JP2000193390A - Plate heat exchanger - Google Patents

Abstract

(57) [Problem] To provide a plate heat exchanger suitable for heat exchange between different kinds of fluids and fluids having different flow rates. SOLUTION: A large number of rectangular first plates (P1) and second plates are alternately laminated, and a first passage (41) and a second passage (42) are formed between the plates (P1, ...). Form alternately. Each plate (P1,...) Has a herringbone-shaped corrugated portion (11). Corrugated part of the first plate (P1) (1
In 1), the top surface of the projection (13) becomes a flat flat top surface (16), and the bottom surface of the recess (12) becomes a flat bottom surface (15) wider than the flat top surface (16). I have. The flat top surface (16) and the flat bottom surface (15) are continuous by a linearly extending slope (17). In the corrugated portion of the second plate, the bottom surface of the concave portion is a flat flat bottom surface, and the top surface of the convex portion is a flat top surface wider than the flat bottom surface. The flat top surface and the flat bottom surface are continued by a straightly extending slope.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a plate heat exchanger, and more particularly, to a measure for miniaturization by optimizing heat transfer performance and pressure loss.

[0002]

2. Description of the Related Art Conventionally, as disclosed in Japanese Patent Application Laid-Open No. Hei 7-260384, a plate heat exchanger constituted by laminating a number of heat transfer plates is known. Specifically, a corrugated heat transfer portion is formed on each of the heat transfer plates. The heat transfer portion is formed in a herringbone shape in which each wave-shaped ridge has an inverted V-shape. These heat transfer plates are alternately stacked by being inverted by 180 degrees on a plane, and a gasket is sandwiched between the heat transfer plates. Frames are respectively provided on the uppermost layer and the lowermost layer in the stacking direction of the stacked heat transfer plates, and both frames are fastened with bolts and nuts to be integrally formed. In the plate heat exchanger, a first passage and a second passage are formed with each heat transfer plate interposed therebetween. Further, since the heat transfer plates are alternately inverted and stacked as described above, each passage is formed in a complicated shape that repeats expansion and contraction. And
The plate heat exchanger is configured to exchange heat with the fluid in each passage via the heat transfer plate.

Further, there is known a plate-type heat exchanger in which a heat transfer plate adjacent to a heat transfer plate at a peripheral portion thereof is joined together by brazing without providing a gasket. . In this type of plate heat exchanger, corrugated heat transfer portions of adjacent heat transfer plates come into contact with each other, and even at the contacted portions, the adjacent heat transfer plates are brazed and joined. That is, the heat transfer plates are joined to each other not only at the peripheral portion but also at the contact portions of a large number of heat transfer portions to ensure sufficient pressure resistance.

[0004]

By the way, in the plate heat exchanger, the first passage and the second passage have the same volume. For this reason, in the case where the same type of fluid (for example, cold water and hot water) having the same flow rate is subjected to heat exchange, the fluid flows at substantially the same flow velocity in each passage. Therefore, the heat transfer coefficient between the fluid and the heat transfer plate in each passage is substantially equal, and the pressure loss when flowing through each passage is also substantially equal.

However, when different kinds of fluids (for example, water and refrigerant) are allowed to flow through the respective passages, or when the flow rates of the respective kinds of passages differ greatly, the fluids in the respective passages and the heat transfer plate However, there is a problem that the heat transfer coefficient and the pressure loss when flowing through each passage greatly differ.

For example, when a plate heat exchanger is used as an evaporator of a chiller that generates cold water by a refrigerator,
Refrigerant flows through one passage of the plate heat exchanger and water flows through the other passage to exchange heat with each other. And
While the refrigerant evaporates, the water is cooled to low temperature cold water. In this case, the heat transfer coefficient on the water side and the heat transfer coefficient on the refrigerant side largely differ depending on the presence or absence of a phase change, a difference in flow rate, and the like. Specifically, the heat transfer coefficient on the water side with respect to the refrigerant side becomes about 3 to 4 times. Since the heat transfer coefficient of the refrigerant side is lower than that of the water side, the heat transmission coefficient is also lower. Therefore, there has been a problem that a sufficient heat exchange capacity cannot be obtained, and an attempt to secure the capacity results in an increase in size.

Further, in the above chiller, the refrigerant circulates in the refrigerant pipe by the compressor, while water circulates in the water pipe by the pump. Therefore, although the flow resistance of the refrigerant in the plate heat exchanger, that is, the pressure loss on the refrigerant side does not matter so much, the flow resistance of the water, that is, the pressure loss on the water side, needs to be suppressed to a certain value or less. And
To reduce the pressure loss on the water side, it is necessary to increase the number of stacked heat transfer plates to increase the number of passages, reduce the flow rate of water in each passage, and reduce the flow velocity. For this reason, there has been a problem that the size of the plate heat exchanger is increased.

In order to solve the problem of pressure loss, the above publication discloses a method in which a predetermined vertical groove is formed in a corrugated heat transfer portion of a heat transfer plate. In other words, in this heat transfer section, a flat vertical groove extending at a predetermined width along the flow direction of the fluid is formed,
Thereby, the pressure loss is reduced. However, in this measure, there is a possibility that the heat transfer plate may be difficult to process, or a heat transfer coefficient may be deteriorated due to a change in a flow state in the passage.

The present invention has been made in view of the above points, and an object of the present invention is to provide a plate heat exchanger suitable for heat exchange between different kinds of fluids and fluids having different flow rates. It is in.

[0010]

According to the present invention, the volume of the first passage (41) through which the first fluid flows and the volume of the second passage (42) through which the second fluid flows are different from each other. .

Specifically, the first solution taken by the present invention is to provide a plurality of first heat transfer plates (P1) and a plurality of second heat transfer plates (P1).
The heat transfer plates (P2) are alternately stacked, and a first fluid and a second fluid are interposed between the stacked heat transfer plates (P1, P2) via the heat transfer plates (P1, P2). The first passages (41) through which the first fluid flows and the second passages (42) through which the second fluid flows are formed alternately so as to exchange heat with each other. Concave (12,22) and convex (13,2)
3) are alternately arranged to form a corrugated portion (11, 21), and the corrugated portions (11, 21) of the two heat transfer plates (P1, P2) are combined with the concave portion (1) of one heat transfer plate (P1). 12) and a convex portion (23) of another heat transfer plate (P2) facing the concave portion (12) intersects and abuts with each other, and is in contact with a convex portion (13) of one heat transfer plate (P1). The heat transfer plate (P1, P2) is formed so that the concave portion (22) of the other heat transfer plate (P2) facing the convex portion (13) intersects and abuts with each other. , 21),
The volume of the first passage (41) and the volume of the second passage (42) are different from each other in accordance with the heat transfer characteristics of the first fluid and the second fluid.

[0012] A second solution taken by the present invention is:
In the first solution, the first heat transfer plate (P
The corrugated portion (11) of (1) is formed so that the width of the concave portion (12) at the amplitude center of the corrugated portion (11) is wider than the width of the convex portion (13), and the second heat transfer plate (P2 ) Waveform part (21)
Is formed such that the width of the convex portion (23) at the center of the amplitude of the waveform portion (21) is wider than the width of the concave portion (22).

[0013] A third solution taken by the present invention is:
In the first solution, the first heat transfer plate (P
In the corrugated portion (11) of 1), the top surface of the convex portion (13) is formed as a flat flat top surface (16) having a predetermined width, and the bottom surface of the concave portion (12) is wider than the flat top surface. Formed on a flat flat bottom surface (15), the flat top surface (16) and the flat bottom surface (15) are continued by a linearly extending slope (17), while the waveform of the second heat transfer plate (P2) In the portion (21), the bottom surface of the concave portion (22) is formed as a flat flat bottom surface (25) having a predetermined width, and the top surface of the convex portion (23) is formed as a flat flat top surface wider than the flat top surface. (26)
And the flat top surface (26) and the flat bottom surface (25) are connected by a linearly extending inclined surface (27).

A fourth solution taken by the present invention is:
In the first solution, the first heat transfer plate (P
In the corrugated portion (11) of (1), the top surface of the convex portion (13) is formed as a flat flat top surface (16) having a predetermined width, and the bottom surface of the concave portion (12) is formed as a flat flat bottom surface (15) having a predetermined width. ), And the flat top surface (1
6) and the flat bottom surface (15) are connected to the first passage (41) side by a slightly bulging slope (17), while the corrugated portion (21) of the second heat transfer plate (P2) has a concave portion (22). ) Is formed on a flat flat bottom surface (25) having a predetermined width, the top surface of the projection (23) is formed on a flat flat top surface (26) having a predetermined width, and the flat top surface (26) is formed. The flat bottom surface (25) is connected to the first passage (41) side by a slightly swelled slope (27).

[0015] The fifth solution taken by the present invention is:
In the first solution, the first heat transfer plate (P
In the corrugated portion (11) of (1), the top surface of the convex portion (13) is formed as a flat flat top surface (16) having a predetermined width, and the bottom surface of the concave portion (12) is formed as a flat flat bottom surface (15) having a predetermined width. ), And the flat top surface (1
6) and the flat bottom surface (15) are connected by a linearly extending slope (17), and the slope (17) has a number of bulging protrusions bulging toward the first passage (41). While (18) is provided, in the corrugated portion (21) of the second heat transfer plate (P2), the bottom surface of the concave portion (22) is formed to have a flat flat bottom surface
The top surface of the projection (23) is formed as a flat flat top surface (26) having a predetermined width, and the flat top surface (26) and the flat bottom surface (25) are linearly extended with a slope (27). ), The slope (27) is provided with a number of bulging projections (28) bulging in a protruding manner toward the first passage (41).

[0016] A sixth solution taken by the present invention is:
In the first solution, the volume of the first heat transfer passage (41a) formed by the corrugated portions (11, 21) of the heat transfer plates (P1, P2) in the first passage (41) is increased by a second value. 2 passages (4
In 2), the volume ratio of the second heat transfer passage (42a) formed by the corrugated portions (11, 21) of the heat transfer plates (P1, P2) is 1
And 2.7 or less.

Further, a seventh solution taken by the present invention is:
In the first solution, the volume of the first heat transfer passage (41a) formed by the corrugated portions (11, 21) of the heat transfer plates (P1, P2) in the first passage (41) is increased by a second value. 2 passages (4
In 2), the ratio of the volume of the second heat transfer passage (42a) formed by the corrugated portions (11, 21) of the heat transfer plates (P1, P2) is 1.4 or more and 1.8 or less. It is configured as follows.

An eighth solution taken by the present invention is:
In any one of the first to seventh solving means, of the first passage (41) and the second passage (42), a refrigerant having a small volume flows through a refrigerant having a small volume and a phase-change refrigerant flows in the passage. The large passage is configured such that a sensible heat medium that does not change phase flows in the passage.

-Operation- In the first solution, the first heat transfer plate (P1) and the second heat transfer plate (P2) are alternately stacked, and each heat transfer plate (P1, P2) Between the first passage (41) and the second passage (4
2) and are alternately formed. Here, each heat transfer plate (P
A predetermined corrugated portion (11, 21) is formed in (1, P2), and corrugated portions (11, 21) of adjacent heat transfer plates (P1, P2) are in contact with each other. Then, the first fluid and the second fluid in the first passage (41) are
The second fluid in the passage (42) exchanges heat with each other. At this time, in each passage (41, 42), the flow of the fluid is disturbed by the corrugated portions (11, 21) of the heat transfer plates (P1, P2), and heat transfer is promoted by forced convection.

The first passage (41) and the second passage (42) are formed so as to have mutually different volumes. Therefore, when the heat transfer characteristics of the first fluid and the second fluid are different,
For example, when the first fluid and the second fluid are different fluids, such as a case where the first fluid is a refrigerant and the second fluid is water, or the first fluid and the second fluid are the same type of fluid, but the flow rates of the two fluids are significantly different from each other. Even in such a case, the average flow velocity of each fluid in each passage is an appropriate value.

Further, in the second or third solving means,
The concave portions (12, 22) and the convex portions (13, 23) that form the corrugated portions (11, 21) of the heat transfer plates (P1, P2) have a predetermined shape, so that the first portions having different volumes from each other. A passage (41) and a second passage (42) are formed. Then, the first heat transfer plate (P) in the stacking direction of the heat transfer plates (P1, P2)
The volume of the passage located above 1) and below the second heat transfer plate (P2) is below the first heat transfer plate (P1) and above the second heat transfer plate (P2). It is larger than the volume of the passage located.

In the fourth solution, the slope of the corrugated portion (11, 21) of each heat transfer plate (P1, P2) is formed in a predetermined shape, so that the volume of the first passage (41) is reduced. It becomes smaller than the volume of the second passage (42).

Further, in the fifth solution means, by forming a predetermined bulging projection on the slope at the corrugated portion (11, 21) of each heat transfer plate (P1, P2), the first passage (41) is formed. Is smaller than the volume of the second passage (42).

Further, in the sixth or seventh solving means,
A plurality of heat transfer plates (P1, P2) are stacked, and a first passage (41) and a second passage (4) are interposed between the heat transfer plates (P1, P2).
2) and are alternately formed. The first passage (41) and the second passage
The first fluid and the second fluid flow through the passages (42), and the two fluids exchange heat via the heat transfer plates (P1, P2). At this time, in the heat transfer passage in each passage, the flow of the fluid is disturbed by the corrugated portions (11, 21) of the heat transfer plates (P1, P2), and heat transfer is promoted by forced convection.

The first heat transfer passage (41) of the first passage (41)
a) and the second heat transfer passage (42a) of the second passage (42) are formed such that their volumes are different from each other and the volume ratio is within a predetermined range. Thus, for example, if the first fluid is a refrigerant and the second fluid
Even when the first fluid and the second fluid are different fluids, such as water, or when the first fluid and the second fluid are the same type of fluid but their flow rates are significantly different, each heat transfer The average flow velocity of each fluid in the passage is an appropriate value.

In the eighth solution, specifically, in the plate-type heat exchanger, the refrigerant, which is a different fluid, and the sensible heat medium exchange heat.

[0027]

Therefore, according to the above solution, the first aspect
Even when the heat transfer characteristic of the fluid and the heat transfer characteristic of the second fluid are different, the average flow velocity of the first fluid in the first passage (41) and the average flow velocity of the second fluid in the second passage (42). The average flow velocity can be an appropriate value corresponding to the heat transfer characteristics of each fluid. Therefore, the heat transfer coefficient between the first fluid and the heat transfer plate (P1, P2), that is, the heat transfer coefficient on the first fluid side, and the heat transfer coefficient between the second fluid and the heat transfer plate (P1, P2) Heat transfer coefficient, ie the second
The heat transfer coefficient on the fluid side can be optimized, and the heat transmission coefficient can be improved.

Specifically, when heat exchange between different kinds of fluids such as refrigerant and water is performed, in a conventional plate heat exchanger in which the volumes of the passages are equal to each other, the heat transfer coefficient on the refrigerant side is on the water side. Was much lower than the heat transfer coefficient and the heat transmission coefficient was low. On the other hand, in the present solution, since the average flow velocity of each fluid is optimized, in the above-described case, the heat transfer coefficient on the refrigerant side, which was lower than that on the water side, can be improved. Rate can be improved. As a result, the size of the plate heat exchanger can be reduced, and the cost can be reduced.

In general, the plate heat exchanger is designed so that a predetermined heat exchange amount is secured when fluids having a predetermined flow rate exchange heat, and the pressure loss of the fluid is equal to or less than a predetermined value. You. Therefore, in a conventional plate heat exchanger in which the volume of each passage is equal, when the pressure loss of one fluid exceeds a predetermined value, even if the amount of heat exchange is sufficient, It was necessary to reduce the pressure loss by increasing the number of passages by increasing the number of sheets.
On the other hand, according to the above solution, as described above, the first passage (41) and the second passage (42) can have different volumes. Therefore, the pressure loss of one fluid can be reduced without increasing the number of heat transfer plates (P1, P2). That is, it is possible to satisfy the demand for reducing the pressure loss while keeping the plate heat exchanger small.

According to the second to fifth solutions, the basic shapes of the corrugated portions (11, 21) of the heat transfer plates (P1, P2), that is, the concave portions (12, 22) and the convex portions are provided. The first passage (41) and the second passage (4) having different capacities from each other without changing the shape in which (13, 23) are formed alternately from the conventional one.
2) and can be formed. Therefore, it is possible to improve the heat transfer rate by optimizing the heat transfer coefficient between the fluid and the heat transfer plates (P1, P2) in each passage while promoting the heat transfer by forced convection as in the related art. Further, since the basic shape of the heat transfer plates (P1, P2) is not changed as described above, the workability of the heat transfer plates (P1, P2) can be maintained at the same level as before.

In the sixth and seventh solving means, the volume of the first heat transfer passage (41a) and the volume of the second heat transfer passage (42a) are set at a predetermined ratio. For this reason,
The average flow velocity of the first fluid in the first heat transfer passage (41a) and the average flow velocity of the second fluid in the second heat transfer passage (42a) can be set to optimal values. The size can be reduced. That is, for example, when the average flow velocity in the first heat transfer passage (41a) is increased, the average flow velocity in the second heat transfer passage (42a) is decreased accordingly, so that the first fluid and the heat transfer plate (P1 , P2), but the heat transfer coefficient between the second fluid and the heat transfer plates (P1, P2) decreases. Accordingly, an appropriate range exists for the volume ratio between the first heat transfer passage (41a) and the second heat transfer passage (42a). Further, according to this solution, it is possible to define the range of the volume ratio in which the size of the plate heat exchanger can be reduced. Further, in the seventh solution, an optimal range of the volume ratio can be defined.

Further, according to the eighth solution, a plate heat exchanger suitable for heat exchange between the refrigerant, which is a different fluid, and the sensible heat medium can be constituted.

[0033]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Although not shown, the plate heat exchanger of the present embodiment includes a water circulation path having a pump and circulating water therein, and a refrigerator having a compressor for cooling water. It is provided on the chiller that produces it. In this plate heat exchanger, a refrigerator and a water circulation path are connected, and constitute an evaporator of the refrigerator. And in the plate heat exchanger,
The refrigerant in the refrigerator and the water in the water circulation path exchange heat, thereby cooling the water to generate low-temperature cold water. That is, in the plate heat exchanger, the refrigerant as the first fluid and the water as the second fluid exchange heat.

As shown in FIGS. 1 and 2, the plate heat exchanger comprises a front frame (51) and a rear frame (5).
5), a plurality of first heat transfer plates (P1) and second heat transfer plates (P2) are alternately laminated and formed in a rectangular parallelepiped shape. The front frame (51), the rear frame (55) and the heat transfer plates (P1, P2,...) Are joined together by brazing, and the heat transfer plates (P1, P2,.
Between them, first passages (41) and second passages (42) are formed alternately.

The front frame (51) is provided with a total of four pipe connections, one at each of the four corners, and two refrigerant pipe connections (52a) located on the right side of the front frame (51) in FIG. , 52b), the two located on the left side are configured as water pipe connection portions (53a, 53b). Each refrigerant pipe connection (52a, 52b) communicates with the first passage (41), and each water pipe connection (53a, 53b) communicates with the second passage (42).
Is in communication with Although not shown, a refrigerant pipe of the refrigerator is connected to the refrigerant pipe connection part (52a, 52b), and a water pipe of the water circulation path is connected to the water pipe connection part (53a, 53b). I have.

As shown in FIGS. 3 and 4, the heat transfer plates (P1, P2) are rectangular plates made of a metal plate, and are formed into a predetermined shape by press working. Then, a first plate (P1) which is a first heat transfer plate and a second plate (P1) which is a second heat transfer plate
2) are formed in shapes different from each other.

At each of the four corners of the first and second plates (P1, P2), one circular opening (1) is provided.
~ 4) are formed. Specifically, in the first and second plates (P1, P2) shown in FIGS. 3 and 4, the first opening (1) is located at the lower right corner, the second opening (2) is located at the upper right corner, and the third opening (1). (3) is formed at the upper left corner, and the fourth opening (4) is formed at the lower left corner. That is, the first and second plates (P1, P
A first opening (1) and a fourth opening (4) are formed side by side at one end in the longitudinal direction of 2), and a second opening (2) and a third opening (3) are formed at the other end. They are formed side by side.

Around the openings (1 to 4) in the first and second plates (P1, P2), seal portions (6a, 7a, 6b, 7b) bulging in a predetermined direction with a fixed width are formed. Have been. Specifically, the first plate (P1) has convex seal portions (6) around the first opening (1) and around the second opening (2), respectively.
a, 6a) are formed, and concave seal portions (7a, 7a) are formed around the third opening (3) and around the fourth opening (4). In the second plate (P2), concave seal portions (7b, 7b) are formed around the first opening (1) and around the second opening (2), respectively. A convex seal portion (6b, 6b) is formed around the periphery and around the fourth opening (4). Each of the convex seal portions (6a, 6b) swells toward the near side of the paper surface of FIG. 3 or FIG. 4, and each of the concave seal portions (7a, 7b) of FIG.
Alternatively, it protrudes to the far side of the plane of FIG.

The outer peripheral portions of the first and second plates (P1, P2) are bent to the inner side of the paper in FIGS. 3 and 4 to form a peripheral portion (5). Then, in a state where the first plate (P1,...) And the second plate (P2,...) Are stacked, as shown in FIG. 2, the plate (P1, P2,. The inner surface of the peripheral portion (5) and the outer surface of the peripheral portion (5) of the plate (P1, P2,...) Located below come into contact with each other and are joined to each other.

The first passages (41) and the second passages (42) are alternately formed between the stacked plates (P1, P2,...). Specifically, in the stacking direction of the plates (P1, P2,...), The first passage (41) is formed above the second plate (P2) and below the first plate (P1). (42) is formed above the first plate (P1) and below the second plate (P2). Therefore, the first in FIG.
The near side of the plate (P1) on the paper surface is the second passage (42), and the far side is the first passage (41). In addition, the near side of the paper surface of the second plate (P2) in FIG. 4 is the first passage (41), and the far side is the second passage (42).

In the state where the above-mentioned plates (P1, P2,...) Are stacked, the lower plate (P1, P2,
2, ...) and the upper plate (P1,
P2,...) Are in contact with the concave seal portions (7a, 7b), and the contacting seal portions (6a, 7a, 6b, 7b) are joined together. Thereby, the refrigerant introduction path (31) corresponding to the first opening (1) of each plate (P1, P2,...) And the refrigerant outlet path (32) corresponding to the second opening (2) The water introduction path (33) corresponds to the third opening (3), and the water outflow path (3) corresponds to the fourth opening (4).
4) is formed respectively. The refrigerant pipe connection portions (52a, 52b) of the front frame (51) are connected to the refrigerant introduction path (3).
1) or only the first passage (41) is communicated by the refrigerant outlet passage (32), and the water pipe connection portions (53a, 53b) are connected to the water introduction passage (33).
Alternatively, it communicates only with the second passage (42) by the water outlet passage (34).

As shown in FIGS. 3 and 4, the first and second plates (P1, P2) have first and fourth openings (1, 1).
A corrugated plate-like corrugated portion (11, 21) is formed over almost the entire surface between the fourth and fourth and second and third openings (2, 3).

As shown in FIGS. 3 and 5, the corrugated portion (11) of the first plate (P1) has a concave portion (12) and a convex portion (13).
Are in a corrugated shape formed in a large number alternately in the longitudinal direction of the plate (P1). This wave shape has a convex part (1
3) An upper inclined portion (14a) formed so that the extension direction of the concave portion (12) is inclined upward toward the right in FIG. 3, and a downward inclined portion formed so as to be inclined downward. (14b). The corrugated portion (11) has an upper inclined portion (14a) in the right half of the first plate (P1) in FIG. 3, and a lower inclined portion (14) in the left half.
b) are formed, so-called herringbone shapes.

In particular, the first heat transfer passage (41a) and the second heat transfer passage (42a) form the corrugated portions (11, 21) of the first and second plates (P1, P2) in a predetermined shape. By,
They are formed so that their volumes are different from each other.

More specifically, as shown in FIG. 5, the corrugated portion (11) of the first plate (P1) is formed in a predetermined sectional shape. Specifically, the top surface of the convex portion (13) of the corrugated portion (11) is formed as a flat flat top surface (16) having a predetermined width: w1. The bottom surface of the concave portion (12) of the corrugated portion (11) is formed as a flat flat bottom surface (15) having a predetermined width: w2. The flat bottom surface (15) is formed such that its width: w2 is wider than the width: w1 of the flat top surface (16). Further, the flat top surface (16) and the flat bottom surface (15)
It is continued by a linearly extending slope (17).

The corrugated portion (11) of the first plate (P1) has a convex portion (1) at the center of amplitude of the corrugated portion (11).
It can be considered that the width w3 of 3) is different from the width w4 of the concave portion (12). In this case, the concave portion (12) and the convex portion (13) are formed such that the width: w4 of the concave portion (12) is wider than the width: w3 of the convex portion (13).

On the other hand, as shown in FIGS. 4 and 6, the corrugated portion (21) of the second plate (P2) has a concave portion (22) and a convex portion (23) in the longitudinal direction of the plate (P2). It has a corrugated shape formed in a large number alternately. This corrugated shape is similar to the corrugated portion (11) of the first plate (P1), and the upwardly inclined portion (24) in which the extending direction of the convex portion (23) and the concave portion (22) is different
a) and a downwardly inclined portion (24b). The corrugated portion (21) has a so-called herringbone shape in which a lower inclined portion (24b) is formed in the right half of the second plate (P2) and an upper inclined portion (24a) is formed in the left half of FIG. Has become.

As shown in FIG. 6, the second plate (P
The corrugated portion (21) of 2) is formed in a predetermined sectional shape. Specifically, the top surface of the convex portion (23) of the corrugated portion (21)
It is formed on a flat flat top surface (26) having a predetermined width: w2. The bottom surface of the concave portion (22) of the corrugated portion (21) is formed as a flat flat bottom surface (25) having a predetermined width: w1. That is, the flat top surface (26) has the same width as the flat bottom surface (15) of the first plate (P1), and the flat bottom surface (15)
Has the same width as the flat top surface (16) of the first plate (P1). The flat top surface (26) is formed such that its width: w2 is wider than the width: w1 of the flat top surface (26). Further, the flat top surface (26) and the flat bottom surface (25) are connected by a slope (27) extending linearly.

The corrugated portion (21) of the second plate (P2) has a concave portion (2) at the center of amplitude of the corrugated portion (21).
It can also be considered that the width w3 of 2) and the width w4 of the convex portion (23) are formed differently. In this case, the concave portion (22) and the convex portion (23) are formed such that the width: w4 of the convex portion (23) is wider than the width: w3 of the concave portion (22).

As described above, the first plate (P1) and the second plate (P2) are alternately stacked. In this state, the protrusions (13,...) Of the first plate (P1,...) Cross each other and abut on the recesses (22,...) Of the adjacent one of the second plates (P2). With both plates (P1, P2,
…) Are joined together. In addition, the first plate (P
) Of the second plate (P2), which is adjacent to the second plate (P2) of the other, intersects and abuts with each other. …) Are joined together.

That is, as shown in FIG. 7, the flat top surface (16) of the convex portion (13) of the first plate (P1) is connected to the flat bottom surface (25) of the concave portion (22) of the second plate (P2). And the first
The flat bottom (15) of the recess (12) of the plate (P1)
It is joined to the flat top surface (26) of the projection (23) of the plate (P2). The portion of the first passage (41) between the corrugated portions (11, 21) of the adjacent plates (P1, P2) is configured as a first heat transfer passage (41a), while the second heat passage (41a) is formed. Aisle (4
2), the corrugated part (11,2) of the adjacent plate (P1, P2)
The portion between 1) is configured as a second heat transfer passage (42a).

FIG. 7 shows the first plate (P) shown in FIG.
1) and the second plate (P2) shown in FIG.
FIG. 2 shows a cross section taken along the line CC in a stacked state. However, as described above, each plate (P1, P2,
..) And the protruding portions (13, 23,...) Intersect and abut, so that the cross section shown in FIG. 7 does not actually exist.
Therefore, FIG. 7 is for the sake of understanding, and does not show an actual cross section.

As described above, the first heat transfer passage (41a)
The second heat transfer passage (42a) and the second heat transfer passage (42a) are formed so as to have different volumes from each other. In this case, the volume ratio of the second heat transfer passage (42a) to the first heat transfer passage (41a) is set to be larger than 1. It is desirable to be large and 2.7 or less, more preferably 1.
It is good to be 4 or more and 1.8 or less.

The reason for setting the volume ratio will be described with reference to FIG. The horizontal axis of FIG.
The volume ratio of the second heat transfer passage (42a) to the first heat transfer passage (41a) is shown. The vertical axis represents the number of heat transfer plates (P1, P2) required in the present embodiment with respect to the number of heat transfer plates required in the conventional case when design requirements such as the heat exchange amount and pressure loss are satisfied. ) Indicates the ratio of the number of sheets. For example, when the value of the vertical axis is 0.9, it is shown that 90 heat transfer plates (P1, P2) may be used in the present embodiment, whereas 100 heat transfer plates are conventionally required. I have.

According to FIG. 8, the first heat transfer passage (41)
If the volume of the second heat transfer passage (42a) is made larger than that of a), the number of necessary heat transfer plates (P1, P2) once decreases, but increases from a certain point, and eventually the conventional heat transfer plate (P1, P2) increases. More heat transfer plates (P1, P2) are required. Therefore, in the present embodiment, the volume ratio of the second heat transfer passage (42a) to the first heat transfer passage (41a) is larger than 1 and 2.7 or less, which is a range in which the number of plates can be reduced. It is desirable to be within the range. Further, it is desirable that the number of plates be in the range of 1.4 or more and 1.8 or less which can minimize the number of plates.

-Operating operation- In the chiller, when the compressor is driven, the refrigerant circulates in the refrigerant pipe of the refrigerator, and when the pump is driven, water circulates in the water pipe of the water circulation path. Then, the refrigerant of the refrigerator and the water of the water circuit flow into the plate heat exchanger.

More specifically, the refrigerant of the refrigerator flows into the plate heat exchanger through the refrigerant pipe connection (52a). This refrigerant passes through the refrigerant introduction path (31) and is diverted to each of the first
It flows into the passage (41). Thereafter, the refrigerant flows to the first heat transfer passage (41a) of the first passage (41). On the other hand, the water in the water circulation path flows into the plate heat exchanger through the water pipe connection (53a). This water passes through the water channel (33)
It is split and flows into each second passage (42). Thereafter, the refrigerant flows to the second heat transfer passage (42a) of the second passage (42).

The refrigerant in the first heat transfer passage (41a) and the water in the second heat transfer passage (42a) exchange heat, the refrigerant evaporates to a gaseous refrigerant, and the water is cooled to produce low-temperature cold water. Becomes Then, the gas refrigerant in each of the first passages (41) flows to the refrigerant outlet path (32) and joins, and flows out of the plate heat exchanger through the refrigerant pipe connection part (52b). On the other hand, the cold water in the second passage (42) flows into the water outlet path (34), merges, and flows out of the plate heat exchanger through the water pipe connection portion (53b). At this time, the flow of the refrigerant in the first heat transfer passage (41a) and the flow of water in the second heat transfer passage (42a) are violently disturbed, so that heat transfer is promoted by forced convection.

In the plate heat exchanger, the first
The heat transfer passage (41a) is configured to have a smaller volume than the second heat transfer passage (42a). For this reason, the average flow velocity of the refrigerant in the first heat transfer passage (41a) is increased and the heat transfer coefficient on the refrigerant side is increased as compared with the case where the volumes of the heat transfer passages are equal as in the related art. Further, the average flow velocity of water in the second heat transfer passage (42a) decreases, and the heat transfer coefficient on the water side decreases.
Here, when the conventional plate heat exchanger was used for the chiller, the heat transfer coefficient on the water side was about 3 to 4 times the heat transfer coefficient on the refrigerant side. Therefore, according to the present embodiment, the heat transfer coefficient on the water side, which was conventionally high, decreases, but the heat transfer coefficient on the refrigerant side, which has been low conventionally, rises.

In the present embodiment, the average flow velocity of the refrigerant in the first heat transfer passage (41a) increases, and the average flow velocity of water in the second heat transfer passage (42a) decreases, as compared with the prior art. Therefore, the pressure loss of the refrigerant in the first heat transfer passage (41a) increases, but the pressure loss of water in the second heat transfer passage (42a) decreases. Here, in the chiller, the refrigerant is circulated by a compressor, and the water is circulated by a pump.
For this reason, it is desired to reduce the pressure loss on the water side in the plate heat exchanger, but the plate heat exchanger of the present embodiment meets such requirements.

According to the first embodiment, the volume of the first heat transfer passage (41a) is made smaller than the volume of the second heat transfer passage (42a), so that the heat transfer on the refrigerant side is achieved. The imbalance between the heat transfer coefficient and the water side heat transfer coefficient can be reduced, and the heat transmission coefficient can be improved. Further, since the volume of the second heat transfer passage (42a) is larger than that of the conventional heat transfer passage, the water-side pressure loss can be reduced. For this reason, the required number of heat transfer plates (P1, P2) can be reduced while maintaining the heat exchange amount and the water-side pressure loss equal to those in the related art. As a result, the size of the plate heat exchanger can be reduced, and the cost can be reduced.

In this embodiment, the corrugated portions (11, 21) are formed in the first and second plates (P1, P2). This is common to that of the conventional heat transfer plate in that the protrusions are alternately formed. Therefore, in the first and second heat transfer passages (41a, 42a), it is possible to promote heat transfer by forced convection as in the related art. Further, the workability of the heat transfer plates (P1, P2) can be maintained at the same level as before.

-Modification of Embodiment 1-In the above-described embodiment, the predetermined flat bottom surface () is formed on the concave portions (12, 22) and the convex portions (13, 23) of the first and second plates (P1, P2). 15, 25) and a flat top surface (16, 26). That is, the bottom surface of the concave portion (12, 22) and the top surface of the convex portion (13, 23) are made flat. On the other hand, the bottom surface of the concave portion (12, 22) and the top surface of the convex portion (13, 23) may be formed in an arc shape.

[0064]

Second Embodiment A second embodiment of the present invention is the same as the first embodiment except that the shapes of the corrugated portions (11, 21) of the first and second plates (P1, P2) are changed.

The corrugated portion (11) of the first plate (P1) is formed by alternately arranging a large number of concave portions (12) and convex portions (13).
It has the same herringbone shape as the first plate (P1) of the first embodiment.

The corrugated portion (11) of the first plate (P1)
Are formed in a sectional shape as shown in FIG. Specifically, the top surface of the convex portion (13) of the corrugated portion (11) is formed as a flat flat top surface (16) having a constant width. The bottom surface of the concave portion (12) of the corrugated portion (11) is formed as a flat flat bottom surface (15) having a constant width. The flat bottom surface (15) is formed to have the same width as the flat top surface (16).

The flat top surface (16) and the flat bottom surface (15) are continuous by a slope (17). This slope (17)
Is composed of a steep slope (17a) and a gentle slope (17b), and has a shape slightly bulging upward in FIG. 9, that is, toward the first passage (41). Specifically, a steep slope (17a) is formed continuously with the flat bottom surface (15), and a gentle slope (17b) is formed continuously with the flat top surface (16) and the steep slope (17a).

On the other hand, the corrugated portion (21) of the second plate (P2)
A large number of concave portions (22) and convex portions (23) are formed alternately side by side, and have the same herringbone shape as the second plate (P2) of the first embodiment.

The corrugated portion (21) of the second plate (P2)
Are formed in a sectional shape as shown in FIG. Specifically, the top surface of the convex portion (23) of the corrugated portion (21) is formed as a flat flat top surface (26) having a constant width. The bottom surface of the concave portion (22) of the corrugated portion (21) is formed as a flat flat bottom surface (25) having a constant width. This flat bottom (25)
It is formed so as to have the same width as the flat top surface (26).

The flat top surface (26) and the flat bottom surface (25) are continuous by a slope (27). This slope (27)
Consists of a steep slope (27a) and a gentle slope (27b).
Of the first passage (41) is slightly swelled downward. Specifically, a steep slope (27a) is formed continuously with the flat bottom surface (25), and the flat top surface (26) is formed.
A gentle slope (27b) is formed continuously from the steep slope (27a).

The first plate (P1) and the second plate (P2) are alternately laminated in the same manner as in the first embodiment.
Each plate (P1, P2,...) Is an abutting portion of a convex portion (13, 23,...) Or a concave portion (12, 22,.
2) is joined. Then, as shown in FIG.
Between each plate (P1, P2, ...), the first passage (41) and the second passage
A passage (42) is formed, and the first passage (41) is configured to have a smaller volume than the second passage (42).
Therefore, according to the present embodiment, the same effects as those of the first embodiment can be obtained.

Modification of Embodiment 2 In this embodiment, the steep slopes (17a, 27a) and the gentle slopes (17b, 2b)
A slope (17, 27) is formed by 7b), whereby the slope (17, 27) has a shape bulging toward the first passage (41). On the other hand, the slope (17, 27) is connected to the first passage (41).
It may be formed in an arc shape bulging to the side.

[0073]

Third Embodiment A third embodiment of the present invention is the same as the first embodiment except that the shapes of the corrugated portions (11, 21) of the first and second plates (P1, P2) are changed.

The corrugated portion (11) of the first plate (P1) is formed by alternately arranging a large number of concave portions (12) and convex portions (13).
It has the same herringbone shape as the first plate (P1) of the first embodiment.

The corrugated portion (11) of the first plate (P1)
Is formed in a sectional shape as shown in FIG. Specifically, the top surface of the convex portion (13) of the corrugated portion (11) is formed as a flat flat top surface (16) having a constant width. The bottom surface of the concave portion (12) of the corrugated portion (11) is formed as a flat flat bottom surface (15) having a constant width. This flat bottom (15)
It is formed so as to have the same width as the flat top surface (16).

The flat top surface (16) and the flat bottom surface (15) are continued by a linearly extending slope (17).
On the slope (17), a large number of dimples (18) are formed in a row along the extension direction of the concave portion (12) and the convex portion (13). The dimple (18) is formed to protrude upward in FIG. 12, that is, toward the first passage (41), and forms a protruding protrusion.

On the other hand, the corrugated portion (21) of the second plate (P2)
A large number of concave portions (22) and convex portions (23) are formed alternately side by side, and have the same herringbone shape as the second plate (P2) of the first embodiment.

The corrugated portion (21) of the second plate (P2)
Are formed in a sectional shape as shown in FIG. Specifically, the top surface of the convex portion (23) of the corrugated portion (21) is formed as a flat flat top surface (26) having a constant width. The bottom surface of the concave portion (22) of the corrugated portion (21) is formed as a flat flat bottom surface (25) having a constant width. This flat bottom (25)
It is formed so as to have the same width as the flat top surface (26).

The flat top surface (26) and the flat bottom surface (25) are connected by a linearly extending inclined surface (27).
A large number of dimples (28) are formed on the slope (27) in a row along the extension direction of the concave portion (22) and the convex portion (23). The dimple (28) is formed so as to protrude downward in FIG. 13, that is, toward the first passage (41) side, and forms a protruding protrusion.

The first plate (P1) and the second plate (P2) are alternately laminated as in the first embodiment.
Each plate (P1, P2,...) Is an abutting portion of a convex portion (13, 23,...) Or a concave portion (12, 22,.
2) is joined. Then, as shown in FIG.
Between each plate (P1, P2, ...), the first passage (41) and the second passage
A passage (42) is formed, and the first passage (41) is configured to have a smaller volume than the second passage (42).
Therefore, according to the present embodiment, the same effects as those of the first embodiment can be obtained.

[Brief description of the drawings]

FIG. 1 is a schematic exploded perspective view of a plate heat exchanger according to a first embodiment.

FIG. 2 is a schematic sectional view showing an AA section in FIG. 1;

FIG. 3 is a front view of a first plate according to the first embodiment.

FIG. 4 is a front view of a second plate according to the first embodiment.

FIG. 5 is a sectional view showing a BB section in FIG. 3;

FIG. 6 is a cross-sectional view showing a CC section in FIG. 4;

FIG. 7 is a schematic cross-sectional view of a first plate and a second plate in a stacked state according to the first embodiment.

FIG. 8 is a correlation diagram showing a relationship between the volume ratio of the heat transfer passage and the number of stacked plates.

FIG. 9 is a diagram corresponding to FIG. 5 in the second embodiment.

FIG. 10 is a diagram corresponding to FIG. 6 in the second embodiment.

FIG. 11 is a diagram corresponding to FIG. 7 in the second embodiment.

FIG. 12 is a diagram corresponding to FIG. 5 in the third embodiment.

FIG. 13 is a diagram corresponding to FIG. 6 in the third embodiment.

FIG. 14 is a diagram corresponding to FIG. 7 in the third embodiment.

[Explanation of symbols]

 (P1) 1st plate (heat transfer plate) (11) Corrugated section (12) Concave section (13) Convex section (15) Flat bottom (16) Flat top (17) Slope (18) Dimple (bulging projection) ( P2) 2nd plate (heat transfer plate) (21) Corrugated portion (22) Concave portion (23) Convex portion (25) Flat bottom surface (26) Flat top surface (27) Slope (28) Dimple (bulging protrusion) (41 ) 1st passage (41a) 1st heat transfer passage (42) 2nd passage (42a) 2nd heat transfer passage

Claims (8)

[Claims] A plurality of first heat transfer plates (P1) and a plurality of second heat transfer plates (P2) are alternately stacked, and between the stacked heat transfer plates (P1, P2). The first fluid (41) and the second passage (41) through which the first fluid flows so that the first fluid and the second fluid exchange heat through the heat transfer plates (P1, P2).
The second passages (42) through which the fluid flows are formed alternately, and the heat transfer plates (P1, P2) have a large number of recesses (12, 22).
And the convex portions (13, 23) are formed alternately. Corrugated portions (11, 21) are formed. The corrugated portions (11, 21) of the two heat transfer plates (P1, P2) are formed of one heat transfer plate. The concave portion (12) of (P1) and the convex portion (23) of another heat transfer plate (P2) opposed to the concave portion (12) intersect and abut each other, and the heat transfer plate (P1) The protrusion (13) and another heat transfer plate (P
The heat transfer plates (P1, P2) are formed so that the concave portions (22) of (2) intersect and contact each other.
The first passage (4) corresponding to the heat transfer characteristic between the fluid and the second fluid.
A plate heat exchanger wherein the volume of 1) and the volume of the second passage (42) are different from each other. 2. The plate heat exchanger according to claim 1, wherein the corrugated portion (11) of the first heat transfer plate (P1) has a width of a concave portion (12) at the center of amplitude of the corrugated portion (11). Is convex (13)
The width of the corrugated portion (21) of the second heat transfer plate (P2) is greater than the width of the concave portion (22) at the center of the amplitude of the corrugated portion (21).
A plate heat exchanger formed to be wider than the width of the plate. 3. The plate type heat exchanger according to claim 1, wherein the corrugated portion (11) of the first heat transfer plate (P1) has a flat top having a predetermined width. The flat bottom (15) is formed on the surface (16), and the bottom surface of the recess (12) is formed on a flat flat bottom (15) wider than the flat top. In the corrugated portion (21) of the second heat transfer plate (P2), the bottom surface of the concave portion (22) is formed as a flat flat bottom surface (25) having a predetermined width while being continuous by the linearly extending slope (17). The top surface of the projection (23) is formed on a flat flat top surface (26) wider than the flat top surface, and the flat top surface (26) and the flat bottom surface (25) extend linearly. Plate heat exchanger connected by slope (27). 4. The plate type heat exchanger according to claim 1, wherein the corrugated portion (11) of the first heat transfer plate (P1) has a flat top having a predetermined width. The bottom surface of the recess (12) is formed on a flat flat bottom surface (15) having a predetermined width, and the flat top surface (16) and the flat bottom surface (15) are formed in the first passage (41).
On the side of the second heat transfer plate (P2), the bottom surface of the concave portion (22) is formed as a flat flat bottom surface (25) having a predetermined width, while the bottom surface of the second heat transfer plate (P2) is continuous. The top surface of the projection (23) is formed on a flat flat top surface (26) having a predetermined width, and the flat top surface (26) and the flat bottom surface (25) are connected to the first passage (41).
A plate-type heat exchanger connected by a slightly bulging slope (27) to the side. 5. The plate type heat exchanger according to claim 1, wherein the corrugated portion (11) of the first heat transfer plate (P1) has a flat top having a predetermined width. The bottom surface of the concave portion (12) is formed on a flat flat bottom surface (15) having a predetermined width, and the flat top surface (16) and the flat bottom surface (15) extend linearly. 17), the slope (17) has a number of bulging protrusions (18) bulging in a protruding manner toward the first passage (41) side, while the second heat transfer plate (P2) has In the corrugated portion (21), the bottom surface of the concave portion (22) is formed on a flat flat bottom surface (25) having a predetermined width, and the top surface of the convex portion (23) is formed on a flat flat top surface (26) having a predetermined width. The flat top surface (26) and the flat bottom surface (25) are continued by a linearly extending slope (27), and the slope (27) protrudes in a projecting manner toward the first passage (41). Many Plate heat exchanger has a bulging protrusion (28). 6. The plate heat exchanger according to claim 1, wherein the first heat transfer passage formed by the corrugated portions (11, 21) of the heat transfer plates (P1, P2) in the first passage (41). (41a), the heat transfer plates (P1, P
A plate heat exchanger configured such that the volume ratio of the second heat transfer passage (42a) formed by the corrugated portions (11, 21) of 2) is larger than 1 and 2.7 or less. . 7. The plate heat exchanger according to claim 1, wherein the first heat transfer passage formed by the corrugated portions (11, 21) of the heat transfer plates (P1, P2) in the first passage (41). (41a), the heat transfer plates (P1, P
Plate type heat exchange configured such that the volume ratio of the second heat transfer passage (42a) formed by the corrugated portions (11, 21) of 2) is not less than 1.4 and not more than 1.8. vessel. 8. The plate heat exchanger according to claim 1, wherein a small volume of the first passage (41) and the second passage (42) has a phase within the passage. A plate heat exchanger in which a changing refrigerant flows and a sensible heat medium that does not change phase flows in a passage having a large volume.