JPH03140795A - Lamination type heat exchanger - Google Patents

Abstract

PURPOSE:To improve the imbalance of a thermal load in the section of a refrigerant passage and unify the distribution of refrigerant into respective flat tubes by a method wherein the width of passage orthogonal to a heat transfer plate in the flat heat transfer tube is formed so as to be equalized from an inlet tank section to an outlet tank section substantially. CONSTITUTION:The thickness of a passage orthogonal to a heat transfer tube plate 1a is formed so as to be constant substantially between an inlet port header and an outlet port header, heat transfer tubes, equipped with a continuous refrigerant passage, are connected and even amount of refrigerant flows stably. In this case, the outer peripheral end 7b of U-shape sumit of a meandering refrigerant passage, neighboring to a tank section, is formed proximate to the outermost peripheral connecting rib 7 of the heat transfer tube plate while the width (h1) of an inlet tank and the width (h2) of an outlet tank are designed so as to be substantially equal to the width W1 of a first refrigerant passage 8a and the width W4 of a fourth refrigerant passage 8d respectively.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a laminated heat exchanger used in air conditioners and the like, and particularly to a laminated heat exchanger suitable for an evaporator for a car air conditioner.

[Conventional technology]

The conventional stacked heat exchanger used as an evaporator is
For example, as described in Japanese Patent Application Laid-Open No. 119373/1983, two heat transfer plates are combined to form a shallow U-shaped recess to serve as a refrigerant flow path, leaving a flow path partition in the middle.
A large number of flat heat exchanger tubes forming a shaped refrigerant passage and corrugated fins on the air side to be cooled are stacked alternately, and a refrigerant inlet and an outlet tank are provided at both ends of the U-shaped passage so as to communicate with adjacent heat exchanger tubes. It has a similar structure. The refrigerant that has flowed into the air downstream passage through the tank portion flows perpendicularly to the air, makes a U-turn at the bend in the flow path, reaches the air upstream side, and flows out of the evaporator through the outlet tank portion.

The refrigerant in the pipe exchanges heat with the air via the air-side corrugated fins, removes heat from the air, and the liquid refrigerant evaporates, increasing the proportion of gas refrigerant as it flows toward the outlet, until it reaches the outlet tank. Almost completely becomes a gas refrigerant and flows out of the evaporator exchanger.

The air flowing into the heat exchanger is first cooled by heat exchange with the refrigerant while crossing the upstream air passage of the U-shaped passage, and then cooled to a predetermined temperature while crossing the air downstream refrigerant passage. Cold air was flowing out of the heat exchanger.

[Problem to be solved by the invention]

In conventional heat exchangers with the above configuration, the refrigerant passage is only divided into two parts in a U-shape, and the heat load distribution within the cross section of the heat transfer tube along the air flow direction is extremely large on the air inflow side. There is a significant imbalance in that the downstream side is large and the downstream side is small.

For this reason, in the air inflow side cross section where the heat load is large, there is a shortage of liquid refrigerant and most of the heat transfer tube becomes a gas refrigerant region with poor heat transfer coefficient. Since the amount of liquid refrigerant is small, the refrigerant cannot evaporate, and a portion of the liquid refrigerant flows into the outlet tank portion without effectively exchanging heat, resulting in a problem that the heat exchange efficiency decreases.

On the other hand, by forming the refrigerant passage in a W-shape, the refrigerant passage is divided into four parts in the air flow direction, and the cooling part on the front side and the cooling part on the rear side in the air flow direction are formed by this refrigerant passage. A method of providing a notch between the two parts is disclosed in Japanese Utility Model Application No. 63-109876. According to this method, since the refrigerant passage is divided into four in the air flow direction, the unbalanced amount of the heat load is reduced. Furthermore, since the condensed water generated when the air is cooled is drained from the notch provided in the center of the flow path, drainage performance is also improved. However, in the conventional heat exchanger having the above configuration, the U-turn portion located between the inlet tank portion and the outlet tank portion provided at both ends of the W-shaped refrigerant passage is formed in the shape of a tank. and adjacent passages communicate with each other via this central tank portion. Therefore, the refrigerant passage formed in one set of flat tubes is substantially divided by the central tank portion, and the liquid refrigerant flowing from the upstream side is decelerated in the tank portion and stagnates there.

Gas refrigerant bubbles are mixed into the liquid refrigerant that remains in the tank, and as these gas refrigerant bubbles cause intermittent bubbling, the flow of the liquid refrigerant becomes intermittent and unstable, reducing the cooling capacity. There was a problem in that the outlet air temperature fluctuated uncomfortably and the heat exchange efficiency decreased.

Further, according to the configuration of the conventional heat exchanger, the W-shaped refrigerant passage is substantially divided into two U-shaped flow passages at the front stage and the rear stage by the central tank part. The refrigerant passage resistance is also halved by approximately 1/2.

For this reason, when the refrigerant is distributed from the inlet tank section into each heat transfer tube, the proportion of passage resistance in the tank section increases, causing problems in the refrigerant distribution. In other words, in heat exchanger tubes in which a small amount of refrigerant flows, most of the tube is occupied by the gas refrigerant region with poor heat transfer coefficient, resulting in a decrease in heat exchange efficiency, and in heat exchanger tubes in which a large amount of refrigerant flows, heat cannot be exchanged sufficiently with the air. There was a problem in that the liquid refrigerant that was not fully evaporated would flow out, causing uneven discharge temperature.

An object of the present invention is to provide a laminated heat exchanger that improves the unbalance of heat load in a cross section of a refrigerant passage, distributes refrigerant evenly to each flat tube, and reduces fluctuations and unevenness in discharge temperature. With the goal.

Another object of the present invention is to provide a laminated heat exchanger having a structure capable of improving heat exchange efficiency.

[Means to solve the problem]

In order to achieve the above object, the laminated heat exchanger of the present invention has two transmission sheets, each of which has a refrigerant passage formed by a recessed part, and which is formed so that the refrigerant passage meanderes at least twice in the flow direction. When the hot plates are combined, a large number of flat heat exchanger tubes having an inlet tank section at one end and an outlet tank section at the other end are stacked so that the tank sections of adjacent flat tubes are in communication with each other. In the laminated heat exchanger, the passage width in the direction perpendicular to the heat exchanger tube plate in the flat heat exchanger tubes is formed to be approximately equal from the inlet tank part to the outlet tank part. .

In addition, inlet tank section to achieve the above purpose.

The outlet tank portion is formed up to the center line side of the heat exchanger tube plate.

[Effect]

The refrigerant that has flowed into the inlet tank flows evenly into the flat heat transfer tubes, which have a meandering refrigerant passage with a constant passage thickness from the inlet to the outlet that communicates with the tank, and winds as it meanderes through each flat tube. Since the refrigerant flows stably upward, the unbalance of heat load within the cross section of the heat transfer tube is improved, and heat exchange between the air and the refrigerant is performed efficiently. Since the refrigerant passage width is gradually increased from the refrigerant inlet to the outlet in accordance with the increase in the specific volume of the refrigerant, the pressure loss in the refrigerant passage is kept low and the heat exchange efficiency is improved.

〔Example〕

An embodiment of the present invention will be described below with reference to FIGS. 1 to 4.

The overall structure of the laminated heat exchanger according to the present invention is shown in FIGS. 3 and 4. FIG. 3 is a front view, and FIG. 4 is a top view of FIG. The heat exchanger according to the present invention includes a flat tube 1 having a muro tank portion 2. An inlet header 2a and an outlet header 3a are formed by stacking the outlet tank parts 3 so as to communicate with each other through communication holes A and B, respectively, and a plurality of meandering refrigerant passages are provided which communicate with these headers. A corrugated fin 4 is inserted and fixed in the space formed between adjacent flat tubes.

An inlet pipe 5 communicating with the ladder 2a is connected to the downstream side of the cooled air (a), and an outlet pipe 6 communicating with the ladder 3a is connected to the upstream side.

The flat tube 1 is composed of a pair of heat exchanger tube plates 1a and lb. As shown in FIG. 1, the heat exchanger tube plate 1a has protruding ribs a and b aligned in a predetermined direction, leaving a joining rib portion 7 for forming a sealed flow path around the entire circumference of the flat material plate.
It has a structure in which a zigzag meandering recess 8, which is to serve as a refrigerant passage, is extruded, and the inlet tank part 2 and outlet tank part 3 are further extruded and molded deeper than this. Furthermore, a plurality of intermediate partition walls 9 are provided which are alternately connected to the joining rib portions 7 and form meandering refrigerant passages 8 . Muro tank part 2. Communication holes A and B are punched out in the outlet tank part 3.

The opposite end of the heat exchanger tube plate 1a to the tank is provided with a folded portion 10 for maintaining the spacing between the flat heat exchanger tubes 1 during assembly.

The heat exchanger tube plate 1b has the same structure as the heat exchanger tube plate 1a, and is symmetrically formed so that the protruding ribs a and b intersect in an X-shape when the two plates are assembled.

Side plates 11 and 12 are provided on both end surfaces of the heat exchanger.
is attached to the side plate 12, and an inlet header 2a is attached to the side plate 12.
A communication hole communicating with the outlet header 3a is punched out, and the inlet pipe 5. is in contact with this communication hole. The outlet pipe 6 is joined by brazing. The opposite end of the header to the pipe is sealed by a side plate 11.

In the above configuration, the cold soot flowing in from the inlet pipe 2 flows in the longitudinal direction of the ladder 2a toward the end of the flow path to the inlet located on the downstream side of the air, and then flows through the flattened soot connected to the inlet and the ladder 2a. The refrigerant flows into the meandering refrigerant passage 8 in the tube 1 in a substantially evenly distributed manner. The refrigerant that has flowed into the meandering refrigerant passage meanders up and down, forms a perpendicular counterflow to the air, flows toward the upstream side of the air, and reaches the outlet header where it merges, as shown by the arrow in Figure 2. and flows out from the outlet pipe 6. In contrast to the conventional U-turn type passage, in this embodiment, the refrigerant flows in a meandering manner multiple times, so the width of the refrigerant passage in the air flow direction is approximately 1/2.
2 or less, the imbalance of heat load within the cross section of the refrigerant passage is improved, and the heat exchange efficiency is improved. Furthermore, the conventional heat exchanger is provided with an intermediate tank section that communicates the adjacent refrigerant passages at an intermediate position between the inlet header and the outlet header. This made the flow unstable and caused the temperature of the air discharged from the heat exchanger to fluctuate uncomfortably.

Generally, the amount of refrigerant distributed to the plurality of heat transfer tubes connected between the inlet header and the outlet header is basically determined based on the passage resistance when the refrigerant flows in the longitudinal direction while branching (merging) inside the header. It is well known that the greater the passage resistance when flowing through a heat pipe, the more evenly the heat tends to be distributed.

However, since the conventional heat exchanger includes the intermediate tank section, the intermediate tank section functions as an outlet header and an inlet header for the upstream refrigerant passage and the downstream passage, respectively. The length of the refrigerant passage between the inlet header and the outlet header is approximately halved, and the resistance of the refrigerant passage between the two headers is also halved, resulting in poor refrigerant distribution (resulting in a decrease in heat exchange efficiency).

In contrast, in the heat exchanger according to the present invention, the passage thickness in the direction perpendicular to the heat exchanger tube plate 1a is formed between the inlet header and the outlet header to be approximately constant, and the heat exchanger tubes with continuous refrigerant passages are connected. This allows an equal amount of refrigerant to stably flow into each heat transfer tube.

A second embodiment of the present invention will be described with reference to FIG.

Similar to FIG. 1, FIG. 5 shows details of the heat exchanger tube plate 1a of the stacked exchanger shown in FIG. In the first embodiment, the outer peripheral end 7b of the U-shaped top of the meandering refrigerant passage adjacent to the tank portion is formed close to the outermost peripheral joining rib portion 7 of the heat exchanger tube plate, and the input tank width h1. The output tank width h2 is the width W1 of the first refrigerant passage 8a and the fourth refrigerant passage 8d, respectively.
The width W4 was set to be approximately equal to the width W4. On the other hand, the second
In the embodiment, the position of the outer circumferential end 7d of the U-shaped top is closer to the center of the heat exchanger tube plate with respect to the tank parts 2 and 3,
In addition, the input tank width h1. The outlet tank width h2 is compared with the width W1 of the first refrigerant passage 8a and the width W4 of the fourth refrigerant passage 8d, respectively, so that h l>W L .

The difference from the first embodiment is that hz>W4 is set. In the second embodiment, the ladder 2a to the entrance,
Since the passage cross-sectional area of the outlet header 3a can be set larger than the refrigerant passage width, there is an effect that the passage resistance of the refrigerant flowing inside the header is reduced and the refrigerant distribution is further improved. Other operations are the same as in the first embodiment.

Next, a third embodiment of the present invention will be described with reference to FIGS. 6 to 10. In this embodiment, inner fins 102 are disposed within the flat heat exchanger tube 1 to increase the heat exchange efficiency by increasing the heat transfer area within the tube and to improve the pressure resistance. The configuration of the third embodiment will be explained below.

The heat exchanger according to this embodiment has an input tank section 2 of a flat tube 1.
．． The inlet header 2a is formed by stacking the outlet tank parts 3 so as to communicate with each other through the communication holes A and B, respectively.

A ladder 3a is formed to the outlet and a plurality of meandering refrigerant passages communicating with these headers are provided. Inner fins 102 are arranged within the refrigerant passage of the flat tube 1 . Other configurations are the same as in the first embodiment.

The flat tube 1 has a structure in which an inner fin 102 is sandwiched between a pair of heat exchanger tube plates 101 a and 101 b. Since the heat exchanger tube plates 101a and 101b have a symmetrical structure, only the heat exchanger tube plate 101a will be explained below. As shown in FIG. 6, the heat exchanger tube plate 101a has a joint rib portion 7 for forming a sealed flow path left over the entire circumference of the material flat plate, and a zigzag meandering recess portion 8 for forming a refrigerant passage. Extrusion molding and deeper inlet tank part 2. It has a structure in which the output tank part 3 is extruded and molded. Further, a plurality of intermediate partition walls 9 are provided which are alternately connected to the outer circumferential joint rib portion 7 and form a meandering refrigerant passage 8 .

As shown in FIGS. 7 and 8, the inner fin 102 has a houndstooth check structure in which a large number of fin elements 103, which are formed by bending a thin plate into a corrugated shape, are arranged in the flow direction with their positions shifted by half a pitch. Partition wall 9 when placed in a flat tube
The inner fins 102 are provided with slits 104 alternately cut in the longitudinal direction so as not to hit the inner fins.

9 and 10 show how the inner fins 102 are arranged within the flow path section 8 of the heat exchanger tube plate 101a. It escapes from the channel partition wall 9 through the slit 104. Furthermore, there is a gap S between the end surfaces 102a, 102b of the inner fin 102 and the outer circumferential ends 7a, 7b, 7c of the refrigerant passage bend portions.
is provided.

The operation of the heat exchanger of the third embodiment having the above configuration will be explained below. The refrigerant flowing from the inlet header 2a flows into the refrigerant passage 8 through the communication hole A formed in the inlet tank 2, flows in a meandering manner in the refrigerant passage while contacting the inner fins 102 in a complicated manner, and then flows into the outlet tank. It flows out from the communication hole B opened in 3, reaches the outlet tank 3a, joins together, and flows out of the heat exchanger. The heat transfer characteristics within the tube are greatly improved due to the effect of expanding the heat transfer area within the tube and the effect of promoting turbulence due to the inner fins. Therefore, the tube wall temperature of the heat exchanger tube plate 101a decreases to approach the refrigerant evaporation temperature, so the discharge temperature of the air to be cooled also decreases, and the amount of exchanged heat increases. Further, at the bend portion of the refrigerant passage, there are refrigerant passage walls 7a to 7c and fin end surfaces 102.
Since the gap S is provided between a to 102c, the refrigerant can smoothly make a U-turn without causing problems such as an increase in pressure loss at the vent portion.

A fourth embodiment of the present invention will be explained with reference to FIG.

Similar to FIG. 1, FIG. 11 shows in detail the heat exchanger tube plate 201a that constitutes the flat tube 1 of the laminated heat exchanger shown in FIG. Said 1st. In the second implementation, the protruding ribs a and b in the refrigerant passage have the same inclination angle with respect to the refrigerant flow direction,
However, in this embodiment, the inclination angle of the protruding ribs with respect to the refrigerant flow direction is small in the refrigerant passage on the air upstream side (refrigerant inlet side), and in the downstream passage (
refrigerant discharge side). 1st
~Protruding ribs a, a, b, b provided in the fourth refrigerant passage
' angles θ1°θ2. θ3. If it is number θ, then θ
1>θ2>θ3>0, and the angle becomes smaller toward the windward side.

Next, the operation of the heat exchanger with the above configuration will be explained.

The refrigerant flowing in through the communication hole A provided in the inlet tank portion 2 flows in the meandering refrigerant passage toward the air upstream side as shown in FIG. During this time, the liquid refrigerant exchanges heat with the air and cools the air, and the liquid refrigerant evaporates in proportion to the amount of heat taken from the air. Therefore, as the air advances toward the upstream side, the proportion of the gas refrigerant increases, the specific volume increases, and the flow rate of the refrigerant also increases. In this embodiment, in accordance with this increasing tendency of the refrigerant flow velocity, the angles 01 to θ of the protruding ribs in the passage are set so that the refrigerant passage on the air upstream side where the refrigerant flow velocity is high is smaller. therefore.

In a passage with a high refrigerant flow rate, the shape resistance of the groove ribs is reduced, and an increase in pressure loss due to an increase in the flow rate can be prevented.

FIG. 12 is a plan view of a heat exchanger tube plate 301a showing a fifth embodiment of the present invention. The width of the refrigerant passage in the first to fourth embodiments is approximately constant, but in the case of this example, the width increases from the refrigerant inlet side passage (air outlet side) to the refrigerant outlet side passage (air inlet side). , the refrigerant passage width W1 to W4 is W4>W
The flow path partition portion 9 is provided so as to gradually increase in size according to the relationship 3>W2>Wl. It is important to note that in this embodiment, it is important to gradually change the channel width, and the gist of the invention does not change even if protruding ribs or inner fins are provided in the refrigerant channel, so these are shown in FIG. is not shown. The operation of this embodiment will be explained below.

As described above, the liquid refrigerant evaporates due to heat exchange with the air, and the specific volume of the gas refrigerant in the refrigerant passage increases as it advances toward the upstream side of the air. In accordance with this increase in specific volume, in this embodiment, the width W1 of the refrigerant passage partitioned by the heat exchanger tube plate 201a is
Since the cross-sectional area of the refrigerant passage is increased by gradually increasing ~W4, an increase in the refrigerant flow rate can be suppressed, and a decrease in heat exchange efficiency due to an increase in pressure loss can be prevented.

FIG. 13 shows the refrigerant passage pressure loss when the ratio W4/W1 of the width W1 of the first refrigerant passage and the width W4 of the fourth refrigerant passage is changed. The vertical axis of the figure is the refrigerant passage pressure loss ΔP W4/W
This is the pressure loss ratio ΔP/ΔPS obtained by dividing by the pressure loss ΔPs when t=1.0. A test heat exchanger manufactured by AQ in which inner fins 102 were arranged in the refrigerant passage was used. The inner fin has a plate thickness of 0.2 mm and a fin height h
= 2.0I, fin pitch P = 1.6m+. In the case of a typical refrigeration cycle for a car air conditioner (not shown), refrigeration oil is circulated together with a refrigerant to lubricate the movable parts of the cycle components. In order to meet this condition, in the experiment, the circulation rate of the refrigerating machine oil contained in the refrigerant was changed from 0 to 6W.
Changed to t%. In the experiment, the pressure loss in the refrigerant passage was measured with the evaporation temperature constant at 0° C. in the case of pure refrigerant and in the case of oil mixed in the refrigerant (oil circulation rate of 1 to 6 wt%).

From FIG. 13, the pressure loss ratio ΔP/ΔPS gradually decreases until the passage width ratio W4/Wt=1.5, and increases beyond that point. That is, it is shown that there is an appropriate value of the passage width ratio W 4 /W 1 for reducing pressure loss. From this experimental result, W4/W1=
The pressure loss is lower than when it is 1.0 (ΔP/ΔP
The range of the appropriate passage width ratio W4/W1 (s<1.0) can be read as W4/W1=1.0 to 2.7. In addition, the refrigerant passage width ratio W
The main reason why the pressure loss increases as 4/W1 increases is that the width Wl of the first refrigerant passage becomes too small, and the refrigerant flow rate there becomes excessive, resulting in an increase in pressure loss. Furthermore, it goes without saying that the same effects can be obtained by the present invention, regardless of the type of refrigerant or oil, as long as the refrigerant and refrigerating machine oil are combined with good compatibility.

The overall structure of heat exchange in the heat exchangers of the first to fifth embodiments is shown in FIG. 14, and the refrigerant flowing into the inlet header 2a through the inlet pipe 5 is connected to this. The refrigerant flows approximately evenly into the plurality of refrigerant passages 8 , meandering up and down in the refrigerant passages 8 a to 8 b in a manner similar to that of the air flow (A), and flows toward the outlet again at the ladder 3 a to join the outlet pipe 6 .
This allows the refrigerant to flow more easily. That is, the refrigerant flowing in all the stacked flat tubes uniformly forms a flow perpendicular to the air flow, but the effect of the present invention is to divide the flat tubes into a plurality of tube groups and at least This can be achieved by configuring the refrigerant flowing in the most downstream group of tubes connected to the pipes to flow perpendicularly to the air flow.

FIG. 15 shows a flat tube 1 whose communication hole A of an inlet tank 2 is blocked by an inter-header partition member 22, and which is divided into two tube groups by arranging one flat tube 1 in the center of the heat exchanger. An example is shown below.

The tank parts 2 and 3 of the flat tube 1 are stacked to form the windward header 202.
．． A leeward header 203 is formed, and the windward header 202 is divided into an inlet header 202a and an outlet header 202b by an inter-header dividing member 22.

An inlet pipe 20 is connected to the inlet header 202a, and an outlet pipe 21 is connected to the outlet ladder 202b through communication holes 23. The refrigerant flowing from the inlet pipe 20 meanders through the first flat tube group 204 connected to the ladder 202a to the inlet, reaches the leeward header 203, and then flows into the second flat tube group connected via the leeward header. Flows into group 205. The refrigerant that has almost evenly flowed into the plurality of flat tubes constituting the second flat tube group flows in the refrigerant passages 8a to 8a.
While meandering up and down within 8d, the air flows opposite to the air flow (a), joins again at the outlet header 202b, passes through the communication hole 23, and flows out from the outlet pipe 21.

〔Effect of the invention〕

According to the present invention, the refrigerant flowing inside the flat tube stably flows in orthogonal countercurrents while meandering up and down multiple times in the direction of air inflow without causing liquid accumulation in the middle of the flow path. Since the imbalance in the heat load distribution within the cross section can be reduced and made uniform, it has the effect of improving heat exchange efficiency.

Furthermore, by changing the width of the refrigerant passage, the cross-sectional area of the passage is gradually increased in the direction of refrigerant discharge, thereby keeping the refrigerant flow rate low and reducing pressure loss, which has the effect of improving heat exchange efficiency.

Furthermore, by arranging the inner fins within the refrigerant passage, the heat transfer area within the tubes can be expanded, which has the effect of improving heat conductivity within the tubes and improving heat exchange efficiency.

[Brief explanation of the drawing]

FIG. 1 is a plan view of a heat exchanger tube plate according to an embodiment of the present invention. Fig. 2 is a schematic diagram showing a refrigerant flow path, Fig. 3 is a front view of a heat exchanger according to an embodiment of the present invention, and Fig. 4 is a plan view of a heat exchanger tube plate showing a third and fifth embodiment. , FIG. 13 Example
Schematic % formula showing the flow of refrigerant %... Heat exchanger tube plate, 2, 3... Inlet, outlet tank section, 2
a. 2b...Inlet, outlet header, 4...Air side fin,
7... Joining rib portion, 7a to 7c... Coolant flow path outer peripheral end portion, 8... Channel recessed portion, 8a to 8d... First to fourth coolant flow paths, 9... Flow road partition part, 11... side plate, 102... inner fin; It is a figure which shows the 3rd Example by this invention, and is a top view of a heat exchanger tube plate, and a top view of an inner fin, respectively. Perspective view of the main parts of the inner fin, heat exchanger tube plate and inner half) Figure 2nd section Ba, ~3ct, - Pillow is an explanatory i supply bowl ~8be 1st grade 1~wa Kobaku Rengo Kyou 3 National Sheep Figure Ha Figure 7, Figure 9, 0 Figure 11, Sister) 7' plate θI~ θ4--N, the deceased's mother, JK Hosuke L, and the middle Oraripui, 41 Kakuzuki Shitaku. 3 Kuni Karumi Wln W41 A1 ~ Sakaki is on the floor with the rod

Claims (1)

[Claims] 1. When two heat exchanger tube plates are combined, each of which has a refrigerant passage formed by a recessed part and is formed so that the refrigerant passage meanderes at least twice in the flow direction of the refrigerant, one In a laminated heat exchanger in which a large number of flat heat exchanger tubes having an inlet tank part at one end and an outlet tank part at the other end are stacked so that adjacent outlet tank parts and inlet tank parts communicate with each other, A laminated heat exchanger, characterized in that the passage width in the direction perpendicular to the heat exchanger tube plate in the flat heat exchanger tube is approximately equal from the inlet tank part to the outlet tank part. 2. The laminated heat exchanger according to claim 1, wherein the inlet tank portion and the outlet tank portion are formed up to the center line side of the heat exchanger tube plate. 3. Claim 1 or 2, wherein a protruding rib is provided in the refrigerant passage.
The laminated heat exchanger described in . 4. The laminated heat exchanger according to claim 1 or 2, wherein an inner fin member is provided in the refrigerant passage. 5. The laminated heat exchanger according to claim 4, wherein the inner fin member is provided with a slit portion for escaping the partition portion of the refrigerant flow path when placed in the refrigerant path. 6. The laminated heat exchanger according to claim 3, wherein the inclination angle of the protruding ribs with respect to the refrigerant flow direction is set gradually smaller in the refrigerant discharge direction. 7. The laminated heat exchanger according to claim 1, wherein the width of the refrigerant passage excluding meandering of the refrigerant passage is such that the width becomes wider as the refrigerant passage is located on the refrigerant discharge side. 8. Introducing the refrigerant from the refrigerant passage located on the downstream side of the air,
Assuming that the air downstream passage width is W_1 and the most upstream passage width is W_4, the passage width ratio W_4/W_1 is W_4/W_1=1.
The laminated heat exchanger according to claim 7, wherein the heat exchanger is set in a range of 0 to 2.7. 9. A partition plate is provided in the header formed by connecting the inlet tank and the outlet tank portion, and the refrigerant flows through the tube group to which at least the outlet pipe is connected, out of the plurality of tube groups partitioned by providing a partition plate. The laminated heat exchanger according to claim 7 or 8, configured to provide orthogonal counterflow.