EP2402701A1 - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- EP2402701A1 EP2402701A1 EP10745943A EP10745943A EP2402701A1 EP 2402701 A1 EP2402701 A1 EP 2402701A1 EP 10745943 A EP10745943 A EP 10745943A EP 10745943 A EP10745943 A EP 10745943A EP 2402701 A1 EP2402701 A1 EP 2402701A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- refrigerant
- tank
- block
- heat exchanger
- flows
- 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- Withdrawn
Links
Images
Classifications
-
- 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
-
- 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
- F28F9/0202—Header boxes having their inner space divided by partitions
- F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
- F28F9/0207—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions the longitudinal or transversal partitions being separate elements attached to header boxes
-
- 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
- F28F9/0202—Header boxes having their inner space divided by partitions
- F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
- F28F9/0214—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only longitudinal partitions
- F28F9/0217—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only longitudinal partitions the partitions being separate elements attached to header boxes
-
- 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
- F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with channels
Definitions
- the present invention relates to a heat exchanger, and more particularly to a heat exchanger suitably used in an evaporator in a refrigeration cycle for an air conditioner mounted in an automobile.
- a known heat exchanger that constitutes an evaporator (or condenser) used in a refrigeration cycle includes a core in which a plurality of tubes and a plurality of fins alternately stacked, and a tank to which ends of the tubes are connected.
- a refrigerant is introduced into the heat exchanger from an inlet header provided in the tank, passes through the tubes while performing heat exchange with air using heat transferred to the core, and then is discharged to the outside from an outlet header provided in the tank.
- An evaporator mounted in an automobile is required to have high performance and also be small and lightweight as described later.
- a circulation amount Gr [kg/s] of a refrigerant flowing in a refrigeration cycle during operation is generally the same throughout a refrigerant channel.
- the circulation amount Gr of the refrigerant is the same throughout the refrigerant channel.
- the refrigerant is gradually vaporized while performing heat exchange with air.
- the refrigerant on a side closer to an outlet is gasified, has lower density, and has higher flow rate.
- pressure loss of the refrigerant is relatively higher on the side closer to the outlet.
- an evaporator used in an automobile generally has a multi-flow structure in which a refrigerant is distributed from one tank to a plurality of tubes, and thus distribution of the refrigerant (particularly, a liquid component that influences cooling performance) needs to be uniform. If the refrigerant distribution is non-uniform, a heat transmission area A of a part with a few liquid component is small (cannot be effectively used), thereby reducing performance Q.
- FIG. 9 shows a heat exchanger 100 disclosed in Patent Document 1.
- the heat exchanger 100 includes a group of tubes 105 in two or more rows constituted by a plurality of heat exchange tubes (hereinafter referred to as tubes) 104 between an refrigerant flow-in/out side tank 102 and a refrigerant turn-side tank 103.
- An inside of a refrigerant inlet header chamber 106 in the refrigerant flow-in/out side tank 102 is partitioned into two spaces 106a and 106b in a height direction by a dividing resistance plate 107.
- the tubes 104 are connected to the refrigerant flow-in/out side tank 102 so as to face the first space 106a.
- One refrigerant passing hole 108 is formed in a middle in a length direction of the dividing resistance plate 107.
- the refrigerant having flowed into the first space 106a of the refrigerant inlet header chamber 106 in the refrigerant flow-in/out side tank 102 flows through the refrigerant passing hole 108 into the second space 106b, flows through the tubes 104 into the refrigerant turn-side tank 103. Then, the refrigerant changes its flow direction and flows through the tubes 104 into a refrigerant outlet header chamber 109 in the refrigerant flow-in/out side tank 102.
- the refrigerant is fed into the second space 106b of the refrigerant inlet header chamber 106 in the refrigerant flow-in/out side tank 102, flows through one refrigerant passing hole 108 in the dividing resistance plate 107 into the first space 106a, and is divided from the first space 106a into all the tubes 104 communicating with the refrigerant inlet header chamber 106. Since only one refrigerant passing hole 108 is formed in the dividing resistance plate 107, the refrigerant gradually flows from the second space 106b into the first space 106a, reaches the entire first space 106a, and flows into all the tubes 104.
- a ratio between a gas component and a liquid component in a refrigerant in the heat exchange tubes connected to the refrigerant inlet header chamber in the refrigerant flow-in/out side tank, that is, refrigerant distribution is made uniform, thereby increasing heat exchange performance of the heat exchanger.
- a refrigerant circuit includes two blocks (a first block on a refrigerant inlet side and a second block on a refrigerant outlet side).
- the refrigerant is equally distributed to all the tubes, and the ratio between the gas component and the liquid component in each tube tends to be non-uniform. This tendency is particularly noticeable in the second block on the outlet side in which vaporization of the refrigerant proceeds to increase the ratio of the gas component.
- a dividing auxiliary resistance plate 110 that vertically partitions the refrigerant outlet header chamber 109 is provided.
- the refrigerant circuit includes the two blocks in order to reduce pressure loss, but the dividing auxiliary resistance plate 110 is provided in the refrigerant outlet header chamber 109 in which most of the refrigerant is gasified for uniform refrigerant distribution.
- pressure loss is eventually increased, and a sufficient effect of reducing pressure loss cannot be obtained in terms of increasing performance Q.
- the present invention is achieved in view of such technical problems, and has an object to provide a heat exchanger that reduces pressure loss and can provide uniform refrigerant distribution in a second block.
- a heat exchanger of the present invention is configured so that a refrigerant successively passes through a first block and a second block and flows out of the second block.
- the first block includes a first tank having a refrigerant inlet through which the refrigerant flows in, a plurality of first tubes into which the refrigerant having flowed into the first tank is distributed and flows therein, and a second tank in which the refrigerant flowing in the first tubes merges.
- the second block includes a third tank into which the refrigerant having merged in the second tank flows, a plurality of second tubes into which the refrigerant having flowed into the third tank is distributed and flows therein, and a fourth tank in which the refrigerant flowing in the second tube merges, and having a refrigerant outlet through which the merged refrigerant flows out.
- a refrigerant passage through which the refrigerant flows from the second tank into the third tank is locally placed on the side opposite to the refrigerant inlet.
- non-uniform refrigerant distribution that occurs in the first block is eliminated in the second block in such a manner that the refrigerant passage through which the refrigerant flows from the second tank into the third tank, that is, from the first block into the second block is locally placed on the side opposite to the refrigerant inlet (hereinafter referred to as a counter-inlet side).
- a counter-inlet side the side opposite to the refrigerant inlet
- the first block and the second block are placed in parallel with each other, the first tank and the fourth tank are placed on a vertically upper side, and the second tank and the third tank are placed on a vertically lower side.
- the refrigerant is guided vertically downward from the first tank to the second tank, and the refrigerant is guided vertically upward from the third tank to the fourth tank.
- the refrigerant flows from the second tank toward the third tank on the lower side, that is, from the counter-inlet side toward an inlet side, thereby enabling a liquid component to easily flow to an inlet side of the third tank, and providing uniform distribution of a gas component and the liquid component in the second block (second tubes).
- the refrigerant passage through which the refrigerant flows from the second tank into the third tank is formed by providing a plurality of holes in a partition member provided between the second tank and the third tank. This can facilitate mixing of the gas component and the liquid component, and improve uniformity of refrigerant distribution in the second block (second tubes).
- the third tank includes at least one resistor against the refrigerant therein, and the resistor is placed on a rear side of the refrigerant passage in a flow direction of the refrigerant.
- a distribution amount of the liquid component in the refrigerant flowing in the third tank is particularly made uniform in the third tank.
- the liquid component is under vaporization, and pressure loss can be reduced even with the resistor in the third tank.
- the third tank may include a plurality of resistors.
- the third tank includes a first resistor, and a second resistor placed on a rear side of the first resistor in the flow direction of the refrigerant, and an opening rate of the second resistor is equal to or lower than an opening rate of the first resistor. This is because gradually reducing a liquid component amount toward the refrigerant inlet side is preferable in more uniformly distributing the gas component and the liquid component.
- a refrigerant channel area in the fourth tank that constitutes the second block is larger than a refrigerant channel area in the first tank that constitutes the first block.
- a refrigerant channel area in the third tank that constitutes the second block is larger than a refrigerant channel area in the second tank that constitutes the first block.
- a refrigerant channel area of the second tube that constitutes the second block is larger than a refrigerant channel area of the first tube that constitutes the first block.
- non-uniform refrigerant distribution that occurs in the first block is eliminated in such a manner that the refrigerant passage through which the refrigerant flows from the second tank into the third tank, that is, from the first block into the second block is locally placed on the counter-inlet side.
- refrigerant distribution in the second block is made uniform to improve heat exchange performance of the heat exchanger.
- a heat exchanger 10 according to this embodiment is suitably used in an evaporator in a refrigeration cycle for an air conditioner mounted in an automobile.
- the heat exchanger 10 includes a core 20 in which a plurality of first tubes 21 and second tubes 22 through which a refrigerant flows, and a plurality of fins 23 are alternately stacked, an upper tank 30 to which one end (upper end in the drawings) of each of the first tubes 21 and the second tubes 22 is connected, and a lower tank 40 to which the other end (lower end in the drawings) of each of the first tubes 21 and the second tubes 22 is connected.
- the heat exchanger 10 performs heat exchange of the refrigerant using heat transferred to the core 20.
- the first tubes 21 and the second tubes 22 are made of copper, a copper alloy, aluminum, or an aluminum alloy, and are members produced by extrusion molding or roll molding of a plate material and having a hollow portion and a rectangular section.
- the first tubes 21 and the second tubes 22 are arranged in two rows in a width direction (Y direction in FIG. 2 ).
- the upper ends of the first tubes 21 and the second tubes 22 are connected to the upper tank 30, and the lower ends of the first tubes 21 and the second tubes 22 are connected to the lower tank 40.
- the upper tank 30, the first tubes 21, the second tubes 22, and the lower tank 40 are communicated with each other to allow passage of the refrigerant. This connection is generally performed by blazing.
- the sectional shape of the first tube(s) 21 and the second tube(s) 22 is not limited to the rectangular shape, but may be a circular shape or other shapes.
- the fin 23 is made of the same material as that of the first tube 21 and the second tube 22.
- a corrugated fin molded by roll molding is used, but not limited to this, a plate fin may be used.
- the first and second tubes 21, 22, and the fins 23 are alternately stacked in a longitudinal direction (X direction in FIG. 2 ) of the heat exchanger 10, and the both ends are sealed by side plates 24.
- the side plate 24 functions as a reinforcing member of the core 20, and the both ends in a longitudinal direction thereof are supported by the upper tank 30 and the lower tank 40.
- the upper tank 30 mainly includes a tank plate 31 and an end plate 32, and is assembled so that openings of the plates face each other.
- an upper partition plate 33 is provided along a longitudinal direction.
- the upper partition plate 33 partitions an inside of the upper tank 30 at a middle in a width direction.
- One of partitioned sides constitutes a first tank T1, and the other constitutes a fourth tank T4.
- the first tube 21 is connected to a lower surface of the first tank T1
- the second tube 22 is connected to a lower surface of the fourth tank T4. Since the upper partition plate 33 is provided between the first tank T1 and the fourth tank T4, the refrigerant is not directly moved between the tanks T1 and T4.
- a cap 34 is provided on one end side in the longitudinal direction of the upper tank 30.
- the cap 34 has a refrigerant inflow hole h in and a refrigerant outflow hole h ex .
- a cap 35 is provided on the other end side in the longitudinal direction of the upper tank 30. The cap 35 seals the other end in the longitudinal direction of the upper tank 30.
- the lower tank 40 mainly includes a tank plate 41 and an end plate 42, and is assembled so that openings of the plates face each other.
- a lower partition plate 43 is provided along a longitudinal direction.
- the lower partition plate 43 partitions an inside of the lower tank 40 at a middle in a width direction.
- One of partitioned sides constitutes a second tank T2, and the other constitutes a third tank T3.
- the first tube 21 is connected to an upper surface of the second tank T2, and the second tube 22 is connected to an upper surface of the third tank T3.
- the lower partition plate 43 has refrigerant passages 43h passing therethrough in a thickness direction.
- the plurality of (seven in this example) refrigerant passages 43h are locally provided on one end side in a longitudinal direction of the lower partition plate 43.
- the refrigerant passages 43h are placed on the opposite side of the refrigerant inflow hole h in that is a refrigerant inlet in the longitudinal direction of the heat exchanger 10.
- the lower partition plate 43 is provided between the second tank T2 and the third tank T3, but the refrigerant flows from the second tank T2 into the third tank T3 through the plurality of refrigerant passages 43h locally placed on the opposite side of the refrigerant inlet (hereinafter referred to as a counter-inlet side).
- the refrigerant passages 43h are preferably provided within a range of 20% or less of the entire length of the lower partition plate 43. Increasing a flow rate of the refrigerant having passed through the refrigerant passages 43h is effective for uniformly mixing the gas component and the liquid component in the refrigerant.
- the refrigerant passages 43h are constituted by a plurality of circular holes, but may be one or more wide refrigerant passages having a longer diameter in the longitudinal direction of the lower partition plate 43. However, in order to uniformly mix the gas component and the liquid component, it is preferable to provide the plurality of refrigerant passages 43h having a small diameter as in this embodiment.
- distribution adjusting plates (resistors) 46, 47 and 48 are provided in the third tank T3.
- the distribution adjusting plates 46, 47 and 48 are placed in this order from the counter-inlet side at a predetermined interval.
- the distribution adjusting plates 46, 47 and 48 have through holes 46h, 47h and 48h, respectively, through which the refrigerant passes.
- the refrigerant having flowed through the refrigerant passages 43h into the third tank T3 successively passes through the through holes 46h, 47h and 48h and flows downward with the distribution adjusting plates 46, 47 and 48 as the resistors.
- the distribution adjusting plates 46, 47 and 48 in the third tank T3 Without the distribution adjusting plates 46, 47 and 48 in the third tank T3, the liquid component in the refrigerant tends to flow to a downstream side, and the gas component tends to stay in an upstream side. When the liquid component is uneven in the longitudinal direction to provide non-uniform refrigerant distribution, sufficient vaporization performance cannot be obtained.
- the distribution adjusting plates 46, 47 and 48 are particularly used as the resistors for the liquid component, and thus the liquid component and the gas component in the refrigerant are distributed as equally as possible over upstream and downstream regions of the third tank T3.
- the distribution adjusting plates 46, 47 and 48 function as the resistors and thus cause pressure loss of the refrigerant.
- the distribution adjusting plates 46, 47 and 48 are provided in the third tank T3 in which most of the liquid component is under vaporization, and thus the pressure loss can be minimized.
- the three distribution adjusting plates 46, 47 and 48 are provided, but one distribution adjusting plate may be provided.
- the distribution adjusting plate 46 (first distribution adjusting plate from an upstream end, "first resistor") provided for the above-described purpose is preferably provided in a position relatively close to the upstream end of the third tank T3. As a specific index, the distribution adjusting plate 46 is provided within a range of 30% or less of the entire length of the lower partition plate 43 from the upstream end.
- An opening rate of the through holes 46h, 47h and 48h provided in the distribution adjusting plates 46, 47 and 48 is preferably within a range of 15% to 30%. This is because the liquid component and the gas component can be equally distributed over the upstream and downstream regions without increasing pressure loss of the refrigerant more than necessary.
- the opening rate herein refers to a ratio of each of the through holes 46h, 47h and 48h to an area (sectional area) of a refrigerant channel in the third tank T3.
- opening rates of through holes 47h and 48h in the second and thereafter distribution adjusting plate 47 (second resistor) and distribution adjusting plate 48 (second resistor) from an upstream end are preferably equal to or lower than opening rates of through holes 47h and 48h on an adjacent upstream side. This is because the opening rate is reduced in a position closer to the downstream side to retain, on the upstream side, the liquid component that tends to flow to the downstream side.
- a cap 44 is provided on one end side in the longitudinal direction of the lower tank 40.
- the cap 44 seals one end side in the longitudinal direction of the lower tank 40.
- a cap 45 is provided on the other end side in the longitudinal direction of the lower tank 40. The cap 45 seals the other end side in the longitudinal direction of the lower tank 40.
- the refrigerant channel is constituted by the first block and the second block, and the refrigerant flows in the heat exchanger 10 in order of the first block and the second block.
- the first block includes the first tank T1, the first tube 21, and the second tank T2, and the second block includes the third tank T3, the second tube 22, and the fourth tank T4.
- the refrigerant having brought into a gas-liquid two-phase state by an expansion valve placed on the upstream side with respect to the heat exchanger 10 flows through the refrigerant inflow hole h in (refrigerant inlet) into the first tank T1.
- the refrigerant having flowed into the first tank T1 flows vertically downward in the first tube 21 and reaches the second tank T2. During flowing in the first tube 21, the refrigerant is subjected to heat exchange with air passing through the core 20 with the liquid component being vaporized.
- the ratio between the gas component and the liquid component varies in the longitudinal direction of the heat exchanger 10. This is schematically shown in FIG. 7A .
- the ratio of the liquid component in the refrigerant is shown by arrows.
- the ratio of the liquid component is higher in the first tube 21 on the side closer to the refrigerant inlet. Since the liquid component has higher resistance to an inner wall of the first tank T1 than the gas component, the liquid component is hard to flow in a position farther from the refrigerant inlet.
- the refrigerant having flowed into the second tank T2 flows through the refrigerant passage 43h into the third tank T3. Since the refrigerant passages 43h are locally provided on the counter-inlet side of the lower partition plate 43, the refrigerant having flowed in the first tube 21 in a position closer to the counter-inlet side among the first tubes 21 first flows through the refrigerant passages 43h into the third tank T3.
- the refrigerant having flowed into the third tank T3 flows vertically upward in the second tube 22 and reaches the fourth tank T4.
- the refrigerant is subjected to heat exchange with air passing through the core 20 while the liquid component is vaporized.
- the refrigerant with the liquid component being vaporized during flowing through the heat exchanger 10 flows through the fourth tank T4, and is discharged from the refrigerant flow-out hole h ex toward a compressor placed on the downstream side.
- the ratio of the liquid component of the refrigerant flowing vertically upward in the second tube 22 (second block) is higher in the second tube 22 on the side closer to the refrigerant inlet as shown in FIG. 7B because the state of the first tube 21 (first block) is taken over. This state is shown by dash-single-dot lines in FIG. 5B .
- the refrigerant passages 43h are locally provided on the counter-inlet side of the lower partition plate 43, and thus the refrigerant having flowed in the first tube 21 in the position closer to the counter-inlet side among the first tubes 21 first flows through the refrigerant passages 43h into the third tank T3.
- the second block as shown by solid lines in FIG. 5B , non-uniform distribution of the gas component and the liquid component in the longitudinal direction that has occurred in the first block ( FIGS. 5A and 7A ) is eliminated.
- the dash-single-dot lines in FIG. 5B indicate the ratio of the liquid component when the refrigerant passages 43h are formed over the entire region in the longitudinal direction of the third tank T3.
- the position and shape of the upper partition plate 33 may be adjusted so that the refrigerant channel area of the fourth tank T4 is larger than the refrigerant channel area of the first tank T1.
- the position and shape of the lower partition plate 43 may be adjusted so that the refrigerant channel area of the third tank T3 is larger than the refrigerant channel area of the second tank T2. This can reduce pressure loss in the third tank T3 and the fourth tank T4 in which the ratio of the gas component is higher than in the first tank T1 and the second tank T2 without changing the external size of the heat exchanger 10. Further, as shown in FIG.
- a width (refrigerant channel area) of the second tube 22 that constitutes the second block may be larger than a width (refrigerant channel area) of the first tube 21 that constitutes the first block. This can reduce pressure loss of the refrigerant in the second block in which the ratio of the gas component is higher than in the first block without changing the external size of the heat exchanger 10.
Abstract
A heat exchanger 10 includes a first block and a second block. The first block includes a first tank T1 having a refrigerant inlet through which the refrigerant flows in, a plurality of first tubes 21 into which the refrigerant having flowed into the first tank T1 is distributed and flows therein, and a second tank T2 in which the refrigerant flowing in the first tubes 21 merges. The second block includes a third tank T3 into which the refrigerant having merged in the second tank T2 flows therein, a plurality of second tubes 22 into which the refrigerant having flowed into the third tank T3 is distributed and flows, and a fourth tank T4 in which the refrigerant flowing in the second tube merges, and having a refrigerant outlet through which the merged refrigerant flows out. A refrigerant passage 43h through which the refrigerant flows from the second tank T2 into the third tank T3 is locally placed on the opposite side of the refrigerant inlet.
Description
- The present invention relates to a heat exchanger, and more particularly to a heat exchanger suitably used in an evaporator in a refrigeration cycle for an air conditioner mounted in an automobile.
- A known heat exchanger that constitutes an evaporator (or condenser) used in a refrigeration cycle includes a core in which a plurality of tubes and a plurality of fins alternately stacked, and a tank to which ends of the tubes are connected. A refrigerant is introduced into the heat exchanger from an inlet header provided in the tank, passes through the tubes while performing heat exchange with air using heat transferred to the core, and then is discharged to the outside from an outlet header provided in the tank.
- An evaporator mounted in an automobile is required to have high performance and also be small and lightweight as described later.
- Generally, performance Q of an evaporator is represented by Q = K·A·(Ta-Tr), where K is a overall heat transmission coefficient, A is a heat transmission area, Ta is an air temperature, and Tr is a refrigerant temperature. Since the refrigerant temperature Tr is lower with lower pressure loss of a refrigerant in an evaporator, it is important to minimize pressure loss of the refrigerant in the evaporator in order to increase the evaporator performance Q (increase (Ta-Tr)).
- Also, a circulation amount Gr [kg/s] of a refrigerant flowing in a refrigeration cycle during operation is generally the same throughout a refrigerant channel. Also in the evaporator, the circulation amount Gr of the refrigerant is the same throughout the refrigerant channel. In the evaporator, the refrigerant is gradually vaporized while performing heat exchange with air. The refrigerant on a side closer to an outlet is gasified, has lower density, and has higher flow rate. Thus, pressure loss of the refrigerant is relatively higher on the side closer to the outlet.
- From the above, it is demanded to reduce pressure loss of the refrigerant, particularly, reduce pressure loss of the refrigerant on the side closer to the outlet in order to increase the evaporator performance Q.
- Meanwhile, an evaporator used in an automobile generally has a multi-flow structure in which a refrigerant is distributed from one tank to a plurality of tubes, and thus distribution of the refrigerant (particularly, a liquid component that influences cooling performance) needs to be uniform. If the refrigerant distribution is non-uniform, a heat transmission area A of a part with a few liquid component is small (cannot be effectively used), thereby reducing performance Q.
- Currently, if a width of an evaporator is reduced in view of a demand for size reduction for mounting in an automobile, a refrigerant passage in the evaporator is reduced to increase pressure loss of a refrigerant, thereby reducing evaporator performance. Thus, an evaporator is proposed in which the number of partitions of a refrigerant circuit is reduced in the evaporator to reduce pressure loss of a refrigerant (Patent Document 1).
-
FIG. 9 shows aheat exchanger 100 disclosed inPatent Document 1. Theheat exchanger 100 includes a group oftubes 105 in two or more rows constituted by a plurality of heat exchange tubes (hereinafter referred to as tubes) 104 between an refrigerant flow-in/outside tank 102 and a refrigerant turn-side tank 103. An inside of a refrigerantinlet header chamber 106 in the refrigerant flow-in/outside tank 102 is partitioned into twospaces resistance plate 107. Thetubes 104 are connected to the refrigerant flow-in/outside tank 102 so as to face thefirst space 106a. Onerefrigerant passing hole 108 is formed in a middle in a length direction of the dividingresistance plate 107. The refrigerant having flowed into thefirst space 106a of the refrigerantinlet header chamber 106 in the refrigerant flow-in/outside tank 102 flows through therefrigerant passing hole 108 into thesecond space 106b, flows through thetubes 104 into the refrigerant turn-side tank 103. Then, the refrigerant changes its flow direction and flows through thetubes 104 into a refrigerantoutlet header chamber 109 in the refrigerant flow-in/outside tank 102. - In the
heat exchanger 100 inPatent Document 1, the refrigerant is fed into thesecond space 106b of the refrigerantinlet header chamber 106 in the refrigerant flow-in/outside tank 102, flows through onerefrigerant passing hole 108 in the dividingresistance plate 107 into thefirst space 106a, and is divided from thefirst space 106a into all thetubes 104 communicating with the refrigerantinlet header chamber 106. Since only onerefrigerant passing hole 108 is formed in the dividingresistance plate 107, the refrigerant gradually flows from thesecond space 106b into thefirst space 106a, reaches the entirefirst space 106a, and flows into all thetubes 104. Thus, a ratio between a gas component and a liquid component in a refrigerant in the heat exchange tubes connected to the refrigerant inlet header chamber in the refrigerant flow-in/out side tank, that is, refrigerant distribution is made uniform, thereby increasing heat exchange performance of the heat exchanger. -
- Patent Document 1: Japanese Patent Laid-Open No.
2005-43040 - However, in the
heat exchanger 100, a refrigerant circuit includes two blocks (a first block on a refrigerant inlet side and a second block on a refrigerant outlet side). In both the first block and the second block, the refrigerant is equally distributed to all the tubes, and the ratio between the gas component and the liquid component in each tube tends to be non-uniform. This tendency is particularly noticeable in the second block on the outlet side in which vaporization of the refrigerant proceeds to increase the ratio of the gas component. Thus, inPatent Document 1, a dividingauxiliary resistance plate 110 that vertically partitions the refrigerantoutlet header chamber 109 is provided. - In
Patent Document 1, the refrigerant circuit includes the two blocks in order to reduce pressure loss, but the dividingauxiliary resistance plate 110 is provided in the refrigerantoutlet header chamber 109 in which most of the refrigerant is gasified for uniform refrigerant distribution. Thus, pressure loss is eventually increased, and a sufficient effect of reducing pressure loss cannot be obtained in terms of increasing performance Q. - The present invention is achieved in view of such technical problems, and has an object to provide a heat exchanger that reduces pressure loss and can provide uniform refrigerant distribution in a second block.
- A heat exchanger of the present invention is configured so that a refrigerant successively passes through a first block and a second block and flows out of the second block.
- In the heat exchanger of the present invention, the first block includes a first tank having a refrigerant inlet through which the refrigerant flows in, a plurality of first tubes into which the refrigerant having flowed into the first tank is distributed and flows therein, and a second tank in which the refrigerant flowing in the first tubes merges. In the heat exchanger of the present invention, the second block includes a third tank into which the refrigerant having merged in the second tank flows, a plurality of second tubes into which the refrigerant having flowed into the third tank is distributed and flows therein, and a fourth tank in which the refrigerant flowing in the second tube merges, and having a refrigerant outlet through which the merged refrigerant flows out.
- In the heat exchanger of the present invention, a refrigerant passage through which the refrigerant flows from the second tank into the third tank is locally placed on the side opposite to the refrigerant inlet.
- In the heat exchanger of the present invention, non-uniform refrigerant distribution that occurs in the first block is eliminated in the second block in such a manner that the refrigerant passage through which the refrigerant flows from the second tank into the third tank, that is, from the first block into the second block is locally placed on the side opposite to the refrigerant inlet (hereinafter referred to as a counter-inlet side). Thus, without special resistance means provided in the fourth tank (corresponding to the refrigerant
outlet header chamber 109 in Patent Document 1) in which most of the refrigerant is gasified, refrigerant distribution in the second block is made uniform to improve heat exchange performance of the heat exchanger. - In the heat exchanger of the present invention, it is preferable that the first block and the second block are placed in parallel with each other, the first tank and the fourth tank are placed on a vertically upper side, and the second tank and the third tank are placed on a vertically lower side.
- According to the heat exchanger, the refrigerant is guided vertically downward from the first tank to the second tank, and the refrigerant is guided vertically upward from the third tank to the fourth tank. As such, the refrigerant flows from the second tank toward the third tank on the lower side, that is, from the counter-inlet side toward an inlet side, thereby enabling a liquid component to easily flow to an inlet side of the third tank, and providing uniform distribution of a gas component and the liquid component in the second block (second tubes).
- In the heat exchanger of the present invention, it is preferable that the refrigerant passage through which the refrigerant flows from the second tank into the third tank is formed by providing a plurality of holes in a partition member provided between the second tank and the third tank. This can facilitate mixing of the gas component and the liquid component, and improve uniformity of refrigerant distribution in the second block (second tubes).
- In the heat exchanger of the present invention, it is preferable that the third tank includes at least one resistor against the refrigerant therein, and the resistor is placed on a rear side of the refrigerant passage in a flow direction of the refrigerant. With such a resistor, a distribution amount of the liquid component in the refrigerant flowing in the third tank is particularly made uniform in the third tank. In the third tank, the liquid component is under vaporization, and pressure loss can be reduced even with the resistor in the third tank.
- The third tank may include a plurality of resistors. In this case, it is preferable that the third tank includes a first resistor, and a second resistor placed on a rear side of the first resistor in the flow direction of the refrigerant, and an opening rate of the second resistor is equal to or lower than an opening rate of the first resistor. This is because gradually reducing a liquid component amount toward the refrigerant inlet side is preferable in more uniformly distributing the gas component and the liquid component.
- In the heat exchanger of the present invention, it is preferable that a refrigerant channel area in the fourth tank that constitutes the second block is larger than a refrigerant channel area in the first tank that constitutes the first block.
- Similarly, it is preferable that a refrigerant channel area in the third tank that constitutes the second block is larger than a refrigerant channel area in the second tank that constitutes the first block.
- This can reduce pressure loss in the second block in which the ratio of the gas component is higher than in the first block without changing an external size of the heat exchanger. From the same intention, it is preferable that a refrigerant channel area of the second tube that constitutes the second block is larger than a refrigerant channel area of the first tube that constitutes the first block.
- According to the present invention, non-uniform refrigerant distribution that occurs in the first block is eliminated in such a manner that the refrigerant passage through which the refrigerant flows from the second tank into the third tank, that is, from the first block into the second block is locally placed on the counter-inlet side. Thus, without special resistance means provided in the fourth tank (corresponding to the refrigerant
outlet header chamber 109 in Patent Document 1) in which most of the refrigerant is gasified, refrigerant distribution in the second block is made uniform to improve heat exchange performance of the heat exchanger. -
- [
FIG. 1] FIG. 1 is a perspective view showing a heat exchanger according to this embodiment. - [
FIG. 2] FIG. 2 is an exploded perspective view of the heat exchanger according to this embodiment. - [
FIG. 3] FIG. 3A is a front view of the heat exchanger according to this embodiment, andFIGS. 3B to 3D are sectional views taken along the arrowed lines A-A, B-B, and C-C inFIG. 3A . - [
FIG. 4] FIG. 4 shows a refrigerant channel in the heat exchanger according to this embodiment. - [
FIG. 5 ]FIGS. 5A and5B schematically show a state where a refrigerant (liquid component) flows in the heat exchanger according to this embodiment,FIG. 5A shows a first block of the heat exchanger, andFIG. 5B shows a second block of the heat exchanger. - [
FIG. 6 ]FIGS. 6A and6B schematically show a state where a refrigerant (liquid component) flows in another heat exchanger according to this embodiment,FIG. 6A shows a first block of the heat exchanger, andFIG. 6B shows a second block of the heat exchanger. - [
FIG. 7 ]FIGS. 7A and7B schematically show a state where a refrigerant (liquid component) flows in a heat exchanger of a comparative example,FIG. 7A shows a first block of the heat exchanger, andFIG. 7B shows a second block of the heat exchanger. - [
FIG. 8] FIG. 8 is a sectional view of a tank in the heat exchanger according to this embodiment. - [
FIG. 9] FIG. 9 is a perspective view showing a heat exchanger disclosed inPatent Document 1. - Now, an embodiment of the present invention will be described in detail. A
heat exchanger 10 according to this embodiment is suitably used in an evaporator in a refrigeration cycle for an air conditioner mounted in an automobile. - As shown in
FIGS. 1 to 4 , theheat exchanger 10 includes a core 20 in which a plurality offirst tubes 21 andsecond tubes 22 through which a refrigerant flows, and a plurality offins 23 are alternately stacked, anupper tank 30 to which one end (upper end in the drawings) of each of thefirst tubes 21 and thesecond tubes 22 is connected, and alower tank 40 to which the other end (lower end in the drawings) of each of thefirst tubes 21 and thesecond tubes 22 is connected. Theheat exchanger 10 performs heat exchange of the refrigerant using heat transferred to thecore 20. - The
first tubes 21 and thesecond tubes 22 are made of copper, a copper alloy, aluminum, or an aluminum alloy, and are members produced by extrusion molding or roll molding of a plate material and having a hollow portion and a rectangular section. In theheat exchanger 10, thefirst tubes 21 and thesecond tubes 22 are arranged in two rows in a width direction (Y direction inFIG. 2 ). The upper ends of thefirst tubes 21 and thesecond tubes 22 are connected to theupper tank 30, and the lower ends of thefirst tubes 21 and thesecond tubes 22 are connected to thelower tank 40. Thus, theupper tank 30, thefirst tubes 21, thesecond tubes 22, and thelower tank 40 are communicated with each other to allow passage of the refrigerant. This connection is generally performed by blazing. The sectional shape of the first tube(s) 21 and the second tube(s) 22 is not limited to the rectangular shape, but may be a circular shape or other shapes. - The
fin 23 is made of the same material as that of thefirst tube 21 and thesecond tube 22. In this embodiment, a corrugated fin molded by roll molding is used, but not limited to this, a plate fin may be used. - In the
core 20, the first andsecond tubes fins 23 are alternately stacked in a longitudinal direction (X direction inFIG. 2 ) of theheat exchanger 10, and the both ends are sealed byside plates 24. Theside plate 24 functions as a reinforcing member of the core 20, and the both ends in a longitudinal direction thereof are supported by theupper tank 30 and thelower tank 40. - The
upper tank 30 mainly includes atank plate 31 and anend plate 32, and is assembled so that openings of the plates face each other. In theupper tank 30, anupper partition plate 33 is provided along a longitudinal direction. Theupper partition plate 33 partitions an inside of theupper tank 30 at a middle in a width direction. One of partitioned sides constitutes a first tank T1, and the other constitutes a fourth tank T4. Thefirst tube 21 is connected to a lower surface of the first tank T1, and thesecond tube 22 is connected to a lower surface of the fourth tank T4. Since theupper partition plate 33 is provided between the first tank T1 and the fourth tank T4, the refrigerant is not directly moved between the tanks T1 and T4. - A
cap 34 is provided on one end side in the longitudinal direction of theupper tank 30. Thecap 34 has a refrigerant inflow hole hin and a refrigerant outflow hole hex. Acap 35 is provided on the other end side in the longitudinal direction of theupper tank 30. Thecap 35 seals the other end in the longitudinal direction of theupper tank 30. - The
lower tank 40 mainly includes atank plate 41 and anend plate 42, and is assembled so that openings of the plates face each other. In thelower tank 40, alower partition plate 43 is provided along a longitudinal direction. Thelower partition plate 43 partitions an inside of thelower tank 40 at a middle in a width direction. One of partitioned sides constitutes a second tank T2, and the other constitutes a third tank T3. Thefirst tube 21 is connected to an upper surface of the second tank T2, and thesecond tube 22 is connected to an upper surface of the third tank T3. - The
lower partition plate 43 hasrefrigerant passages 43h passing therethrough in a thickness direction. The plurality of (seven in this example)refrigerant passages 43h are locally provided on one end side in a longitudinal direction of thelower partition plate 43. Therefrigerant passages 43h are placed on the opposite side of the refrigerant inflow hole hin that is a refrigerant inlet in the longitudinal direction of theheat exchanger 10. - In the
lower tank 40, thelower partition plate 43 is provided between the second tank T2 and the third tank T3, but the refrigerant flows from the second tank T2 into the third tank T3 through the plurality ofrefrigerant passages 43h locally placed on the opposite side of the refrigerant inlet (hereinafter referred to as a counter-inlet side). Therefrigerant passages 43h are preferably provided within a range of 20% or less of the entire length of thelower partition plate 43. Increasing a flow rate of the refrigerant having passed through therefrigerant passages 43h is effective for uniformly mixing the gas component and the liquid component in the refrigerant. InFIG. 2 , therefrigerant passages 43h are constituted by a plurality of circular holes, but may be one or more wide refrigerant passages having a longer diameter in the longitudinal direction of thelower partition plate 43. However, in order to uniformly mix the gas component and the liquid component, it is preferable to provide the plurality ofrefrigerant passages 43h having a small diameter as in this embodiment. - In the
lower tank 40, distribution adjusting plates (resistors) 46, 47 and 48 are provided in the third tank T3. Thedistribution adjusting plates distribution adjusting plates holes refrigerant passages 43h into the third tank T3 successively passes through the throughholes distribution adjusting plates distribution adjusting plates distribution adjusting plates - The
distribution adjusting plates distribution adjusting plates distribution adjusting plates - The distribution adjusting plate 46 (first distribution adjusting plate from an upstream end, "first resistor") provided for the above-described purpose is preferably provided in a position relatively close to the upstream end of the third tank T3. As a specific index, the
distribution adjusting plate 46 is provided within a range of 30% or less of the entire length of thelower partition plate 43 from the upstream end. - An opening rate of the through
holes distribution adjusting plates holes - when a plurality of
distribution adjusting plates holes holes - A
cap 44 is provided on one end side in the longitudinal direction of thelower tank 40. Thecap 44 seals one end side in the longitudinal direction of thelower tank 40. Acap 45 is provided on the other end side in the longitudinal direction of thelower tank 40. Thecap 45 seals the other end side in the longitudinal direction of thelower tank 40. - The flow of the refrigerant in the
heat exchanger 10 configured as described above will be described. In theheat exchanger 10, the refrigerant channel is constituted by the first block and the second block, and the refrigerant flows in theheat exchanger 10 in order of the first block and the second block. The first block includes the first tank T1, thefirst tube 21, and the second tank T2, and the second block includes the third tank T3, thesecond tube 22, and the fourth tank T4. - When the
heat exchanger 10 is used as the evaporator of the refrigeration cycle, the refrigerant having brought into a gas-liquid two-phase state by an expansion valve placed on the upstream side with respect to theheat exchanger 10 flows through the refrigerant inflow hole hin (refrigerant inlet) into the first tank T1. - The refrigerant having flowed into the first tank T1 flows vertically downward in the
first tube 21 and reaches the second tank T2. During flowing in thefirst tube 21, the refrigerant is subjected to heat exchange with air passing through the core 20 with the liquid component being vaporized. - In the refrigerant flowing vertically downward in the
first tube 21, the ratio between the gas component and the liquid component varies in the longitudinal direction of theheat exchanger 10. This is schematically shown inFIG. 7A . InFIG. 7A , the ratio of the liquid component in the refrigerant is shown by arrows. The ratio of the liquid component is higher in thefirst tube 21 on the side closer to the refrigerant inlet. Since the liquid component has higher resistance to an inner wall of the first tank T1 than the gas component, the liquid component is hard to flow in a position farther from the refrigerant inlet. - The refrigerant having flowed into the second tank T2 flows through the
refrigerant passage 43h into the third tank T3. Since therefrigerant passages 43h are locally provided on the counter-inlet side of thelower partition plate 43, the refrigerant having flowed in thefirst tube 21 in a position closer to the counter-inlet side among thefirst tubes 21 first flows through therefrigerant passages 43h into the third tank T3. The refrigerant having flowed into the third tank T3 flows vertically upward in thesecond tube 22 and reaches the fourth tank T4. During flowing in thesecond tube 22, the refrigerant is subjected to heat exchange with air passing through the core 20 while the liquid component is vaporized. The refrigerant with the liquid component being vaporized during flowing through theheat exchanger 10 flows through the fourth tank T4, and is discharged from the refrigerant flow-out hole hex toward a compressor placed on the downstream side. - If the
refrigerant passages 43h are formed over the entire region in the longitudinal direction of the second tank T2 (or the third tank T3), the ratio of the liquid component of the refrigerant flowing vertically upward in the second tube 22 (second block) is higher in thesecond tube 22 on the side closer to the refrigerant inlet as shown inFIG. 7B because the state of the first tube 21 (first block) is taken over. This state is shown by dash-single-dot lines inFIG. 5B . - On the other hand, in the
heat exchanger 10, therefrigerant passages 43h are locally provided on the counter-inlet side of thelower partition plate 43, and thus the refrigerant having flowed in thefirst tube 21 in the position closer to the counter-inlet side among thefirst tubes 21 first flows through therefrigerant passages 43h into the third tank T3. Thus, in the second block, as shown by solid lines inFIG. 5B , non-uniform distribution of the gas component and the liquid component in the longitudinal direction that has occurred in the first block (FIGS. 5A and7A ) is eliminated. The dash-single-dot lines inFIG. 5B indicate the ratio of the liquid component when therefrigerant passages 43h are formed over the entire region in the longitudinal direction of the third tank T3. - In the above embodiment, the example in which the refrigerant inlet and the refrigerant outlet are provided on the same side of the
upper tank 30 has been described. However, as shown inFIGS. 6A and6B , the same applies to a heat exchanger in which a refrigerant outlet is provided on the opposite side of the refrigerant inlet. - The embodiment of the present invention has been described, but further, the configurations described in the embodiment may be chosen or changed to other configurations without departing from the gist of the present invention.
- For example, as shown in
FIGS. 8A and 8B , the position and shape of theupper partition plate 33 may be adjusted so that the refrigerant channel area of the fourth tank T4 is larger than the refrigerant channel area of the first tank T1. Similarly, the position and shape of thelower partition plate 43 may be adjusted so that the refrigerant channel area of the third tank T3 is larger than the refrigerant channel area of the second tank T2. This can reduce pressure loss in the third tank T3 and the fourth tank T4 in which the ratio of the gas component is higher than in the first tank T1 and the second tank T2 without changing the external size of theheat exchanger 10. Further, as shown inFIG. 8C , a width (refrigerant channel area) of thesecond tube 22 that constitutes the second block may be larger than a width (refrigerant channel area) of thefirst tube 21 that constitutes the first block. This can reduce pressure loss of the refrigerant in the second block in which the ratio of the gas component is higher than in the first block without changing the external size of theheat exchanger 10. -
- 10 ... heat exchanger
- 20 ... core, 21 ... first tube, 22 ... second tube, 23 ... fin
- 30 ... upper tank, 33 ... upper partition plate
- 40 ... lower tank, 43 ... lower partition plate, 43h ... refrigerant passage
- 46, 47, 48 ... distribution adjusting plate, 46h, 47h, 48h ... through hole
- T1 ... first tank, T2 ... second tank, T3 ... third tank, T4 ... fourth tank
Claims (9)
- A heat exchanger in which a refrigerant successively passes through a first block and a second block and flows out of the second block,
wherein the first block includes a first tank having a refrigerant inlet through which the refrigerant flows in, a plurality of first tubes into which the refrigerant having flowed into the first tank is distributed and flows therein, and a second tank in which the refrigerant flowing in the first tubes merges,
the second block includes a third tank into which the refrigerant having merged in the second tank flows, a plurality of second tubes into which the refrigerant having flowed into the third tank is distributed and flows therein, and a fourth tank in which the refrigerant flowing in the second tube merges, and having a refrigerant outlet through which the merged refrigerant flows out, and
a refrigerant passage through which the refrigerant flows from the second tank into the third tank is locally placed on the opposite side of the refrigerant inlet. - The heat exchanger according to claim 1, wherein the first block and the second block are placed in parallel with each other,
the first tank and the fourth tank are placed on a vertically upper side, and
the second tank and the third tank are placed on a vertically lower side. - The heat exchanger according to claim 1 or 2, wherein the refrigerant passage through which the refrigerant flows from the second tank into the third tank is formed by providing a plurality of holes in a partition member provided between the second tank and the third tank.
- The heat exchanger according to claim 1, wherein the third tank includes at least one resistor against the refrigerant, and
the resistor is placed on a rear side of the refrigerant passage in a flow direction of the refrigerant. - The heat exchanger according to claim 4, wherein the third tank includes a plurality of the resistors.
- The heat exchanger according to claim 5, wherein the third tank includes a first resistor, and a second resistor placed on a rear side of the first resistor in the flow direction of the refrigerant, and
an opening rate of the second resistor is equal to or lower than an opening rate of the first resistor. - The heat exchanger according to claim 2, wherein a refrigerant channel area in the fourth tank that constitutes the second block is larger than a refrigerant channel area in the first tank that constitutes the first block.
- The heat exchanger according to claim 2, wherein a refrigerant channel area in the third tank that constitutes the second block is larger than a refrigerant channel area in the second tank that constitutes the first block.
- The heat exchanger according to claim 1, wherein a refrigerant channel area of the second tube that constitutes the second block is larger than a refrigerant channel area of the first tube that constitutes the first block.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2009044726A JP2010197008A (en) | 2009-02-26 | 2009-02-26 | Heat exchanger |
PCT/JP2010/001125 WO2010098056A1 (en) | 2009-02-26 | 2010-02-22 | Heat exchanger |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2402701A1 true EP2402701A1 (en) | 2012-01-04 |
EP2402701A4 EP2402701A4 (en) | 2013-01-16 |
Family
ID=42665274
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10745943A Withdrawn EP2402701A4 (en) | 2009-02-26 | 2010-02-22 | Heat exchanger |
Country Status (4)
Country | Link |
---|---|
US (1) | US20110220336A1 (en) |
EP (1) | EP2402701A4 (en) |
JP (1) | JP2010197008A (en) |
WO (1) | WO2010098056A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN108253665A (en) * | 2016-12-28 | 2018-07-06 | 株式会社京滨冷暖科技 | Evaporator |
WO2019219076A1 (en) * | 2018-05-17 | 2019-11-21 | 杭州三花研究院有限公司 | Heat exchanger |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012052715A (en) * | 2010-08-31 | 2012-03-15 | Mitsubishi Heavy Ind Ltd | Heat exchanger |
FR2965606B1 (en) * | 2010-09-30 | 2015-04-17 | Valeo Systemes Thermiques | HEAT EXCHANGER FOR MOTOR VEHICLE |
JP5829055B2 (en) * | 2011-06-03 | 2015-12-09 | サンデンホールディングス株式会社 | Heat exchanger |
JP5913913B2 (en) * | 2011-11-07 | 2016-04-27 | サンデンホールディングス株式会社 | Indoor condenser |
KR101826365B1 (en) * | 2012-05-04 | 2018-03-22 | 엘지전자 주식회사 | A heat exchanger |
JP6228730B2 (en) * | 2012-09-07 | 2017-11-08 | 富士通株式会社 | Radiator, electronic device and cooling device |
KR101462176B1 (en) * | 2013-07-16 | 2014-11-21 | 삼성전자주식회사 | Heat exchanger |
KR20150133035A (en) * | 2014-05-19 | 2015-11-27 | 한온시스템 주식회사 | Outdoor heat exchanger |
US20220134845A1 (en) * | 2019-02-25 | 2022-05-05 | Hanon Systems | Heat exchanger and vehicle air conditioning system |
WO2020245836A1 (en) * | 2019-06-04 | 2020-12-10 | Pranav Vikas India Pvt. Limited | Ccf heater core assembly |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0626780A (en) * | 1992-07-13 | 1994-02-04 | Nippondenso Co Ltd | Heat exchanger |
EP1065453A2 (en) * | 1999-07-02 | 2001-01-03 | Denso Corporation | Refrigerant evaporator with refrigerant distribution |
US20050247443A1 (en) * | 2004-04-28 | 2005-11-10 | Kim Jae H | Header pipe evaporator for use in an automobile |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3391339B2 (en) * | 1999-07-02 | 2003-03-31 | 株式会社デンソー | Refrigerant evaporator |
JP2002147990A (en) * | 2000-11-09 | 2002-05-22 | Zexel Valeo Climate Control Corp | Heat exchanger |
JP2004163036A (en) * | 2002-11-14 | 2004-06-10 | Japan Climate Systems Corp | Double row heat exchanger |
JP4630591B2 (en) | 2003-07-08 | 2011-02-09 | 昭和電工株式会社 | Heat exchanger |
JP5046771B2 (en) * | 2007-07-27 | 2012-10-10 | 三菱重工業株式会社 | Refrigerant evaporator |
-
2009
- 2009-02-26 JP JP2009044726A patent/JP2010197008A/en active Pending
-
2010
- 2010-02-22 WO PCT/JP2010/001125 patent/WO2010098056A1/en active Application Filing
- 2010-02-22 US US13/130,459 patent/US20110220336A1/en not_active Abandoned
- 2010-02-22 EP EP10745943A patent/EP2402701A4/en not_active Withdrawn
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0626780A (en) * | 1992-07-13 | 1994-02-04 | Nippondenso Co Ltd | Heat exchanger |
EP1065453A2 (en) * | 1999-07-02 | 2001-01-03 | Denso Corporation | Refrigerant evaporator with refrigerant distribution |
US20050247443A1 (en) * | 2004-04-28 | 2005-11-10 | Kim Jae H | Header pipe evaporator for use in an automobile |
Non-Patent Citations (1)
Title |
---|
See also references of WO2010098056A1 * |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN108253665A (en) * | 2016-12-28 | 2018-07-06 | 株式会社京滨冷暖科技 | Evaporator |
CN108253665B (en) * | 2016-12-28 | 2020-08-11 | 株式会社京滨冷暖科技 | Evaporator with a heat exchanger |
WO2019219076A1 (en) * | 2018-05-17 | 2019-11-21 | 杭州三花研究院有限公司 | Heat exchanger |
EP3745069A4 (en) * | 2018-05-17 | 2021-09-15 | Zhejiang Sanhua Intelligent Controls Co., Ltd. | Heat exchanger |
US11268767B2 (en) | 2018-05-17 | 2022-03-08 | Hangzhou Sanhua Research Institute Co., Ltd. | Heat exchanger |
Also Published As
Publication number | Publication date |
---|---|
WO2010098056A1 (en) | 2010-09-02 |
EP2402701A4 (en) | 2013-01-16 |
JP2010197008A (en) | 2010-09-09 |
US20110220336A1 (en) | 2011-09-15 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2402701A1 (en) | Heat exchanger | |
US9366463B2 (en) | Evaporator | |
US8176750B2 (en) | Heat exchanger | |
US6827139B2 (en) | Heat exchanger for exchanging heat between internal fluid and external fluid and manufacturing method thereof | |
EP2853843B1 (en) | A refrigerant distributing device, and heat exchanger equipped with such a refrigerant distributing device | |
JP4810203B2 (en) | Heat exchanger | |
JP4281634B2 (en) | Refrigerant evaporator | |
US20090166017A1 (en) | Heat exchanger | |
US7367388B2 (en) | Evaporator for carbon dioxide air-conditioner | |
US20070131398A1 (en) | Heat exchanger | |
EP2865983B1 (en) | Heat-exchanger header and heat exchanger provided therewith | |
JP2006132920A (en) | Heat exchanger | |
US8302427B2 (en) | Evaporator | |
JP2006170598A (en) | Heat exchanger | |
JP2006105581A (en) | Laminated heat exchanger | |
US10408510B2 (en) | Evaporator | |
JP2005195316A (en) | Heat exchanger | |
JP2012052715A (en) | Heat exchanger | |
JP2011257111A (en) | Evaporator | |
JP5194279B2 (en) | Evaporator | |
US20180149431A1 (en) | Evaporator | |
JP5674376B2 (en) | Evaporator | |
JP4547205B2 (en) | Evaporator | |
JP4095818B2 (en) | Heat exchanger | |
KR100585403B1 (en) | heat exchanger of header type |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20110520 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR |
|
DAX | Request for extension of the european patent (deleted) | ||
A4 | Supplementary search report drawn up and despatched |
Effective date: 20121219 |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F28F 9/02 20060101AFI20121213BHEP |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN |
|
18D | Application deemed to be withdrawn |
Effective date: 20130718 |