WO1998050745A1 - Zweiflutiger und in luftrichtung einreihiger hartverlöteter flachrohrverdampfer für eine kraftfahrzeugklimaanlage - Google Patents
Zweiflutiger und in luftrichtung einreihiger hartverlöteter flachrohrverdampfer für eine kraftfahrzeugklimaanlage Download PDFInfo
- Publication number
- WO1998050745A1 WO1998050745A1 PCT/EP1998/002634 EP9802634W WO9850745A1 WO 1998050745 A1 WO1998050745 A1 WO 1998050745A1 EP 9802634 W EP9802634 W EP 9802634W WO 9850745 A1 WO9850745 A1 WO 9850745A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- flat tube
- tube evaporator
- evaporator according
- flat
- tubes
- Prior art date
Links
Classifications
-
- 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
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
- F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00321—Heat exchangers for air-conditioning devices
- B60H1/00335—Heat exchangers for air-conditioning devices of the gas-air type
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H1/3204—Cooling devices using compression
- B60H1/3227—Cooling devices using compression characterised by the arrangement or the type of heat exchanger, e.g. condenser, evaporator
-
- 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
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
Definitions
- the invention relates to a double-flow brazed flat tube evaporator made of aluminum or an aluminum alloy for a motor vehicle air conditioning system with the features of the preamble of claim 1.
- a double-flow flat tube evaporator is known from DE-195 15 526 Cl in addition to other more than two-flow embodiments .
- the depth of the evaporator is identical to the corresponding width dimension of the flat tube.
- the width dimension of the flat tube can, however, also be somewhat smaller, in particular if one includes a corresponding front overhang of the ribbing by the zigzag lamellas.
- the invention is based on the knowledge that this assumption is based on a prejudice.
- the invention is based on the knowledge that even with otherwise constant parameters of known generic flat tube evaporators, a reduction in the overall depth is at least partially compensated for by increasing the efficiency of the distribution device. With a reduced overall depth, the refrigerant only needs to be distributed to a smaller number of chambers of the flat tubes per inlet chamber fed by the distribution channel on the inlet side.
- the invention describes a way rather than the way of increasing the number of floods the double flow to obtain an optimization by reducing the depth.
- the invention has for its object to increase the efficiency of a generic double-flow flat tube evaporator in a structurally particularly simple manner.
- the structurally particularly simple design of the double-flow flat tube evaporator according to the invention can already be recognized from the fact that the increase in the relative efficiency enables a significant saving in installation depth, particularly in the small installation space of motor vehicles, without having to deteriorate the thermal output of the evaporator. This also saves building material in the direction of the building depth, and longitudinal transverse walls due to multiple flooding become unnecessary.
- EP-A2-0 414 433 does not show, like the flat tube evaporator according to the invention, a single-row design in the air direction, which determines the structural depth, but an in Air direction double-row design (so-called duplex arrangement) also of an evaporator (column 6, lines 34-37) with two separate heat exchanger blocks also using flat tubes, which are arranged one behind the other in the air direction.
- This arrangement is based on the concept that the heat output, in contrast to the invention, is obtained not by reducing but by increasing the installation depth. Even if the dimensions in the individual heat exchanger block of this duplex arrangement overlap with the combination of values according to the invention, the combination according to the invention cannot be excited in a flat tube evaporator with a single-row design.
- DE-Al-30 20 424 relates generally to a heat exchanger constructed with flat tubes, which is developed under the conditions of an engine cooler of motor vehicles.
- this prior publication assumes an engine cooler with a construction depth of 32 to 35 mm and, in another combination of values, reduces it to 23 mm and less. It is not possible to transfer these conditions of a heat exchanger such as a water cooler in motor vehicles to a flat tube evaporator in motor vehicles. This is already clear from the fact that the conventional flat tube evaporators have never known an installation depth smaller than 60 mm.
- FIG. 1 shows a perspective and partially broken-open representation of an example of a double-flow flat tube evaporator, to which the dimensions of the invention relate;
- FIG. 2 shows a plan view of the tube plate of the collector serving as a distributor from the interior thereof, specifically with reference to an inlet chamber in a group of flat tubes;
- FIG. 3 shows a cross section through the block of the flat tubes of the evaporator according to FIG. 1 and FIG. 2, which is ribbed with zigzag ribs;
- FIG. 6 shows a diagram with the overall depth B of the evaporator as the abscissa, the flow cross-sectional area F for the refrigerant as the ordinate and the space LH as the parameter curve family,
- Fig. 7 is a diagram with the depth B as the abscissa, the heat exchanger efficiency ⁇ as the ordinate and Slat division T as a family of curves.
- the flat tube evaporator shown in FIGS. 1 to 3 consists of all of its parts made of aluminum or an aluminum alloy and is brazed on its parts.
- the flat tubes 2 each have parallel flat sides 4 of the same type and front ends 6, which have a streamlined profile here without restricting the generality, but can also be designed differently rounded or even angular or obtuse at right angles to the flat sides.
- chambers 8 are partitioned by intermediate walls 10 as continuous channels.
- the number of substantially equally sized chambers considered in the context of the invention is preferably between 5 and 15, depending on the actual structural depth.
- the flat tubes 2 are ribbed with each other at a constant mutual distance LH as a block via sandwiched zigzag lamellae, which are preferably flush on the air inlet side with the relevant end faces 6 and, for better water drainage on the air outlet side, are preferably somewhat opposite the flat side 6 there according to the drawing in FIG 3 survive.
- the overall depth B is specified as the distance between the two front fronts of the zigzag fins 12 in the inflow direction LR of the outside air, the upstream side, as mentioned, the front end being flush with the relevant end face 6 of the flat tubes or flush in the transverse direction of the inflow direction LR, while on the outflow side the end face protrudes beyond the adjacent end faces L of the flat tubes 2.
- the mutual distance between adjacent flat sides 4 of a pair of adjacent flat tubes 2 is designated LH because it is identical to the so-called fin height of the respective zigzag fin.
- Each flat tube 2 has a tube thickness d measured between its two opposite flat sides 4 and a wall thickness w between each chamber 8 and the outer one Flat side 4 of the relevant flat tube 2.
- Each zigzag lamella 12 also has a pitch T, which describes the distance between adjacent, similar phases of the zigzag lamella, such as the distance between adjacent vertices on one side of the zigzag lamella in question.
- the external action on the flat tubes 2 serving as heat exchange tubes of the evaporator is carried out by outside air in the motor vehicle according to the arrow LR (air direction) in FIGS. 1 and 3.
- each flat tube 2 is double flow according to the reversing arrow UP in Fig. 1.
- For the flow reversal at one end of the respective flat tubes in the block serve individual end caps 14 as shown in FIG. 1, but their function of a common deflection box or other flow deflection member can be taken over.
- the refrigerant is fed into the evaporator in accordance with the inlet arrow Z in FIG. 1 through a connecting piece 16 on the end face of a header box 18 comprising a tube sheet 20 and a lid 22.
- the ends of the flat tubes 2 facing away from the end caps 14 are in slots or outer and / and or inner collar of the tube sheet 20 so that they can communicate with the interior of the collector 18.
- the inlet-side connecting piece 16 of the collector 18 merges into a distributor pipe 24 of a distributor, which is closed at its free end and has an outlet opening 26 on its circumference, each with an inlet chamber 28 of a group of more than one in the tube plate 20 inserted flat tube 2 communicates.
- the number of flat tubes assigned to an inlet chamber can change depending on the distance of the respective outlet opening 26 as a function of the connecting piece 16, but this is not realized in FIG. 2, where two flat tubes each communicate with an inlet chamber 28 without restricting the generality. Practically comes in connection with According to the invention, in particular the number of only one flat tube 2 per entry chamber up to five flat tubes per entry chamber is in question, as mentioned both with a constant number and with adapted variability between the limits 1 and 5 mentioned.
- the second flood of all flat tubes in the flow direction of the refrigerant communicates with a common outlet chamber 30 in the collector 18, which extends over its entire length and is separated from the individual inlet chambers 28 in terms of flow by a longitudinal partition wall 32 which also extends along the collector 18 in this.
- the entry chambers 28, for their part, are at least largely or entirely separated from one another by transverse walls 34.
- the transverse walls 34 extend at right angles from that side of the longitudinal partition wall 32 which faces away from the exit chamber 30.
- the outlet chamber 30 communicates with an external flow outlet 36 of the refrigerant from the evaporator.
- the flow outlet can also be designed as an outer connection connection according to the drawing in FIG. 1.
- Flow entry and flow exit are of course also possible for any other possible design, including one in which the two exits are provided on opposite end faces of the collector 18.
- the input-side and the output-side collecting devices are formed by separate collectors, so that the longitudinal transverse wall 32 is then omitted for each of these separate collectors.
- the heat exchanger index (kx A A ) is plotted against the overall depth (B) of the flat tube evaporator.
- the heat exchanger index is formed from the Product of the heat transfer coefficient (k) and the total outer air contact area (A A ) and has the unit watt / Kelvin.
- the overall depth is plotted in millimeters.
- Fig. 4 illustrates the surprising effect of the invention that with a suitable choice of the pipe thickness (d) and the space occupied by the lamella (LH), the heat exchanger index (kx A A ) can still be kept constant by halving the overall depth (B).
- this performance equality is achieved with a halved overall depth (B), since the lack of inner and outer heat transfer surface due to an improved refrigerant distribution in the flat tubes of reduced overall depth (B) and due to significantly higher heat transfer coefficients is compensated on the inside as well as on the outside.
- the construction depth is halved when the evaporator is used in motor vehicle air conditioning systems with considerable advantages in terms of installation space and weight.
- the flow area (F) is also of crucial importance.
- the internal heat transfer coefficient must be very high on the one hand, which is achieved by a high flow velocity and a small flow cross-section (F), and on the other hand the refrigerant-side pressure loss must not be too great due to an excessively high flow velocity, otherwise the effective temperature difference between the refrigerant and the incoming ambient air is reduced too much.
- a flow area (F) of 400-600 mm 2 is required for the medium performance range of the motor vehicle air conditioning systems. This minimum flow area (F) can be effectively achieved by reducing the overall depth (B) according to FIG. 6 by increasing the number of tubes and thus by reducing the space (LH) occupied by the lamella.
- Fig. 7 shows the influence of the fin division (T) on the heat exchanger efficiency ( ⁇ ), which is plotted as the ordinate over the structural depth (B) as the abscissa.
- the influence of the lamella division is considerably greater at small depths than at the usual large depths of more than 60 mm.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Air-Conditioning For Vehicles (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/214,539 US6161616A (en) | 1997-05-07 | 1998-05-05 | Hard-soldered flat tube evaporator with a dual flow and one row in the air flow direction for a motor vehicle air conditioning system |
EP98924277A EP0910779A1 (de) | 1997-05-07 | 1998-05-05 | Zweiflutiger und in luftrichtung einreihiger hartverlöteter flachrohrverdampfer für eine kraftfahrzeugklimaanlage |
BR9804883A BR9804883A (pt) | 1997-05-07 | 1998-05-05 | Evaporador de tubos chatos |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19719252A DE19719252C2 (de) | 1997-05-07 | 1997-05-07 | Zweiflutiger und in Luftrichtung einreihiger hartverlöteter Flachrohrverdampfer für eine Kraftfahrzeugklimaanlage |
DE19719252.1 | 1997-05-07 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1998050745A1 true WO1998050745A1 (de) | 1998-11-12 |
Family
ID=7828861
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP1998/002634 WO1998050745A1 (de) | 1997-05-07 | 1998-05-05 | Zweiflutiger und in luftrichtung einreihiger hartverlöteter flachrohrverdampfer für eine kraftfahrzeugklimaanlage |
Country Status (6)
Country | Link |
---|---|
US (1) | US6161616A (de) |
EP (1) | EP0910779A1 (de) |
CN (1) | CN1225716A (de) |
BR (1) | BR9804883A (de) |
DE (1) | DE19719252C2 (de) |
WO (1) | WO1998050745A1 (de) |
Cited By (1)
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KR100821823B1 (ko) * | 2000-06-26 | 2008-04-11 | 쇼와 덴코 가부시키가이샤 | 증발기 |
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JP2018054256A (ja) * | 2016-09-30 | 2018-04-05 | ダイキン工業株式会社 | 熱交換ユニット |
IL248304B (en) * | 2016-10-10 | 2021-07-29 | Magen Eco Energy A C S Ltd | Heat exchanger and its module |
SI3339792T1 (sl) | 2016-12-20 | 2020-08-31 | Alfa Laval Corporate Ab | Zbiralnik za toplotni izmenjevalnik in toplotni izmenjevalnik |
DE112018001417T5 (de) * | 2017-03-17 | 2020-04-09 | Valeo Systèmes Thermiques | Verdampfer eines Klimakreislaufs, insbesondere für ein Kraftfahrzeug |
EP3809087B1 (de) * | 2019-10-18 | 2022-04-27 | Hamilton Sundstrand Corporation | Wärmetauscher |
US20210381730A1 (en) * | 2020-06-09 | 2021-12-09 | Mahle International Gmbh | Heat exchanger |
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DE3020424A1 (de) | 1980-04-30 | 1981-11-05 | Nippondenso Co., Ltd., Kariya, Aichi | Waermetauscher mit gewellten rippen |
EP0414433A2 (de) | 1989-08-23 | 1991-02-27 | Showa Aluminum Kabushiki Kaisha | Duplex-Wärmetauscher |
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EP0566899A1 (de) | 1992-04-16 | 1993-10-27 | Behr GmbH & Co. | Wärmetauscher, insbesondere Verdampfer |
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DE19515526C1 (de) | 1995-04-27 | 1996-05-23 | Thermal Werke Beteiligungen Gm | Flachrohrwärmetauscher mit mindestens zwei Fluten für Kraftfahrzeuge |
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US3605882A (en) * | 1968-07-02 | 1971-09-20 | Ass Eng Ltd | Heat exchangers |
JP2936775B2 (ja) * | 1991-04-05 | 1999-08-23 | 株式会社デンソー | 熱交換器 |
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JP3358250B2 (ja) * | 1992-10-21 | 2002-12-16 | 株式会社デンソー | 冷媒蒸発器 |
US5431217A (en) * | 1993-11-09 | 1995-07-11 | General Motors Corporation | Heat exchanger evaporator |
-
1997
- 1997-05-07 DE DE19719252A patent/DE19719252C2/de not_active Revoked
-
1998
- 1998-05-05 US US09/214,539 patent/US6161616A/en not_active Expired - Lifetime
- 1998-05-05 WO PCT/EP1998/002634 patent/WO1998050745A1/de not_active Application Discontinuation
- 1998-05-05 CN CN98800597A patent/CN1225716A/zh active Pending
- 1998-05-05 EP EP98924277A patent/EP0910779A1/de not_active Withdrawn
- 1998-05-05 BR BR9804883A patent/BR9804883A/pt not_active Application Discontinuation
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DE2506631A1 (de) * | 1974-04-25 | 1975-11-13 | Chausson Usines Sa | Einreihiges waermeaustauscherbuendel |
DE3020424A1 (de) | 1980-04-30 | 1981-11-05 | Nippondenso Co., Ltd., Kariya, Aichi | Waermetauscher mit gewellten rippen |
US5076354A (en) * | 1989-04-26 | 1991-12-31 | Diesel Kiki Co., Ltd. | Multiflow type condenser for car air conditioner |
EP0414433A2 (de) | 1989-08-23 | 1991-02-27 | Showa Aluminum Kabushiki Kaisha | Duplex-Wärmetauscher |
EP0566899A1 (de) | 1992-04-16 | 1993-10-27 | Behr GmbH & Co. | Wärmetauscher, insbesondere Verdampfer |
EP0710811A2 (de) * | 1994-11-04 | 1996-05-08 | Nippondenso Co., Ltd. | Wellrippen-Wärmetauscher |
DE19515526C1 (de) | 1995-04-27 | 1996-05-23 | Thermal Werke Beteiligungen Gm | Flachrohrwärmetauscher mit mindestens zwei Fluten für Kraftfahrzeuge |
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KR100821823B1 (ko) * | 2000-06-26 | 2008-04-11 | 쇼와 덴코 가부시키가이샤 | 증발기 |
Also Published As
Publication number | Publication date |
---|---|
DE19719252C2 (de) | 2002-10-31 |
US6161616A (en) | 2000-12-19 |
DE19719252A1 (de) | 1998-11-12 |
EP0910779A1 (de) | 1999-04-28 |
CN1225716A (zh) | 1999-08-11 |
BR9804883A (pt) | 1999-08-24 |
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