-08-04 2010-02-04 John Dain Flow Control of a Cryogenic Element to Remove Heat
US20120145246A1 (en) * 2010-12-13 2012-06-14 Heatcraft Refrigeration Products Llc System and method for distribution of refrigerant to a plurality of heat exchanger evaporator coil circuits
JP2018162920A (ja) * 2017-03-27 2018-10-18 株式会社富士通ゼネラル 空気調和機

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2182664A (en) * 1936-12-17 1939-12-05 Gen Electric Refrigerant distributor for cooling units
US2232568A (en) * 1940-02-27 1941-02-18 Gen Electric Cooling unit
US2426238A (en) * 1941-03-15 1947-08-26 Int Standard Electric Corp Variable flow restrictor
US2461876A (en) * 1946-06-28 1949-02-15 Betz Corp Liquid distributor for refrigerating systms
US2787138A (en) * 1955-04-18 1957-04-02 Betz Corp Fluid mixing device
US3120743A (en) * 1962-01-18 1964-02-11 Carrier Corp Refrigeration system including metering and distributing means
US3563055A (en) * 1969-03-17 1971-02-16 Sporlan Valve Co Refrrigerant distribvtor
US3745787A (en) * 1971-11-16 1973-07-17 Chrysler Corp Evaporator coil refrigerant distributor
EP0043383A1 (fr) * 1980-07-08 1982-01-13 Riedel Kälte- und Klimatechnik GmbH & Co, KG Evaporateur pour liquides et/ou gaz, spécialement pour équipements frigorifiques et thermopompes

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2084755A (en) * 1935-05-03 1937-06-22 Carrier Corp Refrigerant distributor

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2182664A (en) * 1936-12-17 1939-12-05 Gen Electric Refrigerant distributor for cooling units
US2232568A (en) * 1940-02-27 1941-02-18 Gen Electric Cooling unit
US2426238A (en) * 1941-03-15 1947-08-26 Int Standard Electric Corp Variable flow restrictor
US2461876A (en) * 1946-06-28 1949-02-15 Betz Corp Liquid distributor for refrigerating systms
US2787138A (en) * 1955-04-18 1957-04-02 Betz Corp Fluid mixing device
US3120743A (en) * 1962-01-18 1964-02-11 Carrier Corp Refrigeration system including metering and distributing means
US3563055A (en) * 1969-03-17 1971-02-16 Sporlan Valve Co Refrrigerant distribvtor
US3745787A (en) * 1971-11-16 1973-07-17 Chrysler Corp Evaporator coil refrigerant distributor
EP0043383A1 (fr) * 1980-07-08 1982-01-13 Riedel Kälte- und Klimatechnik GmbH & Co, KG Evaporateur pour liquides et/ou gaz, spécialement pour équipements frigorifiques et thermopompes

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0566899A1 (fr) * 1992-04-16 1993-10-27 Behr GmbH & Co. Echangeur de chaleur, notamment évaporateur
AT396834B (de) * 1992-05-04 1993-12-27 Friedmann Kg Alex Kältemaschine
DE19515527A1 (de) * 1995-04-27 1996-10-31 Thermal Werke Beteiligungen Gm Verdampfer in Flachrohr- oder Plattenbauweise für den Kältemittelkreislauf einer Kraftfahrzeugklimaanlage
DE19824881A1 (de) * 1998-06-04 1999-12-16 Reisner Gmbh Kaeltetechnischer Kältemittelverdampfer zur Kühlung eines fluiden Mediums, insbesondere Wasser

Also Published As

Publication number Publication date
ES279746Y (es) 1985-06-01
ES279746U (es) 1984-11-16
DE3327179A1 (de) 1985-02-07
EP0132620B1 (fr) 1987-09-16
EP0132620A3 (en) 1985-12-18
US4543802A (en) 1985-10-01
DE3466276D1 (en) 1987-10-22

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