EP2338019A1 - Dispositif de raccordement pour un échangeur de chaleur intérieur - Google Patents

Dispositif de raccordement pour un échangeur de chaleur intérieur

Info

Publication number
EP2338019A1
EP2338019A1 EP09778667A EP09778667A EP2338019A1 EP 2338019 A1 EP2338019 A1 EP 2338019A1 EP 09778667 A EP09778667 A EP 09778667A EP 09778667 A EP09778667 A EP 09778667A EP 2338019 A1 EP2338019 A1 EP 2338019A1
Authority
EP
European Patent Office
Prior art keywords
connection
bore
heat exchanger
hole
cross
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Withdrawn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
EP09778667A
Other languages
German (de)
English (en)
Inventor
Joan Aguilar
Karl-Heinz Schlegel
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.)
Otto Egelhof GmbH and Co KG
Original Assignee
Otto Egelhof 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 Otto Egelhof GmbH and Co KG filed Critical Otto Egelhof GmbH and Co KG
Publication of EP2338019A1 publication Critical patent/EP2338019A1/fr
Withdrawn legal-status Critical Current

Links

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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-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 arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-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 arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F28F9/0251—Massive connectors, e.g. blocks; Plate-like connectors
    • F28F9/0253—Massive connectors, e.g. blocks; Plate-like connectors with multiple channels, e.g. with combined inflow and outflow channels

Definitions

  • the invention relates to a connection device for an internal heat exchanger, which is provided in a refrigeration cycle.
  • a refrigeration cycle is apparent, which is used in an air conditioner for a vehicle.
  • the condensed refrigerant is supplied to an expansion valve via an internal heat exchanger and via an adjoining pipe.
  • the high-pressure refrigerant is expanded by the expansion valve and flows with low pressure to the evaporator.
  • the evaporator is in turn connected via a separate line with the inner heat exchanger in connection.
  • a connection is provided which leads to the compressor.
  • the invention is therefore based on the object to provide a connection device for an inner heat exchanger, which reduces the number of connections and allows a space-saving arrangement.
  • connection device has a cross-sectional constriction in the connection block in the first through-bore between the inlet opening and the outlet opening, which is designed as a throttle point.
  • a throttle point By this arrangement is thus made possible that two additional connection points for the integration of a throttle point between the inner heat exchanger and the evaporator can be saved.
  • a space-saving arrangement can be provided, since the throttle point is integrated in the connection block of the connection device.
  • a simple and cost-effective production is made possible by the direct formation of the throttle point in the connection block by a cross-sectional constriction of the first through hole further. Additional components for the design of the throttle point are not required because this throttle point is incorporated as a cross-sectional constriction directly into the terminal block.
  • connection device provides that the cross-sectional constriction designed as a throttle point has a cross-sectional area which is smaller than the cross-sectional area of the outlet opening in the first through-bore.
  • a throttle point is created in a simple manner, which is formed by the geometric relationships of the cross-sectional area of the outlet opening and the cross-sectional area of the cross-sectional constriction in the through-bore.
  • the cross-sectional constriction channel-shaped or nozzle-shaped and preferably a multiple smaller than the average cross section of the first through-hole between the inlet and outlet opening is formed.
  • a throttle point can be introduced into the connection block in a structurally simple manner, which preferably consists of a solid material, in which the first and second through-holes are incorporated by drilling / milling or the like.
  • the cross-sectional constriction can also be designed stepped.
  • This throttle point is preferably designed as a fixed throttle, that is to say that the connecting device with a first and second through-bore in the first through-bore comprises a fixed throttle in order to expand a high-pressure refrigerant at the throttle point and to lead with low pressure to the evaporator.
  • a flow through the cross-sectional constriction mass flow with a valve closure member of an insertable into the through hole expansion valve is controllable.
  • This arrangement has the advantage that the connection device can be formed with an expansion valve without requiring additional interfaces for connections between the expansion valve and hose lines from the inner heat exchanger and to the evaporator.
  • the expansion valve which can be inserted into the connection block of the connection device is preferably designed as a pressure difference valve.
  • the working range of this differential pressure valve is determined by the pressure difference between the inlet side and the outlet side of the through-hole, that is, by the high pressure applied to the inlet opening of the first through-hole and the low-pressure applied to the outlet opening of the first through-hole.
  • the expansion valve which can be inserted into the connection block preferably has a guide element receiving the valve closure element, a restoring device and an adjusting device.
  • the integrated arrangement allows such an expansion valve with a extremely small number of components can be formed. These components can for example be successively used one after the other in the through hole, preferably via the outlet opening of the first through hole.
  • the deployable expansion valve preferably has a guide element which is designed as a disk-shaped sleeve or as a sleeve with tongue-shaped tabs.
  • the design as a disk-shaped sleeve has the advantage that a simple geometric structure is given, for example, centrally a valve closure member can be arranged, which is surrounded by one or more through-holes.
  • An outer circumferential surface of the guide element is supported on a bore wall of the first through hole and can be guided coaxially to this displaceable.
  • the alternative embodiment of the sleeve with spring-shaped tabs represents an alternative method of production as a sheet-metal bent part.
  • the spring-shaped tabs also act on the wall section of the through-hole, so that the guide element is arranged coaxially displaceable.
  • the guide element and the valve closing member are firmly connected to each other or formed in one piece.
  • a secure lifting and guiding the valve closure member is made possible via the guide element.
  • the one-piece embodiment can also be chosen as an embodiment in which the valve closure member is firmly connected to the guide member, such as by a welding or clamping connection.
  • the deployable expansion valve preferably has an adjusting device, which comprises at least one adjusting nut.
  • This adjusting nut engages in a threaded portion in the first through hole, which is preferably provided downstream of the cross-sectional constriction.
  • a biasing force of the return device can be adjusted, which in turn determines the opening time of the expansion valve.
  • the adjusting device has a holder for Receiving or supporting the return device in order to allow a central recording. This holder may also be integrally provided on the adjusting nut or fixedly connected thereto.
  • the adjusting nut of the deployable expansion valve is provided at least with arc segment-shaped recesses on the outer circumference or through holes or both.
  • the inlet opening of the first through-hole and the outlet opening of the second through-hole is located in a common connection bore in the connection block, which adjoins a side wall of the connection block and preferably as a blind hole.
  • the outlet opening of the first through-hole and the inlet opening of the second through-hole, as well as the connection point of the connection bore are to be sealed off from the external environment, so that there are only three connection points to be sealed to the outside.
  • connection bore is formed as a stepped bore for connection of a double-tubular inner heat exchanger.
  • stepped bore an inner tube of the double-tube heat exchanger at a first stage and the outer tube of the inner heat exchanger at a second stage of the stepped connection hole can be assigned, whereby a structurally simple separation of the supplied and high-pressure refrigerant and the discharged and low-pressure refrigerant is possible.
  • connection bore in the connection block it is preferably provided that during the introduction of a connection bore in the connection block, the longitudinal axis of the cross-sectional constriction is aligned radially to the connection bore and in the connection hole opens.
  • the cross-sectional constriction opens upstream in an annular channel, which is preferably formed after the introduction of the double-tubular inner heat exchanger with the connection bore in the stepped connection bore. This annular channel forms after insertion of the double-tube inner heat exchanger, the inlet opening of the first through hole.
  • the outlet bore arranged in the connection block is preferably arranged coaxially with the outlet opening of the second through-bore.
  • a double-tubular inner heat exchanger can be inserted into the connection bore and at least one screen element is arranged therebetween.
  • the filter element which can be inserted into the connection bore of the connection block is preferably of tubular or frustoconical design and preferably has annular sealing elements at least on the respective end surfaces.
  • the one seal member seals the atmosphere to the high pressure side, and the other seal member seals the high pressure side to the low pressure side.
  • the screen element can also be provided for receiving the sealing elements and the respective seal at the same time.
  • connection of the double-tubular inner heat exchanger with the terminal block is hermetically sealed.
  • FIG. 2 shows a perspective view of a first embodiment of a connection device
  • FIG. 3 shows a schematic sectional illustration of an alternative embodiment of the connection device to FIG. 2,
  • FIG. 4a shows a schematic detail view of an expansion valve in the connection device
  • FIG. 4b shows a schematic detail view of an adjusting device of the expansion valve according to FIG. 4a, FIG.
  • Figure 5 is a schematic detail view of an alternative
  • FIG. 6 is a schematic sectional view of a connection device according to FIG. 3 with an alternative connection of an internal heat exchanger.
  • FIG. 1 shows a conventional construction of a refrigeration or heat cycle 11, in particular an air conditioner, which is preferably used in motor vehicles.
  • a refrigerant in particular R134a
  • the compressed refrigerant is supplied to a condenser 13 with heat exchange between the compressed refrigerant and the ambient to cool the refrigerant.
  • the capacitor 13 nachgege- An accumulator 17 or collector can be provided to separate refrigerant from the gas phase and the liquid phase and at the same time to collect liquid refrigerant.
  • the refrigerant leaving the condenser 13 or accumulator 17 reaches an internal heat exchanger 14. Between the internal heat exchanger 14 and an evaporator 16, an expansion valve 15 is provided.
  • the expansion valve 18 By the expansion valve 18, the mass flow of the refrigeration relationship as heat cycle 11 is controlled in response to the upcoming pressure difference.
  • the high-pressure refrigerant is expanded through the expansion valve 15 and reaches the low-pressure side to the evaporator 16. From the evaporator 16, the refrigerant absorbs heat from the environment. From there, the refrigerant is fed back to the compressor 12 via the inner heat exchanger.
  • the depiction of the refrigeration circuit 11 deviates from the view that the expansion valve 15 is not arranged separately in a line section between the inner heat exchanger 14 and the evaporator 16, but integrated in the inner heat exchanger 14 is.
  • FIG. 2 shows in perspective a first embodiment of the connection device 21.
  • This connection device 21 comprises a connection block 22, which is preferably solid or formed from a solid material.
  • a first through hole 24 and a second through hole 25 is introduced.
  • the first through-bore 24 comprises an inlet opening 26 which can be connected to a connection of an internal heat exchanger 14 on the high-pressure side.
  • an outlet opening 27 is provided, which is connectable to a pipe not shown or directly to the evaporator 16.
  • the second through-bore 25 has an inlet opening 28 parallel to the outlet opening 27, so that refrigerant coming from the evaporator 16 can be introduced into the connection block 22 or the second through-bore 25.
  • an outlet port 29 is provided, which leads the refrigerant to the inner heat exchanger 14.
  • the through holes 24 and 25 may be formed as a straight, extending through the terminal block 22 holes.
  • a Kocheckan angel be provided, as shown for example in Figure 2. It is not absolutely necessary that the inlet opening 26 of the first through-bore 24 must be arranged on a same side wall with the outlet opening 29 of the second through-bore 25. The same applies to the outlet opening 27 of the first through-hole and inlet opening 28 of the second through-hole 25. These can be arranged application-specific offset from each other.
  • the first through-bore 24 has two bore sections which are arranged at right angles to one another.
  • a cross-sectional constriction 31 is formed, which acts as a throttle point.
  • the cross-sectional constriction 31 is incorporated directly into the terminal block 22.
  • the throttle body is formed integrally with the terminal block 22.
  • FIG. 3 shows an alternative embodiment of a connection device to FIG.
  • the inlet opening 26 of the first through-hole 24 and the outlet opening 29 of the second through-hole 25 are provided in a common connection bore 33.
  • a stepped connection bore 33 is provided.
  • the transition region 34 is formed by a bore section 35 and the outlet opening 29 of the second through-bore 25, wherein the bore section 35 is preferably larger than the outlet opening 29.
  • Radial to the bore section 35 aligned and spaced from the outlet opening 29, the cross-sectional constriction 31 is provided. This preferably opens radially into the bore section 35.
  • connection bore 33 is designed to receive the double-tubular inner heat exchanger 14.
  • the inner heat exchanger 14 has an outer tube 36, whose outer circumference bears against the bore section 35 of the connection bore 33 and extends at least partially into the connection bore 33.
  • an annular collar 37 or a flange or sleeve-like fastening element is preferably provided, which rests against an end face 38 of the connection block 22 and the inner heat exchanger 14 is positioned and fixed to the connection block 22.
  • This collar 37 can be made for hermetic sealing by a weld or solder joint or by a seal, such as an O-ring seal or the like.
  • the outer tube 36 of the inner heat exchanger 14 extends close to or to the cross-sectional constriction 31, without overlapping.
  • An inner tube 39 of the inner heat exchanger 14 protrudes from the outer tube 36 and preferably abuts against an end face 40 which is formed in the transition region 34 between the outlet opening 29 and the bore section 35.
  • This arrangement has the advantage that only one sealing point or connection point to the inner heat exchanger 14 is provided, so that in this connection device 21, the number of connections is reduced by one connection point with respect to the connection device in FIG.
  • connection device 21 has, for example, an expansion valve 45 connected downstream of the cross-sectional constriction 31 in the flow direction of the refrigerant downstream.
  • This expansion valve 45 regulates in dependence speed of the pressure forms between the high pressure and low pressure side of the mass flow.
  • a first embodiment of the expansion valve 45 is shown enlarged in Figure 4a and a partial view in Figure 4b.
  • an alternative embodiment of an expansion valve 45 is also shown enlarged.
  • the expansion valve 45 according to FIGS. 4a and 4b is provided as a so-called installation expansion valve, which may be formed from an extremely small number of components.
  • valve closure member 47 At a valve seat 36 of the cross-sectional constriction 31 and a connection distance is a valve closure member 47 at.
  • This valve closing member 47 which is for example conical, is positioned by a guide element 48 to the valve seat 46 and guided in the first through hole 24 during an opening and closing movement by the guide member 48 axially displaceable in the through hole 24.
  • the guide element 48 is preferably formed as a disk-shaped sleeve 58 and centrally receives the valve closure member 47.
  • An outer circumferential surface of the sleeve 58 engages a wall portion of the first through hole 24, so that the valve closing member 47 is guided axially displaceable.
  • a return unit 51 preferably in the form of a compression spring, is provided, which positions the valve closing member 47 in a closed position as a rest position or starting position.
  • the adjusting device 49 comprises at least one adjusting nut 50, which has recesses 52 on the outer circumference, in particular arcuate recesses 52, as shown for example in FIG. 4b.
  • a central bore 53 may be provided.
  • This bore 53 can also be used to position the adjusting nut 50 on a threaded portion 54 in the through bore 24.
  • the return device 51 engages a holder 56, which is positioned centrally to the adjusting nut 50.
  • the bore 53 in the adjusting nut 50 may also be formed as a tool holder for mounting the adjusting device 49.
  • the expansion valve 45 may consist of, for example, only four components. These are formed by the adjusting nut 50, the holder 56, the return device 51 and by the arranged on the guide member 48 valve closure member 47.
  • the guide member 48 and the valve closing member 47 may be integrally formed or consist of two parts and then firmly connected to each other.
  • FIG. 5 shows an alternative embodiment of the expansion valve 45 to FIG.
  • This embodiment differs in terms of the design of the valve closure member 47 and the guide member 48 from.
  • the components are preferably identical.
  • the valve closure member 47 is formed instead of a conical tip as a ball, which is mounted on a sleeve 58 with spring-shaped tabs 59 or legs. These spring-shaped tabs 59 abut against the bore wall of the first through-bore 24, so that an axially displaceable arrangement of the valve-closure member 47 relative to the cross-sectional constriction 31 is made possible.
  • FIG. 6 shows an alternative embodiment of a connection device 21 with an internal heat exchanger 14 which can be connected thereto.
  • This embodiment differs from that of FIG. 3 only in that a sieve element 61 is arranged between the end of the outer tube 36 arranged in the connection bore 33 and the inner tube 39.
  • This sieve element 61 is for example formed gel-shaped and has at the respective end faces sealing elements 62 and annular sealing elements 62 on. These serve on the one hand to position the sieve 61 in the correct position and on the other to a seal between the outer tube 36 and the bore portion 35 of the connection bore 33, as well as a seal between the inlet opening 26 of the first through hole 24 and the outlet opening 29 of second through-hole 25 to form.
  • This sealing element 62 may abut the end face 40 on the end face 40 according to the embodiment of the connection device 21 in FIG. 3 or in a further step of the connection bore 33, as shown in FIG.
  • connection bore 33 is independent of the use of an expansion valve 45 in the connection device 31.
  • the diameter of the cross-sectional constriction 31 and its length and / or its geometry can be adapted to the respective requirement for expansion of the refrigerant at this throttle point.
  • the cross-sectional constriction 31 of the through-hole 24 is formed as a connection channel or connection passage.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Temperature-Responsive Valves (AREA)

Abstract

L'invention concerne un dispositif de raccordement pour un échangeur de chaleur intérieur (14) comprenant un bloc de raccordement (21) qui présente un premier et un deuxième alésage de passage (24, 25), une ouverture d'entrée (26) du premier alésage de passage (24) pouvant être reliée du côté haute pression à un raccord de l'échangeur de chaleur intérieur (14) et une ouverture de sortie (27) du premier alésage de passage (24) pouvant être relié à une entrée d'un évaporateur (16) et une ouverture d'entrée (28) du deuxième alésage de passage (25) pouvant être reliée à une sortie de l'évaporateur (16) et une ouverture de sortie (28) du deuxième alésage de passage (25) pouvant être reliée du côté basse pression à un raccord de l'échangeur de chaleur intérieur (14), un rétrécissement (31) de la section transversale du premier alésage de passage (24), qui agit comme un goulot d'étranglement, étant réalisé dans le bloc de raccordement (22) entre l'ouverture d'entrée (26) et l'ouverture de sortie (27).
EP09778667A 2008-10-21 2009-09-23 Dispositif de raccordement pour un échangeur de chaleur intérieur Withdrawn EP2338019A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008052550A DE102008052550A1 (de) 2008-10-21 2008-10-21 Anschlusseinrichtung für einen inneren Wärmetauscher
PCT/EP2009/006864 WO2010046009A1 (fr) 2008-10-21 2009-09-23 Dispositif de raccordement pour un échangeur de chaleur intérieur

Publications (1)

Publication Number Publication Date
EP2338019A1 true EP2338019A1 (fr) 2011-06-29

Family

ID=41650352

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09778667A Withdrawn EP2338019A1 (fr) 2008-10-21 2009-09-23 Dispositif de raccordement pour un échangeur de chaleur intérieur

Country Status (5)

Country Link
US (1) US20110271710A1 (fr)
EP (1) EP2338019A1 (fr)
CN (1) CN102203537B (fr)
DE (1) DE102008052550A1 (fr)
WO (1) WO2010046009A1 (fr)

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Publication number Priority date Publication date Assignee Title
KR101211637B1 (ko) * 2011-12-12 2012-12-18 주식회사 화승알앤에이 다방향 커넥터를 구비하는 이중관 열교환기 및 이를 구비하는 차량용 냉방 장치
CN112874263B (zh) * 2021-02-26 2023-05-09 常州市盛士达汽车空调有限公司 内导式热传递同轴管

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Also Published As

Publication number Publication date
CN102203537A (zh) 2011-09-28
DE102008052550A1 (de) 2010-04-22
US20110271710A1 (en) 2011-11-10
WO2010046009A1 (fr) 2010-04-29
CN102203537B (zh) 2015-06-17

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