JP2010175168A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an evaporator capable of reducing the number of components and a region of a superheat part. <P>SOLUTION: The evaporator 1 includes: a pair of header tanks 2, 3 arranged at intervals between them; a plurality of flat heat exchange pipes 4 which are arranged between both header tanks 2, 3 so as to make the width direction face the forward/backward direction and be lined up in the length direction of the both header tanks 2, 3 at intervals and have both ends connected to both header tanks 2, 3, respectively; and fins arranged between the adjacent heat exchange pipes 4. Within a pipe line 22 of the heat exchange pipe 4, first flow control members 23 extended rearward from a front edge of the pipe line 22 and second flow control members 24 extended forward from a rear edge of the pipe line 22 are alternately provided, at intervals in the length direction of the heat exchange pipe 4. The length of the both flow control members 23, 24 is set to be 1/2 or more of the width in the forward/backward direction of the pipe line 22 in the heat exchange pipe 4. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an evaporator suitably used for, for example, a car air conditioner mounted on an automobile.

  In this specification and claims, the downstream side of the air flowing in the ventilation gap between adjacent heat exchange pipes (the direction indicated by the arrow X in FIGS. 1, 3, 6, 7 and 9). The front and the opposite side are the back.

  In recent years, as a heat exchanger used in an evaporator for a car air conditioner that can be reduced in size, weight, and performance, the present applicant has previously made a pair of header tanks spaced apart from each other, and both header tanks. A plurality of flat heats arranged in two rows in the front and rear, with the width direction facing in the front-rear direction and spaced in the longitudinal direction of the header tank. Proposed heat exchanger that has exchange pipes and corrugated fins arranged between adjacent heat exchange pipes, and each heat exchange pipe has a plurality of refrigerant channels arranged in the width direction (See Patent Document 1).

  However, in the heat exchanger described in Patent Document 1, since the heat exchange tubes are arranged in two rows in the ventilation direction, the number of heat exchange tubes increases and the number of parts increases.

  As an evaporator with a reduced number of parts, a pair of header tanks arranged at a distance from each other, and a distance between the header tanks in the length direction of the header tank so that the width direction faces the front-rear direction. A plurality of flat heat exchange pipes arranged in a row and having both upper and lower ends connected to both header tanks, and corrugated fins arranged between adjacent heat exchange pipes. An evaporator having a plurality of refrigerant channels in which exchange tubes are arranged in the width direction is conceivable.

  However, the evaporator having the heat exchange tubes arranged in a row has the following problems. That is, the refrigerant flowing through the refrigerant flow path upstream in the ventilation direction in the heat exchange pipe evaporates in a short time and becomes overheated, so that the refrigerant flowing downstream in the ventilation direction is also easily heated, and as a result, the refrigerant is completely discharged. The part which becomes a superheated state as a phase, that is, the region of the superheat part becomes large.

JP 2008-20098 A

  An object of the present invention is to provide an evaporator that can solve the above problems, reduce the number of parts, and reduce the area of the superheat section.

  In order to achieve the above object, the present invention comprises the following aspects.

  1) A pair of header tanks that are spaced apart from each other, and between the header tanks, the width direction is directed in the front-rear direction and the header tanks are arranged in a row at intervals in the length direction of the header tank. And a plurality of flat heat exchange pipes whose both ends are connected to both header tanks, and fins arranged between adjacent heat exchange pipes, in the pipe line of the heat exchange pipe, The first flow control member extending rearward from the front edge of the pipe and the second flow control member extending forward from the rear edge of the pipe are alternately provided at intervals in the length direction of the heat exchange pipe. An evaporator in which the lengths of both flow control members are ½ or more of the width in the front-rear direction of the pipe line in the heat exchange pipe.

  2) The distances between the rear ends of all the first flow control members and the rear edge of the pipe are equal, and the distances between the front ends of all the second flow control members and the front edge of the pipe are equal. The effective heat exchange length of the heat exchange pipe is L, the total number of the first flow control member and the second flow control member is N, and the distance between the rear end of the first flow control member and the rear edge of the pipe is D1, where the distance between the front end of the second flow control member and the front edge of the pipeline is D2, the above 1 satisfying the relationship of 1.5L <(D1 + D2) / 2 × (N−1) + L <2.5L Evaporator as described.

  3) The distance D1 between the rear end of the first flow control member and the rear edge of the pipe is equal to the distance D2 between the front end of the second flow control member and the front edge of the pipe, and the first The evaporator according to the above item 2) that satisfies the relationship of 0.5D1 <S <1.5D1, where S is the distance between the flow control member and the second flow control member.

  4) A refrigerant outlet header portion having a refrigerant outlet is provided in one of the header tanks, and the first flow control member and the second flow control member adjacent to each other in the heat exchange pipe communicated with the refrigerant outlet header portion. The evaporator according to any one of the above items 1) to 3), in which the distance between the first and second refrigerants becomes wider toward the refrigerant outlet header.

  5) A plurality of protrusions are formed inwardly on the inner surfaces of a pair of side walls facing each other of the heat exchange pipe, and the protrusions on one side wall are joined to the protrusions on the other side wall. The evaporator according to any one of 4).

  6) Two or more heat exchange tube groups are arranged in the length direction of the header tank, and one end portion in the length direction of the header tank. The heat exchange pipe group is the most upstream side heat exchange pipe group in which the refrigerant first flows in the heat exchange pipe constituting the heat exchange pipe group, and the heat exchange pipe group at the other end in the length direction of the header tank is It is the most downstream side heat exchange tube group in which the refrigerant flows last in the heat exchange tube constituting the heat exchange tube group, and the refrigerant flows from one first header tank side to the other second header tank side. And a flow from the second header tank side to the first header tank side following the flow from the first header tank side to the second header tank side, and from the most upstream side heat exchange tube group to the most downstream side heat exchange tube The bottom of the first header tank is made to flow towards the group A refrigerant inlet and a refrigerant outlet are formed at an end portion on the side where the side heat exchange pipe group is provided, and the first header tank has a first flow-in member extending over the entire length of the first header tank by the flow dividing control member. A plurality of compartments divided into a space and a second space that extends to the entire length of the first header tank and communicates with the heat exchange pipe, and the inside of the second space is aligned in the length direction of the first header tank by a partition member And the heat exchange tubes of each heat exchange tube group are communicated with the compartments of the second space, the first space communicates with the refrigerant inlet, and the heat exchange of the most downstream heat exchange tube group in the second space. A section that communicates with the pipe communicates with the refrigerant outlet, and the first space in the first header tank communicates with the section that communicates with the heat exchange pipe of the most upstream side heat exchange pipe group in the second space. Heat exchange of the uppermost stream side heat exchange tube group in space The above-mentioned 1) to 4), in which the section through which the exchange pipe communicates is the refrigerant inlet header section, and the section through which the heat exchange pipe of the most downstream side heat exchange pipe group is also communicated is the refrigerant outlet header section. The evaporator according to any one of the above.

  According to the above evaporators 1) to 3), the two tanks are arranged so that the width direction is directed in the front-rear direction and the header tanks are arranged in a line at intervals in the length direction of the header tanks. Since a plurality of flat heat exchange tubes connected to both header tanks are provided, the number of components can be reduced as compared with the evaporator described in Patent Document 1 provided with heat exchange tubes arranged in two rows. It becomes possible.

  In addition, the first flow control member extending backward from the front edge of the pipe and the second flow control member extending forward from the rear edge of the pipe in the pipe of the heat exchange pipe are the length of the heat exchange pipe. Since the lengths of both flow control members are ½ or more of the internal width of the heat exchange pipe, the refrigerant is contained in the heat exchange pipe line. It will flow in a meandering manner while changing the flow direction. Therefore, when the refrigerant flows through the gap between the rear end of the first flow control member and the rear edge of the pipe in the pipe of the heat exchange pipe, the rear of the gap (the upstream side in the ventilation direction) The flowing refrigerant is heated by high-temperature air and evaporates in a short time to become a gas phase. However, when the flow direction is changed in the pipe, it flows near the front of the gap (downstream in the ventilation direction). Efficiently mixed with liquid phase refrigerant. As a result, it is possible to reduce the region where the refrigerant is completely vaporized and becomes superheated, that is, the region of the superheat portion.

  According to the evaporator of 4) above, in the heat exchange pipe communicated with the refrigerant outlet header portion, the interval between the adjacent first flow control member and second flow control member becomes wider toward the refrigerant outlet header portion. Therefore, it is possible to suppress an increase in passage resistance at a portion where a lot of gas-phase refrigerant flows.

  According to the evaporator 5), the mixing effect of the refrigerant flowing in the pipe lines described in 1) to 3) is improved, and the region of the superheat portion can be reduced. Moreover, the pressure resistance of the heat exchange tube is improved.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a partially cutaway perspective view showing an overall configuration of an evaporator according to Embodiment 1 of the present invention. FIG. 2 is a partially omitted vertical cross-sectional view of the evaporator of FIG. 1 viewed from the rear to the front. It is the sectional view on the AA line of FIG. FIG. 4 is an enlarged sectional view taken along line B-B in FIG. 3. FIG. 4 is an enlarged sectional view taken along the line CC in FIG. 3. It is a figure which shows the flow of the refrigerant | coolant in the evaporator of FIG. It is a vertical sectional view showing a modification of the heat exchange pipe of the most downstream heat exchange pipe group of the evaporator of FIG. It is a figure which shows the modification of a heat exchange pipe | tube. FIG. 7 is a view corresponding to FIG. 6, showing an evaporator according to Embodiment 2 of the present invention.

  Embodiments of the present invention will be described below with reference to the drawings. In the embodiment described below, the evaporator according to the present invention is applied to a car air conditioner using a chlorofluorocarbon refrigerant.

  In the following description, the term “aluminum” includes aluminum alloys in addition to pure aluminum.

  In the following description, the upper and lower sides and the left and right sides of FIGS.

  Moreover, the same code | symbol is attached | subjected to the same part and the same thing through all drawings, and the overlapping description is abbreviate | omitted.

  1 and 2 show the overall structure of the evaporator according to the present invention, and FIGS. 3 to 5 show the structure of the main part thereof. FIG. 6 shows how the refrigerant flows in the evaporator.

  1 to 3, the evaporator (1) includes an aluminum first header tank (2) and an aluminum second header tank (3) that extend in the left-right direction and are spaced apart in the vertical direction. Between the header tanks (2) and (3), the width direction is oriented in the front-rear direction and the left and right sides are arranged in a row, and both upper and lower ends are located on both header tanks (2) and (3). The flat aluminum heat exchange pipe (4) connected and the ventilation gap between the adjacent heat exchange pipes (4) and the heat exchange pipes (4) arranged outside the heat exchange pipes (4) at both left and right ends ( 4) an aluminum corrugated fin (5) brazed to (4) and an aluminum side plate (6) disposed outside the corrugated fin (5) at both ends and brazed to the corrugated fin (5). Lined up continuously in the left-right direction (length direction of header tanks (2) and (3)) Consisting a plurality of heat exchange tubes (4), wherein the two heat exchange tube group (7A) (7B), are arranged in the lateral direction. In the heat exchange tube group (7A) on the left side (one end in the length direction of the header tanks (2) and (3)), the fluid first passes through the heat exchange tube (4) constituting the heat exchange tube group (7A). The heat exchange pipe group (7B) on the right side (the other end in the length direction of the header tanks (2) and (3)) constitutes the heat exchange pipe group (7B). This is the most downstream side heat exchange pipe group in which the fluid finally flows in the heat exchange pipe (4).

  A refrigerant inlet (8) and a refrigerant outlet (9) are formed at the right end of the first header tank (2). The first header tank (2) has a first space (12) through which the refrigerant (fluid) flows, and a first header, over the entire length of the first header tank (2) by a plate-like flow dividing control member (11). The tank (2) is divided into a second space (13) extending over the entire length of the tank (2) and leading to the heat exchange pipe (4). The flow dividing control member (11) is formed by pressing separately from the first header tank (2), and includes a lower end portion of the front wall (2a) of the first header tank (2) and an upper wall ( 2b) is arranged so as to straddle between the front part and the front part of the front and rear direction, and is joined to the first header tank (2), from the front edge part toward the rear edge part. Inclined upward. The space surrounded by the front wall (2a), the upper wall (2b) and the flow control member (11) of the first header tank (2) becomes the first space (12), and the first header tank (2) A space surrounded by the rear wall (2c), the upper wall (2b), the lower wall (2d), and the flow control member (11) is a second space (13). The left and right end portions of the flow dividing control member (11) are joined to the left and right end walls of the first header tank (2). Therefore, the flow dividing control member (11) divides the first space (12) and the second space (13). The refrigerant inlet (8) communicates with the first space (12).

  In the second space (13) of the first header tank (2), a vertical plate-like partition member disposed at the center in the left-right direction and joined to the first header tank (2) and the flow control member (11). (14) is divided into two compartments (15A) (15B) of the same number as the heat exchange tube groups (7A) (7B) arranged in the left-right direction, and each heat exchange tube group (7A) (7B) A heat exchange pipe (4) is connected to each section (15A) (15B) of the second space (13). The refrigerant outlet (9) communicates with the right compartment (15B) of the second space (13). The left compartment (15A) through which the heat exchange pipe (4) of the uppermost stream side heat exchange pipe group (7A) in the first space (12) and the second space (13) communicates with the flow dividing control member (11) A plurality of fluid passage holes (16) that communicate with each other are formed at intervals in the left-right direction. The section (15A) through which the heat exchange pipe (4) of the uppermost stream side heat exchange pipe group (7A) in the second space (13) communicates is the refrigerant inlet header portion (17), A section (15B) through which the heat exchange pipe (4) of the downstream heat exchange pipe group (7B) communicates forms a refrigerant outlet header (18).

  As shown in FIGS. 3 to 5, the heat exchange tube (4) is formed by brazing the front and rear side edges of two vertically long rectangular aluminum plates (21) over the entire length, A pipe line (22) extending in the vertical direction and having both upper and lower ends opened is formed between both aluminum plates (21). In the pipe line (22) of the heat exchange pipe (4), a first flow control member (23) extending rearward from the front edge of the pipe line (22) and a first flow control member extending forward from the rear edge of the pipe line (22). Two flow control members (24) are alternately provided in the up-down direction (the length direction of the heat exchange pipe (4)) at intervals. The lengths T of the two flow control members (23) and (24) are equal to each other, and the lengths T of the two flow control members (23) and (24) correspond to the pipe lines (22 in the heat exchange pipe (4)). ) Of the width W in the front-rear direction. The distances D1 between the rear ends of all the first flow control members (23) and the rear edges of the pipes (22) are equal, and the front ends of all the second flow control members (24) and the pipes The distance D2 from the front edge of (22) is equal. Further, the distance D1 between the rear end of the first flow control member (23) and the rear edge of the pipe (22), and the distance between the front end of the second flow control member (24) and the front edge of the pipe (22). D2 is equal. Further, the total distance S between the adjacent first flow control member (23) and the second flow control member (24) is equal. Both flow control members (23), (24) are provided by forming protrusions (21a) projecting inward on both aluminum plates (21) and brazing the protrusions (21a). .

  Here, the effective heat exchange length of the heat exchange pipe (4) is L, the total number of all the first flow control members (23) and all the second flow control members (24) is N, and the first flow control. When the distance between the rear end of the member (23) and the rear edge of the pipe (22) is D1, and the distance between the front end of the second flow control member (24) and the front edge of the pipe (22) is D2, It is preferable that the relationship of 1.5L <(D1 + D2) / 2 × (N−1) + L <2.5L is satisfied. In this case, the distance of the flow path through which the refrigerant flows can be made longer than the length of the heat exchange pipe (4), and the area of the superheat section described later can be reduced. The effective heat exchange length L is a portion where the wind hits between the header tanks (2) and (3) in the heat exchange pipe (4). Further, when the interval between the adjacent first flow control member (23) and the second flow control member (24) is S, it is preferable that the relationship of 0.5D1 <S <1.5D1 is satisfied. In this case, even if the width W in the front-rear direction of the pipe line (22) changes, the passage resistance can be lowered.

  In addition, a plurality of protrusions (21b) are formed in both aluminum plates (21) constituting the heat exchange pipe (4) so as to protrude inward, and the protrusions (25) of both aluminum plates (21) are mutually connected. It is brazed. That is, a plurality of projections (25) are formed inwardly projecting on the inner surfaces of a pair of side walls facing each other of the heat exchange pipe (4), and the projection (25) on one side wall is a projection on the other side wall (25).

  The evaporator (1) described above constitutes a refrigeration cycle that uses a chlorofluorocarbon refrigerant together with a compressor and a condenser as a refrigerant cooler, and is mounted on a vehicle, for example, an automobile, as a car air conditioner. And at the time of air_conditionaing | cooling operation, the two-phase refrigerant | coolant of the gas-liquid mixed phase which passed the compressor, the capacitor | condenser, and the expansion valve flows as shown in FIG. That is, the gas-liquid mixed phase two-phase refrigerant enters the first space (12) of the first header tank (2) through the refrigerant inlet (8). The refrigerant entering the first space (12) of the first header tank (2) flows to the left, passes through the fluid passage hole (16), and is the refrigerant in the left compartment (15A) of the second space (13). Enter the inlet header (17).

  The refrigerant that has entered the refrigerant inlet header portion (17) of the first header tank (2) is diverted into the pipe (22) of the heat exchange pipe (4) of the most upstream heat exchange pipe group (7A). Inflow. The refrigerant that has flowed into the pipe (22) of the heat exchange pipe (4) of the uppermost stream side heat exchange pipe group (7A) flows downward in the pipe (22) into the second header tank (3). enter. The refrigerant that has entered the second header tank (3) flows to the right, splits, and flows into the pipe (22) of the heat exchange pipe (4) of the most downstream heat exchange pipe group (7B). The refrigerant that has flowed into the pipe line (22) of the heat exchange pipe (4) of the most downstream side heat exchange pipe group (7B) flows upward in the pipe line (22) and flows into the first header tank (2). The refrigerant enters the refrigerant outlet header portion (18) which is the right section (15B) of the two spaces (13). The refrigerant that has entered the refrigerant outlet header portion (18) of the first header tank (2) flows to the right in the refrigerant outlet header portion (18) and flows out through the refrigerant outlet (8). That is, the refrigerant follows the flow from the first header tank (2) side to the second header tank (3) side and the flow from the first header tank (2) side to the second header tank (3) side. 2 Flow from the header tank (3) side to the first header tank (2) side once and flow from the most upstream side heat exchange pipe group (7A) toward the most downstream side heat exchange pipe group (7B) .

  While the refrigerant flows in the pipe line (22) of the heat exchange pipe (4), the air passing through the ventilation gap between the adjacent heat exchange pipes (4) (see arrows X in FIG. 1 and FIG. 6) and heat After replacement, the refrigerant flows out as a gas phase.

  When the refrigerant flows downward in the pipe line (22) of the heat exchange pipe (4) of the uppermost stream side heat exchange pipe group (7A), as shown in FIG. Enter the header tank (3). That is, it flows downward between the rear end of the first flow control member (23) and the rear edge of the pipe line (22), hits the second flow control member (24), changes the flow direction, and flows forward. The flow direction is changed by hitting the front edge of (22), and flows downward between the front end of the second flow control member (24) and the front edge of the pipe (22), and further hits the first flow control member (23). It repeats that it changes the direction and flows backward, flows downward, and enters the second header tank (3). When the refrigerant flows upward in the pipe (22) of the heat exchange pipe (4) of the most downstream heat exchange pipe group (7B), the heat exchange of the most upstream heat exchange pipe group (7A) It flows upwardly in a meandering manner in a manner opposite to that flowing downward in the pipe line (22) of the pipe (4) and enters the refrigerant outlet header portion (18) of the first header tank (2).

  When the refrigerant flows through the gap between the rear end of the first flow control member (23) and the rear edge of the pipe (22) in the pipe (22) of the heat exchange pipe (4), the gap Refrigerant flowing downstream (upstream side in the ventilation direction) is heated by high-temperature air and evaporates in a short time to become a gas phase. However, the refrigerant flows in front of the gap (downstream in the ventilation direction). Since most of the liquid is in the liquid phase, the gas phase refrigerant and the liquid phase refrigerant are efficiently mixed when the flow direction is changed in the pipe (22). As a result, the part where the refrigerant is completely vaporized and overheated, that is, the superheat part, appears only at the upper end part of the most downstream heat exchange pipe group (7B), and the area of the superheat part is reduced. can do.

  FIG. 7 shows a modification of the heat exchange pipe of the most downstream side heat exchange pipe group (7B).

  In the case of the heat exchange pipe (30) of the most downstream side heat exchange pipe group (7B) shown in FIG. 7, the distance between the adjacent first flow control member (23) and second flow control member (24) is the second. It is widened toward the right partition (15B) of the space (13), that is, toward the refrigerant outlet header (18).

  In the heat exchange pipe (4) of the uppermost stream side heat exchange pipe group (7A), the distance between the adjacent first flow control member (23) and second flow control member (24) is the second header tank. (3) That is, it is preferably widened toward the downstream side in the refrigerant flow direction.

  FIG. 8 shows another modification of the heat exchange tube of the first embodiment.

  In the heat exchange pipe (31) shown in FIG. 8, instead of brazing the front and rear side edges of two aluminum plates, one aluminum plate (32) is bent and the side edge portions are joined together. It is formed by brazing.

  FIG. 9 shows another embodiment of the evaporator.

  The evaporator (35) shown in FIG. 9 includes an aluminum first header tank (2) and an aluminum second header tank (3) that extend in the left-right direction and are spaced apart in the vertical direction, and both header tanks ( Between 2) and (3), the width direction is oriented in the front-rear direction and arranged in a line at intervals in the left-right direction, and the upper and lower ends are connected to both header tanks (2) and (3). Aluminum which is placed outside the heat exchange pipe (4) between the heat exchange pipe (4) and the adjacent heat exchange pipe (4) and outside the heat exchange pipe (4) at the left and right ends and brazed to the heat exchange pipe (4) Corrugated fins (not shown) made of aluminum, and aluminum side plates (not shown) brazed to the corrugated fins are provided outside the corrugated fins at both ends. The first header tank (2) is not divided into two spaces.

  A refrigerant inlet (36) is formed at the right end of the second header tank (3), and a refrigerant outlet (37) is formed at the right end of the first header tank (1). The entire first header tank (2) is a refrigerant inlet header portion (38), and the entire second header tank (3) is a refrigerant outlet header portion (39).

  Instead of the heat exchange pipe (4), the distance between the adjacent first flow control member (23) and the second flow control member (24) as shown in FIG. A heat exchange pipe (30) that is widened toward the refrigerant outlet header (39) may be used.

  The evaporator according to the present invention is suitably used for a refrigeration cycle constituting a car air conditioner.

(1) (35): Evaporator
(2) (3): Header tank
(4) (30) (31): Heat exchange pipe
(5): Corrugated fin
(7A): Most upstream heat exchange tube group
(7B): Most downstream heat exchange tube group
(8) (36): Refrigerant inlet
(9) (37): Refrigerant outlet
(11): Shunt control member
(12): First space
(13): Second space
(15A) (15B): Section
(17) (38): Refrigerant inlet header
(18) (39): Refrigerant outlet header
(22): Pipe line
(23): First flow control member
(24): Second flow control member
(25): Projection

Claims (6)

A pair of header tanks spaced apart from each other, and arranged between the header tanks so that the width direction is directed in the front-rear direction and the header tanks are arranged in a line at intervals in the length direction; and It is provided with a plurality of flat heat exchange pipes whose both ends are connected to both header tanks, and fins arranged between adjacent heat exchange pipes. The first flow control member extending backward from the front edge of the pipe and the second flow control member extending forward from the rear edge of the pipe are alternately provided in the length direction of the heat exchange pipe, An evaporator in which the lengths of both flow control members are at least 1/2 of the width in the front-rear direction of the pipe line in the heat exchange pipe. The distances between the rear ends of all the first flow control members and the rear edge of the pipe line are equal, and the distances between the front ends of all the second flow control members and the front edge of the pipe line are equal; The effective heat exchange length of the heat exchange pipe is L, the total number of the first flow control member and the second flow control member is N, the distance between the rear end of the first flow control member and the rear edge of the pipe is D1, 2. The relationship of 1.5L <(D1 + D2) / 2 * (N-1) + L <2.5L is satisfied, where D2 is a distance between the front end of the second flow control member and the front edge of the pipe. The evaporator. The distance D1 between the rear end of the first flow control member and the rear edge of the pipe is equal to the distance D2 between the front end of the second flow control member and the front edge of the pipe, and the adjacent first flow control The evaporator according to claim 2, wherein when the distance between the member and the second flow control member is S, the relationship of 0.5D1 <S <1.5D1 is satisfied. Either one of the header tanks is provided with a refrigerant outlet header portion having a refrigerant outlet, and the adjacent first flow control member and second flow control member in the heat exchange pipe communicated with the refrigerant outlet header portion. The evaporator according to any one of claims 1 to 3, wherein the interval is widened toward the refrigerant outlet header. 5. A plurality of projections are formed inwardly projecting from the inner surfaces of a pair of opposite side walls of the heat exchange tube, respectively, and the projections on one side wall are joined to the projections on the other side wall. The evaporator as described in any one of them. Two or more heat exchange tube groups comprising a plurality of heat exchange tubes arranged continuously in the length direction of the header tank are provided side by side in the length direction of the header tank, and heat at one end of the header tank in the length direction is provided. The exchange tube group becomes the most upstream side heat exchange tube group in which the refrigerant first flows in the heat exchange tube constituting the heat exchange tube group, and the heat exchange tube group at the other end in the length direction of the header tank The most downstream side heat exchange pipe group in which the refrigerant flows last in the heat exchange pipe constituting the exchange pipe group, and the refrigerant flows from one first header tank side to the other second header tank side, and Including the flow from the second header tank side to the first header tank side following the flow from the first header tank side to the second header tank side, the most upstream side heat exchange tube group is changed to the most downstream side heat exchange tube group. The most downstream in the first header tank A refrigerant inlet and a refrigerant outlet are formed at the end portion on the side where the heat exchange pipe group is provided, and the first header tank has a first space in which the refrigerant flows through the entire length of the first header tank by the flow control member. And the second space that extends over the entire length of the first header tank and communicates with the heat exchange pipe, and the second space is divided into a plurality of sections arranged in the length direction of the first header tank by the partition member. In addition to being divided, the heat exchange tubes of each heat exchange tube group are communicated with a section of the second space, the first space communicates with the refrigerant inlet, and the heat exchange tube of the most downstream heat exchange tube group in the second space. Is connected to the refrigerant outlet, and the first space in the first header tank and the section in the second space through which the heat exchange pipe of the most upstream heat exchange pipe group communicates are communicated with each other. Heat exchange in the most upstream heat exchange tube group The section through which the pipe communicates serves as the refrigerant inlet header, and the section through which the heat exchange pipe of the most downstream heat exchange pipe group communicates serves as the refrigerant outlet header. The evaporator as described in any one of.

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