GB2250336A - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
GB2250336A
GB2250336A GB9122075A GB9122075A GB2250336A GB 2250336 A GB2250336 A GB 2250336A GB 9122075 A GB9122075 A GB 9122075A GB 9122075 A GB9122075 A GB 9122075A GB 2250336 A GB2250336 A GB 2250336A
Authority
GB
United Kingdom
Prior art keywords
pipe
heat exchanger
tube
perforated pipe
flow paths
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
GB9122075A
Other versions
GB9122075D0 (en
GB2250336B (en
Inventor
Yoshiyuki Yamauchi
Masahiro Simoya
Etuo Hasegawa
Yoshio Suzuki
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.)
Denso Corp
Original Assignee
Nippondenso Co Ltd
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 JP27813090A priority Critical patent/JPH04155194A/en
Application filed by Nippondenso Co Ltd filed Critical Nippondenso Co Ltd
Publication of GB9122075D0 publication Critical patent/GB9122075D0/en
Publication of GB2250336A publication Critical patent/GB2250336A/en
Application granted granted Critical
Publication of GB2250336B publication Critical patent/GB2250336B/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02Header boxes; End plates
    • F28F9/026Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027Header 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
    • F28F9/0273Header 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

Abstract

A heat exchanger (1) has a plurality of tube elements (7) for exchanging heat from an external gas to an internal fluid and has the same number of inlet chambers (5) as tube elements (7) in order to individually supply internal fluid to the tube elements. An inlet pipe (13) is connected to an elongate perforated pipe (9) which runs through the inlet chambers (5). The inside of the pipe (9) is divided into a plurality of flow paths (10) which discharge internal fluid through holes (14) into respective inlet chambers (5). By using the pipe (9), individual supplies of internal fluid to the tube elements (7) are provided in a compact and simple manner. Uniform distribution of internal fluid to the tube elements (7) ensures efficient working of the heat exchanger. <IMAGE>

Description

HEAT EXCHANGER The present invention relates to a heat exchanger such as a coolant evaporator, a coolant condenser, a heater core, a radiator or an oil cooler.

Recently, thin heat exchangers having elongate cores have been used for automotive refrigeration cycles.

To reduce the pressure drop caused by the thin width of such heat exchangers, it has been necessary to change from units 111 with W-shaped tubes as shown in Fig. 17 to units 112 with U-shaped tubes as shown in Fig. 18.

The heat exchanger having U-shaped tubes requires about twice the number of tubes compared with the heat exchanger shown in Fig. 17, to maintain the same heat exchange capacity.

Moreover, because this type of heat exchanger has elongate cores, it is more difficult to distribute the coolant uniformly to the tubes.

Non-uniform distribution of the coolant flow causes low efficiency heat exchange because the coolant flow rates and the vapor-liquid ratios of the tubes are not uniform.

To solve the above problems, the laminated coolant evaporator 100 shown in Fig. 19 distributes the coolant uniformly to the tubes to maintain efficient heat exchange.

The laminated coolant evaporator 100 is fabricated from plural elements each consisting of a pair of formed plates 104 having an inlet chamber 101 at one end of the plates 104, an outlet chamber 102 at the other end and a flow path 103 connecting both chambers 101 and 102.

Plural distribution pipes 107 are connected between the inlet chambers 101 and a throttling plate 106 at one end of a supply pipe 105 in order to distribute the coolant uniformly to the flow paths 103.

This laminated coolant evaporator, however, requires a large volume for the plural distribution pipes 107, because the evaporator has connections on the outside of the inlet chambers 101.

According to the present invention, there is provided a heat exchanger comprising: a plurality of tube elements for exchanging heat between an internal fluid and an external gas; an inlet pipe for supplying said internal fluid; and an elongate perforated pipe disposed at one end of said tube elements, the inside of said perforated pipe being divided into a plurality of flow paths, each flow path communicating with said inlet pipe and, via a respective hole in the outer surface of said perforated pipe, with a respective one of said tube elements.

Because of the perforated pipe, the heat exchanger does not require a large volume to maintain efficient heat exchange by ensuring uniform distribution of the internal fluid.

The invention will now be described by way of non-limiting embodiments with reference to the accompanying drawings, in which: Fig. 1 is a partial sectional view of a laminated coolant evaporator which is the first embodiment of the present invention; Fig. 2 is an enlarged section of the main part of Fig. 1; Fig. 3 is a front view of the main part of Fig. 1; Fig. 4 is a partial sectional view of a laminated coolant evaporator which is the second embodiment of the present invention; Fig. 5 is a front view of the main part of Fig. 4; Fig. 6 is a partial sectional view of a laminated coolant evaporator which is the third embodiment of the present invention; Fig. 7 is a front view of the main part of Fig. 6; Fig. 8 is a partial sectional view of a laminated coolant evaporator which is the fourth embodiment of the present invention;; Fig. 9 is an enlarged section of the main part of Fig. 8; Fig. 10 is a front view of the main part of Fig. 8; Fig. 11 is a view of the perforated pipe for the fifth embodiment of the present invention; Fig. 12 is an enlarged section of the main part of the fifth embodiment; Fig. 13 is a front view of the main part of Fig. 12; Fig. 14 is a front view of the main part of the sixth embodiment of the present invention; Fig. 15 is a partial sectional view of a laminated coolant evaporator which is the seventh embodiment of the present invention; Fig. 16 is a front view of the main part of Fig. 15; Fig. 17 is a view of a conventional heat exchanger having W-shaped tubes; Fig. 18 is a view of a conventional heat exchanger having U-shaped tubes; and Fig. 19 is a front view of a conventional laminated evaporator.

Figs. 1, 2 and 3 show the first embodiment of the present invention. Figs. 1 and 2 show a laminated coolant evaporator, and Fig. 3 shows a formed plate thereof.

The laminated coolant evaporator 1 changes the coolant from a gas-liquid mixed state into gas by exchanging heat between the coolant that flows along the flow path and the air that flows around the flow path.

The laminated coolant evaporator 1 is fabricated from plural elements each having a flow path 3 and made by bonding a pair of formed plates 2 and corrugated fins 4 welded to the outside of the formed plates 2.

Each formed plate 2 is made of thin aluminium alloy sheet by pressing it like a shallow dish.

At one end of the flow path, an inlet chamber 5 is formed and at the other end of the flow path an outlet chamber 6 is formed. The flow path is shaped like a tube 7 and connects the inlet and outlet chambers and conducts heat from the coolant to the air, or vice versa.

It is possible to form the tube and also the inlet and outlet chambers by pressing the aluminium alloy sheet.

A heat exchanger using this type of formed plate is known as a drawn cup heat exchanger.

The inlet chamber is shaped like an egg, is connected to a tube and has a cylindrical perforated pipe 9 extending through openings 8 into the inlet chamber 5.

The inside of the perforated pipe 9 is divided by partitions 11 into the same number of flow paths 10 as the number of tubes. Each flow path 10 has the same sectional area.

Note that the inlet of the perforated pipe 9 is connected to a supply pipe 13 through a throttling plate 12 for spraying coolant.

In the outer surface of the perforated pipe 9, holes 14 are drilled spirally to distribute the coolant into each inlet chamber 5 through a respective hole.

Note that it is possible to change the sectional area in order to effect a uniform pressure drop along each flow path. In this case, the sectional areas of the flow paths do not need to be uniform.

The outlet chamber 6 is also shaped like an egg and collects the coolant from the respective tube 7. A drain pipe 15 is connected to the outlet chambers 6.

The tube 7 of the formed plates 2 is shaped like an elliptical cylinder and has plural internal ribs 16.

The coolant in a gas-liquid mixed state is supplied frorn an expansion valve (not shown) and flows to the throttling plate 12 through the supply pipe 13. The coolant sprays into the inlet side of the perforated pipe 9 arranged in the plural inlet chambers 5.

The sprayed coolant is distributed uniformly to the flow paths formed in the perforated pipe 9. In other words,-the same quantity of the coolant flows along each flow path. The coolant supplied from the flow paths flows into the inlet chambers 5 through the holes 14.

Note that, as each inlet chamber 5 has its own tube 7, the coolant in each inlet chamber 5 flows into its own tube 7.

The coolant changes from a gas-liquid mixed state into a gas state because the coolant is heated by air that flows around the tubes 7, and finally all of the coolant becomes gas.

Because the coolant is distributed uniformly to the flow paths, the temperature of the air when leaving the heat exchange is also uniform, and therefore efficient heat exchange occurs.

Moreover, because the perforated pipe 9 uniformly distributing the coolant into the tubes 7 is arranged in the inlet chambers 5, the space for a distributor and/or pipes required by the conventional heat exchanger, shown in Fig. 19, is not necessary. Therefore, the volume of space required for the laminated evaporator is less than that for the conventional heat exchanger, and it is possible to arrange the laminated evaporator 1 in a narrow space such as an air-conditioning duct.

Figs. 4 and 5 show the second embodiment of the present invention.

Note that the same elements as shown in Fig. 1 have the same reference numerals.

In the second embodiment, an elliptical perforated cylinder 20 is used instead of the perforated pipe 9 used in the first embodiment. The reference numeral 21 designates flow paths formed in the elliptical perforated cylinder 20, and the reference numeral 22 is a hole for supplying a respective tube 7.

Figs. 6 and 7 show the third embodiment of the present invention.

Note that the same elements as shown in Fig. 1 have the same reference numerals.

In the third embodiment, a square perforated pipe 30 is used instead of the perforated pipe 9 used in the first embodiment. The reference numeral 31 designates flow paths formed in the square perforated pipe 30, and the reference numeral 32 is a hole for supplying a respective tube 7.

Figs. 8, 9 and 10 show the fourth embodiment of the present invention.

In the fourth embodiment, a perforated pipe 40 which swirls the coolant is installed in the inlet chambers 5. This perforated pipe 40 consists of an inner pipe 42 having a spiral channel 41 therein, a cylindrical part 44 having the same number of flow paths 43 as there are tubes 7 and a return element 45 that transfers the coolant from the inner pipe 42 to the flow paths 43. This return element 45 is brazed or welded to the cylindrical part 44 after the inner pipe 42 and cylindrical part 44 have been inserted in the openings of the inlet chambers 5 of the formed plates 2.

The coolant supplied from the inlet pipe 13 to the inner pipe 42 is swirled as it passes through the inner pipe 42. Because the coolant flowing out of the inner pipe 42 is swirled, the coolant is uniformly distributed to the flow paths 43 and flows out of holes 46 and into respective tubes 7.

In this embodiment, the throttling plate 12 used in the first embodiment is not required because the inner pipe 42 installed in the perforated pipe 40 performs the throttling function.

Figs. 11, 12 and 13 show the fifth embodiment of the present invention.

Note that the same elements as shown in Fig. 1 have the same reference numerals.

In this embodiment, a twisted perforated pipe 50 having a length L equal to the width of the laminated coolant evaporator is installed in the inlet chambers 5. The flow paths 51 in this twisted perforated pipe 50 are twisted and therefore the holes 52 can be formed in a line. The holes 52 are spaced apart by a distance e equal to the pitch of the twisted perforated pipe 50, which satisfies the following equation: L = t x (the number of tubes 7) The twist angle is 3600 per L, that is, 3600/(the number of tubes 7) per e.

In this embodiment, the coolant flows out of the holes 52 unidirectionally because the holes are in a line. Therefore, it is possible to make the inlet chambers smaller than in the first embodiment.

Fig. 14 shows the sixth embodiment of the present invention.

In this embodiment, the twisted perforated pipe 60 has an inner pipe having a spiral channel 61 therein, a cylindrical part having plural twisted flow paths 63 and a return element (not shown) that transfers the coolant from the inner pipe 62 to the flow paths 63.

In this embodiment, the throttling plate is not required, as was the case for the fourth embodiment.

Figs. 15 and 16 show the seventh embodiment of the present invention.

This embodiment has a corrugated-fin tube type heat exchanger 70 consisting of elliptical tubes 71 and a header 72 (the inlet chambers).

The header 72 has openings 73 into which the elliptical tubes 71 are inserted, and a twisted perforated pipe 74 is welded to the header 72.

The flow paths 75 formed in the twisted perforated pipe 74 are twisted as in the fifth embodiment, and the holes 76 are arranged in a line.

When the perforated pipe has holes in a line, it is possible to insert the tubes directly in the holes of the perforated pipe and dispense with the inlet chambers.

Though the above described embodiments concern evaporators, it is possible to apply the present invention to coolant condensers, heater cores, radiators, oil coolers and the like. The present invention can be applied to any type of heat exchanger and is not limited to the laminated type, the corrugated-fin tube type or the plate-fin tube type.

It is also possible to apply the present invention to a heat exchanger having one or more flow paths per tube, having one flow path passing through one or more tubes and/or having plural holes per tube.

It is also possible to make a perforated pipe by twisting the plural flow pipes in which the plural flow paths are formed, and it is possible to form each tube in the shape of a U.

When a pressure reducing device, such as an expansion valve, is installed near the heat exchanger (for example, a coolant evaporator), a throttling device is not necessary. Moreover, a swirling device, such as a spiral channel, can be used instead of the throttling device.

Claims (14)

1. A heat exchanger comprising: a plurality of tube elements for exchanging heat between an internal fluid and an external gas; an inlet pipe for supplying said internal fluid; and an elongate perforated pipe disposed at one end of said tube elements, the inside of said perforated pipe being divided into a plurality of flow paths, each flow path communicating with said inlet pipe and, via a respective hole in the outer surface of said perforated pipe, with a respective one of said tube elements.
2. A heat exchanger according to claim 1, further comprising the same number of inlet chambers as tube elements, each inlet chamber providing communication between a respective one of said holes and the associated one of said tube elements.
3. A heat exchanger according to claim 2, wherein each inlet chamber is defined with its associated tube element between a pair of opposed shaped plates.
4. A heat exchanger according to any one of claims 1 to 3, wherein said perforated pipe is cylindrical and is divided into said plurality of flow paths by radial partitions and said plurality of holes are spirally disposed along said pipe.
5. A heat exchanger according to any one of claims 1 to 3, wherein said perforated pipe is substantially rectangular in cross-section and is divided into said plurality of flow paths by transversely intersecting partitions.
6. A heat exchanger according to any one of claims 1 to 3, wherein said perforated pipe is substantially square in cross-section and is divided into said plurality of flow paths by radial partitions and said plurality of holes are spirally disposed along said pipe.
7. A heat exchanger according to any one of claims 1 to 3, wherein said perforated pipe is cylindrical and comprises an inner pipe communicating at one end with said inlet pipe and having means for spiralling said internal fluid as it flows along within said inner pipe, an outer pipe, with said plurality of flow paths being defined by radial partitions between said inner and outer pipes, and a diverter for diverting said internal fluid, as it leaves the other end of said inner pipe, into said flow paths and said plurality of holes are spirally disposed along said outer pipe.
8. A heat exchanger according to any one of claims 1 to 3, wherein said perforated pipe is cylindrical and is divided into said plurality of flow paths by radial partitions twisted around the longitudinal axis of said perforated pipe and said plurality of holes are substantially linearly disposed along said pipe.
9. A heat exchanger according to claim 7, wherein said radial partitions are twisted around the longitudinal axis of said perforated pipe and said plurality of holes are not spirallly disposed along said outer pipe but are instead substantially linearly disposed along said outer pipe.
10. A heat exchanger according to claim 8 when dependent on claim 2, wherein said tube elements are elliptical in cross-section, said inlet chambers form a manifold having openings into which are inserted said elliptical tubes and said perforated pipe is disposed in said manifold.
11. A heat exchanger according to claims 1 and 8 or claims 1, 7 and 9, wherein said tube elements are inserted directly into said holes disposed substantially linearly along said perforated pipe.
12. A heat exchanger according to any one of claims 1 to 11, wherein said tube elements are parallel.
13. A heat exchanger substantially as herein described with reference to and/or as Ulustrated in Figs. 1 to 3, Figs. 4 and 5, Figs. 6 and 7, Figs. 8 to 10, Figs. 11 to 13, Fig. 14 or Figs. 15 and 16.
14. All novel features and combinations thereof.
GB9122075A 1990-10-17 1991-10-17 Heat exchanger Expired - Fee Related GB2250336B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP27813090A JPH04155194A (en) 1990-10-17 1990-10-17 Heat exchanger

Publications (3)

Publication Number Publication Date
GB9122075D0 GB9122075D0 (en) 1991-11-27
GB2250336A true GB2250336A (en) 1992-06-03
GB2250336B GB2250336B (en) 1994-07-06

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GB9122075A Expired - Fee Related GB2250336B (en) 1990-10-17 1991-10-17 Heat exchanger

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GB (1) GB2250336B (en)

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0670988A1 (en) * 1992-12-07 1995-09-13 Multistack International Limited Improvements in plate heat-exchangers
US5651268A (en) * 1995-01-05 1997-07-29 Nippondeso Co., Ltd. Refrigerant evaporator
EP0797067A1 (en) * 1996-03-22 1997-09-24 Sanden Corporation Distribution device capable of uniformly distributing a medium to a plurality of tubes of a heat exchanger
EP0798533A1 (en) * 1996-03-29 1997-10-01 Sanden Corporation Heat exchanger with a distribution device capable of uniformly distributing a medium to a plurality of exchanger tubes
EP0828130A2 (en) * 1996-09-09 1998-03-11 Mitsubishi Heavy Industries, Ltd. Laminated heat exchanger having refrigerant tubes and heads
FR2826439A1 (en) * 2001-06-26 2002-12-27 Valeo Climatisation Heat exchanger, particularly evaporator, with improved perfermance
WO2006055276A2 (en) 2004-11-12 2006-05-26 Carrier Corporation Parallel flow evaporator with spiral inlet manifold
US7377126B2 (en) 2004-07-14 2008-05-27 Carrier Corporation Refrigeration system
WO2008064219A1 (en) * 2006-11-22 2008-05-29 Johnson Controls Technology Company Multichannel evaporator with flow mixing manifold
US7398819B2 (en) 2004-11-12 2008-07-15 Carrier Corporation Minichannel heat exchanger with restrictive inserts
US7841393B2 (en) 2006-08-02 2010-11-30 Denso Corporation Heat exchanger
US7921558B2 (en) * 2008-01-09 2011-04-12 Delphi Technologies, Inc. Non-cylindrical refrigerant conduit and method of making same
CN102072684A (en) * 2011-01-06 2011-05-25 三花丹佛斯(杭州)微通道换热器有限公司 Refrigerant distributing device and heat exchanger with same
US8113270B2 (en) 2005-02-02 2012-02-14 Carrier Corporation Tube insert and bi-flow arrangement for a header of a heat pump
US20120273178A1 (en) * 2007-06-28 2012-11-01 Exxonmobil Research And Engineering Company Plate heat exchanger port insert and a method for alleviating vibrations in a heat exchanger
US20130126126A1 (en) * 2011-11-21 2013-05-23 Hyundai Motor Company Condenser for Vehicle
WO2015180388A1 (en) * 2014-05-26 2015-12-03 杭州三花微通道换热器有限公司 Adjustable refrigerant distribution device and heat exchanger having same
US9297595B2 (en) 2013-08-22 2016-03-29 King Fahd University Of Petroleum And Minerals Heat exchanger flow balancing system
CN106852169A (en) * 2014-10-16 2017-06-13 大金工业株式会社 Coolant flow divider
FR3059407A1 (en) * 2016-11-30 2018-06-01 Valeo Systemes Thermiques DEVICE FOR MIXING A REFRIGERANT FLUID INSIDE A COLLECTOR BOX OF A HEAT EXCHANGER
FR3059398A1 (en) * 2016-11-30 2018-06-01 Valeo Systemes Thermiques Device for dispensing a refrigerant fluid inside a collector box of a heat exchanger for an air conditioning installation of a vehicle
US10107572B2 (en) 2012-06-14 2018-10-23 Alfa Lavalcorporate Ab Plate heat exchanger
US10161686B2 (en) 2009-04-13 2018-12-25 Carrier Corporation Microchanel heat exchanger evaporator
EP3418666A4 (en) * 2016-02-17 2019-11-06 IHI Corporation Heat treatment apparatus
FR3086042A1 (en) * 2018-09-13 2020-03-20 Valeo Systemes Thermiques Heat exchanger and corresponding heating and / or ventilation and / or air conditioning installation

Families Citing this family (8)

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JP3332428B2 (en) * 1992-11-30 2002-10-07 昭和電工株式会社 Stacked condenser and method of manufacturing the same
JPH08136086A (en) * 1994-11-01 1996-05-31 Nippondenso Co Ltd Refrigerant evaporator
JPH10288479A (en) * 1997-04-15 1998-10-27 Daikin Ind Ltd Heat exchanger
JP3094979B2 (en) * 1997-12-10 2000-10-03 ダイキン工業株式会社 Plate heat exchanger
JP4568973B2 (en) * 2000-08-10 2010-10-27 ダイキン工業株式会社 Plate type heat exchanger
JP5519353B2 (en) * 2010-03-19 2014-06-11 株式会社ティラド heatsink
JP6213362B2 (en) * 2014-04-17 2017-10-18 株式会社デンソー Heat exchanger and heat exchanger manufacturing method
JP6048515B2 (en) * 2015-01-19 2016-12-21 ダイキン工業株式会社 Refrigerant shunt

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EP0121079A1 (en) * 1983-03-30 1984-10-10 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH &amp; Co. KG Heat exchanger

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Cited By (47)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0670988A4 (en) * 1992-12-07 1995-11-22 Multistack Int Ltd Improvements in plate heat-exchangers.
EP0670988A1 (en) * 1992-12-07 1995-09-13 Multistack International Limited Improvements in plate heat-exchangers
US5651268A (en) * 1995-01-05 1997-07-29 Nippondeso Co., Ltd. Refrigerant evaporator
EP0797067A1 (en) * 1996-03-22 1997-09-24 Sanden Corporation Distribution device capable of uniformly distributing a medium to a plurality of tubes of a heat exchanger
US5979547A (en) * 1996-03-22 1999-11-09 Sanden Corporation Distribution device capable of uniformly distributing a medium to a plurality of tubes of a heat exchanger
EP0798533A1 (en) * 1996-03-29 1997-10-01 Sanden Corporation Heat exchanger with a distribution device capable of uniformly distributing a medium to a plurality of exchanger tubes
US5901785A (en) * 1996-03-29 1999-05-11 Sanden Corporation Heat exchanger with a distribution device capable of uniformly distributing a medium to a plurality of exchanger tubes
EP0828130A2 (en) * 1996-09-09 1998-03-11 Mitsubishi Heavy Industries, Ltd. Laminated heat exchanger having refrigerant tubes and heads
EP0828130A3 (en) * 1996-09-09 1998-08-12 Mitsubishi Heavy Industries, Ltd. Laminated heat exchanger having refrigerant tubes and heads
US5983999A (en) * 1996-09-09 1999-11-16 Mitsubishi Heavy Industries, Ltd Laminated heat exchanger having refrigerant tubes and heads
CZ296755B6 (en) * 2001-06-26 2006-06-14 Valeo Climatisation Improved performance heat-exchange apparatus, particularly evaporator
WO2003001134A1 (en) * 2001-06-26 2003-01-03 Valeo Climatisation Improved performance heat exchanger, in particular an evaporator
FR2826439A1 (en) * 2001-06-26 2002-12-27 Valeo Climatisation Heat exchanger, particularly evaporator, with improved perfermance
US7059395B2 (en) * 2001-06-26 2006-06-13 Valeo Climatisation Performance heat exchanger, in particular an evaporator
US7377126B2 (en) 2004-07-14 2008-05-27 Carrier Corporation Refrigeration system
EP1809969A4 (en) * 2004-11-12 2011-09-07 Carrier Corp Parallel flow evaporator with spiral inlet manifold
EP1809969A2 (en) * 2004-11-12 2007-07-25 Carrier Corporation Parallel flow evaporator with spiral inlet manifold
WO2006055276A3 (en) * 2004-11-12 2007-03-29 Carrier Corp Parallel flow evaporator with spiral inlet manifold
US8302673B2 (en) 2004-11-12 2012-11-06 Carrier Corporation Parallel flow evaporator with spiral inlet manifold
US7398819B2 (en) 2004-11-12 2008-07-15 Carrier Corporation Minichannel heat exchanger with restrictive inserts
US7806171B2 (en) * 2004-11-12 2010-10-05 Carrier Corporation Parallel flow evaporator with spiral inlet manifold
WO2006055276A2 (en) 2004-11-12 2006-05-26 Carrier Corporation Parallel flow evaporator with spiral inlet manifold
US8113270B2 (en) 2005-02-02 2012-02-14 Carrier Corporation Tube insert and bi-flow arrangement for a header of a heat pump
US7841393B2 (en) 2006-08-02 2010-11-30 Denso Corporation Heat exchanger
US7895860B2 (en) 2006-11-22 2011-03-01 Johnson Controls Technology Company Multichannel evaporator with flow mixing manifold
WO2008064219A1 (en) * 2006-11-22 2008-05-29 Johnson Controls Technology Company Multichannel evaporator with flow mixing manifold
US20120273178A1 (en) * 2007-06-28 2012-11-01 Exxonmobil Research And Engineering Company Plate heat exchanger port insert and a method for alleviating vibrations in a heat exchanger
US7921558B2 (en) * 2008-01-09 2011-04-12 Delphi Technologies, Inc. Non-cylindrical refrigerant conduit and method of making same
US10161686B2 (en) 2009-04-13 2018-12-25 Carrier Corporation Microchanel heat exchanger evaporator
CN102072684B (en) * 2011-01-06 2012-10-17 三花控股集团有限公司 Refrigerant distributing device and heat exchanger with same
CN102072684A (en) * 2011-01-06 2011-05-25 三花丹佛斯(杭州)微通道换热器有限公司 Refrigerant distributing device and heat exchanger with same
US20130126126A1 (en) * 2011-11-21 2013-05-23 Hyundai Motor Company Condenser for Vehicle
US9109821B2 (en) * 2011-11-21 2015-08-18 Hyundai Motor Company Condenser for vehicle
US10107572B2 (en) 2012-06-14 2018-10-23 Alfa Lavalcorporate Ab Plate heat exchanger
US9297595B2 (en) 2013-08-22 2016-03-29 King Fahd University Of Petroleum And Minerals Heat exchanger flow balancing system
WO2015180388A1 (en) * 2014-05-26 2015-12-03 杭州三花微通道换热器有限公司 Adjustable refrigerant distribution device and heat exchanger having same
US10088254B2 (en) 2014-05-26 2018-10-02 Sanhua (Hangzhou) Micro Channel Heat Exchanger Co., Ltd. Adjustable refrigerant distribution device and heat exchanger having same
CN106852169A (en) * 2014-10-16 2017-06-13 大金工业株式会社 Coolant flow divider
EP3208560A4 (en) * 2014-10-16 2018-06-27 Daikin Industries, Ltd. Refrigerant flow divider
US10436527B2 (en) 2014-10-16 2019-10-08 Daikin Industries, Ltd. Refrigerant diverter
CN106852169B (en) * 2014-10-16 2019-07-23 大金工业株式会社 Coolant flow divider
EP3418666A4 (en) * 2016-02-17 2019-11-06 IHI Corporation Heat treatment apparatus
WO2018100301A1 (en) * 2016-11-30 2018-06-07 Valeo Systemes Thermiques Device for mixing a refrigerant fluid inside a collector box of a heat exchanger
CN110214257A (en) * 2016-11-30 2019-09-06 法雷奥热系统公司 Device for the mix refrigerant fluid in the header of heat exchanger
FR3059407A1 (en) * 2016-11-30 2018-06-01 Valeo Systemes Thermiques DEVICE FOR MIXING A REFRIGERANT FLUID INSIDE A COLLECTOR BOX OF A HEAT EXCHANGER
FR3059398A1 (en) * 2016-11-30 2018-06-01 Valeo Systemes Thermiques Device for dispensing a refrigerant fluid inside a collector box of a heat exchanger for an air conditioning installation of a vehicle
FR3086042A1 (en) * 2018-09-13 2020-03-20 Valeo Systemes Thermiques Heat exchanger and corresponding heating and / or ventilation and / or air conditioning installation

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GB9122075D0 (en) 1991-11-27
GB2250336B (en) 1994-07-06
JPH04155194A (en) 1992-05-28

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