KR20060028809A - Heat exchanger - Google Patents

Abstract

A heat exchanger 1 comprises a refrigerant inlet-outlet tank 2, a refrigerant turn tank 3, and tube groups 5 in the form of at least two rows arranged between the two tanks 2, 3 and each comprising a plurality of heat exchange tubes 4. The refrigerant inlet-outlet tank 2 has its interior divided into a refrigerant inlet header chamber 13 and a refrigerant outlet header chamber 14. The refrigerant turn tank 3 has its interior divided by a divided flow control plate 44 into a refrigerant inflow header chamber 32 and a refrigerant outflow header chamber 33. The divided flow control plate 44 has refrigerant dam portions 45A, 45B at respective opposite end portions thereof, and a refrigerant passing portion 46 provided between the dam portions 45A, 45B and having one or at least two refrigerant passing holes 43. The heat exchanger 1 exhibits improved heat exchange performance when used as an evaporator.

Description

Heat exchanger {HEAT EXCHANGER}

Related Applications

This application is directed to US 35 U.S.C. 35 U.S.C., filed on the filing date of US Provisional Application Nos. 60 / 486,897 and 60 / 486,898, filed July 15, 2003, under §119 (b). 35 U.S.C. Claiming Benefits Under §119 (e) (1) Corresponds to US application filed under § 111 (a).

The present invention relates to a heat exchanger, and more particularly to a heat exchanger suitable for use as an evaporator of an automotive air conditioner, which is a refrigeration cycle to be mounted on an automobile.

The term "aluminum" as used herein and in the claims includes not only pure aluminum but also aluminum alloys.

BACKGROUND ART Conventionally, as a vehicle evaporator, a plurality of flat hollow bodies formed by opposing a pair of dish-shaped plates and brazing each other along its peripheral edge are arranged in parallel and attaching louvers between adjacent flat hollow bodies. So-called laminated plate type evaporators have been widely used, in which louvered corrugated fins are arranged and brazed to flat hollow bodies. However, in recent years, further miniaturization and high performance of the evaporator is required.

In order to satisfy this demand, the applicant has already provided a tube group consisting of a plurality of heat exchange tubes arranged in parallel with each other in the longitudinal direction of both tanks between the refrigerant inlet and outlet tanks and the refrigerant turn-side tanks which are arranged to be spaced apart from each other. And a plurality of rows spaced apart in the air flow direction through the evaporator, and both ends of the heat exchange tubes of each tube group are connected to the respective tanks, and the inside of the refrigerant inlet / outer tank is arranged in the air passage direction by the partition wall. Comprising a header chamber and a refrigerant outlet header chamber, the two header chambers communicate with the heat exchange tubes of each of the two tube groups, and the refrigerant introduced into the inlet header chamber of the refrigerant inlet / outlet tank is connected to the refrigerant turn-side tank through the corresponding heat exchange tube. Can be introduced, where the course is altered and through the corresponding heat exchange tube to the outlet header chamber of the refrigerant And an evaporator which is partitioned into a first space communicating with a corresponding heat exchange tube and a second space through which refrigerant flows out, by means of a diaphragm having a refrigerant passage hole inside the outlet header chamber of the refrigerant entry-side tank. (JP-A-2003-75024). In this evaporator, by the action of a diaphragm provided in the outlet header chamber and having a refrigerant passage hole, the refrigerant can flow in a uniform amount through the heat exchange tubes of the two tube groups, thereby improving the heat exchange performance of the evaporator. have.

However, as a result of further investigation by the present inventors, it has been found that even in the evaporator described in the above publication, there are still matters to be improved in the uniformity of the refrigerant flow through the heat exchange tubes of the tube group and the heat exchange performance.

An object of the present invention is to solve the above problems and to provide a heat exchanger having excellent heat exchange performance.

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

(1) A tube group consisting of a plurality of heat exchange tubes arranged in parallel with each other in the longitudinal direction of both tanks between the refrigerant inlet / outtake tanks and the refrigerant turn-side tanks disposed to be spaced apart from each other, in the air flow direction through the heat exchanger Installed in a plurality of rows, both ends of the heat exchange tubes of each tube group are connected to respective tanks, and the inside of the refrigerant inlet / outer tank is partitioned into a refrigerant inlet header chamber and a refrigerant outlet header chamber arranged in a direction of air flow by a partition wall; Each of the header chambers communicates with the heat exchange tubes of the tube group of at least one row, and the refrigerant introduced into the inlet header chamber of the refrigerant inlet / outer tank may be introduced into the refrigerant turn-side tank through the corresponding heat exchange tube, wherein the course A heat exchanger configured to flow into the outlet header chamber of the refrigerant inlet / outlet tank through a corresponding heat exchange tube;

And the coolant turn side tank is provided with a homogenizing member for equalizing coolant flow from the inlet header chamber to the heat exchange tube in communication with the inlet header chamber.

(2) The method according to (1), wherein the homogenizing member includes a sorting control panel for dividing the inside of the refrigerant turn-side tank into two spaces arranged in the air flow direction, the two spaces being in communication with each other, And a heat exchange tube communicating with one space in the refrigerant turn side tank, and a heat exchange tube communicating with the outlet header chamber communicate with another space in the refrigerant turn side tank.

(3) The heat exchanger according to the above (2), wherein the flow control panel is provided with one or more refrigerant passage holes, and the two spaces communicate with each other through the refrigerant passage holes.

(4) The heat exchanger according to (3), wherein the refrigerant flows through the refrigerant passage hole of the flow control panel in a counter flow relationship with the air flow.

(5) The method according to (3), wherein refrigerant dam portions are respectively provided at both ends of the classification control panel, and refrigerant passage portions having one or two refrigerant passage holes are provided between the refrigerant refrigerant portions. The heat exchanger whose length of each refrigerant | coolant interruption | blocking part is 15% or more of the total length of a sorting control panel, and whose total area of the total refrigerant passing-through hole formed in the refrigerant | coolant passage part is 130-510 mm <2>.

(6) The refrigerant passing portion according to the above (3), wherein a refrigerant blocking portion is provided at each end of the flow control panel, and a refrigerant passage portion having one or more refrigerant passage holes is provided between both refrigerant blocking portions, and each refrigerant is provided. A heat exchanger having an opening ratio of 20 to 75%, wherein the length of the blocking portion is 15% or more of the total length of the splitting control panel, and is a ratio of the number of refrigerant passage holes formed in the refrigerant passage portion to the number of heat exchange tubes of each tube group.

(7) In the above (3), the refrigerant blocking portions are respectively provided at both ends of the classification control panel, and between each refrigerant blocking portion, a refrigerant passage portion having one or more refrigerant passage holes is provided. The length of the blocking portion is not less than 15% of the total length of the sorting control panel, the total area of the total refrigerant passage holes formed in the refrigerant passage portion is 130 to 510 mm 2, and the refrigerant formed in the refrigerant passage portion relative to the number of heat exchange tubes in each tube group. A heat exchanger having an aperture ratio of 20 to 75%, which is a ratio of the number of through holes.

(8) The second extrusion member according to (2), wherein the refrigerant turn-side tank is made of an aluminum first member to which a heat exchange tube is connected, and an aluminum extrusion brother second member brazed to the first member at a portion opposite to the heat exchange tube. And a fractionating control panel integrally formed with the second member.

(9) The method according to the above (1), wherein the inside of the outlet header chamber of the coolant inlet / outer tank is partitioned by a diaphragm into a first space communicating with a corresponding heat exchange tube, and a second space from which coolant flows out therefrom. , The two spaces are in communication with each other.

(10) The heat exchanger according to (9), wherein the diaphragm is provided with one or more refrigerant passage holes, and the two spaces are in communication with each other through the refrigerant passage holes.

(11) The second extrusion extruder according to (9), wherein the refrigerant inlet / outer tank is a first aluminum member to which a heat exchange tube is connected, and a second aluminum extrusion brother brazed to a portion opposite to the heat exchange tube to the first member. And a partition and a diaphragm integrally formed with the second member.

(12) The heat exchanger according to (9), wherein one end of the refrigerant inlet / outer tank is provided with a refrigerant inlet communicating with the inlet header chamber and a refrigerant outlet communicating with the second space of the outlet header chamber.

(13) The heat exchanger of (1) above, wherein each group of tubes comprises at least seven heat exchange tubes.

(14) A refrigeration cycle comprising a compressor, a condenser, and an evaporator, wherein the evaporator is a heat exchanger according to any one of (1) to (13) above.

(15) A vehicle in which a refrigeration cycle according to (14) is mounted as an air conditioner.

(16) A tube group consisting of a plurality of heat exchange tubes arranged in parallel between and spaced apart in the longitudinal direction of both tanks between the refrigerant inlet / outlet tanks and the refrigerant turn-side tanks disposed to be spaced apart from each other in the air flow direction through the heat exchanger Installed in a plurality of rows, both ends of the heat exchange tubes of each tube group are connected to respective tanks, and the inside of the refrigerant inlet / outer tank is partitioned into a refrigerant inlet header chamber and a refrigerant outlet header chamber arranged in a direction of air flow by a partition wall; And each of the two header chambers communicates with the heat exchange tubes of the tube group of at least one row, and the refrigerant flowing into the inlet header chamber of the refrigerant inlet / outer tank may be introduced into the refrigerant turn-side tank via the corresponding heat exchange tube, wherein The heat exchanger is adapted to enter the outlet header chamber of the refrigerant inlet / outlet tank through a corresponding heat exchange tube. Come on.

The inside of the inlet header chamber of the coolant entry / exit tank is partitioned into a first space communicating with a corresponding heat exchange tube and a second space into which a refrigerant flows by a resistance plate for classification, and one refrigerant passage hole in the classification resistance plate. This formed heat exchanger.

(17) The heat exchanger according to (16), wherein the refrigerant passage hole is formed in a central portion in the longitudinal direction of the resistance plate for dividing.

(18) The heat exchange tube according to the above (16), wherein the coolant through hole is formed between a pair of heat exchange tubes adjacent to each other in the longitudinal direction of the coolant intake side tank among the heat exchange tubes communicating with the inlet header chamber of the coolant intake side tank. Located heat exchanger.

(19) The heat exchanger according to the above (16), wherein the refrigerant passage hole has an area larger than the total transverse area of the refrigerant passages in one heat exchange tube.

(20) The heat exchanger according to the above (16), wherein the refrigerant passage hole is circular and has a diameter of 3 to 8 mm.

(21) The coolant passage hole according to (16), wherein the coolant inlet / outer tank has a wall portion to which a heat exchange tube communicating with the first space is connected, and a coolant passage hole in a portion of the wall portion corresponding to the coolant passage hole. A heat exchanger, wherein a flow dividing member for dividing the refrigerant having passed through in the longitudinal direction of the inlet header chamber protrudes inward.

(22) The heat exchanger according to (21), wherein the flow dividing member is a ridge that projects in an angle shape toward the resistance plate and extends in the width direction of the inlet header chamber.

(23) The method according to the above (16), wherein the interior of the outlet header chamber of the coolant inlet / outer tank is partitioned into a first space in communication with a corresponding heat exchange tube, and a second space from which coolant flows out therefrom by a diaphragm. And a heat exchanger having a refrigerant passage hole formed in the diaphragm.

(24) The second extrusion extruder according to (23), wherein the refrigerant inlet / outer tank is a first aluminum member to which a heat exchange tube is connected, and a second aluminum extrusion brother brazed to a portion opposite to the heat exchange tube to the first member. A heat exchanger comprising a member, wherein the partition wall, the splitter resistance plate, and the diaphragm are integrally formed with the second member.

(25) The heat exchanger according to (16), wherein one end of the refrigerant inlet / outer tank is provided with a refrigerant inlet communicating with the second space of the inlet header chamber and a refrigerant outlet communicating with the outlet header chamber.

(26) The method according to (16), wherein the inside of the refrigerant turn-side tank is connected to the first space communicating with the heat exchange tube communicating with the first space of the inlet header chamber of the refrigerant entering / exiting tank by the flow control panel, and the refrigerant entering / exiting. And a second space communicating with the heat exchange tube communicating with the outlet header chamber of the side tank, wherein the flow control panel is provided with a refrigerant blocking portion at a position corresponding to the refrigerant passage hole of the resistance plate for sorting in the longitudinal direction of both tanks. And a refrigerant passage portion having a refrigerant passage hole at a position other than the refrigerant blocking portion.

(27) The heat exchanger according to (26), wherein the refrigerant blocking portion of the flow control panel has a length of 28 mm or more.

(28) The heat exchanger according to (26), wherein the aperture ratio is 20 to 90%, which is a ratio of the number of refrigerant passage holes formed in the flow control panel to the number of heat exchange tubes in each tube group.

(29) The second extrusion member according to (26), wherein the refrigerant turn-side tank is made of an aluminum first member to which a heat exchange tube is connected, and an aluminum extrusion-type second member brazed to the first member at a portion opposite to the heat exchange tube. And a fractionating control panel integrally formed with the second member.

(30) A refrigeration cycle comprising a compressor, a condenser, and an evaporator, wherein the evaporator is a heat exchanger according to any one of (16) to (29) above.

(31) A vehicle in which a refrigeration cycle according to (30) is mounted as an air conditioner.

According to the heat exchanger of (1) to (4), the flow rate of the refrigerant through the heat exchange tube connected to the inlet header chamber of the entry and exit tank is uniform by the action of the equalization member, so that the heat exchange performance of the heat exchanger can be improved. .

According to the heat exchanger of the above (5) to (7), the amount of refrigerant flow through the heat exchange tube connected to the inlet header chamber of the refrigerant inlet / outer tank is uniform, so that the heat exchange performance of the heat exchanger can be improved.

According to the heat exchanger of the above (8), the flow control panel of the refrigerant turn-side tank is formed integrally with the aluminum extruded second member. Therefore, the operation of installing the control panel inside the refrigerant turn-side tank can be simplified.

According to the heat exchanger of (9) and (10), the amount of refrigerant flow through the heat exchange tube connected to the inlet header chamber of the refrigerant inlet / outlet tank is uniform by the action of the diaphragm, and the heat exchanger is connected to the outlet header chamber of the outlet tank. Since the amount of refrigerant flowing through the tube is also uniform, the heat exchange performance of the heat exchanger can be improved.

According to the heat exchanger of the above (11), since the partitions and diaphragms of the refrigerant inlet / outer tank are formed integrally with the second member, the operation of installing the partitions and the diaphragm in the inlet / outlet tank can be simplified.

As in the heat exchanger of (12) above, when one end of the refrigerant inlet / outer tank is provided with a refrigerant inlet communicating with the inlet header chamber and a refrigerant outlet in communication with the second space of the outlet header chamber, the refrigerant exchanges heat in the tube group. Remarkably non-uniform flow through the tube, but even in this case the refrigerant through the heat exchange tube when the heat exchanger has the configuration described in any one of (1) to (7), (9) and (10) above. Flow can be homogenized.

If each tube group comprises seven or more heat exchange tubes as in the heat exchanger of (13) above, the refrigerant flows significantly non-uniformly through the heat exchange tubes of the tube group, but even in this case the heat exchanger Having the configuration according to any one of (7), (9), and (10), the refrigerant flow through the heat exchange tube can be made uniform.

According to the heat exchanger of the above (16), the refrigerant is supplied into the second space of the inlet header chamber of the refrigerant inlet / outlet tank, and flows into the first space through one refrigerant passage hole of the resistance plate for dividing, and the first space. The refrigerant from there flows splitting through all heat exchange tubes in communication with the inlet header chamber. Since only one refrigerant passage hole is formed in the resistance plate, the refrigerant flows gently into the first space from the second space, spreads over the entire first space, and flows into all the heat exchange tubes. Therefore, the amount of refrigerant flow through the heat exchange tube communicating with the inlet header chamber of the refrigerant inlet / outlet tank is uniform, so that the heat exchange performance of the heat exchanger can be improved.

According to the heat exchanger of (17) to (20), the flow rate of the refrigerant through the heat exchange tube communicating with the inlet header chamber of the refrigerant inlet / outer tank is further uniformized, so that the heat exchange efficiency of the heat exchanger can be improved.

According to the heat exchanger of (21) and (22), the refrigerant flowing through the refrigerant passage hole of the flow dividing resistor plate can spread over the entire area of the first space of the inlet header chamber. Therefore, the flow rate of the refrigerant through the heat exchange tube communicating with the inlet header chamber of the refrigerant inlet / outer tank is further uniformized, so that the heat exchange efficiency of the heat exchanger can be improved.

According to the heat exchanger of (23), the refrigerant changes its course inside the refrigerant turn-side tank, flows into the first space of the outlet header chamber of the refrigerant inlet / outtake tank, and enters the second space through the refrigerant passage hole of the diaphragm. do. Since the diaphragm provides resistance to the refrigerant flow, the flow into the heat exchange tube communicating with it from the first space of the inlet header chamber is further uniformized, and the flow into the heat exchange tube communicating with it from the refrigerant turn-side tank is further uniformed. . Thus, the amount of refrigerant flowing through the heat exchange tubes of the entire tube group is made uniform, thereby improving the heat exchange performance of the heat exchanger.

According to the heat exchanger of (24), the partition, the resistance plate for dividing, and the diaphragm are integrally formed with the second member. This facilitates the operation of providing a partition, a resistance plate for dividing, and a diaphragm inside the refrigerant inlet / outer tank.

When the refrigerant inlet communicating with the inlet header chamber and the refrigerant outlet communicating with the outlet header chamber are provided at one end of the refrigerant inlet / outer tank as in the heat exchanger of (25) above, the refrigerant is remarkably passed through the heat exchange tube of the tube group. Although unevenly flowing, even in this case, the refrigerant flow through the heat exchange tube can be uniform when the heat exchanger has the configuration described in any one of (16) to (23) above.

The heat exchanger of the above (26) to (28) is a refrigerant blocking portion for providing resistance to the refrigerant flowing into the first space of the refrigerant turn-side tank through the corresponding heat exchange tube from the first space of the inlet header chamber of the refrigerant intake-side tank. Has Thus, the amount of refrigerant flowing through the heat exchange tube in communication with the inlet header chamber of the entry and exit tank is further uniformed.

In the heat exchanger of (29), the flow control panel of the refrigerant turn-side tank is integrally formed with the second member of the aluminum extrusion mold. Thus, the control panel can be installed in the turn side tank in a simple operation.

1 is a perspective view showing the overall configuration of a first embodiment of an evaporator according to the present invention.

FIG. 2 is a partially omitted vertical cross-sectional view of the evaporator of FIG.

3 is a cross-sectional view taken on the line A-A in FIG.

4 is a partially omitted enlarged view taken on line B-B in FIG.

FIG. 5 is a partially omitted enlarged view taken on line C-C in FIG.

FIG. 6 is an exploded perspective view of the refrigerant inlet and outlet tank of the evaporator of FIG.

7 is an exploded perspective view of the refrigerant turn side tank of the evaporator of FIG.

FIG. 8 is a view showing how a refrigerant flows through the evaporator of FIG.

9 is a view corresponding to FIG. 8, showing a second embodiment of the evaporator according to the present invention.

10 is a view corresponding to FIG. 8, showing a third embodiment of an evaporator according to the present invention.

Fig. 11 is a view corresponding to Fig. 8, showing a fourth embodiment of the evaporator according to the present invention.

12 is a view corresponding to FIG. 8, showing a fifth embodiment of an evaporator according to the present invention.

13 is a view corresponding to FIG. 2, showing a sixth embodiment of an evaporator according to the present invention.

Fig. 14 is a horizontal sectional view of the refrigerant inlet / outer tank showing the seventh embodiment of the evaporator according to the present invention.

FIG. 15 is a partially enlarged cross-sectional view taken on line D-D in FIG.

Fig. 16 is an exploded perspective view of the refrigerant inlet and outlet tank of the evaporator of the seventh embodiment.

Fig. 17 is an exploded perspective view of the refrigerant turn side tank of the evaporator of the seventh embodiment.

FIG. 18 is a diagram showing how the refrigerant flows through the evaporator of the seventh embodiment.

Fig. 19 is a view corresponding to Fig. 18, showing an eighth embodiment of an evaporator according to the present invention.

Fig. 20 is an enlarged vertical sectional view showing main parts showing the ninth embodiment of the evaporator according to the present invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. This embodiment is an evaporator according to the invention.

In the following description, the top, bottom, left and right sides of Figs. 1, 2 and 13 will be referred to as “top”, “bottom”, “left” and “right” respectively, and each adjacent heat exchange tube pair The downstream side of the air flow through the air passage gap between (i.e., the direction indicated by arrow X in FIG. 1, and the right side of FIGS. will be. Throughout the drawings, similar parts will be referred to by like reference numerals and will not be described repeatedly.

1 to 5 show the overall configuration of the evaporator as the first embodiment of the present invention, Figures 6 and 7 show the configuration of the main portion, Figure 8 is a manner in which the refrigerant flows through the evaporator of the first embodiment To show.

1 to 3, the evaporator 1 is disposed in the left and right directions of the evaporator between the coolant entry and exit aluminum tanks 2, the coolant turn-side aluminum tanks 3, and both tanks 2 and 3 that are vertically spaced apart. , Ie, a plurality of heat exchange tubes 4 made of aluminum, which are spaced apart laterally and arranged in parallel, and are arranged in a plurality of rows spaced apart in the front and rear direction of the evaporator, that is, in this embodiment, two rows of tube groups. (5), in the air passage gap between adjacent pairs of heat exchange tubes (4) of each tube group (5) and outside the heat exchange tubes (4) at the left and right ends of each tube group (5), respectively. An aluminum corrugated pin 6 brazed to 4) and an aluminum side plate 7 disposed outside the corrugated pin 6 at both left and right ends thereof.

As shown in Figs. 4 to 6, the refrigerant inlet / out side tank 2 is formed of an aluminum brazing sheet having a brazing material layer on at least its outer surface (lower surface) and a plate-shaped first to which a heat exchange tube 4 is connected. A member 8, a second member 9 made of bare aluminum extrudate and covering the upper side of the first member 8, and an aluminum cap 11 closing the respective left and right openings; 12). The tank 2 comprises a refrigerant inlet header chamber 13 located at the front and a refrigerant outlet header chamber 14 located at the rear.

The 1st member 8 has the curvature cross-sectional arc-shaped curved part 15 of the small curvature which the center part protruded below, respectively in the front-back both sides part. In the curved portion 15, a plurality of tube insertion slits 16 long in the front-rear direction are formed to be spaced apart in the left-right direction. The pairs of corresponding slits 16 in the front and rear curved portions 15 are each at the same position with respect to the left and right directions. At the front edge of the front curve 15 and the rear edge of the rear curve 16, each upstanding wall 17 extending over the entire length of the member 8 is integrally formed. The first member 8 has a flat portion 18 between both curved portions 15, and a plurality of through holes 19 are formed in the flat portion 18 so as to be spaced apart in the left and right directions.

The second member 9 has a substantially m-shaped cross section and opens downward, and the second member has a central portion between the front and rear walls 21 and 22 extending in the horizontal direction and the front and rear walls 21 and 22. A partition 23 which is installed and extends in the left and right directions and divides the inside of the refrigerant inlet / outer tank 2 into two front and rear spaces, and the partition 23 is integrally formed at each of the front and rear walls 21 and 22 at an upper end thereof. It comprises two approximately arcuate connecting walls 24 which project upwardly. The rear wall 22 and the partition 23 are integrally connected at their lower end over the entire length of the member 9 by diaphragms 25. Alternatively, a plate separate from the rear wall 22 and the partition 23 may be secured to these walls 22, 23 as diaphragms 25. In the rear part of the diaphragm 25, the refrigerant | coolant passage holes 26 and 26a long in the left-right direction are formed in the part except the both left and right ends of the diaphragm, and spaced apart in the left-right direction. The refrigerant passage hole 26a in the left and right center portions of the diaphragm 25 has a length shorter than the distance between adjacent heat exchange tubes 4 of the rear tube group 5, and at the middle of the rear tube group 5. It is formed between two adjacent heat exchange tubes (4). The other refrigerant passage hole 26 has a longer length than the hole 26a. A ridge 25a projecting downward is integrally formed over the entire length of the rear edge portion of the bottom surface of the diaphragm 25. In the lower edge portion of the inner surface of the front wall 21, the ridge 21a protruding downward is integrally formed. The lower end of the partition wall 23 protrudes downward past the lower ends of both ridges 21a and 25a and is integrally provided with a plurality of protrusions 23a fitted in the through holes 19 of the first member 8, and these The protrusion 23a protrudes downward from the lower edge of the wall 23 and is spaced apart in the left and right directions. The protrusion 23a is formed by cutting a predetermined portion of the partition 23.

The caps 11 and 12 are formed of a bare material by pressing, forging or cutting, each of which is recessed inward to the left and right in which the corresponding ends of the first and second members 8 and 9 are fitted. Has The right cap 12 is provided with a refrigerant inlet 12a in communication with the refrigerant inlet header chamber 13 and a refrigerant outlet 12b in communication with an upper portion of the refrigerant outlet header chamber 14 higher than the diaphragm 25. It is. The right side cap 12 is brazed by an aluminum refrigerant inlet / outer 27 having a refrigerant inlet 27a communicating with the refrigerant inlet 12a and a refrigerant outlet 27b communicating with the refrigerant outlet 12b.

The two members 8, 9 are inserted into the through hole 19 of the first member 8 by the projection 23a of the second member 9 and crimped at the same time as the upright wall of the first member 8. In a state in which 17 is engaged with the ridges 21a and 25a of the second member 9, the brazing material layers of the first member 8 are mutually brazed. Both caps 11 and 12 are brazed to the first and second members 8 and 9 using the sheet of brazing material to form the refrigerant inlet / out tank 2. The portion of the tank 2 in front of the partition 23 of the second member 9 serves as the refrigerant inlet header chamber 13, and the portion behind the partition 23 is the refrigerant outlet header chamber 14. Works. In addition, the refrigerant outlet header chamber 14 is partitioned into upper and lower spaces 14a and 14b by the diaphragm 25, and these spaces 14a and 14b communicate with each other through the refrigerant passage holes 26 and 26a. . The lower space 14b is a first space in communication with the heat exchange tube 4 of the rear tube group 5, and the upper space 14a is a second space through which the refrigerant flows out of the evaporator.

4, 5, and 7, the refrigerant turn-side tank 3 is formed of an aluminum brazing sheet having a brazing material layer on at least an outer surface (upper surface) and a plate-shaped first to which a heat exchange tube 4 is connected. A member 28, a second member 29 formed of a bare aluminum extruded member and covering the lower side of the first member 28, and an aluminum cap 31 for closing the left and right both end openings are included. The tank 3 includes a refrigerant inlet side header chamber 32 as a space located in front and a refrigerant outlet side header chamber 33 as a space located in the rear.

The coolant turn side tank 3 has a top surface 3a, both front and rear sides 3b, and a bottom surface 3c. The top surface 3a of the coolant turn-side tank 3 is formed in an arc shape so that its center portion in the front-back direction becomes the top 34 and gradually lowers from the top 34 toward both front and rear sides. have. In the front and rear both side portions of the tank 3, a plurality of grooves 35 extending from the front and rear sides of the uppermost part 34 of the top surface 3a to the front and rear sides 3b are spaced apart in the left and right directions. Each groove 35 has a flat bottom surface. Each groove 35 has a first portion 35a present on the top surface 3a of the tank 3, the first portion having the same depth over its entire length. Both side surfaces of the first portion 35a of the groove 35 are respectively inclined upward and outward in the tank, and the width of the first portion 35a of the groove 35 gradually moves from the groove bottom toward the opening. Widens Moreover, in the longitudinal section of each groove 35, the shape of the bottom face of the 1st part 35a is circular arc shape extended downward from the highest part 34 side of the tank top surface 3a toward the front-back direction outer side. It is.

The groove 35 has a second portion 35b present at the junction 3d of the top surface 3a of the refrigerant turn-side tank 3 and the front and rear sides 3b, and the bottom of the second portion is the front-rear outer side. It is inclined downward toward. The bottom of the second portion 35b extends from an end of the bottom of the first portion 35a. Each groove 35 has a third portion 35c present on both front and rear sides 3b of the tank 3, and the bottom of the third portion is vertical. The width of the third portion 35c of the groove is the same from the bottom of the groove 35 to its opening.

The first member 28 has an arc-shaped cross section protruding upward from the center with respect to the front-rear direction, and at both front and rear edges thereof, depending on the entire length of the member 28 integrally therewith depending on the wall 28a. It is formed over. The upper surface of the first member 28 serves as the top surface 3a of the refrigerant turn-side tank 3, and the outer surface of the drooping wall 28a serves as the front and rear sides 3b of the tank 3. Grooves 35 are formed on each of the front and rear sides of the first member 28, and these grooves extend from the uppermost portion 34 at the center of the member 28 to the lower end of the drooping wall 28a with respect to the front and rear directions. . The tube insertion slit 36 elongated in the front-rear direction is formed between each adjacent pair of grooves 35 at the front-rear and both-side portions except the uppermost part 34 in the front-rear center of the first member 28. Each corresponding pair of front and rear tube insertion slits 36 is in the same position with respect to the left and right directions. The first member 28 is formed with the plurality of through holes 37 spaced apart in the left and right directions at the uppermost portion 34 of the central portion thereof. The drooping wall 28a, the groove 35, the tube insertion slit 36, and the through hole 37 of the first member 28 press-process the aluminum brazing sheet to produce the first member 28. Thereby forming simultaneously.

The second member 29 has an approximately w-shaped cross section and is opened upwardly, and the second member 29 has front and rear walls 38 and 39 extending in a left and right direction that is curved upwardly toward the outside in the front-rear direction, and the refrigerant turn-side tank. (3) a vertical bulkhead 41 for dividing the interior of the space into two front and rear spaces, and two connecting walls 42 for integrally connecting the bulkhead 41 to the front and rear both walls 38 and 39 at the bottom thereof. It includes. The outer surface of the connecting wall 42 provides the bottom surface 3c of the tank 3, and the outer surfaces of the front and rear walls 38 and 39 are the joint portions 3e of the front and rear sides 3b and the bottom surface 3c, respectively. ). Both front and rear walls 38 and 39 have ridges 38a and 39a, respectively, each of which protrudes upward from the inner edge of the top of the wall and extends over the entire length of the wall.

The partition 41 has a top projecting upwards past the tops of both front and rear walls 38 and 39, and projects upward from the upper edge of the wall 41 and into each through hole 37 of the first member 28. A plurality of projections 41a to be fitted are provided integrally spaced apart in the left and right directions. Further, in a portion slightly to the left of the central portion of the partition 41, a notch 41b for passage of refrigerant is formed between the pair of protrusions 41a adjacent to each other at the upper edge thereof. The protrusion 41a and the notch 41b are formed by cutting the predetermined part of the partition 41.

The cap 31 is formed of a bare material by pressing, forging or cutting, each of which has a recess directed inward to the left and right in which the corresponding ends of the first and second members 28 and 29 are fitted.

The first and second two members 28 and 29 are each of which the protrusion 41a of the second member 29 is inserted through each hole 37 to crimp and at the same time upright of the first member 28. With the wall 37 engaged with the ridges 38a, 39a of the second member 29, they are brazed together using the brazing material layer of the first member 28. Both caps 31 are further brazed to the first and second members 28, 29 using the brazing material sheet to form the refrigerant turn-side tank 3. The coolant passage hole 43 is formed by closing the top opening of the notch 41b in the partition 41 of the second member 29 by the first member 28. The refrigerant passage hole 43 formed by closing the top opening of the cutout 41b in the partition 41 by the first member 28 may alternatively be a through hole formed in the partition wall 41. The partition 41 of the second member 29 acts as a flow control panel 44 having a refrigerant passage hole 43, which flows the refrigerant turn-side tank 3 so that the refrigerant flows in a uniformly divided state. It acts as a homogenizing member partitioning into the front refrigerant inlet side header chamber 32 and the rear refrigerant outlet side header chamber 33.

Refrigerant cut-off portions 45A and 45B at which the refrigerant passage holes 43 do not exist at all are provided at the left and right ends of the discharge control panel 44 extending from the corresponding ends of the discharge control panel 44 over a predetermined length. . Between the blocking portions 45A, 45B, the classification control panel 44 has a refrigerant passage portion 46 in which one or two or more refrigerant passage holes 43 are formed in this embodiment. The length of the right refrigerant | coolant interruption | blocking part 45B is longer than the length of the left refrigerant | coolant interruption | blocking part 45A, and is approximately half of the total length of the classification | control part control panel 44. FIG. The length of each of the refrigerant blocking portions 45A and 45B is not less than 15% of the total length of the control panel 44, and the total area of the total refrigerant passage holes 43 formed in the refrigerant passage portion 46 is preferably 130 to 510 mm 2. Do. The maximum length of each of the refrigerant blocking portions 45A and 45B is preferably limited so as not to exceed 78% of the total length of the splitting control panel 44. The ratio of the number of refrigerant passage holes 43 of the refrigerant passage portion 46 to the number of heat exchange tubes 4 of each tube group 5, that is, the opening ratio, is preferably 20 to 75%. If the length of each refrigerant blocking portion 45A, 45B is less than 15% of the total length of the splitting control panel 44, the amount of refrigerant flow through the entire heat exchange tube 4 of each tube group will not be sufficiently uniform. In addition, when the total area of the total refrigerant passage holes 43 formed in the refrigerant passage portion 46 is less than 130 mm 2, passage resistance may be greatly increased, which may adversely affect performance. When the total area exceeds 510 mm 2, the classification control panel may be used. (44) may not exercise the classification control function. In addition, when the ratio of the opening ratio, that is, the ratio of the number of the refrigerant passage holes 43 formed in the refrigerant passage portion 46 to the number of the heat exchange tubes 4 of each tube group 5 is less than 20%, the passage resistance greatly increases. There is a risk of adversely affecting the performance, and if it exceeds 75%, the classification control function may not be exhibited at all.

The heat exchange tubes 4 constituting the front and rear tube group 5 are each made of a bare material formed of an aluminum extrusion. Each tube 4 is flat, has a wide width in the front-rear direction, and a plurality of refrigerant passages 4a extending in the longitudinal direction therein are formed in parallel. Both front and rear walls of the heat exchange tube 4 have an arc shape projecting outward. The heat exchange tube 4 of the front tube group 5 and the heat exchange tube 4 of the rear tube group 5 exist at the same position with respect to the left and right directions. The upper end of each heat exchange tube 4 is inserted into the tube inserting slit 16 of the first member 8 of the refrigerant inlet / outer tank 2 and the first member using the brazing material layer of the first member 8. Brazed to (8), the lower end of which is inserted into the tube insertion slit (36) of the first member (28) of the refrigerant turn-side tank (3) and using the layer of brazing material of the first member (28) to make the first member. It is brazing at 28.

The heat exchange tube 4 has a tube height of 0.75 to 1.5 mm, a width of 12 to 18 mm in the front and rear direction, a wall thickness of 0.175 to 0.275 mm in the peripheral wall, and a partition wall separating the refrigerant passages 4a from each other. The thickness is 0.175 to 0.275 mm and the pitch of the partition is 0.5 to. It is preferable that the radius of curvature of the outer surface of the 3.0 mm and front and rear end walls is 0.35 to 0.75 mm.

Instead of the aluminum extruded heat exchanger tube 4, a plurality of refrigerant passages may be used by inserting an inner fin into an aluminum resistance-welded tube. In addition, two flat wall forming portions formed by subjecting the aluminum brazing sheet having a brazing material layer on both sides to be rolled and connected by the connecting portion, and protruding from the side edges on the opposite side of the connecting portion in each flat wall forming portion, respectively. And a plate having integrally formed sidewall forming portions, and a plurality of partition wall forming portions integrally formed by protruding from each flat wall forming portion spaced apart in the width direction of the flat wall forming portion, and bent in a hairpin shape at the connection portion to mutually form the sidewall forming portions. By abutting and brazing, the tube in which the partition was formed by the partition formation part can also be used. The corrugated pins used in this case are made of bare material.

The corrugated pin 6 is manufactured by molding an aluminum brazing sheet having a brazing material layer on both sides in a wavy form. A plurality of louvers 6a are formed in parallel in the front-rear direction at a connection portion connecting the crest portion and the furrow portion of the corrugated sheet. Corrugated fins 6 are commonly used for both front and rear tube groups 5. The front and rear width of the fin 6 is approximately equal to the distance from the front edge of the heat exchange tube 4 of the front tube group 5 to the rear edge of the corresponding heat exchange tube 4 of the rear tube group 5. The corrugated pin 6 preferably has a pin height, that is, a straight line distance from the head portion to the bottom portion, is 7.0 to 10.0 mm, and the pin pitch, that is, the pitch of the connecting portion is 1.3 to 1.8 mm.

The evaporator 1 is manufactured by temporarily fixing a combination of components and brazing-bonding the entire components.

The evaporator 1 constitutes a refrigeration cycle together with a compressor, a condenser, and a decompression means, and is mounted on a vehicle, for example, an automobile, as a car air conditioner.

Referring to Fig. 8 showing the evaporator 1 described above, a two-layer refrigerant in a vapor-liquid mixture phase that has passed through a compressor, a condenser and a decompression means is a refrigerant inlet 27a of the refrigerant inlet / outer 27. And a refrigerant inlet header chamber 13 of the refrigerant inlet / outer tank 2 through the refrigerant inlet 12a of the right cap 12.

The refrigerant supplied into the refrigerant inlet header chamber 13 tends to flow into the heat exchange tube 4 close to the left and right ends of the front tube group 5, but the refrigerant flow control panel 44 of the refrigerant turn-side tank 3 Since the coolant blocking portions 45A and 45B are provided at both ends, resistance is imparted to the coolant flowing in the heat exchange tube 4 close to the left and right ends, and the coolant is evenly divided into the heat exchange tube 4 so that the coolant passage ( It flows into 4a), and flows downward into the refrigerant path 4a, and flows into the refrigerant inflow side header chamber 32 of the refrigerant turn-side tank 3. As shown in FIG.

Thereafter, the refrigerant flows into the refrigerant outlet side header chamber 33 through the refrigerant passage hole 43 of the refrigerant passage portion 46, and is classified to form the refrigerant passage of the entire heat exchange tube 4 of the rear tube group 5. It flows into 4a), changes its course, flows up the refrigerant path 4a, and flows into the lower space 14b of the refrigerant outlet header chamber 14 of the refrigerant inlet / outtake tank 2. Since resistance is imparted to the flow of the refrigerant by the diaphragm 25 provided in the outlet header chamber 14, the sorting from the refrigerant outlet side header chamber 33 to the tube 4 of the rear tube group 5 can be made uniform. In addition, the classification from the refrigerant inlet header chamber 13 to the tube 4 of the front tube group 5 is also uniformized. As a result, the amount of refrigerant flow through the heat exchange tube 4 of both tube groups 5 is equalized.

Thereafter, the refrigerant flows into the upper space 14a of the outlet header chamber 14 through the refrigerant passage holes 26 and 26A of the diaphragm 25, and the refrigerant outlet 12a of the cap 12 and the refrigerant inlet / out member ( It exits from the evaporator through outlet 27b of 27). While flowing through the refrigerant passage 4a of the heat exchange tube 4 of the front tube group 5 and the refrigerant passage 4b of the heat exchange tube 4 of the rear tube group 5, the refrigerant passes the air passage gap in FIG. Heat exchange is performed with air flowing in the arrow X direction shown, and flows out of the evaporator into the gas phase.

At this time, condensed water is generated on the surface of the corrugated fin 6, and the condensed water flows down to the top surface 3a of the refrigerant turn-side tank 3. The condensed water that has flowed down to the top surface 3a of the tank flows into the first portion 35a of the groove 35 by the capillary effect, flows into the groove 35, and coolant turns from the lower end of the third portion 35c to the tank. It falls below (3). This prevents the collection of a large amount of condensed water between the top surface 3a of the refrigerant turn-side tank 3 and the lower end of the corrugated fin 6, thus preventing freezing of the condensed water by collecting a large amount of condensed water. The deterioration of the evaporator 1 is prevented.

According to the first embodiment, the classification control panel 44 having a refrigerant passage hole 43 and partitioning the refrigerant turn-side tank 3 into the refrigerant inlet header chamber 32 in the front and the refrigerant outlet header chamber 33 in the rear. ) Acts as a coolant flow equalizing member for equalizing the coolant flow to the heat exchange tube 4 of the front tube group 5 in communication with the inlet header chamber 13. However, it is not limited to this configuration and can be changed as appropriate.

9 shows a second embodiment of an evaporator according to the invention.

In the case of the embodiment shown in Fig. 9, the refrigerant passage portions 46 are provided in the left and right center portions of the flow control panel 44 in the refrigerant turn-side tank 3, and the lengths are respectively provided on the left and right sides of the refrigerant passage portions 46, respectively. Almost the same refrigerant blocking portions 45A and 45B are provided. The ratio of the length of each refrigerant blocking portion 45A, 45B to the total length of the classification control panel 44, the total area of the total refrigerant passage holes 43 formed in the refrigerant passage portion 46, and of each tube group 5 In the opening ratio which is the ratio of the number of refrigerant passage holes 43 formed in the refrigerant passage portion 46 to the number of heat exchange tubes 4, this embodiment is the same as the first embodiment. In the diaphragm 25 of the refrigerant | coolant entry-and-exit side tank 2, the some refrigerant | coolant passage hole 50 long in the left-right direction is formed in the part corresponding to each refrigerant | coolant cut-off part 45A, 45B of the classification control panel 44 in the left-right direction Are spaced apart from each other. The length of all the refrigerant | coolant through-holes 50 is the same. In other configurations, the second embodiment is the same as the first embodiment.

Also in the case of the second embodiment, the refrigerant flowing through the evaporator flows in a uniform amount through the heat exchange tubes 4 of each tube group.

10 shows a third embodiment of an evaporator according to the invention.

In the case of the embodiment shown in FIG. 10, a slightly longer refrigerant passage portion 46 is provided in the left portion than the left and right central portions of the flow control panel 44 in the refrigerant turn-side tank 3 than in the case of the first embodiment. Refrigerant cut-off parts 45A and 45B are provided on the left and right sides of the coolant passage part 46, respectively. The length of the right refrigerant | coolant interruption | blocking part 45B is longer than the length of the left refrigerant | coolant interruption | blocking part 45A, and is approximately half of the total length of the classification | control part control panel 44. FIG. The ratio of the length of each refrigerant blocking portion 45A, 45B to the total length of the classification control panel 44, the total area of the total refrigerant passage holes 43 formed in the refrigerant passage portion 46, and of each tube group 5 In the opening ratio which is the ratio of the number of refrigerant passage holes 43 formed in the refrigerant passage portion 46 to the number of heat exchange tubes 4, this embodiment is the same as the first embodiment. In the diaphragm 25 of the refrigerant inlet / outer tank 2, one refrigerant passage hole 51 that is long in the left and right direction is formed in a portion corresponding to the left refrigerant blocking portion 45B of the flow dividing control panel 44, and the right refrigerant A plurality of refrigerant passage holes 51 long in the left-right direction are formed to be spaced apart in the left-right direction in a portion corresponding to the blocking portion 45A. The lengths of all the refrigerant passage holes 51 are the same. In other configurations, the third embodiment is the same as the first embodiment.

Also in the case of the third embodiment, the refrigerant flowing through the evaporator flows in a uniform amount through the heat exchange tubes 4 of each tube group.

Figure 11 shows a fourth embodiment of the evaporator according to the invention.

In the case of the embodiment shown in Fig. 11, at least one of both refrigerant blocking portions 45A and 45B of the splitting control panel 44 in the refrigerant turn-side tank 3, in this embodiment, the auxiliary refrigerant through-holes 60 respectively on both sides. Is formed. In other configurations, the fourth embodiment is the same as the first embodiment. Also in the second and third embodiments, an auxiliary coolant through hole may be formed in at least one of both coolant blocking portions 45A and 45B.

Also in the case of the fourth embodiment, the refrigerant flowing through the evaporator flows in a uniform amount through the heat exchange tubes 4 of each tube group.

Figure 12 shows a fifth embodiment of the evaporator according to the invention.

In the case of the embodiment shown in Fig. 12, the refrigerant inlet / outer tank 2 and the refrigerant turn-side tank 3 of the evaporator 61 each extend longer to the right than in the case of the first embodiment. Between these extension parts 2A and 3A, the tube group 5 of 2 front and back rows which consists of the some heat exchange tube 4 arranged in parallel and spaced apart in the left-right direction is arrange | positioned. The heat exchange tube 4 of the front and rear tube group 5 is connected to both front and rear portions of the tank 2 extension portion 2A at its upper end portion, and is connected to the front and rear both side portions of the tank 3 extension portion 3A at its lower end portion. Connected.

No diaphragm is provided in the refrigerant outlet header chamber 14 of the refrigerant inlet / outer tank 2. The right end opening of the extension portion 2A of the tank 2 is closed by a cap (not shown) having no refrigerant inlet and a refrigerant outlet. Both header chambers 32 and 33 of the refrigerant turn-side tank 3 are separated from the extension portions 32A and 33A of these chambers 32 and 33 by diaphragms 62. The right end opening of the extension portion 3A of the tank 3 is closed by a cap (not shown) having a coolant inlet and a coolant outlet, which communicates with a coolant inlet and a coolant outlet that communicate with the coolant inlet. A coolant inlet and out member (not shown) having a coolant outlet is brazed. In other configurations, the fifth embodiment is the same as the first embodiment. Also in the first to fourth embodiments, the same configuration as in the fifth embodiment can be given.

A gas-liquid mixed two-layer refrigerant passing through the compressor, the condenser, and the decompression means flows into the evaporator 610, and more specifically, the refrigerant in the refrigerant turn-side tank 3 through the refrigerant inlet of the refrigerant inlet member and the refrigerant inlet of the cap. It flows into the extension part 32A of the inflow side header chamber 32.

The refrigerant supplied into the extension part 32A flows upward through the refrigerant passage 4a of the heat exchange tube 4 of the front tube group 5 connected to the extension part 3A, and the refrigerant inlet header chamber 13 It flows in and flows through this chamber to the left. Thereafter, the coolant flows into the coolant passage 4a uniformly divided into the heat exchange tube 4 of the front tube group 5 and flows downward into the coolant passage 4a as in the case of the first embodiment. It flows into the refrigerant inflow side header chamber 32 of the tank 3.

Thereafter, the refrigerant flows into the refrigerant outlet side header chamber 33 through the refrigerant passage hole 43 of the refrigerant passage portion 46, and is classified to form a refrigerant passage of the entire heat exchange tube 4 of the rear tube group 5. It flows into 4a), changes its course, and moves up inside the refrigerant passage 4a to flow into the refrigerant outlet header chamber 14 of the refrigerant inlet / outtake tank 2. As shown in FIG. The refrigerant then flows to the right through the outlet header chamber 14, flows into the passage 4a of the heat exchange tube 4 of the rear tube group 5 connected to the extension 2A, and passes through the passage 4a. ) Flows downward into the extension portion 33A of the refrigerant outlet side header chamber 33 of the refrigerant turn-side tank 3, and flows out through the refrigerant outlet of the cap and the outlet of the refrigerant inlet / outer member.

Also in the case of the fifth embodiment, the refrigerant flowing through the evaporator flows in a uniform amount through the heat exchange tubes 4 of each tube group.

Figure 13 shows a sixth embodiment of an evaporator according to the invention.

In the case of the embodiment shown in Fig. 13, the coolant through holes 43 formed in the sorting control panel 44 are shifted from the heat exchange tube 4 and arranged. More specifically, each refrigerant passage hole 43 is located between a pair of adjacent heat exchange tubes 4. In other configurations, the sixth embodiment is the same as the first embodiment. That is, the second to fifth embodiments may also have the same configuration as the sixth embodiment.

14 to 18 show a seventh embodiment of the evaporator according to the invention.

In the case of the embodiment shown in Figs. 14 to 18, the front wall 21 and the partition wall 23 of the second member 9 of the refrigerant inlet / out side tank 2, at the lower end thereof, have a resistance plate 70 for sorting. Are connected together over the entire length of the tank. One refrigerant passage circular hole 71 is formed in the left and right center portions of the resistance plate 70. Alternatively, a plate separate from the front wall 21 and the partition 23 may be secured as a resistance plate 70 to the front wall 21, the rear wall 22, and the partition 23. The refrigerant inlet header chamber 13 is partitioned into two spaces 13a and 13b by the resistance plate 70, and these two spaces are kept in communication with each other through the circular hole 71. The lower space 13b is a first space communicating with the heat exchange tube 4 of the front tube group 5, and the upper space 13a is a second space into which the refrigerant flows. The refrigerant inlet 12a of the right cap 12 communicates with the upper space 13a of the inlet header chamber 13.

A circular coolant through hole 71 of the splitter resistance plate 70 is located between the two heat exchange tubes 4 at the center in the left and right directions of the front tube group 5. The circular hole 71 has a left-right size (diameter) smaller than the distance between the two tubes 4. It is preferable that this hole 71 is 3-8 mm in diameter. When the diameter of the hole 71 is less than 3 mm, the increased passage resistance is imparted to the refrigerant, thereby increasing the load on the air conditioner system, and the flow velocity of the refrigerant is increased, so that the refrigerant passage sound can be increased. When the diameter of the hole 71 exceeds 8 mm, the amount of refrigerant flowing through the intermediate portion increases, and it becomes difficult for the refrigerant to spread over the entire area of the lower space 13b to be described later in the inlet header chamber 13. Can be. The circular refrigerant through hole 71 has an area larger than the total cross sectional area of the refrigerant passages of one heat exchange tube 4. The refrigerant passage hole to be formed in the classification resistance plate 70 is not limited to a circle, and may have an appropriately modified shape such as an ellipse (not limited to a mathematically defined ellipse shape, including a shape close to an ellipse). Even if it has a shape other than circular, the refrigerant passage hole should have such an area, and is thus sized so as to be disposed between the two heat exchange tubes at the center in the left and right directions of the tube group 5.

Referring to Fig. 17, the sorting control panel 44 of the refrigerant turn-side tank 3 has a refrigerant blocking portion 72 in which no refrigerant passage hole exists, and this refrigerant blocking portion is in the longitudinal center portion of the control panel, that is, at the entry and exit side. It is formed at a position corresponding to the circular refrigerant passage hole 71 of the resistance plate 70 for dividing the tank 2. The control panel 44 has a refrigerant passage portion 73 formed on both left and right sides of the blocking portion 72, and the refrigerant passage portion has one or two or more refrigerant passage holes 43 in the present embodiment. Have It is preferable that the left-right direction length of the refrigerant | coolant cutoff part 72 is 28 mm or more. If this length is less than 28 mm, the amount of refrigerant flowing in the center portion will be large. Moreover, it is preferable that the opening ratio which is a ratio of the number of the refrigerant | coolant passage holes 43 formed in each refrigerant | coolant passage part 73 with respect to the number of the heat exchange tubes 4 of each tube group 5 is 20 to 90%. If the opening ratio is less than 20%, the passage resistance to the refrigerant may increase, so that the performance may be degraded. If the aperture ratio exceeds 90%, the classification control function may not be exhibited.

In other configurations, the seventh embodiment is the same as the first embodiment.

Referring to Fig. 18, which shows the evaporator 1 of the seventh embodiment, the gas-liquid mixture-like two-layer refrigerant having passed through the compressor, the condenser, and the decompression means includes the refrigerant inlet 27a and the right cap of the refrigerant inlet / outer 27. One circular hole in the upper space 13a of the refrigerant inlet header chamber 13 of the refrigerant inlet / outer tank 2 through the refrigerant inlet 12a of the tank 12 is disposed in the resistance plate 70 for sorting ( It enters into the lower space 13b through 71 and flows in from the lower space 13b into the refrigerant passage 4a of the entire heat exchange tube 4 of the front tube group 5. Since only one circular refrigerant through hole 71 is formed in the resistance plate 70, the refrigerant flows smoothly into the lower space 13b, spreads out over the entire area of the lower space 13b, It flows into the refrigerant passage 4a. This makes it possible to equalize the flow amount of the refrigerant through these heat exchange tubes 4.

The refrigerant flowing into the refrigerant passage 4a of the entire heat exchange tube 4 flows downward in the passage 4a and flows into the refrigerant inlet side header chamber 32 of the refrigerant turn-side tank 3. The refrigerant flowing into the chamber 32 flows outward from the left and right directions by the action of the blocking portion 72 and flows into the refrigerant outlet side header chamber 33 through the hole 43 of the refrigerant passage portion 73. . That is, since resistance is imparted to the flow of the refrigerant by the refrigerant blocking portion 72, the heat exchange tube located near the circular hole 71 in the front tube group 5 from the lower space 13b of the inlet header chamber 13. Inflow into only the passage 4a of (4) is suppressed, and refrigerant | coolant inflow into the passage 4a of the other heat exchange tube 4 is accelerated | stimulated. Thus, the flow amount of the refrigerant through the heat exchange tube 4 of the front tube group 5 is equalized.

The refrigerant flowing into the refrigerant outlet side header chamber 33 flows into the refrigerant passage 4a of the entire heat exchange tube 4 of the rear tube group 5 and changes its course to change the inside of the refrigerant passage 4a. Flows upward and flows into the lower space 14b of the refrigerant outlet header chamber 14 of the refrigerant inlet / outer tank 2. Since resistance is imparted to the flow of the coolant by the diaphragm 25 in the chamber 14, the coolant is equalized from the coolant outlet side header chamber 33 to the tube 4 of the rear tube group 5, and the inlet header The fractionation from the lower space 13b of the chamber 13 to the heat exchange tube 4 of the front tube group 5 is also uniformized. As a result, the amount of refrigerant flowing through the entire heat exchange tube 4 of both tube groups is equalized.

Thereafter, the refrigerant flows into the upper space 14a of the outlet header chamber 14 through the refrigerant passage holes 26 and 26A of the diaphragm 25, and the refrigerant outlet 12a of the cap 12 and the refrigerant inlet / out member ( It exits from the evaporator through outlet 27b of 27). While flowing through the refrigerant passage 4a of the heat exchange tube 4 of the front tube group 5 and the refrigerant passage 4b of the heat exchange tube 4 of the rear tube group 5, the refrigerant passes the air passage gap in FIG. Heat exchange is performed with air flowing in the arrow X direction shown, and flows out of the evaporator into the gas phase.

Figure 19 shows an eighth embodiment of the evaporator according to the invention.

In the case of the embodiment shown in Fig. 19, in the diaphragm 25 of the refrigerant inlet / outer tank 2, a plurality of refrigerants long in the left and right directions at portions corresponding to the respective refrigerant passage portions 73 of the classification control panel 44 are provided. The through holes 26 are formed to be spaced apart in the left and right directions. The length of all the refrigerant | coolant passage holes 26 is the same. In other configurations, the eighth embodiment is the same as the seventh embodiment.

Also in the case of the eighth embodiment, the refrigerant flowing through the evaporator flows in a uniform amount through the heat exchange tubes 4 of each tube group.

Figure 20 shows a ninth embodiment of an evaporator according to the invention.

In the case of the embodiment shown in FIG. 20, in the left-right direction center part in the 1st member 8 of the refrigerant | coolant entry-side tank 2, it protrudes upward in the part just below the left-right center of the circular refrigerant passage hole 71 And a ridge 75 having a cross-sectional angle shape extending in the front-rear direction. The ridge 75 is formed as a protruding ridge by bending the first member 8 upwards. It is preferable that the front-back direction length of the ridge 75 is the same as the diameter (front-back direction size) of the circular through hole 71 at least. The ridge 75 divides the refrigerant flowing from the upper space 13a of the inlet header chamber 13 into the lower space 13b through the circular hole 71 in the left and right directions in the lower space 13b. It is a classification member. The ridge 75 is formed at the same time when the first member 8 is press-molded from the aluminum brazing sheet. The ridge may be formed by fixing a separate member to the upper surface of the first member 8 instead of bending the first member 8 upward.

In other configurations, the ninth embodiment is the same as the seventh embodiment.

In all the above embodiments, one tube group 5 is provided between the front and rear portions of both tanks 2 and 3, respectively, but is not limited to this configuration, and is the front and rear portions of both tanks 2 and 3. One or two or more tube groups 5 may be provided in between. Further, in all the above embodiments, the uppermost portion 34 is located in the front-back direction center portion of the refrigerant turn-side tank 3, but is not limited to this arrangement, and may be located away from the front-back direction center portion of the refrigerant turn-side tank 3. have. Also in this case, 1 or 2 or more tube groups are provided in the front and back both sides of a top part, respectively. In all the above embodiments, the coolant entry-side tank 2 is located above the coolant turn-side tank 3 in the lower position, but the coolant turn-side tank 3 is located above the coolant entry-side tank 2. You may.

The heat exchanger of the present invention is suitable for use as an evaporator of a vehicle air conditioner, and can improve heat exchange performance.

Claims (31)

Between the refrigerant inlet / outlet tanks and the refrigerant turn-side tanks, which are spaced apart from each other, a tube group consisting of a plurality of heat exchange tubes arranged in parallel in the longitudinal direction of both tanks is installed in a plurality of rows spaced apart in the air flow direction through the heat exchanger. Both ends of the heat exchange tubes of each tube group are connected to respective tanks, and the inside of the refrigerant inlet / outer tank is partitioned into a refrigerant inlet header chamber and a refrigerant outlet header chamber arranged in the air flow direction by a partition wall, and both headers Each of the chambers is in communication with a heat exchange tube of at least one row of tube groups, and the refrigerant flowing into the inlet header chamber of the refrigerant inlet / outer tank can be introduced into the refrigerant turn-side tank via the corresponding heat exchange tube, where the course is changed. Heat exchanger configured to flow into the outlet header chamber of the refrigerant inlet / outlet tank through a corresponding heat exchange tube, And the coolant turn side tank is provided with a homogenizing member for equalizing coolant flow from the inlet header chamber to the heat exchange tube in communication with the inlet header chamber. The heat exchange tube according to claim 1, wherein the homogenizing member comprises a splitting control panel for dividing the inside of the refrigerant turn-side tank into two spaces arranged in the air flow direction, the two spaces communicating with each other, and the heat exchange tube communicating with the inlet header chamber. And a heat exchange tube communicating with one space in the refrigerant turn side tank and communicating with the outlet header chamber in communication with the other space in the refrigerant turn side tank. The heat exchanger of claim 2, wherein one or more refrigerant passage holes are formed in the flow control panel, and the two spaces communicate with each other through the refrigerant passage holes. The heat exchanger of claim 3, wherein the refrigerant flows through the refrigerant passage hole of the flow control panel in a counter flow relationship with the air flow. According to claim 3, Refrigerant blocking portions are respectively provided at both ends of the classification control panel, a refrigerant passage portion having one or more refrigerant passage holes is provided between the two refrigerant blocking portions, the length of each refrigerant blocking portion is A heat exchanger having at least 15% of the total length of the flow control panel and having a total area of the total refrigerant passage holes formed in the refrigerant passage portion of 130 to 510 mm 2. According to claim 3, Refrigerant blocking portions are respectively provided at both ends of the classification control panel, a refrigerant passage portion having one or more refrigerant passage holes is provided between the two refrigerant blocking portions, the length of each refrigerant blocking portion is 15% or more of the total length of the sorting control panel, wherein the heat exchanger has an opening ratio of 20 to 75%, which is a ratio of the number of refrigerant passage holes formed in the refrigerant passage portion to the number of heat exchange tubes of each tube group. According to claim 3, Refrigerant blocking portions are respectively provided at both ends of the classification control panel, a refrigerant passage portion having one or more refrigerant passage holes is provided between the two refrigerant blocking portions, the length of each refrigerant blocking portion is 15% or more of the total length of the classification control panel, the total area of the total refrigerant passage holes formed in the refrigerant passage portion is 130 to 510 mm 2, and the number of refrigerant passage holes formed in the refrigerant passage portion relative to the number of heat exchange tubes in each tube group. The heat exchanger whose aperture ratio which is a ratio is 20 to 75%. The said refrigerant | coolant turn side tank is a 1st member made from aluminum to which a heat exchange tube is connected, and the 2nd member of the extruded aluminum extrusion member brazed by the part on the opposite side to a heat exchange tube, The classification control panel A heat exchanger formed integrally with the second member. The inside of the outlet header chamber of the refrigerant inlet / outer tank is partitioned by a diaphragm into a first space in communication with a corresponding heat exchange tube, and a second space in which refrigerant flows therefrom. Mutually communicating heat exchanger. The heat exchanger of claim 9, wherein one or more refrigerant passage holes are formed in the diaphragm, and the two spaces communicate with each other through the refrigerant passage holes. 10. The method according to claim 9, wherein the refrigerant inlet / out tank comprises an aluminum first member to which a heat exchange tube is connected, and an aluminum extruded second member to be brazed at a portion opposite to the heat exchange tube to the first member, A heat exchanger in which the partition and the diaphragm are integrally formed with the second member. The heat exchanger according to claim 9, wherein a coolant inlet communicating with the inlet header chamber and a coolant outlet communicating with the second space of the outlet header chamber are provided at one end of the coolant inlet / outer tank. The heat exchanger of claim 1, wherein each tube group comprises at least seven heat exchange tubes. A refrigeration cycle comprising a compressor, a condenser, and an evaporator, wherein the evaporator is a heat exchanger according to any one of claims 1 to 13. A vehicle in which a refrigeration cycle according to claim 14 is mounted as an air conditioner. Between the refrigerant inlet / outlet tanks and the refrigerant turn-side tanks, which are spaced apart from each other, a tube group consisting of a plurality of heat exchange tubes arranged in parallel in the longitudinal direction of both tanks is installed in a plurality of rows spaced apart in the air flow direction through the heat exchanger. Both ends of the heat exchange tubes of each tube group are connected to respective tanks, and the inside of the refrigerant inlet / outer tank is partitioned into a refrigerant inlet header chamber and a refrigerant outlet header chamber arranged in the air flow direction by a partition wall, and both headers Each of the chambers is in communication with a heat exchange tube of at least one row of tube groups, and the refrigerant flowing into the inlet header chamber of the refrigerant inlet / outer tank can be introduced into the refrigerant turn-side tank via the corresponding heat exchange tube, where the course is changed. Heat exchanger configured to flow into the outlet header chamber of the refrigerant inlet / outlet tank through a corresponding heat exchange tube, The inside of the inlet header chamber of the coolant entry / exit tank is partitioned into a first space communicating with a corresponding heat exchange tube and a second space into which a refrigerant flows by a resistance plate for classification, and one refrigerant passage hole in the classification resistance plate. This formed heat exchanger. 17. The heat exchanger according to claim 16, wherein said refrigerant passage hole is formed in a central portion in the longitudinal direction of said flow resistance plate. 17. The heat exchanger of claim 16, wherein the refrigerant passage hole is located between a pair of heat exchange tubes adjacent to each other in the longitudinal direction of the refrigerant inlet / outlet tank among the heat exchange tubes communicating with the inlet header chamber of the refrigerant inlet / outside tank. 17. The heat exchanger of claim 16, wherein said refrigerant through hole has an area greater than the total transverse area of the refrigerant passages in one heat exchange tube. 17. The heat exchanger of claim 16, wherein said refrigerant passage hole is circular and has a diameter of 3 to 8 mm. 17. The refrigerant entering and exiting side tank has a wall portion to which a heat exchange tube communicating with the first space is connected, and a portion of the wall portion corresponding to the refrigerant passage hole includes a refrigerant passing through the refrigerant passage hole. A heat exchanger, wherein a flow dividing member for dividing in the longitudinal direction of the inlet header chamber protrudes inward. 22. The heat exchanger according to claim 21, wherein the flow dividing member is a ridge that projects in an angle shape toward the resistance plate and extends in the width direction of the inlet header chamber. The method of claim 16, wherein the interior of the outlet header chamber of the refrigerant inlet / out tank is partitioned by a diaphragm into a first space in communication with a corresponding heat exchange tube, and a second space from which refrigerant flows out. Heat exchanger with a through hole formed. 24. The method according to claim 23, wherein the refrigerant inlet / out tank comprises an aluminum first member to which a heat exchange tube is connected, and an aluminum extruded second member to be brazed at a portion opposite to the heat exchange tube to the first member. The heat exchanger in which a partition, a resistance plate for sorting, and a diaphragm are integrally formed with the second member. The heat exchanger according to claim 16, wherein a coolant inlet communicating with the second space of the inlet header chamber and a coolant outlet communicating with the outlet header chamber are provided at one end of the coolant inlet / outer tank. The inside of the refrigerant turn-side tank is configured by the flow control panel to communicate with a heat exchange tube communicating with a heat exchange tube communicating with a first space of an inlet header chamber of the refrigerant inlet / outer tank, and an outlet header of the refrigerant inlet / out side tank. And a second space communicating with the heat exchange tube communicating with the chamber, wherein the flow control panel is provided with a refrigerant blocking portion at a position corresponding to the refrigerant passage hole of the resistance plate for sorting in the longitudinal direction of both tanks. A heat exchanger other than that provided with a refrigerant passage portion having a refrigerant passage hole. 27. The heat exchanger of claim 26, wherein the refrigerant blocking portion of the fractionation control panel has a length of 28 mm or more. 27. The heat exchanger of claim 26, wherein the aperture ratio is 20 to 90%, which is the ratio of the number of refrigerant passage holes formed in the splitting control panel to the number of heat exchange tubes in each tube group. 27. The method of claim 26, wherein the refrigerant turn-side tank comprises a first aluminum member to which a heat exchange tube is connected, and a second aluminum extruded brother member that is brazed to a portion opposite to the heat exchange tube to the first member. A heat exchanger in which the control panel is integrally formed with the second member. A refrigeration cycle comprising a compressor, a condenser and an evaporator, wherein the evaporator is a heat exchanger according to any one of claims 16 to 29. A vehicle in which a refrigeration cycle according to claim 30 is mounted as an air conditioner.

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