EP0002687A1 - Apparatus using heat exchange - Google Patents

Apparatus using heat exchange Download PDF

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Publication number
EP0002687A1
EP0002687A1 EP78101562A EP78101562A EP0002687A1 EP 0002687 A1 EP0002687 A1 EP 0002687A1 EP 78101562 A EP78101562 A EP 78101562A EP 78101562 A EP78101562 A EP 78101562A EP 0002687 A1 EP0002687 A1 EP 0002687A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
section
area
characterized
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
EP78101562A
Other languages
German (de)
French (fr)
Other versions
EP0002687B1 (en
Inventor
Friedrich Ing. Grad. Schnadt
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.)
KUEPPERSBUSCH
Kueppersbusch AG
Kuppersbusch AG
Original Assignee
KUEPPERSBUSCH
Kueppersbusch AG
Kuppersbusch 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
Priority to DE19772757950 priority Critical patent/DE2757950A1/en
Priority to DE2757950 priority
Application filed by KUEPPERSBUSCH, Kueppersbusch AG, Kuppersbusch AG filed Critical KUEPPERSBUSCH
Publication of EP0002687A1 publication Critical patent/EP0002687A1/en
Application granted granted Critical
Publication of EP0002687B1 publication Critical patent/EP0002687B1/en
Expired legal-status Critical Current

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/08Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
    • F28D7/026Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled the conduits of only one medium being helically coiled and formed by bent members, e.g. plates, the coils having a cylindrical configuration

Abstract

Heat exchanger for evaporating or condensing refrigerant in the refrigerant circuit of a heat pump, in which the refrigerant occurs as a wet steam and away from it as a superheated gas.
In order to achieve that an increase in the heat transfer between the refrigerant and the heat exchanger thus entering into heat exchange is achieved with simple means, the free flow cross section (1, 5) for the refrigerant in the wet steam area is larger than in area (1, 3) for the superheated gas.

Description

  • The invention relates to a heat exchanger according to the preamble of patent claim 1.
  • In a known heat exchanger of this type (DE-PS 341 457), a plurality of tubular bodies are arranged one above the other and running parallel to one another. The tubular bodies consist of concentrically arranged tubes, each of which is connected in terms of flow at opposite ends to the associated adjacent tube. Refrigerant is guided through the flow cross-section between the inner and outer tubes, which is the same in all the tube bodies, and water in countercurrent through the inner tube. The upper area of this heat exchanger is for superheated refrigerant gas and the lower area for wet steam refrigerant.
  • The object of the invention is to take measures in a heat exchanger according to the preamble of claim 1, by means of which simple means increase the heat transfer between the refrigerant and thus the heat exchange standing heat transfer medium is reached.
  • This object is achieved by the characterizing features of patent claim 1.
  • The thermal advantage of dividing the heat exchanger into sections with different flow cross sections is that optimal thermodynamic flow conditions for the heat transfer are achieved for the individual stages of condensation or evaporation.
  • The greater the flow velocity of a gas, the higher the heat transfer at the heat transfer surfaces. Therefore e.g. during the condensation, the superheated refrigerant gas is first introduced into the area with the smaller flow cross-section, which it passes through at high speed and with high heat emission. It goes into the state of saturation with a larger mass flow density. However, the pressure loss increases with a higher mass flow density. Therefore, the refrigerant that changes into wet steam is then led into the area with the enlarged flow cross-section. As a result, depending on the condition of the refrigerant, an optimal heat transfer with little pressure loss is achieved over the length of the heat exchanger.
  • The invention is explained below with reference to the drawings of an embodiment.
  • It shows:
    • 1 shows a heat exchanger in longitudinal section,
    • 2 shows a cross section of the heat exchanger in its area with a large flow cross section,
    • Fig. 3 shows a cross section of the heat exchanger in its area with a small flow cross section and
    • Fig. 4 shows a longitudinal section of the heat exchanger in its area small flow cross section in an enlarged view.
  • A heat exchanger is formed from an outer tube 1 and an inner tube 2 encompassed coaxially therefrom. The outer tube 1 has a constant diameter over its length, while the diameter of the inner tube 2 decreases over its length. The inner tube 2 consists of a cylindrical tube section 3 of large diameter which merges via a conical tube section 4 into a tube section 5 of small diameter. This forms areas in the heat exchanger with different flow cross sections for the refrigerant to be passed between the tubes 1 and 2.
  • In the area with the enlarged flow cross-section there are radially standing and axially extending ribs 6 on the tube section 5 with the small diameter to increase the heat transfer area from the refrigerant to the inner tube 2 or the heat carrier carried therein. In contrast, a wire 7 is wound in turns with a pitch around the tube section 3 with a large diameter, which serves to swirl the superheated refrigerant gas flowing there. The conical pipe section 4 is arranged in the section in which the refrigerant from the overheated state in the passes the wet steam state. By appropriately long 'formation of the pipe section 4, an optimal heat transfer can be achieved in this transition state of the refrigerant and the fact that the transition state can occur, for example, depending on the temperature of the heat transfer medium at different locations along the heat exchanger.
  • When the heat exchanger constructed in this way is used as an evaporator in the refrigerant circuit of a heat pump or refrigeration machine, the refrigerant is introduced after the usual expansion into the region of the enlarged flow cross section between the outer tube 1 and the tube section 5 of the inner tube 2, where it takes heat from the inner tube 2 flowing heat transfer medium and progressively changes to the gaseous state with decreasing saturation. It then passes into the reduced flow cross-section between the outer tube 1 and the tube section 3 of the inner tube 2, where it is quickly overheated due to a much higher speed and a correspondingly increased heat absorption and can be supplied as a pure gas to the compressor of the heat pump.
  • When using the heat exchanger as a condenser, the superheated gaseous refrigerant is first fed in the opposite direction to the reduced flow cross section and, after corresponding heat transfer to the heat transfer medium, changes into wet steam and thereby into the expanded flow cross section.
  • In addition to the thermodynamic improvements, it is also achieved that only the tube section 5 in the region of the large flow cross section has to be produced from ribbed extruded profile which is difficult to produce.

Claims (6)

1. heat exchanger for evaporating or condensing refrigerant in the refrigerant circuit of a heat pump, in which the refrigerant occurs as wet steam and away from it as superheated gas,
characterized,
that the free flow cross-section for the refrigerant in the wet steam area is larger than in the area for the superheated gas.
2. Heat exchanger according to claim 1,
characterized,
that two coaxially arranged tubes (1, 2) are provided, of which one is the same throughout and the other has a section with an enlarged diameter.
3. Heat exchanger according to claim 2,
characterized,
that the diameter of the expanded pipe (2) is continuously expanding from the small to the large diameter.
4. Heat exchanger according to claim 3,
characterized,
that between two tubes (3, 5) of unequal diameter, a kogolige tube section (4) with corresponding end diameters is inserted.
5. Heat exchanger according to claim 1 or one of the following,
characterized,
that heat exchange fins (6) are provided on the inner tube (5) in the expanded area of the flow cross section.
6. Heat exchanger according to claim 1 or one of the following,
characterized,
that swirling elements (7) are arranged in the flow cross section in the area for the superheated gas.
EP19780101562 1977-12-24 1978-12-05 Apparatus using heat exchange Expired EP0002687B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE19772757950 DE2757950A1 (en) 1977-12-24 1977-12-24 heat exchanger
DE2757950 1977-12-24

Publications (2)

Publication Number Publication Date
EP0002687A1 true EP0002687A1 (en) 1979-07-11
EP0002687B1 EP0002687B1 (en) 1982-04-21

Family

ID=6027235

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19780101562 Expired EP0002687B1 (en) 1977-12-24 1978-12-05 Apparatus using heat exchange

Country Status (4)

Country Link
EP (1) EP0002687B1 (en)
AT (1) AT358615B (en)
DE (1) DE2757950A1 (en)
DK (1) DK566378A (en)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2493296A1 (en) * 1980-07-11 1982-05-07 Bertrams Ag Method and device for concentrating alkaline laundry
WO1984002392A1 (en) * 1982-12-15 1984-06-21 Svante Thunberg Ventilation plant
EP0255313A2 (en) * 1986-07-29 1988-02-03 Showa Aluminum Kabushiki Kaisha Condenser
EP0396868A1 (en) * 1989-04-26 1990-11-14 Deutsche Babcock- Borsig Aktiengesellschaft Heat exchanger for cooling cracking gases
US5190100A (en) * 1986-07-29 1993-03-02 Showa Aluminum Corporation Condenser for use in a car cooling system
US5246064A (en) * 1986-07-29 1993-09-21 Showa Aluminum Corporation Condenser for use in a car cooling system
US5458190A (en) * 1986-07-29 1995-10-17 Showa Aluminum Corporation Condenser
US5482112A (en) * 1986-07-29 1996-01-09 Showa Aluminum Kabushiki Kaisha Condenser
WO2004001313A1 (en) * 2002-06-24 2003-12-31 Abb Research Ltd Heat exchanger

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8805401U1 (en) * 1988-04-23 1988-06-16 Sueddeutsche Kuehlerfabrik Julius Fr. Behr Gmbh & Co Kg, 7000 Stuttgart, De

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE341457C (en) * 1919-12-14 1921-10-01 Edmund Altenkirch A process for the utilization of the Waermehoeherer temperature generated by the adiabatic compression in vapor-compression refrigeration
US3749155A (en) * 1970-07-16 1973-07-31 Georges Claude Sa Exchange process
DE2427303A1 (en) * 1974-06-06 1975-12-18 Tsni I Pk Kotloturbiny I Im Po Heat exchanger with tubular elements - consisting of concentric tubes and finned heating tube
US4029142A (en) * 1975-02-04 1977-06-14 U.S. Philips Corporation Heat exchanger
DE7437664U (en) * 1974-11-12 1977-10-13 Hansa-Metallwerke Ag, 7000 Stuttgart Waermetauscher with two spaced surrounding each fuehrungsrohren
EP0000001A1 (en) * 1977-09-02 1978-12-20 Europäische Atomgemeinschaft (Euratom) Thermal heat pump

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE341457C (en) * 1919-12-14 1921-10-01 Edmund Altenkirch A process for the utilization of the Waermehoeherer temperature generated by the adiabatic compression in vapor-compression refrigeration
US3749155A (en) * 1970-07-16 1973-07-31 Georges Claude Sa Exchange process
DE2427303A1 (en) * 1974-06-06 1975-12-18 Tsni I Pk Kotloturbiny I Im Po Heat exchanger with tubular elements - consisting of concentric tubes and finned heating tube
DE7437664U (en) * 1974-11-12 1977-10-13 Hansa-Metallwerke Ag, 7000 Stuttgart Waermetauscher with two spaced surrounding each fuehrungsrohren
US4029142A (en) * 1975-02-04 1977-06-14 U.S. Philips Corporation Heat exchanger
EP0000001A1 (en) * 1977-09-02 1978-12-20 Europäische Atomgemeinschaft (Euratom) Thermal heat pump

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2493296A1 (en) * 1980-07-11 1982-05-07 Bertrams Ag Method and device for concentrating alkaline laundry
WO1984002392A1 (en) * 1982-12-15 1984-06-21 Svante Thunberg Ventilation plant
US5246064A (en) * 1986-07-29 1993-09-21 Showa Aluminum Corporation Condenser for use in a car cooling system
EP0255313A3 (en) * 1986-07-29 1989-08-09 Showa Aluminum Kabushiki Kaisha Condenser
USRE35711E (en) * 1986-07-29 1998-01-06 Showa Aluminum Corporation Condenser for use in a car cooling system
US5190100A (en) * 1986-07-29 1993-03-02 Showa Aluminum Corporation Condenser for use in a car cooling system
EP0255313A2 (en) * 1986-07-29 1988-02-03 Showa Aluminum Kabushiki Kaisha Condenser
US5458190A (en) * 1986-07-29 1995-10-17 Showa Aluminum Corporation Condenser
US5482112A (en) * 1986-07-29 1996-01-09 Showa Aluminum Kabushiki Kaisha Condenser
USRE35655E (en) * 1986-07-29 1997-11-11 Showa Aluminum Corporation Condenser for use in a car cooling system
EP0396868A1 (en) * 1989-04-26 1990-11-14 Deutsche Babcock- Borsig Aktiengesellschaft Heat exchanger for cooling cracking gases
WO2004001313A1 (en) * 2002-06-24 2003-12-31 Abb Research Ltd Heat exchanger
EP1376038A1 (en) * 2002-06-24 2004-01-02 Abb Research Ltd. Heat exchanger

Also Published As

Publication number Publication date
DK566378A (en) 1979-06-25
ATA894178A (en) 1980-02-15
AT358615B (en) 1980-09-25
EP0002687B1 (en) 1982-04-21
DE2757950A1 (en) 1979-06-28

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