WO2010106717A1

WO2010106717A1 - Plate-type heat exchanger and refrigerating air-conditioning device

Info

Publication number: WO2010106717A1
Application number: PCT/JP2009/071230
Authority: WO
Inventors: 伊東　大輔; 悟梁池; 毅浩林
Original assignee: 三菱電機株式会社
Priority date: 2009-03-18
Filing date: 2009-12-21
Publication date: 2010-09-23
Also published as: EP2410278A1; JP2010216754A; CN102356295A; CN102356295B; EP2410278B1; US20120012291A1; JP5106453B2; EP2410278A4

Abstract

A plate-type heat exchanger having increased strength obtained with the heat exchange performance of the plate-type heat exchanger maintained. A plate-type heat exchanger (20) is formed by layering plates (2, 3) on top of one another. Each of the plates (2, 3) has formed in the four corners thereof a first inlet hole (5) serving as the inlet for a first fluid, a first outlet hole (6) serving as the outlet for the first fluid, a second inlet hole (7) serving as the inlet for a second fluid, and a second outlet hole (8) serving as the outlet for the second fluid. Each of the plates (2, 3) has formed between the plate (2, 3) and the plate layered thereon a first flow path for causing the first fluid to flow therethrough and a second flow path for causing the second fluid to flow therethrough, and the first fluid and the second fluid are caused to exchange heat between each other. In each of the plates (2, 3), the length (L1) in the longitudinal direction thereof is four or more times the length (L2) in the lateral direction thereof.

Description

Plate type heat exchanger and refrigeration air conditioner

The present invention relates to, for example, a plate type heat exchanger in which a plurality of plates are stacked, and a refrigeration air conditioning system provided with a plate type heat exchanger.

Patent Document 1 describes a plate-type heat exchanger in which the shape of the inflow hole and the shape of the outflow hole of the fluid are elliptical. Patent Document 1 also describes a plate type heat exchanger in which the diameter of the inflow hole of the fluid and the diameter of the outflow hole are the same.
Patent Document 2 describes a plate-type heat exchanger in which the diameter of the fluid inflow hole and the diameter of the fluid outflow hole are different. Further, Patent Document 2 describes a plate type heat exchanger in which a reinforcing member is provided in the inflow hole of the fluid and the outflow hole of the fluid to increase the strength.

JP-A-9-72685 JP-A-7-508 851

The conventional plate type heat exchanger has the following problems (1) to (3).
(1) The plate type heat exchanger generally has low strength because the plate thickness is thin.
(2) In the plate type heat exchanger in which the reinforcing members are provided in the inflow hole and the outflow hole, the dust is easily clogged in the inflow hole and the outflow hole.
(3) When the flow rate of the fluid is high, the plate type heat exchanger is limited in the flow velocity at the fluid inlet and outlet. Therefore, in order to process a large amount of fluid, it is necessary to widen the opening area of the inflow holes and the outflow holes. However, in order to increase the opening area of the inflow holes and the outflow holes, the width of the inflow holes and the outflow holes must be increased. If the width between the inflow holes and the outflow holes is increased, the strength decreases and the heat transfer area decreases. That is, the plate type heat exchanger having a wide opening area between the inflow hole and the outflow hole has low strength and poor heat exchange performance.

An object of the present invention is, for example, to increase the strength of a plate type heat exchanger while maintaining the heat exchange performance of the plate type heat exchanger.

The plate type heat exchanger according to the present invention is, for example,
A plate heat exchanger formed by laminating a plurality of plates,
Each plate of the plurality of plates
A first inflow hole, which is an inlet for the first fluid, at either end in the longitudinal direction;
A first outflow hole serving as an outlet of the first fluid, at a longitudinal end opposite to the first inflow hole;
A second inflow port, which is an inlet for the second fluid, at either end in the longitudinal direction;
A second outflow port serving as an outlet of the second fluid is provided on the end side in the longitudinal direction opposite to the second inflow port,
Each of the plates is a first flow path for spreading the first fluid, which has flowed in from the first inflow hole, in the lateral direction between the plates stacked next to each other, and the first flow path to flow to the first outflow hole; (2) One flow path is formed with the second flow path which spreads the second fluid flowing in from the inflow hole in the short direction and flows to the second outflow hole, and the first flow which flows in the first flow path Heat exchange between the fluid and the second fluid flowing in the second flow path,
Each plate is characterized in that the length in the longitudinal direction is four or more times the length in the lateral direction.

In the plate type heat exchanger according to the present invention, the length in the longitudinal direction is four times or more the length in the transverse direction. Therefore, the stress applied to the end of the plate can be suppressed. Therefore, the plate type heat exchanger according to the present invention has high strength.

FIG. 2 is a side view of a plate heat exchanger 20. The front view of the side plate 1 for reinforcement. The front view of the 2nd plate 2. FIG. FIG. 5 is a front view of a first plate 3; The front view of the side plate 4 for reinforcement. FIG. 5 is an exploded perspective view of a plate type heat exchanger 20. The figure which shows the size of the

plates

2 and 3 of plate type heat exchanger 20. FIG. The figure which shows the relationship of the ratio of the ratio of the length of the longitudinal direction of the

plates

2 and 3 to the transversal direction, and stress. The figure which shows the relationship of the ratio of the length of the longitudinal direction of the

plates

2 and 3 to the transversal direction, and the weight of the plate type heat exchanger 20. FIG. The figure which shows the

plates

2 and 3 which made the diameter of the primary side inflow-and-outflow hole smaller than the diameter of the secondary side inflow-and-outflow hole. The figure which shows the plate type heat exchanger 20 which made the diameter of the 1st inflow hole 5 small about the

plates

2 and 3 by the side plate 1 side for reinforcement. The figure which shows the size of the

plates

2 and 3 which drew inflow and outflow holes to four corners. Explanatory drawing of the flow of the 1st fluid of the 1st plate 3 which approached the inflow / outflow hole to four corners. Explanatory drawing of the unevenness | corrugation 9 of the 1st plate 3 which approached the inflow / outflow hole to the four corners. The figure which shows the unevenness | corrugation 9 of the 2nd plate 2 which approached the inflow / outflow hole to the four corners. The figure which shows the unevenness | corrugation 9 of the 1st plate 3 which approached the inflow / outflow hole to the four corners. The figure which shows the

plates

2 and 3 which made the 1st inlet-outlet hole and the secondary side inlet-outlet hole different shape. The figure which shows the

plates

2 and 3 which made the 1st inlet-outlet hole and the secondary side inlet-outlet hole different shape. The contrast figure of the case where primary side inflow / outlet hole and secondary side inflow / outlet hole are made the same shape, and the case where primary side inflow / outlet hole and secondary side inflow / outlet hole are made into a different shape. The figure which shows the

plates

2 and 3 which made the primary side inflow-outlet hole and the secondary side inflow-outlet hole the same shape, and were shapes other than a circle. The figure which shows the

plates

2 and 3 which made the primary side inflow-outlet hole and the secondary side inflow-outlet hole the same shape, and were shapes other than a circle. The figure which shows the heating hot-water supply system 29. FIG.

Embodiment 1
1 to 6 are explanatory views of a plate type heat exchanger 20 according to the first embodiment. FIG. 1 is a side view of the plate heat exchanger 20. As shown in FIG. FIG. 2 is a front view of the reinforcing side plate 1. FIG. 3 is a front view of the second plate 2. FIG. 4 is a front view of the first plate 3. FIG. 5 is a front view of the reinforcing side plate 4. FIG. 6 is an exploded perspective view of the plate heat exchanger 20. As shown in FIG.

As shown in FIG. 1, in the plate type heat exchanger 20, a plurality of

plates

2 and 3 are stacked. Further, in the plate type heat exchanger 20, reinforcing

side plates

1 and 4 are laminated on the foremost surface (A side in FIG. 1) and the outermost surface (B side in FIG. 1).
As shown to FIG.3, 4, each

plate

2 and 3 is formed in a substantially rectangular plate shape. Each of the

plates

2 and 3 is provided with a first inflow hole 5 on one end side (upper side) of a substantially rectangular long side direction (longitudinal direction). Each of the

plates

2 and 3 is provided with a first outflow hole 6 at the end (lower side) in the longitudinal direction opposite to the first inflow hole 5. Each of the

plates

2 and 3 is provided with a second inflow hole 7 at the end (lower side) in the same longitudinal direction as the first outflow hole 6. Each of the

plates

2 and 3 is provided with a second outflow hole 8 at the same longitudinal end (upper side) as the first inflow hole 5. Here, the first inflow hole 5 and the first outflow hole 6 are provided on the same end side (left side) of the substantially rectangular short side direction (short side direction) of the

plates

2 and 3. In each of the

plates

2 and 3, the second inflow hole 7 and the second outflow hole 8 are provided on the end side (right side) of the first inflow hole 5 and the first outflow hole 6 in the opposite lateral direction. .
That is, in each of the

plates

2 and 3, the first inflow holes 5, the first outflow holes 6, the second inflow holes 7, and the second outflow holes 8 are provided at four corners. The first inflow hole 5 and the first outflow hole 6 are referred to as the primary side inflow and outflow holes. Similarly, the second inflow holes 7 and the second outflow holes 8 are called secondary side inflow and outflow holes.

As shown in FIGS. 2 and 5, the reinforcing

side plates

1 and 4 are also formed in a substantially rectangular plate shape, similarly to the

plates

2 and 3. As shown in FIG. 2, the reinforcing side plate 1 stacked on the foremost surface has the first inflow hole 5 (first inflow pipe), the first outflow hole 6 (first outflow hole 6) at the same position as the

plates

2 and 3. Pipe), a second inflow hole 7 (second inflow pipe), and a second outflow hole 8 (second outflow pipe).
On the other hand, as shown in FIG. 5, the reinforcing side plate 4 stacked on the back surface is not provided with the first inflow hole 5, the first outflow hole 6, the second inflow hole 7, and the second outflow hole 8. In FIG. 5, the positions of the first inflow hole 5, the first outflow hole 6, the second inflow hole 7, and the second outflow hole 8 are shown by broken lines in the reinforcing side plate 4. These are not necessarily provided.

The

plates

2 and 3 and the reinforcing side plate 1 are stacked such that the first inflow holes 5, the first outflow holes 6, the second inflow holes 7 and the second outflow holes 8 overlap with each other. Further, the second plate 2 and the first plate 3 are alternately stacked.
The

plates

2 and 3 and the reinforcing

side plates

1 and 4 have substantially the same substantially rectangular shape.

Further, as shown in FIGS. 3 and 4, a plurality of V-shaped concave portions and convex portions (concave and convex portions 9) are arranged in the longitudinal direction on the

plates

2 and 3. The unevenness 9 is formed in a V shape having both end portions 13 on both end sides in the short direction and having turning points 12 at positions deviated from the both end portions 13 in the longitudinal direction. The pitch (width) of the unevenness 9 is W shown in FIG. In the second plate 2 and the first plate 3, the directions of the asperities 9 are arranged in the opposite direction. That is, in the second plate 2, the unevenness 9 is formed in a V shape having a turning point 12 below the both end portions 13, whereas in the first plate 3, the turning point upwards than the both end portions 13 The unevenness 9 is formed in a V shape (inverted V shape) having twelve.
As described above, by alternately laminating the

plates

2 and 3 in which the concavities and convexities 9 are formed in the reverse V-shape, a flow passage with good heat transfer efficiency is formed between the

plates

2 and 3. That is, as shown in FIG. 6, the first flow path through which the first fluid flowing from the first inflow hole 5 flows to the first outflow hole 6 is between the back surface of the second plate 2 and the front surface of the first plate 3 It is formed. Similarly, a second flow path through which the second fluid flowing from the second inflow hole 7 flows to the second outflow hole 8 is formed between the back surface of the first plate 3 and the front surface of the second plate 2.
The first fluid flowing in the first flow path and the second fluid flowing in the second flow path are heat exchanged via the

plates

2 and 3.

FIG. 7 is a view showing the sizes of the

plates

2 and 3 of the plate type heat exchanger 20. As shown in FIG. In FIG. 7, the length L1 indicates the length in the longitudinal direction of the

plates

2 and 3. The length L2 indicates the length of the

plates

2 and 3 in the lateral direction. The length L3 indicates the length from the first inflow hole 5 to the end of the short plate in the direction closer to the first inflow hole 5. The length L4 indicates the length from the first outlet hole 6 to the end of the short plate in the direction closer to the first outlet hole 6. The length L5 indicates the length from the second inflow hole 7 to the end of the short plate in the direction closer to the second inflow hole 7. The length L6 indicates the length from the second outlet hole 8 to the end of the short plate in the direction closer to the second outlet hole 8.

FIG. 8 is a view showing the relationship between the ratio of the length of the longitudinal direction of the

plates

2 and 3 to the lateral direction and the stress. The horizontal axis in FIG. 8 indicates the ratio (length ratio) of the length in the longitudinal direction of the

plates

2 and 3 to the length in the lateral direction. That is, the horizontal axis in FIG. 8 indicates the length L1 in the longitudinal direction of the

plates

2 and 3 / the length L2 in the lateral direction of the

plates

2 and 3. The vertical axis in FIG. 8 indicates the stress applied to the ends (peripheral portions) of the

plates

2 and 3. In FIG. 8, stress is expressed as a stress ratio. The reference value of the stress ratio is the value indicated by the second point P from the right in FIG. Here, each point of FIG. 8 shows the calculated value of the stress ratio to the length ratio. The lines in FIG. 8 show the values calculated by the least squares method from each point.
As shown in FIG. 8, as the length L2 in the lateral direction of the

plates

2 and 3 is shorter than the length L1 in the longitudinal direction of the

plates

2 and 3, the stress on the peripheral portions of the

plates

2 and 3 decreases. Become. Therefore, it is desirable to make the length L2 as short as possible with respect to the length L1. In particular, it is desirable to shorten the length L2 so that the length L1 is four or more times the length L2. However, due to the manufacturing limit of the plate heat exchanger 20, the length L2 can not be shortened significantly. Therefore, it is desirable to shorten the length L2 so that the length L1 is about 4 to 6.5 times the length L2.
Further, by shortening the lengths L3, L4, L5 and L6, the stress applied to the ends of the

plates

2 and 3 is reduced. In particular, it is desirable to set the lengths L3, L4, L5, and L6 to 6% or less of the length L2 in the short direction of the

plates

2 and 3. Further, regardless of the length L2 in the short direction of the

plates

2 and 3, the lengths L3, L4, L5 and L6 may be set to 5.6 mm or less. However, due to the manufacturing limit of the plate type heat exchanger 20, the lengths L3, L4, L5 and L6 can not be shortened significantly. Therefore, it is desirable to set the lengths L3, L4, L5, and L6 to 3% or more and 6% or less of the length L2 of the

plates

2 and 3 in the short direction. Similarly, it is desirable to set the lengths L3, L4, L5, and L6 to 3 mm or more and 5.6 mm or less.

FIG. 9 is a view showing the relationship between the ratio of the lengths of the

plates

2 and 3 in the longitudinal direction and the transverse direction and the weight of the plate heat exchanger 20. As shown in FIG. In particular, in FIG. 9, when the lengths in the longitudinal direction of the

plates

2 and 3 are fixed and the lengths in the lateral direction of the

plates

2 and 3 are shortened, how much the weight of the plate heat exchanger 20 is reduced Indicate if you can.
The horizontal axis of FIG. 9 shows the ratio (length ratio) of the length in the longitudinal direction of the

plates

2 and 3 to the length in the transverse direction, as in FIG. The vertical axis | shaft of FIG. 9 shows the reduction rate of the weight of the plate type heat exchanger 20. As shown in FIG. The reduction rate of the weight of the plate type heat exchanger 20 is the plate type heat manufactured by the length ratio (the value indicated by the second point P from the right in FIG. 8) selected as the reference value of the stress ratio in FIG. It is a value calculated based on the weight of the exchanger 20.
By shortening the length L2, the plate type heat exchanger 20 can be miniaturized, and naturally the plate type heat exchanger 20 can be made lighter. However, if the length L2 is shortened, not only the reduction in weight due to the downsizing but also the reduction in thickness of the

plates

2 and 3 and the thickness of the reinforcing

side plates

1 and 4 can be further reduced. That is, when the length L2 is shortened, the strength of the plate heat exchanger 20 is increased. Therefore, the thickness of the

plates

2 and 3 and the thickness of the reinforcing

side plates

1 and 4 can be reduced, and the weight of the plate heat exchanger 20 can be reduced.
As a result, as shown in FIG. 9, by shortening the length L2 with respect to the length L1, the plate type heat exchanger 20 is reduced in weight more than the reduction in weight due to the miniaturization.

As described above, the plate type heat exchanger 20 according to the first embodiment has the length L2 in the short direction of the

plates

2 and 3 shorter than the length L1 in the longitudinal direction of the

plates

2 and 3, The strength of the plate heat exchanger 20 is high.
Moreover, in the plate type heat exchanger 20 according to the first embodiment, the lengths (lengths L3, L4, L5, L6) between the inflow holes 5, 6, 7 and 8 and the plate end portions are shortened. , The strength of the plate heat exchanger 20 is high.
Furthermore, since the strength of the plate heat exchanger 20 is increased, the weight of the plate heat exchanger 20 can be reduced.

Further, by shortening the length L2 in the short direction, the fluid flowing from the first inflow hole 5 and the second inflow hole 7 is likely to spread in the short direction. Therefore, it is not necessary to provide a distribution promoting member for promoting the spread of the fluid around the first inflow hole 5 and the second inflow hole 7. Further, since the strength of the plate type heat exchanger 20 is high, it is not necessary to provide a reinforcing member around the inflow holes (the first inflow holes 5 and the second inflow holes 7). Therefore, since it is not necessary to provide a distribution promoting member or a reinforcing member, pressing of the

plates

2 and 3 is simplified. Therefore, the manufacturing cost of the plate type heat exchanger 20 can be suppressed. Moreover, the variation in the height of the unevenness 9 is also suppressed. That is, the plate-type heat exchanger 20 of stable quality can be manufactured.

In addition, if stagnation occurs in the fluid inside the plate type heat exchanger, dust and scales are easily accumulated in the area where the stagnation has occurred.

Plates

2 and 3 are easily corroded in a portion where dust and scale are accumulated. In addition, if a heat exchanger that may cause stagnation in the fluid is used in the evaporator, uneven flow occurs to cause unevenness in the temperature distribution. Therefore, there is a possibility that a frozen portion may be formed. The formation of a frozen part reduces the strength of the heat exchanger. However, in the plate type heat exchanger 20 according to the first embodiment, since the length in the short direction of the

plates

2 and 3 is short, it is difficult for stagnation in the fluid. Therefore, dust and scale do not easily accumulate, and the strength does not decrease. In addition to the case where the fluid is water, the plate type according to the first embodiment is applicable not only to the case where the fluid is water but also to a fluid having a small density and a large pressure loss (eg, a hydrocarbon refrigerant or low GWP refrigerant). The heat exchanger 20 is effective. The fluorocarbon-based refrigerant is also effective in suppressing the retention of refrigeration oil in the heat exchanger. For this reason, the power consumption of the apparatus using the plate type heat exchanger 20 which concerns on Embodiment 1 can be reduced.

Second Embodiment
In the second embodiment, a plate-type heat exchanger 20 in which the diameter of the primary side inflow / outlet hole is smaller than the diameter of the secondary side inflow / outlet hole will be described. That is, in the second embodiment, the plate-type heat exchanger 20 in which the opening area of the primary side inflow / outlet hole is smaller than the opening area of the secondary side inflow / outlet hole will be described.

FIG. 10 is a diagram showing the

plates

2 and 3 in which the diameter of the primary side inflow / outlet holes is smaller than the diameter of the secondary side inflow / outlet holes.
For example, when the plate type heat exchanger 20 is used to exchange heat such as water with a refrigerant such as fluorocarbon, the inflow hole of the liquid (here, the second inflow hole 7) is worn away by the plate due to erosion. There is a risk of thinning. Therefore, it is necessary to make the diameter of the inflow / outflow hole (the second inflow hole 7, the second outflow hole 8) of the liquid a certain size. However, the diameter of the refrigerant inflow / outlet holes (first inflow hole 5, first outflow hole 6) needs to be increased in accordance with the diameter of the liquid inflow / outlet holes (second inflow hole 7, second outflow hole 8) There is no. That is, the diameter of the first inflow hole 5 and the diameter of the first outflow hole 6 can be smaller than the diameter of the second inflow hole 7 and the diameter of the second outflow hole 8. As described above, when the diameter of the first inflow hole 5 and the diameter of the first outflow hole 6 are reduced, the

plates

2 and 3 can be obtained by reducing the diameter of the first inflow hole 5 and the diameter of the first outflow hole 6. The length in the short side direction of can be shortened. Therefore, as described in the first embodiment, the strength of the plate type heat exchanger 20 is increased, and the weight of the plate type heat exchanger 20 can be reduced.
The refrigerant is not limited to fluorocarbon, but may be a hydrocarbon-based refrigerant or a low GWP refrigerant. In addition, the operating pressure of the CO 2 refrigerant is high, so the strength of the plate heat exchanger 20 is required. When this CO2 refrigerant is used, a configuration in which the outflow and inflow holes of the refrigerant are smaller than the inflow and outflow holes of the liquid is particularly effective. Since the CO 2 refrigerant has a large density and a small pressure loss with respect to the fluorocarbon refrigerant, the diameters of the first inflow hole 5 and the first outflow hole 6 can be further reduced.

FIG. 11 is a view showing a plate type heat exchanger 20 in which the diameter of the first inflow hole 5 is made smaller as the

plates

2 and 3 on the reinforcing side plate 1 side.
The plate type heat exchanger 20 shown in FIG. 11 is not only the diameter of the primary side inflow / outlet holes being smaller than the diameter of the secondary side inflow / outlet holes, but also a plate laminated on the reinforcing side plate 1 side. The diameter of the first inflow hole 5 is small by a few. That is, the diameter of the first inflow hole 5 is smaller in the

plates

2 and 3 stacked on the side plate 1 for reinforcement than in the

plates

2 and 3 stacked on the side plate 4 for reinforcement. In other words, the diameter of the first inflow hole 5 is as small as the

plates

2 and 3 stacked on the inflow side of the first fluid. In particular, the first inflow holes 5 of the

plates

2 and 3 stacked on the reinforcing side plate 1 side are very small like a fine nozzle.
Since the first inflow holes 5 of the

plates

2 and 3 stacked on the reinforcing side plate 1 side are made very small, the flow velocity of the first fluid can be increased even when the number of

stacked plates

2 and 3 is large. Therefore, the first fluid is likely to be distributed also to the

plates

2 and 3 on the side plate 4 for reinforcement.
Further, since the diameter of the first inflow hole 5 is larger as the

plates

2 and 3 stacked on the reinforcing side plate 4 side, the first fluid is evenly distributed to the first flow path formed by the

plates

2 and 3 It is easy to be done.

Third Embodiment
In the third embodiment, a plate-type heat exchanger 20 will be described in which the inflow / outflow holes are disposed not only toward the plate end in the lateral direction but also toward the plate end in the longitudinal direction. That is, in the third embodiment, the plate type heat exchanger 20 in which the inlet and outlet holes are brought close to the four corners (corners) of the

plates

2 and 3 will be described.

FIG. 12 is a view showing the sizes of the

plates

2 and 3 in which the inflow and outflow holes are moved to the four corners. In FIG. 12, a length L <b> 7 indicates the length from the first inflow hole 5 to the longitudinal plate end closer to the first inflow hole 5. The length L8 indicates the length from the first outlet hole 6 to the longitudinal plate end closer to the first outlet hole 6. The length L9 indicates the length from the second inflow hole 7 to the longitudinal plate end closer to the second inflow hole 7. The length L10 indicates the length from the second outflow hole 8 to the longitudinal plate end closer to the second outflow hole 8.
The lengths L7, L8, L9, and L10 are set to be approximately equal to the lengths L3, L4, L5, and L6 illustrated in FIG. 7, respectively. By thus shortening the lengths L7, L8, L9 and L10, it is possible to further reduce the stress applied to the peripheral portion of the plate.

In particular, in the

plates

2 and 3 shown in FIG. 12, the diameter of the primary side inflow / outlet hole is smaller than the diameter of the secondary side inflow / outlet hole. Therefore, the centers of the primary inflow and outflow holes are arranged closer to the four corners of the

plates

2 and 3 than the centers of the secondary inflow and outflow holes.
As described above, the primary inlet and outlet holes (the first inlet and outlet holes 5 and 6) which are smaller in diameter are moved to the four corners of the

plates

2 and 3 to make the first outlet hole 6 through the first inlet hole 5. The distance to get longer. That is, the first flow path becomes longer. Therefore, the heat transfer area becomes longer, and the heat exchange performance of the plate type heat exchanger 20 is improved.

FIG. 13 is an explanatory view of the flow of the first fluid of the first plate 3 in which the inlet and outlet holes are brought close to the four corners. In addition, not the

plates

2 and 3 but the first plate 3 is limited. This is because the seal portion 11 is shown in FIG. That is, the sealing portion 11 is different in the position where the second plate 2 and the first plate 3 are provided.
The approach region 10 can be provided in the vicinity of the first inflow hole 5 in the first flow passage by moving the first inflow hole 5 having a small diameter to the corners of the

plates

2 and 3. The approach area 10 is a narrow area sandwiched between the plate end and the seal portion 11. That is, the width of the approach area 10 (the length L11 from the plate end to the seal portion 11) is narrower than the width (length L2) of the first plate 3 in the lateral direction. The first fluid flowing in from the first inflow hole 5 spreads in the short direction of the plate type heat exchanger 20 after passing through the narrow entrance region 10 and flows to the first outflow hole 6.
The seal portion 11 is a wall that prevents the first fluid flowing from the first inflow hole 5 from flowing to the second outflow hole 8. The seal portion 11 is formed to protrude in a convex shape in the stacking direction of the

plates

2 and 3. Usually, the seal portion 11 is provided in a circular shape around the second outflow hole 8. However, here, the seal portion 11 is provided with the first outflow hole 6 and the second inflow hole 7 from the end portion side (upper side) in the longitudinal direction where the first inflow hole 5 and the second outflow hole 8 are provided. It is provided so that it may approach the end (right side) by the side of the 2nd outflow hole 8 of the transversal direction gradually toward the longitudinal end side (lower side) of that. In particular, in FIG. 13, the seal portion 11 is provided in a curved shape which is gradually bent to the right from the upper side to the lower side.
The first fluid having flowed through the entry region 10 is spread without difficulty by the seal portion 11 to the end (right side) on the second outflow hole 8 side in the short direction. That is, in the approach area 10 and the seal portion 11, there is a rectifying effect that leads the first fluid to the end (right side) on the second outflow hole 8 side in the short direction. By this rectification effect, stagnation of the first fluid can be prevented around the seal portion 11 and around the outer periphery of the

plates

2 and 3, and heat exchange performance is improved. Moreover, the pressure loss of the first fluid can be reduced by this rectification effect. That is, a high performance plate type heat exchanger 20 can be obtained.
In addition, when the seal portion 11 is provided in a circular shape around the second outflow hole 8 as usual, a distribution promoting member is provided around the first inflow hole 5 to prevent the first fluid from drifting. There is a need. For example, the distribution promoting member may be formed in a complex shape such as a radial shape. Therefore, the plate type heat exchanger 20 including the distribution promoting member is difficult to manufacture. However, the plate type heat exchanger 20 according to the third embodiment is only obtained by curving the seal portion 11, and manufacture is easy. Therefore, the plate type heat exchanger 20 according to the third embodiment has high mass productivity.

FIG. 14 is an explanatory view of the unevenness 9 of the first plate 3 in which the inflow / outflow holes are moved to the four corners. FIG. 15 is a view showing the unevenness 9 of the second plate 2 in which the inflow / outflow holes are moved to the four corners. FIG. 16 is a view showing the unevenness 9 of the first plate 3 in which the inflow / outflow holes are moved to the four corners.
As described in the first embodiment, the

plates

2 and 3 have both end portions 13 on both end sides in the short direction, and have the folding points 12 at positions deviated in the longitudinal direction from the both end portions 13 A plurality of concavities and convexities 9 formed in a letter shape are arranged in the longitudinal direction. In addition, the folding | returning point 12 of the unevenness | corrugation 9 of the

plates

2 and 3 shown to FIG. 3, 4 was provided in the center of the transversal direction. That is, the unevenness 9 was formed symmetrically in the left-right direction.
Here, in the

plates

2 and 3 shown in FIG. 14, the diameter of the primary side inflow / outlet holes is smaller than the diameter of the secondary side inflow / outlet holes. That is, in FIG. 14, the diameters of the first inflow holes 5 and the first outflow holes 6 are smaller than the diameters of the second inflow holes 7 and the second outflow holes 8. Therefore, as in the

plates

2 and 3 shown in FIGS. 3 and 4, when the folding point 12 of the unevenness 9 is provided at the center of the short direction, the unevenness 9 is formed in the vicinity of the first inflow hole 5 and the first outflow hole 6. An area that can not be Therefore, in the vicinity of the first inflow hole 5 and the first outflow hole 6 having a small diameter, the folding point 12 of the unevenness 9 is shifted toward the first inflow hole 5 and the first outflow hole 6 to form the unevenness 9. That is, as shown in FIG. 14, the line 15 connecting the turning points 12 of the unevenness 9 is gradually deviated from the center line 14 in the short direction toward the first inflow hole 5 and the first outflow hole 6 It is formed.
Thereby, the unevenness 9 can be formed also in the vicinity of the first inflow hole 5 and the first outflow hole 6, and the heat transfer area becomes long. Therefore, the heat exchange performance of the plate type heat exchanger 20 is improved. Moreover, the

plates

2 and 3 are joined to the

adjacent plates

2 and 3 at the portions where the asperities 9 are formed. In general, the

plates

2 and 3 easily peel off in the vicinity of the inflow / outflow holes. However, by forming the unevenness 9 to the vicinity of the inflow / outflow holes, the bonding points of the

plates

2 and 3 can be increased, and the separation of the

plates

2 and 3 can be prevented. Further, the turning point 12 of the unevenness 9 gradually moves from the first inflow hole 5 to the center in the short direction, and also gradually moves from the center in the short direction to the first outflow hole 6. Therefore, the first fluid flowing from the first inflow hole 5 can be smoothly moved to the center side in the short side direction, and can be smoothly moved from the center side in the short side direction to the first outflow hole 6. Therefore, the pressure loss of the first fluid can be reduced.
As shown in FIG. 16, as for the second plate 2, as in the case of the first plate 3, in the vicinity of the first inflow hole 5 having a small diameter and the first outflow hole 6, the turning point 12 of the unevenness 9 is the first The unevenness 9 is formed by being shifted toward the inflow hole 5 and the first outflow hole 6.

Fourth Embodiment
In the fourth embodiment, a plate type heat exchanger 20 in which the shapes of the primary inflow and outflow holes and the secondary inflow and outflow holes are deformed will be described.

17 to 19 show the

plates

2 and 3 in which the primary inlet and outlet holes and the secondary inlet and outlet holes have different shapes while maintaining the required opening area.
In FIG. 17, the first inlet and outlet holes and the second inlet and outlet holes have substantially different ellipses. In FIG. 18, one circle is divided into two, one is a primary side inflow / outlet hole, and the other is a secondary side inflow / outlet hole. In FIG. 19, the substantially rectangular shape is divided into two, one of which is a primary side inflow / outlet hole and the other is a secondary side inflow / outlet hole.
The diameter of the primary side inflow / outlet holes shown in FIGS. 17 to 19 is smaller than the diameter of the secondary side inflow / outlet holes.

FIG. 20 is a comparison diagram of the case where the primary side inflow / outlet hole and the secondary side inflow / outlet hole have the same shape, and the case where the primary side inflow / outlet hole and the secondary side inflow / outlet hole are different in shape It is. In FIG. 20, the side of the first outflow hole 6 and the second inflow hole 7 in the longitudinal direction of the

plates

2 and 3 is shown. FIG. 20A shows the

plates

2 and 3 in which both the first outflow hole 6 and the second inflow hole 7 are circular. On the other hand, in FIG. 20 (b), as in FIG. 18, one circle is divided into two, one is a primary side inflow / outlet hole, and the other is a secondary side inflow / outlet hole. Indicates Moreover, the diameter of the primary side inflow / outlet hole shown to FIG. 20 (a) and FIG. 20 (b) is a diameter smaller than the diameter of a secondary side inflow / outlet hole.
The first outflow hole 6 shown in FIG. 20 (a) is a circle with a diameter of "12 mm", and the second inflow hole 7 is a circle with a diameter of "28 mm". Further, the first outflow hole 6 and the second inflow hole 7 are separated by "3 mm". Therefore, the opening area of the first outflow hole 6 is “36πm ² ”, and the opening area of the second inflow hole 7 is “196πm ² ”. Moreover, the length from the end of the first outflow hole 6 to the end of the second inflow hole 7 is “43 mm”.
On the other hand, the 1st outflow hole 6 shown in Drawing 20 (b) is 1/4 part of a circle of diameter "24 mm", and the 2nd inflow hole 7 is 3/4 part of a circle of "31 mm." Further, the first outflow hole 6 and the second inflow hole 7 are separated by "3 mm". Therefore, the opening area of the first outlet hole 6 is “36πm ² ”, and the opening area of the second inlet hole 7 is “192πm ² ”. Moreover, the length from the end of the first outflow hole 6 to the end of the second inflow hole 7 is “31 mm”.
That is, the first outflow hole 6 shown in FIG. 20 (a) and the first outflow hole 6 shown in FIG. 20 (b) both have the same opening area of “36πm ² ”. The second inflow holes 7 shown in FIG. 20 (a) and the second inflow holes 7 shown in FIG. 20 (b) have substantially the same opening area of “196πm ² ” and “192πm ² ”. However, the length from the end of the first outflow hole 6 to the end of the second inflow hole 7 is “43 mm” for the

plates

2 and 3 shown in FIG.

Plates

2 and 3 shown in b) are "31 mm". That is, as for the length from the end of the first outflow hole 6 to the end of the second inflow hole 7, the

plates

2 and 3 shown in FIG. Much shorter than three. That is, by forming the first outflow hole 6 and the second inflow hole 7 as shown in FIG. 20B, the plate 2 can be maintained while maintaining the opening areas of the first outflow hole 6 and the second inflow hole 7. The length of the short side direction of 3 can be shortened significantly.

21 to 24 are views showing the

plates

2 and 3 in which the primary inlet and outlet holes and the secondary inlet and outlet holes have the same shape while maintaining the required opening area, and have a shape other than a circle. is there.
In FIG. 21, the primary side inflow / outlet holes and the secondary side inflow / outlet holes are made to be substantially the same oval. In FIGS. 22 and 23, the primary inlet and outlet holes and the secondary inlet and outlet holes have the same fan shape. In FIG. 24, the primary side inflow / outlet holes and the secondary side inflow / outlet holes have the same star shape.

As described above, by setting the shapes of the primary side inflow / outlet holes and the secondary side inflow / outlet holes to be a combination of various shapes, it is possible to shorten the length in the short direction of the

plates

2 and 3. Therefore, the effects described in Embodiment 1 can be obtained. In addition, when the next side inflow-outlet hole and the secondary side inflow-outlet hole are made into the same shape, the plate type heat exchanger 20 can be comprised by one type of

plate

2 and 3. FIG.

Embodiment 5
Embodiment 5 demonstrates the heating hot-water supply system 29 which is an example of utilization of the plate type heat exchanger 20 demonstrated in the above embodiment.

FIG. 25 is a view showing the heating and hot water supply system 29. As shown in FIG.
The heating and hot water supply system 29 includes a compressor 21, a plate type heat exchanger 20, an expansion valve 22, a heat exchanger 23, a water heater 24, a heater 25, a refrigerant passage 26, and a water passage 27. Here, the plate type heat exchanger 20 is the plate type heat exchanger 20 described in the above embodiment. In addition, the compressor 21, the plate type heat exchanger 20, the expansion valve 22, the heat exchanger 23, and the refrigerant passage 26 are a heat exchange system 28.
The refrigerant flows repeatedly in the refrigerant passage 26 in the order of the compressor 21, the plate heat exchanger 20, the expansion valve 22, and the heat exchanger 23. The compressor 21 compresses the refrigerant as described above. The plate heat exchanger 20 exchanges heat between the refrigerant compressed by the compressor 21 and the liquid (here, water) flowing through the water channel 27. Here, the heat exchange in the plate heat exchanger 20 cools the refrigerant and warms the water. The expansion valve 22 controls the expansion of the refrigerant heat-exchanged by the plate heat exchanger 20. The heat exchanger 23 exchanges heat between the expanded refrigerant and air according to the control of the expansion valve 22. Here, the heat exchange in the heat exchanger 23 warms the refrigerant and cools the air. Then, the warmed refrigerant enters the compressor 21.
On the other hand, water flows between the plate heat exchanger 20 and the water heater 24 and the heater 25 in the water channel 27. As described above, water is warmed by heat exchange in the plate heat exchanger 20. Then, the heated water flows to the water heater 24 and the heater 25. The water for hot water supply may not be the water heat-exchanged by the plate type heat exchanger 20. That is, the water flowing through the water channel 27 may be further subjected to heat exchange with the water for hot water supply by the water heater 24 or the like.

The plate type heat exchanger 20 described in the above embodiment is high in strength, small in size, light in weight, and efficient. Therefore, the heat exchange system 28 using the plate type heat exchanger 20 described in the above embodiment is also efficient. Further, the heating and hot water supply system 29 using the heat exchange system 28 is also efficient.
Here, the heat exchange system (ATW (Air To Water) system) which heats water with the refrigerant compressed by plate type heat exchanger 20 explained by the above-mentioned embodiment was explained. However, the present invention is not limited to this, and it is also possible to form a refrigeration cycle (refrigerating air conditioner) that performs heat exchange using the plate type heat exchanger 20 described in the above embodiment to heat or cool a fluid such as air. .

That is, the above embodiment can be summarized as follows.
The plate-type heat exchanger 20 has passage holes serving as fluid inlets and outlets at four corners, and in the plate-type heat exchanger formed by stacking a plurality of plates provided with a fluid inflow pipe and an outflow pipe, the plate width ( It is characterized in that the ratio of height (H) to W) is 4 to 6.5.

Further, the plate type heat exchanger 20 has passage holes serving as a fluid inlet / outlet at four corners, and in the plate type heat exchanger formed by laminating a plurality of plates provided with a fluid inflow pipe and an outflow pipe, It is characterized in that the length in the width direction between the side, the inlet / outlet of the secondary side fluid and the plate outer peripheral edge is 3 to 6% with respect to the width (W) of the plate.

Further, the plate type heat exchanger 20 has passage holes serving as a fluid inlet / outlet at four corners, and in the plate type heat exchanger formed by laminating a plurality of plates provided with a fluid inflow pipe and an outflow pipe, It is characterized in that the length in the width direction between the side, the inlet / outlet of the secondary side fluid and the plate outer peripheral edge portion is 3 to 5.6 mm.

Further, the plate type heat exchanger 20 has passage holes serving as a fluid inlet / outlet at four corners, and in the plate type heat exchanger formed by laminating a plurality of plates provided with a fluid inflow pipe and an outflow pipe, The inlet and outlet diameters of the side fluid and the secondary side fluid are different in size.

Further, the plate type heat exchanger 20 has passage holes serving as a fluid inlet / outlet at four corners, and in the plate type heat exchanger formed by laminating a plurality of plates provided with a fluid inflow pipe and an outflow pipe, The center of the inlet / outlet diameter of the side fluid and the center of the inlet / outlet diameter of the secondary side fluid are shifted, and the inlet / outlet of fluid is brought closer to the outer peripheral edge of the plate.

The plate heat exchanger 20 has passage holes serving as fluid inlets and outlets at four corners, and is a plate heat exchanger formed by stacking a plurality of plates provided with a fluid inflow pipe and an outflow pipe. A peak portion formed by folding is disposed while being gradually shifted from the center of the plate, and an end point of the wave is brought close to the inlet / outlet.

Further, the plate type heat exchanger 20 has passage holes serving as a fluid inlet / outlet at four corners, and in the plate type heat exchanger formed by laminating a plurality of plates provided with a fluid inflow pipe and an outflow pipe, The center of the inlet / outlet diameter of the side fluid and the center of the inlet / outlet diameter of the secondary side fluid are shifted to form a combination of circular, polygonal, etc. shapes while maintaining the required opening area by the treatment flow rate of the secondary side fluid Do.

Further, the plate type heat exchanger 20 has passage holes serving as a fluid inlet / outlet at four corners, and in the plate type heat exchanger formed by stacking a plurality of plates provided with a fluid inflow pipe and an outflow pipe, It is characterized in that it is a combination of the same shape such as a circle and a polygon while maintaining the required opening area by the processing flow rate of the side fluid.

1, 4 reinforcement side plate, 2 second plate, 3 1st plate, 5 1st inflow hole, 6 1st outflow hole, 7 2nd inflow hole, 8 2nd outflow hole, 9 unevenness, 10 approach area, 11 Seal part, 12 turning points, 13 both ends, 14 centerline in the width direction, 15 line connecting 12 turning points, 20 plate type heat exchanger, 21 compressor, 22 expansion valve, 23 heat exchanger, 24 hot water supply , 25 heaters, 26 refrigerant paths, 27 water channels, 28 heat exchange systems.

Claims

A plate heat exchanger formed by laminating a plurality of plates,
Each plate of the plurality of plates
A first inflow hole, which is an inlet for the first fluid, at either end in the longitudinal direction;
A first outflow hole serving as an outlet of the first fluid, at a longitudinal end opposite to the first inflow hole;
A second inflow port, which is an inlet for the second fluid, at either end in the longitudinal direction;
A second outflow port serving as an outlet of the second fluid is provided on the end side in the longitudinal direction opposite to the second inflow port,
Each of the plates is a first flow path for spreading the first fluid, which has flowed in from the first inflow hole, in the lateral direction between the plates stacked next to each other, and the first flow path to flow to the first outflow hole; (2) One flow path is formed with the second flow path which spreads the second fluid flowing in from the inflow hole in the short direction and flows to the second outflow hole, and the first flow which flows in the first flow path Heat exchange between the fluid and the second fluid flowing in the second flow path,
A plate type heat exchanger characterized in that the length in the longitudinal direction of each of the plates is four or more times the length in the lateral direction.
The length from the first inflow hole to the plate end in the lateral direction closer to the first inflow hole, and the plate end in the lateral direction closer to the first outflow hole from the first outflow hole The length to the portion, the length from the second inflow hole to the plate end in the lateral direction closer to the second inflow hole, and the length closer to the second outflow hole from the second outflow hole The plate type heat exchanger according to claim 1, wherein the length to the plate end in the lateral direction is 6% or less of the length in the lateral direction.
The length from the first inflow hole to the plate end in the lateral direction closer to the first inflow hole, and the plate end in the lateral direction closer to the first outflow hole from the first outflow hole The length to the portion, the length from the second inflow hole to the plate end in the lateral direction closer to the second inflow hole, and the length closer to the second outflow hole from the second outflow hole The plate type heat exchanger according to claim 1, wherein the length in the lateral direction to the plate end is a length of 5.6 mm or less.
The opening area of the first inflow hole and the opening area of the first outflow hole are both smaller than the opening area of the second inflow hole and the opening area of the second outflow hole. The plate type heat exchanger according to claim 1.
The center of the first inflow hole and the center of the first outflow hole are provided closer to the plate end than the center of the second inflow hole and the center of the second outflow hole. The plate type heat exchanger according to Item 4.
In the plate type heat exchanger, the first plate and the second plate are alternately stacked,
The first inflow hole and the second outflow hole are provided on the same end side in the longitudinal direction,
The first plate is a seal that prevents the fluid flowing from the first inflow hole from flowing to the second outflow hole, and a convex seal that protrudes in the stacking direction in which the plurality of plates are stacked. And the second outflow in the short direction gradually from the end in the longitudinal direction to the end in the longitudinal direction on the opposite side where the first inflow hole and the second outflow hole are provided. The plate type heat exchanger according to claim 4, wherein the plate type heat exchanger is provided so as to approach the end on the hole side.
Each of the plates
The V-shaped concave and convex portions are arrayed in the longitudinal direction by having both end portions on both end sides in the short direction and having turning points at positions shifted from the both ends in the longitudinal direction. And
In the vicinity of at least one of the first inflow hole and the first outflow hole, the V-shaped concave portion and the convex portion are closer to the hole from the center of the short direction toward the hole as the hole is approached. The plate type heat exchanger according to claim 4, characterized in that a part is formed.
The plurality of plates are stacked such that the first inflow holes overlap, and in order from the first inflow holes of the plates stacked on one side in the stacking direction to the first inflow holes of the plates stacked on the other side The first fluid flows in;
5. The plate type heat exchanger according to claim 4, wherein the diameter of the first inflow hole is smaller as the plate is stacked on the one side to which the first fluid flows.
The first inflow hole and the second outflow hole are provided on the same end side in the longitudinal direction, and the second inflow hole and the first outflow hole are the same end in the longitudinal direction. Provided on the side,
The shape of the first inflow hole is different from the shape of the second outflow hole, and the shape of the second inflow hole is different from the shape of the first outflow hole. The plate type heat exchanger according to 1.
The first inflow hole and the second outflow hole are formed by dividing one circle or one oval or one polygonal hole into two,
10. The apparatus according to claim 9, wherein the second inflow hole and the first outflow hole are formed by dividing one circle or one oval or one polygonal hole into two. Plate heat exchanger.
A refrigeration air conditioner comprising the plate type heat exchanger according to claim 1.
A plate heat exchanger formed by laminating a plurality of plates,
Each plate of the plurality of plates
At a longitudinal end side, a first inflow hole serving as an inlet for the first fluid;
A first outflow hole serving as an outlet of the first fluid, on the end side in the longitudinal direction opposite to the first inflow hole;
At the longitudinal end side, a second inflow hole serving as an inlet for the second fluid;
A second outlet port serving as an outlet of the second fluid is provided on the end side in the longitudinal direction opposite to the second inlet port,
Each of the plates is a first flow path for spreading the first fluid, which has flowed in from the first inflow hole, in the lateral direction between the plates stacked next to each other, and the first flow path to flow to the first outflow hole; (2) One flow path with the second flow path which spreads the second fluid which has flowed in the inflow port in the short direction and flows to the second outflow port, and forms the first flow path which flows in the first flow path Heat exchange with the second fluid flowing in the second flow path,
The length from the first inflow hole to the plate end in the lateral direction closer to the first inflow hole, and the plate end in the lateral direction closer to the first outflow hole from the first outflow hole The length to the portion, the length from the second inflow hole to the plate end in the lateral direction closer to the second inflow hole, and the length closer to the second outflow hole from the second outflow hole A plate type heat exchanger characterized in that the length in the lateral direction to the plate end is 6% or less of the length in the lateral direction.
A plate heat exchanger formed by laminating a plurality of plates,
Each plate of the plurality of plates
At a longitudinal end side, a first inflow hole serving as an inlet for the first fluid;
A first outflow hole serving as an outlet of the first fluid, on the end side in the longitudinal direction opposite to the first inflow hole;
At the longitudinal end side, a second inflow hole serving as an inlet for the second fluid;
A second outlet port serving as an outlet of the second fluid is provided on the end side in the longitudinal direction opposite to the second inlet port,
Each of the plates is a first flow path for spreading the first fluid, which has flowed in from the first inflow hole, in the lateral direction between the plates stacked next to each other, and the first flow path to flow to the first outflow hole; (2) One flow path with the second flow path which spreads the second fluid which has flowed in the inflow port in the short direction and flows to the second outflow port, and forms the first flow path which flows in the first flow path Heat exchange with the second fluid flowing in the second flow path,
The length from the first inflow hole to the plate end in the lateral direction closer to the first inflow hole, and the plate end in the lateral direction closer to the first outflow hole from the first outflow hole The length to the portion, the length from the second inflow hole to the plate end in the lateral direction closer to the second inflow hole, and the length closer to the second outflow hole from the second outflow hole A plate type heat exchanger characterized in that the length in the lateral direction to the plate end is a length of 5.6 mm or less.