JPH0781760B2 - Multilayer evaporator - Google Patents

Description

The present invention relates to a laminated evaporator such as an evaporator used in an air conditioner for automobiles.

[Prior Art] An outline of the structure of an evaporator used in an air conditioner for automobiles as an example of a conventional laminated evaporator is shown in Figs. 16 and 17.
The detailed structure of the flat tube constituting the evaporator is shown in FIGS. 4 to 7. The evaporator B is provided with a refrigerant inlet port 100a and an outlet port 100b at the upper end, and a group of metal flat tubes 100 having a U-shaped refrigerant channel formed in the tube by connecting these ports by brazing. It is formed by stacking and laminating in the flat direction. The refrigerant inlet port 100a (100
Since a gap G corresponding to the thickness of b) is generated, a corrugated fin 102 for increasing the heat transfer area is fitted and brazed to this portion to function as a heat exchange space. Flat tube 100
Since the specific structure of the flat tube is essentially the same as that of the flat tube 1 constituting the heat exchanger according to the present invention, the outline will be described with reference to FIGS. 4 to 7 as a structural explanatory view of the flat tube 1. Then, by pressing an aluminum plate, two tube play 1A having a plane shape as shown in FIG. 4 and forming an extremely shallow tray as a whole.
(1B) is prepared and formed by brazing and joining just like the skins in the middle of the confectionery. Due to the presence of the vertical partition wall 1C in which the lower end is absent in the flat pipe, a U-shaped refrigerant flow passage 12A connecting the inlet port 1a and the outlet port 1b of the refrigerant arranged in parallel at the upper end of the pipe is formed. 12B is formed. Both ports 1a and 1b are provided with a coolant inflow or coolant circulation hole a at both left and right end faces in the flat direction of the respective pipes.

Each of the flat tubes located at the left and right ends of the evaporator B lacks the port of the outer tube plate in a set of tube forming tubes, and instead, the refrigerant supply piping 103
Alternatively, the joint portion 103A or 104A of the refrigerant discharge pipe 104 is brazed and connected. A pair of adjacent flat tubes occupying an intermediate position between the left and right ends is provided with a refrigerant passage blocking plate 120 for blocking communication of the respective refrigerant inlet ports.
Is installed so as to close the. (Although the flat tube 100 lacking the hole a is actually prepared, it is shown as a blocking plate here for the sake of easy understanding of the refrigerant flow path.) The inside of the conventional evaporator B having the above structure is filled with the refrigerant. FIG. 18 schematically shows the flow. The refrigerant flow path is drawn as a flow line whose flow direction is indicated by an arrow. In the figure, 110 is a refrigerant distribution path formed by mutually communicating the refrigerant circulation holes a of the refrigerant inlet port 100a of the flat tubes 100 group, and 111 is also the refrigerant outlet port 100b.
Is a refrigerant collecting path formed by communicating the refrigerant circulation holes a of each other. 112A and 112B are U in the flat tube 100
It represents a V-shaped refrigerant flow path, and there are as many flat tubes 100 as there are stacked layers.

Explaining the outline of the operation of the evaporator B, the high-temperature and high-pressure gas-phase refrigerant discharged from the compressor of the vehicle-mounted refrigerator is
It is sent to the condenser, made into a cooling liquid, and temporarily stored in the receiver. The liquid-phase refrigerant sent from the receiver is passed through the decompression device, becomes a low-pressure atomized body, flows from the refrigerant supply pipe 103 into the evaporator B, and diffuses into the refrigerant distribution path 110 (a). , The refrigerant inlet port 100a of each flat tube 100 constituting this distribution path, reaches the refrigerant outlet port 100b from the refrigerant inlet ports 100a of the respective tubes, reaches the refrigerant outlet port 100b, and is a collection of the ports 100b. It merges again in the path 111 (a).

By the way, as described above, in the evaporator B, the refrigerant inlet port distribution holes a of the pair of flat tubes adjacent to each other occupying the intermediate position between the both ends of the laminated flat tube group 100 have the blocking plate 120.
Since it is blocked by the
The length (a) corresponds to the length from the refrigerant inlet side end of the evaporator B to the blocking plate 120, that is, half the distance between the refrigerant inlet side and outlet side ends of the evaporator B. Therefore, the end portion of the refrigerant collecting passage 111 (a) is none other than the refrigerant outlet port 100b of the flat tube 100 occupying the intermediate position. This outlet port 100b is an adjacent flat tube
It will be communicated with the refrigerant inlet port 100a of 100,
The second refrigerant distribution passage 110 (b) is formed by the continuation of the refrigerant inlet port 100a of the downstream flat tube group 100 including the adjacent flat tubes 100.
Is configured. The refrigerant once diffused in this distribution path is the second refrigerant collecting path 111 constituted by the refrigerant outlet port 100b of the group of flat tubes 100 on the downstream side of the blocking plate 120 in the same manner as described above.
The U-shaped refrigerant channels 112A and 112B in each flat tube 100 are traced toward (b). The refrigerant collected in the refrigerant collecting path 111 (b) is connected to the end of this collecting path by the refrigerant discharge pipe 10.
Although it is discharged to 4, the refrigerant that was in the atomized liquid phase state when flowing into the evaporator B is completely evaporated and vaporized at that time. That is, while sequentially passing through the flat tubes 100 that are connected in a laminated state, the liquid-phase refrigerant is successively sent into the heat exchange gap G that is in contact with these flat tubes by the force-feeding force of the blower. This is because the latent heat of vaporization is absorbed from the warm conditioned air to perform the cooling work, and at the same time it is vaporized and vaporized. The vapor-phase refrigerant discharged from the evaporator B is sucked into the compressor and is compressed to high temperature and high pressure, resulting in the first stroke of the refrigeration cycle.

[Problems to be Solved by the Invention] The reason why the refrigerant flow path blocking plate 120 is provided in the conventional evaporator B having the above-described configuration is that the blocking plate 120 is not provided like the old type evaporator. In this case, the refrigerant flow path C in the evaporator B is in the state shown by the streamline with an arrow in FIG. 19, and the length of the refrigerant distribution path 110 is 2 as compared with the evaporator B of the type having the blocking plate 120. The flat tube 1 in which the refrigerant should be distributed from this distribution path 110
This is to improve the problem that the number of 00s is doubled and naturally it becomes difficult to evenly distribute the flat tubes. If the flat tube 100 located farther from the refrigerant supply pipe 103 has a smaller amount of refrigerant supply than the flat tube 100 occupying the closer position, and therefore the heat exchange capacity also decreases, the evaporator B has a cross section in the ventilation direction. In this case, the air cooling is unevenly performed, which is extremely undesirable. It is a matter of course that, if the number of flat tubes in the refrigerant distribution path 110 is reduced, it becomes easier to equally distribute the refrigerant to the flat tubes.

However, the conventional evaporator B thus improved has the following new problems. That is,
As can be understood by comparing FIG. 19 and FIG. 19, in the conventional evaporator B with the refrigerant flow path blocking plate 120, the U-shaped refrigerant flow having a large flow resistance from the first refrigerant distribution path 110 (a). First refrigerant collecting passage 111 passing through passages 112A and 112B
After once reaching (a), the second refrigerant distribution passage 11 is again provided.
The U-shaped refrigerant flow passage interposed between 0 (b) and the second refrigerant collecting passage 111 (b) is passed, and the refrigerant is twice as much as the refrigerant flow passage C of the conventional evaporator. Therefore, there is an inconvenience that the pressure loss on the refrigerant side increases, the refrigerant cannot be smoothly replenished to the compressor of the refrigerator, and the capacity of the air conditioner deteriorates.

An object of the present invention is to provide a laminated evaporator capable of more evenly distributing the refrigerant to each flat tube without increasing the pressure loss on the refrigerant side.

[Means for Solving the Problems] According to the present invention, a coolant inlet port and a coolant outlet port are provided at one end side, a partition wall is provided in a pipe, and a U-shaped coolant flow path connecting these ports is formed inside. In a laminated evaporator in which a group of flat tubes are laminated and combined, a diversion part that diverts a refrigerant supply pipe line that supplies a refrigerant into two parts, and a diversion part
Two refrigerant supply pipes that connect two branching sides and the refrigerant inlet ports of the flat tubes at both ends of the laminated flat tube group with equal pipelines, respectively, and the refrigerant of the adjacent flat tubes is provided. The inlet ports are communicated with each other, except for the adjoining portion of the central portion of the laminated flat tube group.
With one refrigerant distribution path, the refrigerant outlet ports of the adjacent flat tubes are made to communicate with each other to form a refrigerant collecting path, and a refrigerant discharging pipe is connected to a central portion of the refrigerant collecting path as a technical means. To do.

[Operation] According to the present invention, by the above technical means, the refrigerant supplied from the refrigerant supply pipe is divided into two refrigerant supply pipes in the flow dividing portion, and the flat pipes at both ends of the flat pipe group that are laminated and combined are flattened. The refrigerant inlet ports of the pipes respectively flow toward the refrigerant distribution passages communicating with the refrigerant inlet ports toward the central portion in the stacking direction, and some of them are refrigerant inlets as the refrigerant distribution passages in each flat pipe. The heat is exchanged while being distributed from the ports, passing through the refrigerant passages, toward the refrigerant outlet ports, and passing through the respective refrigerant passages.

Since the refrigerant discharge pipe is connected to the central portion of the refrigerant collecting passage that communicates the refrigerant outlet ports, the refrigerant that has passed through the refrigerant flow path in each flat pipe and reached each refrigerant outlet port side is the refrigerant collecting passage. While merging in the passage, it moves toward the center of the refrigerant collecting passage and is discharged from the refrigerant discharge pipe.

Therefore, all the refrigerant supplied from the refrigerant supply line is
After being divided in the flow dividing portion and passing through the refrigerant supply pipe,
Whichever flat tube passes through, it will pass through the sum of the distance corresponding to half the thickness of the laminated flat tube group and the distance of the refrigerant flow path of each flat tube.

[Examples] Specific configurations of the present invention will be described below based on examples shown in the accompanying drawings.

FIG. 1 to FIG. 8 are explanatory views of the first embodiment, and an evaporator A1 as a laminated evaporator for use in an air conditioner for an automobile has a flat tube 1 group as a refrigerant flow path. It is provided with a structure in which they are laminated and united in the flat direction.

The flat tube 1 is a plan view in FIGS. 4 to 7, and (a)-(a), (b)-(b) and (c) -in these plan views.
(C) Pressed into the shape drawn as a sectional view,
Two tube plates 1A and 1B that form a very shallow tray as a whole
Is formed by sticking each of the recessed sides so as to face each other in the shape of a skin in the middle. Tube plates 1A and 1B (hereinafter simply 1A
Have exactly the same geometry, for example A3
Use a material in which a brazing material such as A4004 is previously clad on both sides of the aluminum plate of 003. Tube plate
At the upper end of 1A, the refrigerant inlet port 1a and the refrigerant outlet port
Two bulging portions functioning as 1b are formed adjacent to each other in the outward direction of the flat tube 1 by drawing. A passage hole a for inflow or outflow of the refrigerant is formed on the side surface of each of the boats. A partition wall 1C for dividing the space in the flat tube 1 into two along the longitudinal center line is stamped and formed, but the lower end is missing, so the flat tube 1 has a refrigerant inlet port inside. U-shaped coolant channels 12A and 12B connecting 1a and the coolant outlet port 1b are formed. 1d and 1e are small punching ribs arranged in a slanting direction in order to give a maze shape to the refrigerant dragon and improve heat exchange efficiency. The peripheral edge of the tube plate 1A is surrounded by a flange-shaped portion 1f which is a bonding surface of the two tube plates. In addition, the lower end is bent and protruded horizontally toward the outside of the pipe (1h in the figure), and by bending the protruding end further downward, a flange-like attachment for brazing with the adjacent flat pipe 1 is made. There is a mating surface of 1g.

In order to assemble the evaporator A1 as shown in the side view in FIG. 1 and the top view in FIG. 2 by stacking a large number of tube plates 1A having such a structure, an appropriate assembly jig is used. First, apply one side plate 9a made of aluminum plate with brazing material clad on both surfaces to be protective plates at both ends of the evaporator A1 to one fixed end face, and thin aluminum plate for increasing heat exchange area. A corrugated fin 2 made of aluminum is added, and then an end plate 9 made of an aluminum plate having an irregularly flat shape, which is one of the outermost flat tubes, is applied.
After stacking 1A, the second corrugated fin 2 is attached to it, and the second flat plate 1 is constructed.
Temporarily assemble the evaporator A1 with the structure shown in the figure by applying 1A, and fix it in this state with a jig and place it in the brazing furnace heated to the melting temperature of the brazing material. , The constituent members are joined at once to complete the main body of the evaporator A1.

In this brazing process, the two tube plates 1A forming each flat tube 1 are brazed with the ribs 1d and 1e to be changed in such a manner that the top surfaces of the opposing members cross in an X shape. Therefore, a strong pipe structure that can withstand high refrigerant vapor pressure can be obtained.

Further, since the side faces of the respective refrigerant inlet ports 1a or the outlet ports 1b of the adjacent flat tubes 1 are brazed to each other by bonding, the groups of the refrigerant inlet ports 1a are connected to each other as shown by the broken line in FIG. A refrigerant distribution path 10 is formed by communicating through the passage holes a, and a refrigerant collecting path 11 is formed by communicating the refrigerant outlet ports 1b group through the passage holes a. However, unlike the refrigerant flow passage C of the conventional evaporator shown in FIG. 19, the refrigerant distribution passage 10 and the collecting passage 11 are both divided at the central portion. In this embodiment, in fact, the evaporator described above is used.
Although the description of the assembly method of A1 is omitted, one set of flat tubes 1 located adjacent to the central part has the refrigerant inlet / outlet ports 1a and 1b of the tube plates A1 on opposite sides removed. As a substitute for this port, a pipe joint 5A having a cylindrical shape for attaching the refrigerant discharge pipe 5 is interposed (see FIG. 8), and this pipe joint 5a is connected to the refrigerant distribution path 10.
It functions as a dividing means that plays the role of dividing. The state of the refrigerant split flow will be described later in the description of the operation.

On both end surfaces of the main body of the evaporator A1, the pipe joints 3A and 4A of the two refrigerant supply pipes 3 and 4 are connected to the evaporator 9 at both ends so as to communicate with both ends of the refrigerant distribution passage 10 respectively. Each is brazed and joined. Reference numeral 6 is a flow dividing joint between the two refrigerant supply pipes 3 and 4, 7 is a refrigerant pipe joint connected to the joint 6, and 8 is an inlet side joint of the refrigerant discharge pipe 5.

8 to 12 exemplify a method of attaching the refrigerant supply pipes 3 and 4 and the refrigerant discharge pipe 5 to the main body of the evaporator A1.

FIG. 9 and FIG. 10 depict the first mounting method of the refrigerant supply pipes 3 or 4, and the pipe joint is formed by deforming the outlet end of the pipe pipe 4 (or 3) into a rectangular tube shape. 4A
Is shaped. The end of the pipe joint 4A is brazed and sealed by a cap body 4B, and the surface of the joint 4A abutting toward the refrigerant flow hole a of the outermost flat tube 1 of the evaporator is the opening of this hole a. A cutout hole d is formed for fitting the folded-back portion formed on the peripheral edge. Flat tube 1
The upper side portion of the side plate 9a is sandwiched between and the pipe joint 4A. Although brazing is performed to join each of these members as seen in FIG. 2, this brazing process may be incorporated in the above-described evaporator assembling step,
It may be a separate post process.

FIG. 11 shows the second mounting method. The end portion of the refrigerant supply pipe 4 is bent by 90 °, and the pipe joint portion is formed by forming a brim-shaped bulging portion 4D by bulging at this bent portion. The end of such a refrigerant supply pipe 4 is inserted into a pipe mounting hole e provided in the end plate 9 of the evaporator A1 and brazed to complete the mounting.

8 and 12 show a method of mounting the refrigerant discharge pipe 5 at the center of the evaporator A1. Refrigerant discharge pipe 5
The end portion of is deformed to form a rectangular tube like the refrigerant supply pipe 4 (or 3) to form a pipe joint 5A. Reference numeral 5B is a cap body which is brazed to the end opening of the joint 5A. Piping attachment holes e are formed on both side wall surfaces of the pipe joint 5A at positions facing the refrigerant circulation holes a formed in the ports of the flat tubes 1 to form the refrigerant collecting passages 11, respectively. The joint 5A communicates with the refrigerant collecting passage 11. In the brazing and assembling process of the evaporator A1, the pipe joint 5A is brazed to the flat tubes 1 on both sides at the same time by interposing it between a pair of flat tubes 1 arranged adjacent to the center of the evaporator. To be done.

Next, the operation of the evaporator A1 of the first embodiment will be described with reference to FIG. 3, FIG. 1, and FIG. As described above, the reduced pressure atomized refrigerant that has reached the location of the diversion joint 6 from the refrigerant pressure reducing device through the pipe is divided into the two refrigerant supply pipes 3 and 4 and is positioned at both ends of the evaporator A1. Are simultaneously supplied to both ends of the refrigerant distribution passage 10 from the respective pipe joints 3A and 4A. The flows of the two refrigerants that have flowed into the distribution passage 10 reach the intermediate position of their entire lengths and are blocked by the interposition of the rectangular tubular joint 5A as described above. Therefore, each of the refrigerant distribution passages divided into two is 1 / third when the number of flat tubes is the same as compared with the conventional evaporator whose refrigerant passage is shown in FIG.
It suffices to take charge of distributing the refrigerant to the two flat tubes 1. Therefore, as a matter of course, the distribution of the refrigerant to the flat tubes 1 is far more evenly performed, and the evaporator A1 can reduce the uneven distribution tendency of the air cooling capacity in the cross section in the ventilation direction. Flat tube divided into 2 groups 1
While passing through each of the U-shaped flow paths in the inside, the refrigerants that have lost the latent heat of vaporization from the air to be cooled, have performed cooling work, and returned to the gas phase, are likewise grouped into two groups and flow into the refrigerant collecting path 11. Since the end of the collecting passage of each group is communicated with the pipe joint 5A of the refrigerant discharge pipe 5, the gas-phase refrigerant that has merged in this joint 5A is traced through the pipe 5 and re-sucked into the compressor of the refrigerator. , And circulation supply to the evaporator A1 was performed.

Now, comparing the refrigerant flow path of the conventional evaporator B shown in FIG. 18 with the refrigerant flow path of the evaporator A1 of the above embodiment shown in FIG. 3, the refrigerant distribution paths 110 and 10 and the refrigerant flow paths are compared. Since the collecting passages 111 and 11 are each divided into two, the purpose of making the distribution of the refrigerant to the flat tubes more equal is fulfilled almost the same, but the flow resistance received by the refrigerant while passing through the evaporator is fulfilled. The degree of is completely different. Third
Reference numeral 20 in the figure is a blocking plate that schematically shows the dividing means of the refrigerant distribution path, and the pipe joint 5A is actually disposed here.

As described above, the cross-sectional area of the refrigerant passage and its shape change extremely complicatedly inside the flat tube and the inlet / outlet portion.
As a matter of course, a great flow resistance is exerted, but in the conventional evaporator B, in order to escape from the refrigerant distribution passage to the refrigerant collecting pipe, it has to pass through the flat pipe twice, so that as described at the beginning, the refrigerant side However, the evaporator A1 according to the present invention passes through the flat tube 1 only once like the refrigerant flow path of the conventional evaporator. Only the above advantages can be obtained without the disadvantage that the pressure loss on the refrigerant side increases. Theoretically, it can be inferred that the evaporator A1 according to the present invention can significantly reduce the pressure loss of the refrigerant by 1/6 to 1/8 as compared with the conventional evaporator B.

FIG. 15 schematically shows, as a Mollier diagram, a refrigeration cycle of a refrigerator in which the evaporator A1 according to the present invention and the conventional evaporator B are incorporated. Graph (a) is for evaporator A1, and graph (b) is for evaporator B.
The graph (C) is a saturated liquid and a saturated vapor line. Area A → B in the figure is the compression process,
B → C is a condensation process, C → D is an expansion process, and D → E is an evaporation process. Point A corresponds to the compressor inlet, and point E corresponds to the evaporator outlet. The meaning of this figure is that the pressure drop ΔP of the refrigerant due to passage through the evaporator is much smaller in the pressure drop ΔP1 of the evaporator A1 of the present invention than in the conventional evaporator B, and therefore the suction pressure at the compressor suction port A is also equal to that of the evaporator.
This means that A1 is increased to increase the circulation amount of the refrigerant flowing through the refrigeration cycle and improve refrigeration efficiency. Δi in the figure represents the cooling effect per unit weight of the refrigerant, and the cooling capacity Q is represented by Δi × G (refrigerant circulation amount).

FIG. 13 is a perspective view of the evaporator A2 of the second embodiment according to the present invention, and FIG. 14 is a refrigerant flow path diagram thereof, and the basic structure of the evaporator is exactly the same as that of the evaporator A1 of the first embodiment. . However, the difference between the two is understood by comparing FIG. 14 with FIG. 3 of the refrigerant flow path diagram of the evaporator A1, and in the evaporator A1, the refrigerant collecting path 11 is divided into two paths with the central part as a boundary. Evaporator A2 was divided into
Is that each of the refrigerant collecting passages 11 divided into two is further divided into two by refrigerant passage blocking plates 21 and 22. As I said earlier, it is actually a blocking plate 21
Instead of 22 and 22, the refrigerant flow hole a is not provided in the tube plate 1A of the flat tube 1 located at the place where this plate is placed.

The operational feature of the evaporator A2 of the second embodiment is that the refrigerant distribution passage 10 is divided into four passages as shown in FIG. 14 as a refrigerant passage diagram.
The number of the flat tubes 1 for which one refrigerant distribution path should play the role of supplying the refrigerant is further halved as compared with that in the first embodiment, and the distribution of the refrigerant to each flat tube 1 constituting the evaporator is further improved. This can be done evenly. However, in this evaporator A2, it has to pass through the U-shaped refrigerant flow path twice before it reaches the collecting path from the refrigerant distribution path, which is accompanied by a disadvantage that the pressure of the refrigerant decreases. In comparison, the degree of pressure drop can be suppressed to a much smaller degree by the effect of dividing the flow path.

In the above-mentioned first and second embodiments, the refrigerant supply pipes are connected to both ends of the refrigerant distribution passage. On the contrary, the refrigerant discharge pipes are divided into two passages by the diversion joint, and the end of each diversion pipe is connected. While connecting to both ends of the refrigerant collecting passage, the refrigerant supply pipe may be attached in the middle of the refrigerant distributing passage. In this case, the cooling efficiency is improved by installing the refrigerant supply pipe on the leeward side and the refrigerant discharge pipe on the upwind side with respect to the direction of air blown to the evaporator.

Next, an evaporator A3 as a third embodiment will be described with reference to FIGS. 20 to 26. The evaporator A3 of this embodiment is different from the evaporators A1 and A2 of the above embodiment in that the use of a flat tube that blocks one of the communication paths of the refrigerant inlet port as the distribution means of the refrigerant distribution path 10 is omitted. . Along with this, the pipe joint 5A for attaching the refrigerant discharge pipe 5 to the evaporator is not required and the pipe mounting structure is simplified.

The flat tube 201 for mounting the refrigerant discharge pipe 5 located at the center of the stacked flat tube 1 group is completely the same as the other flat tubes 1 in the basic structure. The only difference is the 22nd plan view of the tube plate 201A that constitutes this flat tube 201.
As shown in FIG. 22-a as a side view of the tube plate 201B and as FIG. 25 as a cross-sectional view of a portion of the evaporator for installing the refrigerant discharge pipe 5, the refrigerant outlet port 201b is communicated with. The fitting flange of the pipe 5
The point 202 is that the tube plates 201A and 201B are integrally formed during press molding. The end of the refrigerant discharge pipe 5 on the refrigerant inlet side is fixed by brazing while being fitted in the flange portion 202. Reference numeral 201a is a refrigerant inlet port, and other reference numerals in the drawing are common to those in the above-described embodiment.

The operation of the evaporator A3 of this embodiment will be described with reference to FIG. 26 schematically showing the flow of the refrigerant in the evaporator. From the refrigerant supply pipes 3 and 4 attached to both side ends of the evaporator A3, respectively. The atomized refrigerant that has flowed in flows into the refrigerant distribution path formed by connecting the respective refrigerant inlet ports 1a of the group of flat tubes 1 and advances to reach the inlet port 201a of the flat tube 201 located at the center of the evaporator A3. The flow of the refrigerant stops where the pressures of the two refrigerants compete with each other. Since the refrigerant inlet port 1a and the outlet port 1b of each flat tube 1 are communicated with each other through the U-shaped passages 12A and 12B as described above, the refrigerant that has spread to the respective inlet ports 1a is the outlet on the low pressure side. It passes through the U-shaped refrigerant flow path toward the port 1b, and during this time, the latent heat of vaporization is taken from the warm air to perform the cooling work. Refrigerant collecting path 11 formed by connecting the refrigerant outlet ports 1b of the flat tubes 1
As shown in FIG. 26, the two sets of refrigerant flows reach the refrigerant outlet port 201b of the flat tube 201 located in the central portion of the evaporator and merge with each other to reach the end of the refrigerant discharge pipe 5. Is discharged from the pipe 5 by the suction force of the compressor.

Therefore, as in the two embodiments described above, it is not necessary to prepare a flat tube that blocks the communication port on one side of the refrigerant inlet port in order to divide the refrigerant distribution channel or the collecting channel, and the refrigerant distribution channel and the collecting channel are naturally prepared. The flow path of the passage is divided and shortened, and the effect intended by the present invention can be obtained.

In the evaporator A3 described above, the refrigerant discharge pipe 5 is attached to the central portion and the refrigerant supply pipes 3 and 4 are attached to both end portions of the evaporator. May be connected to.

[Effects of the Invention] In the laminated evaporator having the above-described structure, the refrigerant supplied from the refrigerant supply pipe is divided into two, and the refrigerant is supplied from both ends of the flat tube group which is laminated and integrated. Since it is configured to be discharged from each section, and in the meantime, each flat pipe is supplied through the refrigerant distribution path, the number of flat tubes to be distributed per one refrigerant distribution path can be reduced,
It becomes possible to more evenly distribute the refrigerant to each flat tube, which was technically extremely difficult. Therefore, the uneven distribution of the cooling capacity in the cross section in the ventilation direction of the evaporator is improved, and a more evenly cooled blown air flow can be obtained.

In addition, in the evaporator provided with the conventional refrigerant distribution path dividing means, the U-shaped flow having extremely large passage resistance is required until the refrigerant flowing into the refrigerant distribution path follows the U-shaped flow path in the flat pipe and reaches the refrigerant collecting path. Since the evaporator of the present invention only has to pass through the passage twice, the cooling capacity of the refrigerator due to pressure loss of the refrigerant can be sufficiently reduced.

[Brief description of drawings]

1 to 8 are all diagrams of the first embodiment of the present invention, in which FIG. 1 is a front view of a laminated evaporator as an evaporator incorporated in an automobile air conditioner, and FIG. 2 is a top view. 3, FIG. 3 is a refrigerant flow path diagram, FIG. 4 is a plan view of a tube plate as a constituent member of a flat tube which constitutes the evaporator, FIG.
FIGS. 6 and 7 are (a) -of FIG. 4, respectively.
(A), (b)-(b), (c)-(c) sectional view, 8th
The figure is a partial vertical cross-sectional view of the evaporator. Figures 9 and 10
FIG. 11 is an explanatory view of a method of mounting the refrigerant supply pipe, FIG. 11 is an explanatory view of another mounting method of the same, and FIG. 12 is an explanatory view of a method of mounting the refrigerant discharge pipe. FIG. 13 is a perspective view of the evaporator of the second embodiment.
FIG. 14 is a refrigerant flow path diagram thereof. FIG. 15 is a comparison diagram of Mollier diagrams of the conventional evaporator and the evaporator according to the present invention. 16 to 18 are a side view, a top view, and a refrigerant flow path view of a conventional evaporator, respectively, and FIG. 19 is a refrigerant flow path view of a conventional evaporator. 20 to 26 are all views relating to the evaporator of the third embodiment, wherein FIG. 20 is a front view, FIG. 21 is a top view, and FIG. 22 is a tube forming a flat tube in the central portion. The plan view of the plate, FIGS. 22-a and 22-b are the side view and (c)-(c) sectional view of FIG. 22, and FIGS. 23 and 24 are the (a) -of FIG. (A) Cross-sectional view and (b)-(b) cross-sectional view, FIG. 25 is a cross-sectional view of the mounting portion of the refrigerant discharge pipe, and FIG.
The figure is an illustration of a refrigerant flow path in the evaporator. In the figure, A1, A2 ... Multilayer evaporator (evaporator), 1 ...
Flat pipe, 2 ... Corrugated fins, 3, 4 ... Refrigerant supply pipe, 5 ... Refrigerant discharge pipe, 10 ... Refrigerant distribution passage, 11
...... Refrigerant collecting path, 20 to 22 ...... Refrigerant distribution path dividing means, 1a
…… Refrigerant inlet port, 1b …… Refrigerant outlet port, 1c …… Partition wall, 12A + 12B …… U-shaped refrigerant flow path

 ─────────────────────────────────────────────────── ─── Continuation of the front page (56) Bibliography Sho 54-38956 (JP, U) Rikai 51-83966 (JP, U) Rikai 52-150063 (JP, U) Rikai 56- 28578 (JP, U)

Claims (1)

[Claims] 1. A flat tube group in which a refrigerant inlet port and a refrigerant outlet port are provided on one end side, a partition wall is provided in the pipe, and a U-shaped refrigerant channel connecting these ports is formed inside is laminated and combined. In the laminated evaporator, the diversion part that diverts the refrigerant supply pipe for supplying the refrigerant into two parts, and the refrigerant of the flat tubes at both ends of the flat tube group that is laminated and integrated with the two diversion sides of the diversion part An inlet port and two refrigerant supply pipes connected to each other by equivalent pipelines; and the refrigerant inlet ports of the adjacent flat tubes except for an adjoining portion of the central portion of the laminated flat tube group. And the two refrigerant distribution paths are communicated with each other, and the refrigerant outlet ports of the adjacent flat tubes are communicated with each other to form a refrigerant collecting path, and a refrigerant discharge pipe is provided at the center of the refrigerant collecting path. Characterized by being connected Layer type evaporator.