EP0520309A1 - Evaporateur pour un appareil frigorifique à compresseur - Google Patents

Evaporateur pour un appareil frigorifique à compresseur Download PDF

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Publication number
EP0520309A1
EP0520309A1 EP92110195A EP92110195A EP0520309A1 EP 0520309 A1 EP0520309 A1 EP 0520309A1 EP 92110195 A EP92110195 A EP 92110195A EP 92110195 A EP92110195 A EP 92110195A EP 0520309 A1 EP0520309 A1 EP 0520309A1
Authority
EP
European Patent Office
Prior art keywords
tube
evaporator
guide tube
section
coolant
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
EP92110195A
Other languages
German (de)
English (en)
Other versions
EP0520309B1 (fr
Inventor
Dieter Bitter
Eberhard Bornkessel
Helmut Gehrke
Herbert Stember
Horst Schnabel
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.)
Krupp VDM GmbH
Original Assignee
Krupp VDM GmbH
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 Krupp VDM GmbH filed Critical Krupp VDM GmbH
Priority to EP94113040A priority Critical patent/EP0629824B1/fr
Publication of EP0520309A1 publication Critical patent/EP0520309A1/fr
Application granted granted Critical
Publication of EP0520309B1 publication Critical patent/EP0520309B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F25B39/022—Evaporators with plate-like or laminated elements
    • F25B39/024—Evaporators with plate-like or laminated elements with elements constructed in the shape of a hollow panel
    • 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
    • F25B41/37—Capillary tubes
    • 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—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/052—Compression system with heat exchange between particular parts of the system between the capillary tube and another part of the refrigeration cycle
    • 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—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the cycle
    • 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
    • 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

Definitions

  • the invention relates to an evaporator for a compressor cooling device, the evaporator made from a two-layer evaporator board having a coolant channel running between the layers in a meandering manner, in the inlet area of which a small diameter coolant supply line, which acts as a throttle and can be connected to the pressure side of the compressor in the coolant circuit, opens out.
  • a length section of the coolant supply line lying inside the outlet area and inside the suction pipe, the wall of which breaks through the coolant supply line, the coolant supply line also continuing over a substantial part of its length is designed as a throttle capillary tube with a capillary flow cross-section.
  • Evaporators of this type are known, for example, from DE-AS 12 42 646 and are widely used in household refrigerators.
  • the invention is now concerned with the coolant circuit, in particular with the coolant inlet into the evaporator, which takes place in the known cooling devices via a long throttle capillary tube corresponding to the required throttling effect, which according to the prior art is the coolant supply line.
  • This throttle-capillary tube is routed regularly into the inlet area of the coolant channel through a corresponding inlet connection and, in the case of the so-called single-tube connection, also lies in the outlet area of the coolant channel with a section of its length.
  • the coolant channel itself runs in a meandering manner in an originally flat evaporator board, which was made from two aluminum sheets welded together, for example by the so-called roll bond process, and then formed into the refrigerator compartment and closes on the outlet side with an aluminum pipe socket, the so-called intake pipe, which is inserted pressure-tight into the channel end.
  • the throttle capillary tube is so long today in the majority of the refrigerator types manufactured that it can only be accommodated in the inlet area of the coolant channel of the evaporator to a small extent and for the most part is often outside the evaporator with a partial length of several meters. This part length is regularly wound up like a capillary ring to form a capillary curl.
  • a first production simplification has already been achieved by using throttle capillary tubes for evaporators of various types, all of which have an outer diameter of, for example, 1.9 mm, and with inner diameters of, for example, 0.55 to 1.05 mm, which allow a type-specific adaptation.
  • at least connections of the throttle capillary tube or openings can be designed uniformly for this.
  • the dragging of the capillary curl in the final stages of production continues to be a hindrance, just as the capillary curl unfavorably determines the packing density of the evaporators during transport to the cooling device manufacturers.
  • the object of the invention is to simplify the variety in the manufacture of the evaporators caused by the numerous types of cooling devices and to take into account the consequences of using new coolants of lower viscosity.
  • the guide tube is provided with a slightly larger inner diameter than the outer diameter of the throttle capillary tube and a substantially smaller outer diameter than that of the inner diameter of the suction tube, that the throttle capillary tube is inserted into the guide tube from the outside and the compressor-side end area of the inner jacket of the guide tube is connected in a pressure-tight manner to the assigned area of the outer jacket of the throttle capillary tube within a first length section of the coolant supply line and ends in the guide tube, that the guide tube forms a second length section of the coolant supply line with a cross section which is enlarged compared to the capillary flow cross-section, and that the interior space of the guide tube determined by the expanded second length section is connected to the inlet region of the coolant channel.
  • a gap the size of a soldering fit is regularly set, the filling of which is used to connect the tubes when soldering.
  • the invention enables extensive standardization of the evaporator production and basically allows the separate production of the still throttle-capillary tube-free evaporator and the associated capillary tubes up to a final assembly in which the capillary tube is installed in the guide tube, that is, inserted as far as possible into or through this and finally being soldered to this.
  • the length, type and installation of the guide tubes in the evaporator boards can be reduced to a small number of construction variants, thus simplifying the production process.
  • FIG. 2 Another embodiment of the invention is set out in claim 2, in which the guide tube with a soldering gap fit on the evaporator side is attached to a further capillary tube and is connected to the latter in a pressure-tight manner, the further capillary tube being the connection between the interior of the second length section with the inlet area and a third, on the evaporator side forms the last longitudinal section of the coolant supply line.
  • the throttle capillary forms the further capillary tube, which ends near its wall opening in the guide tube attached to the evaporator, in the other side of which the throttle capillary tube is inserted. Establishing this connection can be the last manufacturing step at the evaporator manufacturer or a manufacturing step at the refrigerator manufacturer.
  • a coolant supply line can result which has a total of two length sections of different inner diameters. It is irrelevant that the relatively short last section of the coolant supply line can only exert a slight throttling effect, but instead enables the coolant to be introduced into the coolant channel in a manner which is favorable for flow.
  • the guide tube made of copper is inserted into the wall opening of the intermediate tube and is tightly welded or soldered to the intermediate tube wall. It should be mentioned that in the case of evaporators, an intermediate tube made of copper, which is bent in an S-shape in its central region, is often welded or soldered to the straight intake manifold, with the wall opening in the intake manifold-side first bend and also approximately in the extension of the intake manifold axis.
  • the embodiment of the invention according to claim 6 provides that a section of the guide tube lying in the coolant channel is longer than a section of the capillary tube lying in the coolant channel. This in turn leads to the above-mentioned favorable design of the internal outflow conditions.
  • the embodiment according to claim 7 provides that the guide tube has a constriction as an inner stop for fixing the evaporator-side end of the throttle capillary tube. This can lie behind the opening of the intermediate pipe and thus within the area formed by the intermediate pipe, the suction pipe and the coolant channel, as seen in the inflow direction.
  • the invention makes it possible to easily adapt to different design requirements of the cooling device manufacturers.
  • the inlet area of the coolant channel 2 is fed via a throttle capillary tube 7.
  • This throttle capillary tube 7, which is regularly made of copper, is inserted in a guide tube 8, also made of copper, which is connected to an inlet tube 9 made of aluminum by Cu / Al soldering and is held indirectly by the evaporator plate 1 by the inlet tube 9.
  • FIG. 1 shows a flat evaporator, the coolant channel 2 of which is partially indicated by a broken line.
  • the partly in the intermediate tube 11, the guide tube 8 penetrates the tube wall of the intermediate tube 11 in the S-shaped bend 14 and ends in the suction tube 10, which is held in the evaporator board via a soldered connection 16.
  • a solder joint 17 holds the throttle capillary tube 7 and a further solder joint 18 holds the further capillary tube 12 in the guide tube 8.
  • the further capillary tube 12 is guided up to and beyond an inlet region 3 and outlet region 4 narrowing point 19 in the channel system.
  • the constriction 19 forms the internal fixation of the coolant supply line, while the external fixation takes place in an opening 20 in the tube wall of the intermediate tube 11, into which the guide tube 8 is soldered.
  • a suction pipe 10 with a substantially larger inner diameter than the inlet pipe 9 serves for the coolant outlet.
  • a soldered intermediate pipe made of copper connects to the suction pipe 10 made of aluminum.
  • the suction tube 10 and in the intermediate tube 11 there is another capillary tube 12, which in an approximately S-shaped curvature 14 of the intermediate tube 11 leads through the wall of the intermediate tube to the outside and is inserted into the end of the guide tube 8 on the evaporator side.
  • the guide tube 8 is held on the intermediate tube 11 via an element 13.
  • the throttle capillary 7 is inserted into the other end of the guide tube 8 at a distance from the further capillary tube 12.
  • the throttle capillary tube 7 and the further throttle capillary 12 are connected to the guide tube 8 by soldering. Suitable measures must be taken when soldering so that the capillaries are not accidentally closed by solder.
  • the intake manifold connections shown in FIGS. 2 and 3 are first produced, but still without the throttle capillary tube 7, and then attached to the evaporator board 1.
  • the choke capillary tube 7 is only installed when the evaporator is otherwise finished.
  • the structural unit shown without throttle - capillary tube represents a standard intake manifold connection which can be used for many types of evaporator and in which the further capillary tube 12 has, for example, an inner diameter of 1.1 mm.
  • This standard intake manifold connection is now supplemented with a wide variety of throttles - capillary tubes 7, which correspond only to the outer capillary tube 12, namely with throttle - capillary tubes 7 having a more or less small inner diameter and different lengths.
  • a capillary curl 15 is indicated and shown how particularly long capillary tubes 7 are spatially compressed. 3 shows that the coolant supply line here is composed of the large length section L1, the second length section L2, a short area in the guide tube 8 and the third length section of the further capillary tube 12.
  • FIGS. 4 and 5 are of fundamentally simpler construction, in which the guide tube 8 itself is guided to the narrow point 19 and beyond it into the inlet area 3.
  • both the throttle capillary tube 7 and the guide tube 8 are partially in the inlet area 3 of the coolant channel 2, but the corresponding section of the throttle capillary tube 7 is shorter than the corresponding section of the guide tube 8. This difference forms the second length section here L2 of the coolant supply line.
  • the outer end of the guide tube 8 is expanded to form a funnel 21 and the guide tube 8 further has a constriction 22 as an inner stop for the throttle-capillary tube 7.
  • Fig. 5 is provided on the evaporator-side end of the intermediate tube 11 thorning 23, into which the suction tube is inserted with a solder fit.
  • a particularly reliable Cu / Al solder connection can be produced in this way.

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)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Compressor (AREA)
  • Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)
EP92110195A 1991-06-22 1992-06-17 Evaporateur pour un appareil frigorifique à compresseur Expired - Lifetime EP0520309B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP94113040A EP0629824B1 (fr) 1991-06-22 1992-06-17 Evaporateur pour un appareil frigorifique à compresseur

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4120651 1991-06-22
DE4120651A DE4120651A1 (de) 1991-06-22 1991-06-22 Verdampfer fuer ein kompressor-kuehlgeraet

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP94113040.3 Division-Into 1992-06-17

Publications (2)

Publication Number Publication Date
EP0520309A1 true EP0520309A1 (fr) 1992-12-30
EP0520309B1 EP0520309B1 (fr) 1996-01-10

Family

ID=6434526

Family Applications (2)

Application Number Title Priority Date Filing Date
EP92110195A Expired - Lifetime EP0520309B1 (fr) 1991-06-22 1992-06-17 Evaporateur pour un appareil frigorifique à compresseur
EP94113040A Expired - Lifetime EP0629824B1 (fr) 1991-06-22 1992-06-17 Evaporateur pour un appareil frigorifique à compresseur

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP94113040A Expired - Lifetime EP0629824B1 (fr) 1991-06-22 1992-06-17 Evaporateur pour un appareil frigorifique à compresseur

Country Status (11)

Country Link
US (1) US5269158A (fr)
EP (2) EP0520309B1 (fr)
JP (1) JPH05180535A (fr)
BR (1) BR9202354A (fr)
CA (1) CA2071761A1 (fr)
DE (4) DE9116265U1 (fr)
DK (2) DK0520309T3 (fr)
ES (2) ES2105444T3 (fr)
FI (1) FI922881A (fr)
NO (1) NO176456C (fr)
TR (1) TR26063A (fr)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6110168A (en) * 1993-02-10 2000-08-29 Radiant Medical, Inc. Method and apparatus for controlling a patient's body temperature by in situ blood temperature modifications
JP3540075B2 (ja) † 1995-12-11 2004-07-07 松下電器産業株式会社 空気調和機
IT1288846B1 (it) * 1996-02-07 1998-09-25 Cga Comp Gen Allumino Spa Assemblato per scambio calore e rispettivo processo ed impianto di produzione
SE506059C2 (sv) * 1996-02-28 1997-11-03 Electrolux Ab Anordning vid en förångare
US5765393A (en) * 1997-05-28 1998-06-16 White Consolidated Industries, Inc. Capillary tube incorporated into last pass of condenser
DE29716572U1 (de) * 1997-09-15 1997-12-04 Liebherr Hausgeraete Kühlgerät mit einem Normalkühlraum und einem Tiefkühlfach
US6338727B1 (en) 1998-08-13 2002-01-15 Alsius Corporation Indwelling heat exchange catheter and method of using same
DE19840412A1 (de) * 1998-09-04 2000-03-09 Bsh Bosch Siemens Hausgeraete Verdampferplatine
DE19900701A1 (de) * 1999-01-11 2000-07-13 Vdm Evidal Gmbh Kapillar-Saugrohrsystem für Verdampfersysteme bzw. Kältekreislaufsysteme
DE19907183A1 (de) * 1999-02-19 2000-08-24 Bsh Bosch Siemens Hausgeraete Verdampferplatine
DE10055915A1 (de) * 2000-11-10 2002-05-23 Bsh Bosch Siemens Hausgeraete Kältemittelkreislauf für eine Kältemaschine
DE10360899A1 (de) * 2003-12-23 2005-07-21 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät mit ultraschallverschweißtem Saug- und Drosselrohr
DE202004007836U1 (de) * 2004-05-14 2004-07-15 Dometic S.A.R.L. Kühlsystem
GB2418478A (en) * 2004-09-24 2006-03-29 Ti Group Automotive Sys Ltd A heat exchanger
DE102011006260A1 (de) * 2011-03-28 2012-10-04 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät
DE102013021350A1 (de) * 2013-12-04 2015-06-11 Liebherr-Hausgeräte Lienz Gmbh Kühl- und/oder Gefriergerät
CN109869973B (zh) * 2017-12-05 2022-03-29 松下电器产业株式会社 冷冻冷藏库

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2760346A (en) * 1953-10-01 1956-08-28 Gen Motors Corp Refrigerating apparatus of dissimilar metals
US2776550A (en) * 1952-10-21 1957-01-08 Gen Electric Capillary adaptor
DE1242646B (de) * 1961-02-08 1967-06-22 Schmoele Metall R & G Kaelteeinrichtung fuer Kuehlschraenke
US4449853A (en) * 1983-04-11 1984-05-22 Mennella Robert J Flexible sleeve elbow for gas service lines

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2956421A (en) * 1957-04-04 1960-10-18 Borg Warner Capillary refrigerating systems
US2979924A (en) * 1958-03-17 1961-04-18 Gen Electric Refrigerating system composed of dissimilar metals
US2959027A (en) * 1958-11-28 1960-11-08 James O Ewing Combination evaporator-condenser assembly with concentric tubular construction
US3172272A (en) * 1962-06-19 1965-03-09 Westinghouse Electric Corp Air conditioning apparatus
US3531947A (en) * 1968-10-29 1970-10-06 Gen Electric Refrigeration system including refrigerant noise suppression
DE2231538A1 (de) * 1971-07-03 1973-01-11 Zanussi A Spa Industrie Verbesserung an kuehlmoebelverdampfern und herstellungsverfahren dazu
US4086782A (en) * 1975-04-16 1978-05-02 Aktiebolaget Electrolux Noise reduction arrangement for a compressor type refrigerator
JPS6016277A (ja) * 1984-06-13 1985-01-28 松下冷機株式会社 板状冷却器
US4715187A (en) * 1986-09-29 1987-12-29 Vacuum Barrier Corporation Controlled cryogenic liquid delivery

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2776550A (en) * 1952-10-21 1957-01-08 Gen Electric Capillary adaptor
US2760346A (en) * 1953-10-01 1956-08-28 Gen Motors Corp Refrigerating apparatus of dissimilar metals
DE1242646B (de) * 1961-02-08 1967-06-22 Schmoele Metall R & G Kaelteeinrichtung fuer Kuehlschraenke
US4449853A (en) * 1983-04-11 1984-05-22 Mennella Robert J Flexible sleeve elbow for gas service lines

Also Published As

Publication number Publication date
DK0520309T3 (da) 1996-06-10
DE4120651A1 (de) 1993-01-14
CA2071761A1 (fr) 1992-12-23
DE9116265U1 (fr) 1992-09-03
DE59204980D1 (de) 1996-02-22
JPH05180535A (ja) 1993-07-23
DK0629824T3 (da) 1998-02-23
NO176456B (no) 1994-12-27
FI922881A0 (fi) 1992-06-18
US5269158A (en) 1993-12-14
TR26063A (tr) 1994-12-15
EP0520309B1 (fr) 1996-01-10
NO922427D0 (no) 1992-06-19
EP0629824B1 (fr) 1997-07-30
EP0629824A1 (fr) 1994-12-21
ES2105444T3 (es) 1997-10-16
NO922427L (no) 1992-12-23
FI922881A (fi) 1992-12-23
BR9202354A (pt) 1993-01-26
DE59208763D1 (de) 1997-09-04
NO176456C (no) 1995-04-05
ES2084875T3 (es) 1996-05-16

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