EP0143013A2 - Verfahren und Vorrichtung zum Überhitzen eines Kühlmittels - Google Patents

Verfahren und Vorrichtung zum Überhitzen eines Kühlmittels Download PDF

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Publication number
EP0143013A2
EP0143013A2 EP84401814A EP84401814A EP0143013A2 EP 0143013 A2 EP0143013 A2 EP 0143013A2 EP 84401814 A EP84401814 A EP 84401814A EP 84401814 A EP84401814 A EP 84401814A EP 0143013 A2 EP0143013 A2 EP 0143013A2
Authority
EP
European Patent Office
Prior art keywords
envelope
tube
outlet pipe
refrigerant
bottle
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Withdrawn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
EP84401814A
Other languages
English (en)
French (fr)
Other versions
EP0143013A3 (de
Inventor
Michel Gueneau
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.)
PACTOLE SA
Original Assignee
PACTOLE SA
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 PACTOLE SA filed Critical PACTOLE SA
Publication of EP0143013A2 publication Critical patent/EP0143013A2/de
Publication of EP0143013A3 publication Critical patent/EP0143013A3/de
Withdrawn legal-status Critical Current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
    • 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
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/051—Compression system with heat exchange between particular parts of the system between the accumulator and another part of the cycle

Definitions

  • the present invention relates to a process for the superheating of a gaseous refrigerating fluid before its introduction into the compressor of a heat pump with an internal combustion engine and for at the same time cooling and condensing the water vapor contained in the exhaust gases. of said motor. It also relates to a device for implementing this method.
  • the object of the present invention is therefore to provide a method which makes it possible to obtain overheating of the gaseous part of the refrigerant without reducing the performance of the evaporator, in the case of a heat pump whose compressor is driven. by a heat engine.
  • this process makes it possible at the same time to cool the water vapor contained in the engine exhaust gas and to condense it.
  • a second object of the invention is a device for implementing this method, this device being easily adaptable to existing installations.
  • the first object is achieved in that the invention provides a process for overheating a gaseous refrigerant before its introduction into the compressor of a thermal heat pump, characterized in that the residual thermal energy is used. exhaust gas from said heat engine to effect overheating.
  • a heat exchange takes place between all of the exhaust gases and said fluid in an area located in the immediate vicinity of the compressor.
  • the second object is achieved in that the invention provides a device comprising a heat exchanger allowing an exchange between the refrigerant and the exhaust gases and comprising an acceleration zone of said gaseous refrigerant.
  • this exchanger is contained in an anti-blow bottle located upstream of the compressor.
  • the exchanger uses as an exchange surface the envelope of said anti-blow bottle.
  • said envelope is cylindrical with a vertical axis, closed at its two ends.
  • this impact-resistant bottle has a cylindrical internal skirt closed in its upper end which is located between the intake manifold and the first end of the lower part of the outlet manifold. It is also provided with an orifice for the passage of the upper part of the outlet pipe.
  • the lower end of the skirt is open in its entirety and it is located at a level higher than the end of the lower part of said outlet pipe, which may have one or more lateral orifices, located in the part lower of U.
  • the cylindrical envelope of the anti-blow bottle is surrounded by a cylindrical outer envelope, comprising an intake manifold for the exhaust gases and an outlet manifold.
  • said outer envelope surrounds the lower end of the anti-blow bottle.
  • the device and the method according to the invention make it possible to overheat the gaseous part of the refrigerating fluid which results in an increase in the C.O.P. and the power of the heat pump linked to better use of the evaporator.
  • this allows cooling of the exhaust gases to a temperature of up to 30 or 40 ° C with almost complete condensation of the water vapor and a reduction in noise.
  • the anti-blow bottle (1) shown in FIG. 1 comprises a cylindrical envelope (2) constituted by a side wall (3) and, a lower end (4) and an upper end (5).
  • the two ends (4) and (5) are spherical caps.
  • the upper end (5) is provided with an inlet manifold (6) and an outlet manifold (7).
  • the intake manifold (6) opens slightly below the end (5) at which it is welded in (12).
  • the outlet pipe (7) has a cylindrical upper part (8) which opens to the outside and a lower part (9) which has the shape of a U.
  • the branch (10) of the U is located substantially opposite opposite the tubing (6) but opens at a much lower level.
  • the end (11) is connected to the cylindrical upper part (8).
  • An internal skirt (15) is placed inside the envelope (2). It comprises a side wall (16) and an upper wall (17) provided with an orifice (18) for the passage of the tube (8).
  • the skirt (15) and the envelope (2) define an annular volume (20), an upper dome (27) and a lower dome (26).
  • An outer envelope (30) surrounds the assembly. It is connected to the upper part of the side wall (13) of the envelope (2) by an annular ring (31). It includes an intake manifold (32) and an outlet manifold (33) for the exhaust gases from the compressor drive motor.
  • the envelope (30) and the envelope (2) define an external annular volume (35) and a lower external dome (36). The spacing between the two envelopes is maintained by the series of centering studs (37), (38), (39).
  • the device (1) according to the invention is placed in a heat pump as shown diagrammatically in FIG. 3 in which the evaporator (40), the compressor (41), the condenser (42) and the pressure reducer ( 46), the compressor (41) is rotated by the heat engine (43) whose exhaust gases are sent into the pipe (32) through the pipe (33).
  • the compressor drive is shown in (45).
  • the regulator (46) is a thermostatic regulator with external pressure equalization. It is adjusted according to a T so as to allow the refrigerant in the evaporator to overheat.
  • This device works in the following way: in normal mode, that is to say outside of transient modes the refrigerant gas passes, leaving the evaporator, in the anti-blow bottle (1) where it is overheated before to be introduced into the compressor (41).
  • the gas is introduced into the upper dome (21) and then into the annular volume (20) which constitutes the zone of exchange with the exhaust gas introduced by the pipe (32), the two gases being separated by the envelope (2) of the anti-blow bottle, which thus constitutes the exchange surface of the exchanger.
  • the annular volume (20) constitutes an acceleration zone where the speed of the gas becomes sufficient to obtain the desired heat exchange, contrary to what happens in the anti-blow bottles of the prior art which do not have an inner skirt. During this normal regime, the gas overheats to rid it of the fine droplets of liquid it contains.
  • the exhaust gases are introduced through the tubing (32) into the dome (36) and then collected in the upper part by the tubing (33).
  • Tubing (33) and (32) are tangential to the outer casing.
  • the device according to the invention has the advantage of cooling the exhaust gases and condensing the vapors therein.
  • the device shown in FIG. 1 comprises a tube (60) for discharging the condensates.
  • FIG. 4 and 5 an alternative embodiment of the anti-blow bottle according to the invention. It usually comprises a cylindrical casing (2) and a refrigerant gas outlet pipe (7) comprising a first vertical branch (8), a central U-shaped part (9) and a second vertical branch (10 ).
  • a circulation tube (50) of hot gases from the engine passes right through the cylindrical envelope, along its vertical axis, the inlet orifice (51) being located in the lower part (52).
  • the refrigerating gas is introduced via the annular pipe (55) defined by the tube (56) which surrounds the tube (50) for circulation of the hot gases.
  • the tube (56) is provided in the upper part with an intake manifold (60) situated outside the casing (2) and open in its lower end (61) at a level below the lower level of the central U-shaped part of the tubing (7).
  • the exhaust gas circulation tube (50) is provided in its lower end (52) with an orifice (65) for discharging the condensates.
  • the gas-gas heat exchange wall is formed by the wall of the tube (50) located opposite the tube (56) while the annular gas acceleration zone is defined by the tube (50) for circulation of the hot gases and by the tube (56) for introducing the refrigerating gas.
  • the invention is not limited to the embodiments described. On the contrary, it encompasses all variants, in particular, with regard to the shape of the anti-blow bottle which can, for example, be a capillary system.

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)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Lubrication Details And Ventilation Of Internal Combustion Engines (AREA)
EP84401814A 1983-09-16 1984-09-13 Verfahren und Vorrichtung zum Überhitzen eines Kühlmittels Withdrawn EP0143013A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8314795 1983-09-16
FR8314795A FR2552212B1 (fr) 1983-09-16 1983-09-16 Procede et dispositif de surchauffe d'un fluide frigorifique

Publications (2)

Publication Number Publication Date
EP0143013A2 true EP0143013A2 (de) 1985-05-29
EP0143013A3 EP0143013A3 (de) 1986-01-08

Family

ID=9292293

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84401814A Withdrawn EP0143013A3 (de) 1983-09-16 1984-09-13 Verfahren und Vorrichtung zum Überhitzen eines Kühlmittels

Country Status (6)

Country Link
US (1) US4653282A (de)
EP (1) EP0143013A3 (de)
JP (1) JPS6091164A (de)
ES (1) ES8603059A1 (de)
FR (1) FR2552212B1 (de)
PT (1) PT79198B (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1987005381A1 (en) * 1986-03-03 1987-09-11 Ecr Technologies, Inc. Fluid flow control system
EP0240811A1 (de) * 1986-04-10 1987-10-14 Hiross International Corporation S.A. Regelsystem für Anlagen mit einem Kältemittelkreislauf mit Kapillarrohrentspannung

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5282370A (en) * 1992-05-07 1994-02-01 Fayette Tubular Technology Corporation Air-conditioning system accumulator and method of making same
US5471854A (en) * 1994-06-16 1995-12-05 Automotive Fluid Systems, Inc. Accumulator for an air conditioning system
US5787728A (en) * 1997-01-21 1998-08-04 Carrier Corporation Suction accumulator destratifier
US6026655A (en) * 1997-02-27 2000-02-22 Parker-Hannifin Corporation Liquid accumulator with inlet tube
DE19813673B4 (de) * 1998-03-27 2004-01-29 Daimlerchrysler Ag Verfahren und Vorrichtung zum Heizen und Kühlen eines Nutzraumes eines Kraftfahrzeuges
JP3894701B2 (ja) * 2000-03-22 2007-03-22 株式会社ケーヒン 空調用冷媒受液器
DE10348141B3 (de) * 2003-10-09 2005-02-03 Visteon Global Technologies, Inc., Dearborn Innerer Wärmeübertrager für Hochdruckkältemittel mit Akkumulator
US20050081559A1 (en) * 2003-10-20 2005-04-21 Mcgregor Ian A.N. Accumulator with pickup tube
US7559210B2 (en) * 2005-06-29 2009-07-14 Intel Corporation Method and apparatus for cooling a heat source
JP5019822B2 (ja) * 2005-08-19 2012-09-05 モーディーン・マニュファクチャリング・カンパニー 中間の蒸気過熱経路を備える水蒸発器
US20090323276A1 (en) * 2008-06-25 2009-12-31 Mongia Rajiv K High performance spreader for lid cooling applications
CN102721238A (zh) * 2012-06-29 2012-10-10 赵良全 自身中冷转换器及使用该转换器的制冷系统及冷凝方法
CN106440573B (zh) * 2016-09-30 2019-02-26 青岛海信日立空调系统有限公司 一种热泵系统用气液分离器及其制作方法
US11460225B2 (en) * 2017-06-23 2022-10-04 Jack D. Dowdy, III Power saving apparatuses for refrigeration

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR754234A (de) * 1933-11-02
GB323196A (en) * 1928-09-21 1929-12-23 Max Schlawe Improvements in or relating to air heating devices utilising exhaust gases from internal combustion engines
GB376713A (en) * 1930-01-13 1932-07-14 Jean Sabatier Improvements in or relating to devices for utilizing the heat content from the cooling water and/or exhaust gases of heat engines
US2647377A (en) * 1949-01-24 1953-08-04 Day & Night Mfg Company Apparatus for providing gravity flow in flooded coil refrigeration systems
US3420071A (en) * 1967-03-10 1969-01-07 Edward W Bottum Suction accumulator
US3421339A (en) * 1967-05-31 1969-01-14 Trane Co Unidirectional heat pump system
US3766748A (en) * 1969-07-11 1973-10-23 Chrysler Corp Vehicle air conditioning system with suction accumulator
US3621673A (en) * 1969-12-08 1971-11-23 Trane Co Air-conditioning system with combined chiller and accumulator
US3803865A (en) * 1972-06-20 1974-04-16 Borg Warner Refrigeration control system
US4208887A (en) * 1979-01-22 1980-06-24 Tecumseh Products Company Suction accumulator having heat exchanger
US4236381A (en) * 1979-02-23 1980-12-02 Intertherm Inc. Suction-liquid heat exchanger having accumulator and receiver
US4217765A (en) * 1979-06-04 1980-08-19 Atlantic Richfield Company Heat exchanger-accumulator
DE2930404A1 (de) * 1979-07-26 1981-03-12 1000 Berlin Erich Schultze KG Versorgungs- und schutzeinrichtung fuer kaelteanlagen.
DE3034965C2 (de) * 1980-09-17 1983-05-05 Wieland-Werke Ag, 7900 Ulm Wärmeübertragungseinrichtung für Wärmepumpen
DE3206967A1 (de) * 1982-02-26 1983-09-08 Bedia Maschinenfabrik Verwaltungs-GmbH, 5300 Bonn Durch eine verbrennungskraftmaschine angetriebene waermepumpe
DE3222406C2 (de) * 1982-06-15 1985-07-18 H. Krantz Gmbh & Co, 5100 Aachen Verfahren zur Wärmerückgewinnung
US4517799A (en) * 1983-03-09 1985-05-21 Misawa Home Co., Ltd. Heat utilizing system using internal combustion engine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1987005381A1 (en) * 1986-03-03 1987-09-11 Ecr Technologies, Inc. Fluid flow control system
EP0240811A1 (de) * 1986-04-10 1987-10-14 Hiross International Corporation S.A. Regelsystem für Anlagen mit einem Kältemittelkreislauf mit Kapillarrohrentspannung

Also Published As

Publication number Publication date
FR2552212B1 (fr) 1986-03-21
US4653282A (en) 1987-03-31
ES535815A0 (es) 1985-12-01
FR2552212A1 (fr) 1985-03-22
JPS6091164A (ja) 1985-05-22
EP0143013A3 (de) 1986-01-08
PT79198A (fr) 1984-10-01
PT79198B (fr) 1986-07-17
ES8603059A1 (es) 1985-12-01

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Inventor name: GUENEAU, MICHEL