JP3039462B2 - Plate heat exchanger - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a plate heat exchanger, and more particularly to a plate heat exchanger suitable for producing supercooled water.

[0002]

2. Description of the Related Art Conventionally, various heat exchangers have been used in air conditioners, refrigeration units, refrigeration units, and the like. Among those heat exchangers, the plate heat exchanger is
It is known as a compact heat exchanger having a large heat transfer rate.

As shown in FIG. 24, the plate heat exchanger is configured by stacking a plurality of heat transfer plates (P) between two frames (f1) and (f2).

The heat transfer plate (P) is made of a metal flat plate, and when laminated, the peripheral edges of the heat transfer plates come into contact with each other and flow paths (A, B, A, B) are formed between the heat transfer plates. ,...) Are formed, and the contact portions are joined by brazing to be integrally formed.

In addition, openings (a, b, c, d) are provided at the four corners of the heat transfer plate (P), and seals (e) are provided around the openings, whereby Flow path
A fluid passage communicating only with (A) and a fluid passage communicating only with the other flow path (B) are formed.In FIG. 24, the fluid flows through the flow path (A) as indicated by a solid arrow. As shown by the dashed arrows, the fluid flows through the flow path (B), and both flow paths (A),
The fluids flowing through (B) are configured to exchange heat with each other.

By the way, for example, Japanese Patent Application Laid-Open No. 4-251177
As disclosed in Japanese Unexamined Patent Publication, conventionally, in view of reducing the power demand at the time of the peak of the cooling load and expanding the power demand at the off-peak time, a so-called dynamic ice storage type air conditioner is used. Have been. In this type of air conditioner, when the cooling load is off-peak, slurry ice is generated and stored in a heat storage tank, and the ice is used as a cooling heat source during the peak of the cooling load.

[0007] Such slurry ice is generated by eliminating the supercooled state of the supercooled water. In general,
Supercooled water is generated by cooling low-temperature water using latent heat of vaporization of the refrigerant flowing through the refrigerant circuit.

[0008]

When a plate heat exchanger is used as an evaporator for generating supercooled water in the above air conditioner, the flow path formed by the heat transfer plate (P) flows through the refrigerant. And water flow to perform heat exchange.
However, as shown in FIG. 22, the inlets (a) and (c) and the outlets (b) and (d) of the fluid performing heat exchange are provided at the four corners of the heat transfer plate (P). In addition, the flow velocity of the fluid in each flow path is not uniform in the width direction of the flow path, and causes a drift.

Further, in the flow path of one fluid, a dead water area where the one fluid does not flow much is generated around the inflow port and the outflow port of the other fluid. The flow velocity of the fluid flowing in the flow channel in the width direction is not uniform, and a drift occurs. Then, due to the above-described drift of the fluid, the following problem occurs.

That is, as shown in FIG. 22, for example, when water drift occurs, the flow velocity of water on the left side of FIG. 22 is high, and the flow velocity of water on the right side of FIG. 22 is low. Is lower than the left side region, and becomes uneven in the width direction of the flow path.

On the other hand, when the temperature of the supercooled water falls below a certain limit temperature, the supercooled state is eliminated. Further, the portion that has been supercooled and iced becomes seed ice, which is a factor for eliminating the supercooled state of other supercooled water. Therefore, in order to maintain the supercooled state of the supercooled water, it is necessary to maintain all the regions at a temperature higher than the limit temperature.

In order to efficiently generate supercooled water, it is desirable to make the average temperature of the water as low as possible. Therefore, in order to efficiently generate the supercooled water while maintaining the supercooled state, it is preferable to equalize the temperature of the supercooled water in the heat exchanger. For example, when supercooled water having an average temperature of −3 ° C. is generated, all regions have a temperature of −3 ° C., compared to a state in which the temperature distribution is locally nonuniform and the temperature distribution is uneven. A uniform state is preferred. This is because, assuming that the limit temperature is −4 ° C., in such a non-uniform state, icing occurs in a region of −4 ° C. or less.

However, as described above, in the conventional plate heat exchanger, the temperature distribution of the supercooled water was not uniform due to the drift of the fluid flowing through each flow path, as shown in FIG. Therefore, in order to prevent blockage of the flow path due to elimination of the supercooling, the temperature of the lowest temperature region of the supercooled water needs to be higher than the above-mentioned limit temperature. As a result, the average temperature of the supercooled water could not be lowered, and there was a limit to improving the efficiency of producing slurry ice.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and an object of the present invention is to correct the nonuniform temperature distribution of a heat medium due to the drift of the heat medium and the refrigerant, and to reduce the excess of the heat medium. The purpose is to stabilize the cooling state.

[0015]

The object of the present invention is to achieve the above object by changing the positions of the fluid inlet and the fluid outlet to eliminate the fluid drift in each flow path. .

Specifically, the means taken by the invention of claim 1 is that a plurality of heat transfer plates (P1, P2,...)
A heat medium flow path (65) through which the heat medium flows, and a main refrigerant flow path (66a) through which the refrigerant flows are formed alternately, and the heat exchanger body (5A) so that the heat medium and the refrigerant perform heat exchange. Is intended for a plate-type heat exchanger configured with. The heat exchanger body (5A) has a heat medium inflow path (61) and a heat medium outflow path penetrating through each heat transfer plate (P1, P2,...) And communicating with the heat medium flow path (65). (62) are formed at both ends in the longitudinal direction of the heat transfer plates (P1, P2,...) And at the center in the width direction of the heat transfer plates (P1, P2,. , Each heat transfer plate (P1,
P2, ...) and the main refrigerant inflow path (63a) and the main refrigerant outflow path (64a) communicating with the main refrigerant flow path (66a) form a main refrigerant flow path (66
a) at both ends of the refrigerant flow direction and the heat
More heat transfer than the medium inflow path (61) and heat medium outflow path (62)
(P1, P2,...) Are formed near the center in the longitudinal direction .

According to the present invention, the heat medium flows into the heat medium flow path (65) from the heat medium inflow path (61). That
In this case, the heat medium inflow passage (61) is wider than the width of the heat transfer plates (P1, P2, ...).
Since the heat medium is formed at the center of the heat medium, the heat medium flows from the center of the heat medium flow path (65) in the width direction of the heat medium flow path (65). Then, while performing heat exchange with the refrigerant flowing through the main refrigerant flow path (66a), the heat medium flows through the heat medium flow path (65), and the heat medium outflow path (62)
Leaked to At this time, the heat medium outlet channel (62) is
(P1, P2, ...) formed in the center in the width direction,
The medium flows from the center of the heat medium flow path (65) to the heat medium outflow path (62).
Leaked to On the other hand, the refrigerant flows into the main refrigerant flow path (66a) from the main refrigerant flow path (63a). Then, the heat medium flow path (6
5) Main refrigerant flow path (66a) while performing heat exchange with the heat medium flowing through
Flows out of the main refrigerant outflow passage (64a).

The invention according to claim 2 is characterized in that a heat medium flow path (65) through which a heat medium flows and a refrigerant flow between a plurality of stacked heat transfer plates (P1, P2,...). The flowing refrigerant passages are alternately formed to constitute the heat exchanger main body (5A) so that the heat medium and the refrigerant perform heat exchange, and the refrigerant passage is a heat medium in the heat medium passage (65). Corresponding to the upstream side and the downstream side of the medium, a sub-refrigerant flow path (66b) and a main refrigerant flow path (66a) are formed in order, and the heat exchanger body (5A) has a heat transfer plate. (P
1, P2,...) And communicate with the main refrigerant flow path (66a), the main refrigerant inflow path (63a) and the main refrigerant outflow path (64a) at both ends of the main refrigerant path in the refrigerant flow direction. The sub-coolant inflow passage (63b) and the sub-refrigerant outflow passage which penetrate through each heat transfer plate (P1, P2,...) And communicate with the sub-refrigerant circuit are formed in the heat exchanger body (5A). (64b) are formed at both ends of the sub-refrigerant passage in the flow direction of the refrigerant, while the heat exchanger body (5A) penetrates the heat transfer plates (P1, P2,...). and the heat medium inlet channel communicating with the heat medium flow (65) and the heat medium outlet passage and (62) (61), and transfer a longitudinal end portions of the heat transfer plate (P1, P2, ...) The heat plates (P1, P2,...) Are formed at the center in the width direction .

According to the present invention, the heat medium flows into the heat medium flow path (65) from the heat medium inflow path (61). That
In this case, the heat medium inflow passage (61) is wider than the width of the heat transfer plates (P1, P2, ...).
Since the heat medium is formed at the center of the heat medium, the heat medium flows from the center of the heat medium flow path (65) in the width direction of the heat medium flow path (65). And the main refrigerant flow path (66a) and the sub refrigerant flow path (66b)
Flows through the heat medium flow path (65) while performing heat exchange with the refrigerant flowing through the heat medium, and flows out to the heat medium outflow path (62). At that time, the heat medium
The path (62) is formed at the center in the width direction of the heat transfer plates (P1, P2, ...).
As a result, the heat medium flows out of the center of the heat medium flow path (65) to the heat medium outflow path (62). On the other hand, the refrigerant flowing from the main refrigerant inflow port flows through the main refrigerant flow path (66a) while performing heat exchange with the heat medium flowing through the heat medium flow path (65), and flows out of the main refrigerant outflow path (64a), The refrigerant flowing from the sub-refrigerant inlet flows through the sub-refrigerant channel (66b) while exchanging heat with the heat medium flowing through the heat medium channel (65), and flows out from the sub-refrigerant outlet channel (64b).

The means adopted by the invention of claim 3 is the main refrigerant inflow passage according to the invention of claim 1 or 2.
(63a) is provided at the center in the width direction of the heat transfer plates (P1, P2,...) .

According to the present invention, the refrigerant flows from the main refrigerant flow passage (63a) into the main refrigerant flow path (66a). That
When the main refrigerant flow path (66a) is wider than the width of the heat transfer plates (P1, P2, ...)
Since it is formed at the center in the direction, the refrigerant flows from the center of the main refrigerant flow path (66a) in the width direction of the main refrigerant flow path (66a). Then, it flows through the main refrigerant flow path (66a) while performing heat exchange with the heat medium flowing through the heat medium flow path (65), and flows out from the main refrigerant outflow path (64a).

The means adopted by the invention according to claim 4 is the same as the invention described in claim 1 or 2, except that the heat medium flow path (6
5), an outlet-side closing portion (74) for blocking the flow of the heat medium so that the width of the heat medium flow path (65) becomes narrower toward the heat medium outflow path (62), It is formed corresponding to the peripheral portion of (64a).

According to the present invention, the heat medium flow path
In (65), the heat medium does not flow through the outlet-side closing portion (74), and the refrigerant flowing through the main refrigerant flow path (66a) at a position corresponding to the outlet-side closing portion (74) is heat Does not exchange heat with the medium.

According to a fifth aspect of the present invention, in the fourth aspect of the present invention, the width of the heat medium flow path (65) is provided in the heat medium flow path (65). Inlet-side obstruction that blocks the flow of heat medium so as to narrow toward (61)
(73) is formed corresponding to the peripheral portion of the main refrigerant inflow passage (63a).

According to the present invention, the heat medium passage
In (65), the heat medium does not flow through the inlet-side closing part (73) and the outlet-side closing part (74), and also corresponds to the inlet-side closing part (73) and the outlet-side closing part (74). The refrigerant flowing through the main refrigerant flow path (66a) at the position does not exchange heat with the heat medium.

According to a sixth aspect of the present invention, in the third aspect of the present invention, the width of the heat medium flow path (65) is provided in the heat medium flow path (65). Exit side blocking part that blocks the flow of the heat medium so as to narrow toward (62)
(74) is formed corresponding to the peripheral portion of the main refrigerant outflow passage (64a).

According to the present invention, the refrigerant flows into the main refrigerant flow path (66a) from the main refrigerant flow path (63a), and flows from the center of the main refrigerant flow path (66a) to the main refrigerant flow path (66a). ), While flowing in the width direction, the heat medium flowing through the heat medium flow path (65) does not flow through the outlet side closing portion (74). The refrigerant performs heat exchange with the heat medium flowing through the heat medium flow path (65), and at the position corresponding to the outlet-side closing portion (74), does not perform heat exchange with the heat medium, and It flows through the flow path (66a) and flows out of the main refrigerant outflow path (64a).

[0028]

As described above, according to the first aspect of the present invention, the heat transfer path between the heat medium inflow path (61) and the heat medium outflow path (62) is provided.
Since the heat medium is formed at the center in the width direction of the rates (P1, P2, ...) , the heat medium flows from the center of the heat medium flow path (65) to the heat medium flow path (65).
And spreads evenly in the width direction. For this reason, in each part of the heat medium flow path (65), the heat medium flows in the same direction. Accordingly, the flow velocity of the heat medium in the width direction of the heat medium flow path (65) can be made uniform, so that the temperature of the heat medium in the width direction of the heat medium flow path (65) can be made uniform. As a result, when the supercooled water is generated, the supercooling due to the temperature impact can be prevented from being eliminated, while the supercooling temperature can be lowered, and the ice generation efficiency can be improved.

According to the second aspect of the present invention, in addition to the effects of the first aspect, the heat medium flowing through the heat medium flow path (65) includes a main refrigerant flow path (66a) and a sub refrigerant flow. The heat can be exchanged with the refrigerant flowing through the two different refrigerant channels of the passage (66b). As a result, for example, when used in a dynamic ice storage air conditioner, the preheater (11), the mixer (33), and the supercooling heat exchanger (55) can be integrally formed. The size of the air conditioner can be reduced.

According to the third aspect of the present invention, the main refrigerant inflow passage (63a) is formed at the center in the width direction of the heat transfer plates (P1, P2,...) . Main refrigerant flow path
Since it is possible to uniformly spread and flow in the width direction of the main refrigerant flow path (66a) from the central portion of (66a), the flow velocity of the refrigerant in the width direction of the main refrigerant flow path (66a) is made uniform. be able to. As a result, since the amount of heat exchange between the refrigerant and the heat medium in the width direction of the main refrigerant flow path (66a) can be made uniform, it is possible to more reliably prevent the supercooled state of water from being eliminated, and The supercooling temperature can be reliably reduced.

According to the fourth aspect of the present invention, since the outlet-side closing portion (74) is formed, it is possible to prevent the occurrence of the conventional dead water area. Therefore, the flow velocity of the heat medium in the heat medium flow path (65) can be made uniform, and the heat medium flow path (6
5) Since the temperature distribution of the heat medium in the width direction can be more accurately uniformed in the width direction, it is possible to more reliably prevent the supercooled state of water from being eliminated and to surely lower the supercooled temperature. Can be.

According to the fifth aspect of the present invention, since the inlet-side closing portion (73) is formed in addition to the outlet-side closing portion (74), the occurrence of the conventional dead water area can be prevented. For this reason, the flow velocity of the heat medium in the heat medium flow path (65) can be made uniform, and the temperature distribution of the heat medium in the width direction of the heat medium flow path (65) can be made more uniform. Can be.

According to the sixth aspect of the present invention, the main refrigerant inflow passage (63a) is formed at the center in the width direction of the main refrigerant flow path (66a). Since it is possible to uniformly spread and flow in the width direction of the main refrigerant flow path (66a), the flow velocity of the refrigerant in the width direction of the main refrigerant flow path (66a) can be made uniform. In addition, the formation of the outlet-side closing portion (74) can prevent the occurrence of the conventional dead water area. Thereby, the amount of heat exchange between the refrigerant and the heat medium in the width direction of the main refrigerant flow path (66a) can be made uniform, and the flow velocity of the heat medium in the heat medium flow path (65) can be made uniform. As a result, since the temperature distribution of the heat medium in the width direction of the heat medium flow path (65) can be more accurately uniformed, it is possible to more reliably prevent the supercooled state of water from being eliminated. In addition, the supercooling temperature can be reliably reduced.

[0034]

Embodiment 1 Hereinafter, embodiments of the present invention will be described with reference to the drawings.

-Configuration of Air Conditioner (10)-The air conditioner (10) equipped with the plate heat exchanger according to the first embodiment includes a refrigerant circulation circuit (20) and a water circulation circuit (30). ing.

The refrigerant circuit (20) includes a compressor (21), a four-way switching valve (22), an outdoor heat exchanger (23), an outdoor electric expansion valve (EV-1),
An indoor electric expansion valve (EV-2), an indoor heat exchanger (24), and an accumulator (25) are provided with a reversible operable main refrigerant circuit (27) configured by being connected by a refrigerant pipe (26). I have. Further, the refrigerant circulation circuit (20) is provided with a heat storage refrigerant circuit (2a), a seed ice circuit (2b), and a hot gas circuit (2c).

The heat storage refrigerant circuit (2a) is a circuit in which the refrigerant circulates during a cold heat storage operation described later, and has one end connected to the main refrigerant circuit (2a).
The other end is connected between the outdoor heat exchanger (23) of 7) and the outdoor electric expansion valve (EV-1), and the other end is connected between the four-way switching valve (22) and the accumulator (25). The heat storage refrigerant circuit (2a) includes a first solenoid valve (SV-1), a preheater (11), a heat storage electric expansion valve (EV-3), a supercooling heat exchanger (55) , and a second solenoid valve. (SV-2) are provided in order.

The seed ice circuit (2b) is a circuit for generating seed ice in the water circulation circuit (30). One end of the seed ice circuit is connected to the heat storage electric expansion valve (EV-3) in the heat storage refrigerant circuit (2a) and is supercooled. between the heat exchanger (55), the other end is connected between the supercooling heat exchanger (55) and the second solenoid valve (SV-2). The seed ice circuit (2b) is provided with a capillary tube (CP) and a seed ice generator (13) in order.

The hot gas circuit (2c) is a circuit for supplying the refrigerant discharged from the compressor (21) to the subcooling heat exchanger (55) during a cooling operation using ice stored in the heat storage tank (31). One end is connected to the discharge side of the compressor (21), and the other end is connected between the second solenoid valve (SV-2) and the supercooling heat exchanger (55) in the heat storage refrigerant circuit (2a). , A third solenoid valve (SV-3).

The above is the configuration of the refrigerant circuit (20).

On the other hand, as shown in FIG. 2, the water circulation circuit (30) includes a heat storage tank (31), a pump (32), a preheater (11), and a mixer (3).
3), a supercooling heat exchanger (55) , and a supercooling canceller (34) are sequentially connected by a water pipe (35).

The preheater (11) heats the ice water flowing from the heat storage tank (31) with the refrigerant flowing through the refrigerant circuit (20) and melts the ice pieces flowing through the water pipe (35). It is. The mixer (33) promotes melting of the ice by stirring the water and ice heated by the preheater (11). The seed ice generator (13) cools part of the water flowing through the water pipe (35) with the refrigerant flowing through the refrigerant circulation circuit (20) and turns it into seed ice toward the supercooling canceller (34). Supply. The supercooling canceller (34) stirs the seed ice generated by the seed ice generator (13) and the supercooled water generated by the supercooled heat exchanger (55) to eliminate the supercooled state. I do.

As described above, the supercooling heat exchanger (55) causes heat exchange between the refrigerant flowing in the refrigerant circuit (20) and the water flowing in the water circuit (30). Is cooled to a supercooled state, and is configured using a plate-type heat exchanger which is a feature of the present invention.

-Configuration of Subcooling Heat Exchanger (55) -As shown in FIGS. 3 and 4, the supercooling heat exchanger (55) is provided between the front frame (41) and the rear frame (42). , A plurality of heat transfer plates (P1, P2,...) Are stacked to form a heat exchanger body (5A).

The heat transfer plates (P1, P2,...) Are formed of a metal flat plate, and as described later, a part thereof is formed into a corrugated plate by press working to form a corrugated portion (91). I have. These heat transfer plates (P1, P2,...) Are composed of two types of heat transfer plates having different shapes of a corrugated portion (91) and a swelling direction of a sealing surface (71) described later, that is, a first plate (P1). Second plate (P
2). And supercooling heat exchanger (55)
Is configured such that a first plate (P1) and a second plate (P2) are alternately overlapped, and both plates (P1, P2) are integrally joined by brazing.

The front frame (41) has a pipe connection portion (75 to 7).
8) are formed, and the pipe connection portions (75 to 78) are connected to a water inflow path (61), a water outflow path (62), a main refrigerant inflow path (63a), and a main refrigerant outflow path (64a) to be described later. Communicating with each other,
(75), water outlet (76), refrigerant inlet (77) and refrigerant outlet (7
8).

The periphery (72) of each heat transfer plate (P1, P2,...)
Is bent in one direction, and as shown in FIG.
The heat transfer plates (P1, P2, ...) are overlapped so that the bending direction of the peripheral portion (72) is on the rear frame (42) side. Then, the peripheral portion (72) of the front heat transfer plate (P1,...)
And the peripheral edge of the rear heat transfer plate (P2, ...) (72)
Are in contact with each other, and the contacted portions are brazed and joined to each other.

Each of the heat transfer plates (P1, P2,...) Is provided with an opening (81, 82, 83a, 84a), and a seal surface (71) bulging in a predetermined direction around the opening. ) Are provided, and the sealing surfaces (71) of the heat transfer plates (P1, P2,...) Abut against each other to prevent mixing of water and the refrigerant.

Specifically, in the first plate (P1),
The sealing surfaces (71) of the first opening (81) and the second opening (82) are formed so as to bulge in a direction opposite to the direction in which the peripheral edge (72) is bent, and the third opening (81). 83a) and the fourth opening (84
The sealing surface (71) of (a) is formed so as to bulge in the direction in which the peripheral edge (72) is bent. On the other hand, the second plate (P
In 2), the sealing surfaces of the first opening (81) and the second opening (82)
(71) is formed so as to bulge in the direction in which the peripheral edge (72) is bent, and has the third opening (83a) and the fourth opening (84a).
The sealing surface (71) is formed so as to bulge in a direction opposite to the direction in which the peripheral edge (72) is bent. Then, the first plate (P1) and the second plate (P2) are alternately overlapped with each other, as shown in FIG.
1) are in contact with each other, and the contacted portions are joined by brazing.

Thus, the first opening (81) is formed as a water inflow path (61) as a heat medium inflow path, and the second opening (82) is formed as a water outflow path (62) as a heat medium outflow path. At the same time, the water inflow channel (61) and the water outflow channel (62) communicate only with the water channel (65). On the other hand, the third opening (83a) is formed in the main refrigerant inflow path (63a), the fourth opening (84a) is formed in the main refrigerant outflow path (64a), and the main refrigerant inflow path (63a) and the main refrigerant inflow path (63a) are formed. Refrigerant outflow path (64
a) is formed so as to communicate only with the main refrigerant flow path (66a).

Next, as a feature of the present invention, the first opening (81)
The second opening (82) is formed at the center in the width direction of each heat transfer plate (P1, P2), as shown in FIGS. Specifically, the first opening (81), that is, the water inflow path (6
1) is formed to be located slightly to the right of the lower center of the heat transfer plates (P1, P2). In addition, the second opening (8
2) That is, the water outflow path (62) is formed to be located slightly to the left of the upper center of the heat transfer plates (P1, P2).

The water inflow path (61) is formed such that the water flowing from the water inflow path (61) into each of the water flow paths (65) spreads substantially uniformly in the width direction of the water flow path (65). ), The water outflow path (62) is arranged such that water flowing through the water flow path (65) flows from the water flow path (65) toward the water outflow path (62) from the width direction of the water flow path (65). They are arranged so that they gather and flow out almost uniformly.

On the other hand, the third opening (83a), that is, the main refrigerant inflow path (63a) is formed at the lower left corner of the heat transfer surface (50) described later, and the fourth opening (84a), The refrigerant outflow passage (64a) is formed at the upper right corner of a heat transfer surface (50) described later.

Further, the heat transfer plates (P1, P2) are
A heat transfer surface (50) is formed between the opening (81) and the second opening (82), and a corrugated portion (91) is formed on the heat transfer surface (50).

More specifically, around the first opening (81) and the second opening (82) in the first plate (P1), as shown in FIG. On the other hand, around the third opening (83a) and the fourth opening (84a), a sealing surface (71) is formed by being bent forward, and the front surface of the first plate (P1) is 65), the main refrigerant passage (66
a).

Further, the corrugated portion (91) of the first plate (P1)
Has a wave shape in which peaks (thick lines in FIG. 5) and valleys (thin lines in FIG. 5) that form a sine wave are alternately formed. This wave shape is formed such that the extension direction of the peaks and valleys is inclined upward to the right in FIG. 5, and the upper inclined portion (92 a) is inclined downward. At the same time as the so-called herringbone shape in which the lower inclined portions (92b) are alternately formed, the upper inclined portions (92a) and the lower inclined portions (92b) have an arrangement direction of peaks and valleys, The first plate (P1) is formed so as to be in the longitudinal direction (vertical direction).

On the other hand, the first plate in the second plate (P2)
As shown in FIG. 6, around the opening (81) and the second opening (82), the sealing surface (71) is formed by being bent forward, while the third opening (83a) and the fourth opening ( 84a), a sealing surface (71) is formed by being bent rearward, the front surface of the first plate (P1) is in the main refrigerant flow path (66a), and the rear surface is in the water flow path (65).
It has become.

Further, the corrugated portion (91) of the second plate (P2)
Differs from that of the first plate (P1) in the extension direction of the peaks and valleys. That is, in the above-described first plate (P1), as shown in FIG. 5, the herringbone shape is formed in the order of the upper inclined portion (92a) and the lower inclined portion (92b) from the left end, while As shown in FIG. 6, the plate (P2) has a herringbone shape in the order of a lower inclined portion (92b) and an upper inclined portion (92a) from the left end.

-Operation- Next, the operation of the air conditioner (10) (cold heat storage operation).
Will be described.

In the cold heat storage operation in which the slurry ice is stored in the heat storage tank (31), the four-way switching valve (22) is switched to the solid line side as shown in FIG. Is adjusted to a predetermined opening degree, while the other electric expansion valves (EV-1, EV-2) are closed. The first and second solenoid valves (SV-1, SV-2) are open, and the third solenoid valve (SV-3) is closed.

In this state, in the refrigerant circulation circuit (20), the refrigerant discharged from the compressor (21) exchanges heat with the outside air in the outdoor heat exchanger (23) as shown by the solid arrow in FIG. To condense. Thereafter, the refrigerant is decompressed by the heat storage electric expansion valve (EV-3), and then exchanges heat with water in the supercooling heat exchanger (55) as the supercooling heat exchanger (55) to evaporate. Cool the water to a supercooled state. After that, the above refrigerant is stored in the accumulator (2
After passing through 5), it is sucked into the compressor (21).

In this operation, part of the refrigerant is
After being diverted from the downstream side of the heat storage electric expansion valve (EV-3) to the seed ice circuit (2b), the pressure is reduced by the capillary tube (CP), and the pressure is reduced by the seed ice generator (13), and the accumulator (25) Is sucked into the compressor (21). In the seed ice generator (13), the refrigerant exchanges heat with water flowing through the water pipe (35), and the seed ice is removed from the water pipe.
Generated on the inner wall of (35).

On the other hand, in the water circulation circuit (30), the water is circulated by driving the pump (32). As shown in FIG. 2, the water flowing out of the heat storage tank (31) passes through a pump (32),
After being heated by the preheater (11), it is stirred by the mixer (33).
Thereafter, the water is cooled by exchanging heat with the refrigerant in a subcooling heat exchanger (55) as a supercooling heat exchanger (55) , and is cooled to a predetermined supercooling state, and the water is cooled . ) . The supercooled water flowing out of the supercooling heat exchanger (55) is further cooled in the seed ice generator (13), and generates seed ice on the inner wall surface of the water pipe (35). Thereafter, ice nuclei are generated around the seed ice, and the supercooled water containing the ice nuclei is supplied to the supercooling canceller (34). Then, the ice nuclei and the supercooled water are stirred in the supercooling canceller (34), and slurry-like ice for heat storage is generated and collected and stored in the heat storage tank (31).

Next, the flow of the refrigerant and water in the subcooling heat exchanger (55) will be described. First, the refrigerant flows from the main refrigerant inflow passage (63a) through the refrigerant introduction section (77) to the main refrigerant. Channel (66
a). Then, it flows through the main refrigerant flow path (66a), exchanges heat with water in the adjacent water flow path (65), evaporates, and cools the water. The evaporated refrigerant flows out of the subcooling heat exchanger (55) from the main refrigerant outflow path (64a) through the refrigerant outlet section (78). On the other hand, the water flows into the water flow path (65) from the water inflow path (61) via the water introduction section (75). Then, it flows through the water flow path (65), exchanges heat with the refrigerant in the adjacent main refrigerant flow path (66a), is cooled, and enters a supercooled state. The water cooled to the supercooled state flows out of the supercooling heat exchanger (55) from the water outflow path (62) through the water outlet section (76).

As a feature of the present invention, the water inflow path (6
1) and the water outflow channel (62) are arranged in the center, so that the water flowing from the water inflow channel (61) to the water channel (65)
It flows almost uniformly in the width direction of (P1, P2). Then, the water in the water flow path (65) is transferred to the heat transfer plate (62) by the heat transfer plate.
As a result, the water temperature distribution in the width direction of the heat transfer plate (P1, P2) in the water flow path (65) is reduced as shown in FIG. Become uniform.

As described above, the cold heat storage operation using the plate heat exchanger as the supercooling heat exchanger (55) is performed.

In the air conditioner (10), in addition to the cold storage operation, the four-way switching valve (22) and the solenoid valves (SV-1, SV-
By switching between the SV-2 and the SV-3, etc., it is possible to perform indoor cooling operation using the cold heat of the ice stored in the heat storage tank (31). Further, a normal cooling operation or a normal heating operation for performing indoor air conditioning using only the refrigerant circulation circuit (20) is also possible.

According to the first embodiment, in each of the heat transfer plates (P1, P2) of the subcooling heat exchanger (55) , the first opening (81) and the second opening (8) are provided.
2) is formed at the center in the width direction of the heat transfer plate (P1, P2), so that the water inlet and the water outlet are formed at the center of the water passage (65). In each part in the width direction, water can flow in the direction from the water inflow path (61) to the water outflow path (62), and the uneven flow of water in the width direction of the water flow path (65) can be reduced. As a result, unevenness in the temperature distribution of water can be corrected, and the supercooled state of the heat medium can be stabilized. Therefore, when the supercooled water is generated, the supercooling due to the temperature impact can be prevented from being eliminated, while the supercooling temperature can be lowered, and the ice generation efficiency can be improved.

[0069]

[Embodiment 2] This embodiment 2 is shown in FIGS.
As shown in FIG. 3, the heat transfer surface (50) is formed on almost the entire heat transfer plate (P1, P2) in the first embodiment,
An outlet-side closing portion (74) is formed in (65).

That is, the fourth plate on the first plate (P1)
An outlet-side closing surface (74 ') is formed around the opening (84a). The outlet-side closing surface (74 ') has a width of the heat transfer surface (50) of the fourth.
It is formed in a substantially inverted triangular shape so as to become narrower toward the opening (84a), and is formed so as to bulge forward.

On the other hand, an outlet-side closing surface (74 ') is formed in the second plate (P2) around the fourth opening (84a). The outlet-side closing surface (74 ′) is formed in a substantially inverted triangular shape so that the width of the heat transfer surface (50) decreases toward the fourth opening (84a), and at the same time, bulging rearward. Have been.

Then, the heat transfer plates (P1, P2) are overlapped with each other, and the outlet-side closing surfaces (74 ') of the adjacent heat transfer plates (P1, P2) come into contact with each other, so that both the outlet-side closing surfaces (74). 74 ′) are joined by brazing to form an outlet-side closing portion (74) through which water does not flow in the water flow path (65).

Therefore, in the subcooling heat exchanger (55) in this embodiment, the water flowing from the water inflow path (61) into the water flow path (65) flows toward the water outflow path (62). However, since the width of the water flow path (65) is narrowed by the outlet side closing part (74), water flows near the fourth opening (84a) at a substantially uniform flow rate without stagnation, and exchanges heat with the refrigerant. become.

Other structures and operations are the same as those of the first embodiment.

According to the second embodiment, the outlet-side closing portion (74) is provided in the water flow path (65) around the main refrigerant outflow path (64a).
It is possible to reliably prevent a dead water area as in the related art. As a result, the non-uniformity of the temperature distribution of the water can be further corrected, and the water remaining in the dead water area is cooled and the water flow path (6
It is possible to prevent freezing in 5) and to stabilize the supercooled state of the heat medium.

[0076]

Third Embodiment As shown in FIGS. 10 and 11, the third embodiment is different from the second embodiment in that an outlet-side closing surface (74) is formed in a water flow path (65). Thus, an inlet-side closing portion (73) is formed.

That is, in the first plate (P1), the fourth plate
An outlet-side closing surface (74 ') similar to that of the second embodiment is formed around the opening (84a), and an inlet-side closing surface (73') is formed around the third opening (83a). ) Is formed. The inlet-side closing surface (73 ′) is formed in a substantially triangular shape so that the width of the heat transfer surface (50) decreases toward the third opening (83a), and at the same time, is formed so as to bulge forward. ing.

On the other hand, in the second plate (P2), an outlet-side closing surface similar to that of the second embodiment is provided around the fourth opening (84a).
At the same time as (74 ') is formed, an entrance-side closing surface (73') is formed around the third opening (83a). The inlet-side closing surface (73 ′) is formed in a substantially triangular shape so that the width of the heat transfer surface (50) decreases toward the third opening (83a),
It is formed to bulge rearward.

Then, the heat transfer plates (P1, P2) are superimposed on each other, and both closed surfaces of the adjacent heat transfer plates (P1, P2) are overlapped.
(73, 74) are in contact with each other, the two closed surfaces (73, 74) are joined by brazing, and an inlet-side closed portion through which water does not flow in the water flow path (65).
(73) and an outlet side closing part (74) are formed.

Therefore, in the subcooling heat exchanger (55) in this embodiment, the water flowing from the water inflow path (61) into the water flow path (65) flows toward the water outflow path (62). However, since the width of the water flow path (65) becomes equal over the entire water flow path (65) due to the inlet-side closing surface (73 ′) and the outlet-side closing part (74), the third opening (83a) and the fourth Water flows near the opening (84a) at a substantially uniform flow rate without stagnation, and exchanges heat with the refrigerant.

The other structure and operation are the same as in the first embodiment.

The corrugated portions (91) of the first plate (P1) and the second plate (P2) of the present embodiment are respectively shown in FIG.
11 and FIG. 11, respectively. However, as shown in FIG. 12 and FIG. 13, respectively, the arrangement direction of the upper inclined portion and the lower inclined portion, the peak portion and the valley portion is the heat transfer plate (P1, P
It may be formed to be inclined at a certain angle from the longitudinal direction (vertical direction) of 2).

-Effects of Embodiment 3- According to Embodiment 3, both the inlet side closing portions are provided at both the periphery of the main refrigerant inflow path (63a) and the main refrigerant outflow path (64a) in the water flow path (65). Since the (73) and the outlet-side closing portion (74) are provided, it is possible to reliably prevent the dead water area as in the related art. As a result, the non-uniformity of the temperature distribution of the water can be further corrected, and the water that has accumulated in the dead water area can be prevented from being cooled and frozen in the water flow path (65), and the heat medium can be prevented. The supercooled state can be stabilized.

[0084]

Embodiment 4 As shown in FIGS. 14 and 15, Embodiment 4 is different from Embodiment 1 in that the third opening (83a),
That is, instead of forming the main refrigerant inflow passage (63a) at the lower left corner of the heat transfer surface (50), the main refrigerant inflow passage (63a) is formed at the lower center of the heat transfer surface (50), and at the same time, the first opening (81) That is, instead of forming the water inflow path (61) slightly to the right of the lower center of the heat transfer plates (P1, P2), it is formed at the lower center of the heat transfer plates (P1, P2).

Since the main refrigerant inflow passage (63a) is disposed at the center, the main refrigerant inflow passage (63a) extends from the main refrigerant inflow passage (63a).
The refrigerant flowing to (66a) flows almost uniformly in the width direction of the heat transfer plates (P1, P2). Thereafter, the refrigerant exchanges heat with water flowing in the water flow path (65) and evaporates, and the evaporated refrigerant is discharged to the main refrigerant outflow path (6).
4a). At this time, in the main refrigerant flow path (66a) around the main refrigerant outflow path (64a), since the refrigerant is in a gaseous state, the flow of the refrigerant is hardly affected by the position of the main refrigerant outflow path (64a). That is, the main refrigerant outflow path (64a) is connected to the main refrigerant flow path (66a).
Is not a cause of refrigerant drift. On the other hand, the water flowing in the water flow path (65) flows at a substantially uniform flow velocity in the width direction and exchanges heat with the refrigerant in the main refrigerant flow path (66a), as in the first embodiment. As a result, the water temperature distribution in the width direction of the heat transfer plates (P1, P2) in the water flow path (65) becomes uniform.

The other structures and operations are the same as in the first embodiment.

-Effects of Embodiment 4- According to Embodiment 4, in each of the heat transfer plates (P1, P2), the third opening (83a) is formed at the center of the heat transfer plate (P1, P2) in the width direction. And the main refrigerant inflow passage (63a) is formed at the center of the main refrigerant flow path (66a), so that the refrigerant flowing in the state of the liquid refrigerant flows from the central part to the width of the refrigerant flow path. Thus, the refrigerant can be spread uniformly in the direction, and the drift of the refrigerant in the width direction of the medium flow path can be reduced. Further, as in the first embodiment, since the water inflow path (61) and the water outflow path (62) are formed in the center of the water flow path (65), the water flow path (65)
Of the water in the width direction can be reduced. This makes it possible to equalize the amount of heat exchange between the water and the refrigerant in each portion in the width direction of the heat transfer plates (P1, P2), and as a result, it is possible to correct the uneven temperature distribution of the water. ,
The supercooled state of the heat medium can be stabilized. Therefore, when the supercooled water is generated, the supercooling due to the temperature impact can be prevented from being eliminated, while the supercooling temperature can be lowered, and the ice generation efficiency can be improved.

[0088]

Fifth Embodiment In a fifth embodiment, as shown in FIGS. 16 and 17, in the fourth embodiment, the heat transfer surface (50) is formed on almost the entire heat transfer plate (P1, P2). Instead of this, an outlet-side closing portion (74) is formed in the water flow path (65).

That is, the fourth plate on the first plate (P1)
An outlet-side closing surface (74 ') is formed around the opening (84a). The outlet-side closing surface (74 ') is formed in a substantially inverted triangular shape so that the width of the heat transfer surface (50) decreases toward the fourth opening (84a), and at the same time, swells forward. Is formed.

On the other hand, an outlet-side closing surface (74 ') is formed around the fourth opening (84a) in the second plate (P2). The outlet-side closing surface (74 ') is formed in a substantially inverted triangular shape so that the width of the heat transfer surface (50) decreases toward the fourth opening (84a), and at the same time, bulges rearward. Is formed.

Then, the heat transfer plates (P1, P2) are superimposed on each other, and the outlet-side closing surfaces (74 ') of the adjacent heat-transfer plates (P1, P2) are in contact with each other, so that both outlet-side closing surfaces (74). 74 ′) are joined by brazing to form an outlet-side closing portion (74) through which water does not flow in the water flow path (65).

Therefore, in the supercooling heat exchanger (55) in the present embodiment, the water flowing from the water inflow path (61) into the water flow path (65) flows toward the water outflow path (62). However, since the width of the water flow path (65) is narrowed by the outlet side closing part (74), water flows near the fourth opening (84a) at a substantially uniform flow rate without stagnation, and exchanges heat with the refrigerant. become.

Other structures and operations are the same as those of the fourth embodiment.

According to the fifth embodiment, in addition to the effects of the fourth embodiment, the outlet-side closing portion (74) is provided around the main refrigerant outflow path (64a) in the water flow path (65). ) Can reliably prevent dead water areas as in the prior art. As a result, the non-uniformity of the temperature distribution of the water can be further corrected, and the water that has accumulated in the dead water area can be prevented from being cooled and frozen in the water flow path (65), and the heat medium can be prevented. The supercooled state can be stabilized.

[0095]

[Embodiment 6] In Embodiment 6, the precooling heat exchanger (55) is provided with two refrigerant passages for one water passage (65), whereby the preheating in Embodiment 1 is performed. vessel
(11) and the mixer (33) are integrally formed with the subcooling heat exchanger (55) .

First, the structure of the supercooling heat exchanger (55) is the same as that of the first embodiment in that the heat transfer plates (P1, P2) are overlapped and joined by brazing. Then, at the same time when the water flow path (65), the main refrigerant flow path (66a) and the sub-refrigerant outflow path (64b) are formed, the water flow path (65) is formed by the first opening (81) and the second opening (82). Water inflow channel communicating with
(61) and a water outflow channel (62) are formed respectively, and the third opening (8
3a) and the fourth opening (84a) form a main refrigerant inflow path (63a) and a main refrigerant outflow path (64a) communicating with the main refrigerant flow path (66a), respectively, and the fifth opening (83b) and the sixth The opening (84b) forms a sub-refrigerant inflow path (63b) and a sub-refrigerant outflow path (64b) communicating with the sub-refrigerant flow path (66b).

Next, as a feature of the present invention, the first opening (81)
And the second opening (82), as shown in FIGS. 18 and 19,
The heat transfer plates (P1, P2) are formed at the center in the width direction. Specifically, the first opening (81), that is, the water inflow path
(61) is formed to be located slightly to the right of the lower center of the heat transfer plates (P1, P2). In addition, the second opening (8
2) That is, the water outflow path (62) is formed to be located slightly to the left of the upper center of the heat transfer plates (P1, P2).

The water inflow path (61) is formed such that water flowing into each of the water flow paths (65) from the water inflow path (61) spreads almost uniformly in the width direction of the water flow path (65). ), The water outflow path (62) is arranged such that water flowing through the water flow path (65) flows from the water flow path (65) toward the water outflow path (62) from the width direction of the water flow path (65). They are arranged so as to gather and flow almost uniformly.

On the other hand, the heat transfer plates (P1, P2)
A heat transfer surface (51, 52) is formed between the opening (81) and the second opening (82), and the heat transfer surface (51, 52) is formed by a partition (67) described later by a first portion. In order from the opening (81) toward the second opening (82), a preheating heat transfer surface (52) and a subcooling heat transfer surface (51) are formed and divided into both heat transfer surfaces (51, 52). Has a corrugated portion (91).

Further, the third opening (83a), that is, the main refrigerant inflow passage (63a) is formed at the lower left corner of the supercooling heat transfer surface (51), and the fourth opening (84a), that is, the main refrigerant The outflow passage (64a) is formed at the upper right corner of the supercooled heat transfer surface (51), and has a fifth opening (83).
b), that is, the auxiliary refrigerant inflow path (63b) is formed at the lower left corner of the preheating heat transfer surface (52), and the sixth opening (84b), that is, the auxiliary refrigerant outflow path (64b) It is formed in the upper right corner of the surface (52).

Specifically, around the first opening (81) and the second opening (82) in the first plate (P1), as shown in FIG. Is formed, while around the third opening (83a) and the fourth opening (84a),
It is bent forward to form a seal surface (71), and further bulges rearward to form a partition surface (67 '). The front surface of the first plate (P1) is connected to the water flow path (65), Is the main refrigerant flow path (6
6a) and a sub-coolant flow path (66b).

The shape of the corrugated portion (91) of the first plate (P1) is different between the preheating heat transfer surface (52) and the supercooling heat transfer surface (51). The wave shape is formed in the same herringbone shape as the first plate (P1) of the first embodiment, while the wave shape in the supercooling heat transfer surface (51) is the upper portion ( 51a) and the lower part (51b).

That is, the wave shape at the lower portion (51b) is formed in a herringbone shape similar to that of the first plate (P1) of the first embodiment, while the wave shape at the upper portion (51a) forms a sinusoidal wave. Crests (thick lines in FIG. 18) and troughs (thin lines in FIG. 18) are formed alternately, and at the same time, the extension direction of the crests and troughs is determined by the supercooling heat transfer surface (5).
It is formed so as to be substantially parallel to the longitudinal direction of 1), and further below (5
At the boundary between 1b) and the upper part (51a), the peaks and valleys are formed so as to be continuous.

On the other hand, the fourth opening in the first plate (P1)
An outlet-side closing surface (74 ') is formed in the periphery of (84a). The outlet side closing surface (74 ') is formed in a substantially inverted triangular shape so that the width of the supercooling heat transfer surface (51) decreases toward the fourth opening (84a), and at the same time, expands forward. It is formed out.

The shape of the corrugated portion (91) of the second plate (P2) is different between the preheating heat transfer surface (52) and the supercooling heat transfer surface (51). The wavy shape is formed in the same herringbone shape as the second plate (P2) of the first embodiment, while the wavy shape on the supercooled heat transfer surface (51) has an upper portion (51a) and a lower portion (51a) of the supercooled surface. 51b).

That is, the wave shape in the lower portion (51b) is formed in a herringbone shape similar to that of the second plate (P2) in Embodiment 1, while the wave shape in the upper portion (51a) is a sine wave shape. Crests (thick line portions in FIG. 19) and troughs (thin line portions in FIG. 19) are formed alternately, and at the same time, the extension direction of the crests and troughs is determined by the supercooling heat transfer surface (5).
It is formed so as to be substantially parallel to the longitudinal direction of 1), and further below (5
At the boundary between 1b) and the upper part (51a), the peaks and valleys are formed so as to be continuous.

On the other hand, the fourth opening in the second plate (P2)
An outlet-side closing surface (74 ') is formed in the periphery of (84a). The outlet side closing surface (74 ') is formed in a substantially inverted triangular shape so that the width of the supercooling heat transfer surface (51) decreases toward the fourth opening (84a), and at the same time, expands rearward. It is formed out.

Then, the heat transfer plates (P1, P2) are superimposed on each other, and the outlet-side closing surfaces (74 ') of the adjacent heat transfer plates (P1, P2) are in contact with each other, so that both outlet-side closing surfaces ( 74 ′) are joined by brazing, and at the same time an outlet-side closing portion (74) through which water does not flow in the water flow path (65) is formed, and the partition surfaces (67 ′) of the adjacent heat transfer plates (P1, P2) are formed. ) Abut each other and both partition surfaces (6
7 ′) are joined by brazing to form a partition portion (67), thereby forming a main refrigerant flow path (66a) and a sub-refrigerant flow path (66b).

-Configuration of the air conditioner (10)-The air conditioner (10) according to the sixth embodiment has substantially the same configuration as the air conditioner (10) of the first embodiment. Are different.

That is, in the refrigerant circulation circuit (20), instead of the preheater (11), the sub-coolant flow path (66b) of the subcooling heat exchanger (55) of this embodiment is connected, and The passage (64b) is connected to the main refrigerant inflow passage (63a) via the heat storage electric expansion valve (EV-3), and further, the heat storage electric expansion valve (EV-3) and the main refrigerant inflow passage (63a). Is connected to one end of the seed ice circuit (2b). In the water circulation circuit (30), the preheater (1
1), the mixer (33) is omitted.

-Operation- The operation of the air conditioner (10) in the present embodiment during operation is the same as in the first embodiment.

Next, the flow of the refrigerant and water in the subcooling heat exchanger (55) will be described. The high-temperature liquid refrigerant from the refrigerant circuit (20) flows through the sub-refrigerant inflow passage (63b). Road (66b)
Flows into. Then, the water flows through the sub-refrigerant flow path (66b), exchanges heat with water in the adjacent water flow path (65), and heats the water. Thereafter, the refrigerant flows out of the sub-refrigerant outflow path (64b). The low-pressure liquid refrigerant decompressed by the heat storage electric expansion valve (EV-3) of the refrigerant circuit (20) flows into the main refrigerant flow path (66a) from the main refrigerant inflow path (63a). Then, the main refrigerant flow path (66
a) and exchanges heat with water in the adjacent water flow path (65) to evaporate and cool the water.After that, the refrigerant flows into the main refrigerant outflow path (6).
4a).

On the other hand, the water from the water circulation circuit (30) flows into the water flow path (65) from the water inflow path (61). And the water channel (65)
At the same time, heat is exchanged with the refrigerant in the adjacent sub-refrigerant flow path (66b) and heated, and at the same time, the water flow is disturbed by the corrugated portion (91) of the preheating heat transfer surface (52), and the water is stirred. Then, after the ice contained in the water is melted, the ice is cooled by exchanging heat with the refrigerant in the adjacent main refrigerant flow path (66a), and becomes a supercooled state. The water cooled to the supercooled state flows out of the water outflow channel (62).

As a feature of the present invention, the water inflow path (6
1) and the water outflow channel (62) are arranged in the center, so that the water flowing from the water inflow channel (61) to the water channel (65)
(P1, P2) flows almost uniformly in the width direction.After that, the water in the water flow path (65) flows toward the water outflow path (62).
1, P2) can gather and flow uniformly from the width direction. Further, since the width of the water flow path (65) is narrowed by the outlet side closing part (74), water flows near the fourth opening (84a) at a substantially uniform flow rate without stagnation, and exchanges heat with the refrigerant. become. As a result, the heat transfer plates (P1, P1) in the water flow path (65)
2) The water temperature distribution in the width direction becomes uniform.

As described above, the cold heat storage operation using the plate heat exchanger as the supercooling heat exchanger (55) is performed.

According to the sixth embodiment, in addition to the effects of the third embodiment, the preheater (11), the mixer (33) and the supercooling heat exchanger (55) are replaced by one. Since the plate-type heat exchanger is integrally formed using the two plate-type heat exchangers, the size of the device can be reduced, and the assembling process can be simplified.

The shape of the corrugated portion (91) constituting the supercooling heat transfer surface (51) of the heat transfer plate (P1, P2) is changed to the shape of the supercooling heat transfer surface (5).
1) The upper part (51a) and the lower part (51b) are different. As a result, the main refrigerant flow path (66a) and the water flow path (65) formed by the lower portion (51b) of the supercooled heat transfer surface (51) (the water flow path
(On the upstream side of (65)), the main refrigerant flow path (66a)
And the turbulence of the fluid flowing through the water flow path (65) can be increased, while the main refrigerant flow path (66a) and the water flow path (65) formed by the upper portion (51a) of the supercooled heat transfer surface (51) In the downstream side of the water flow path (65)), turbulence of the fluid flowing through the main refrigerant flow path (66a) and the water flow path (65) can be reduced. Therefore, on the upstream side of the water flow path (65), the heat exchange amount between the water and the refrigerant increases, and the water can be rapidly cooled, while the water is cooled and the water flow path (65) is in a supercooled state. On the downstream side, the turbulence of the flow of water can be reduced.

As a result, on the downstream side of the water flow path (65),
It is possible to prevent supercooling from being eliminated due to the turbulence of the flow and to prevent ice from being generated, and to stabilize the supercooled state of the water.At the same time, the temperature change of the water downstream of the water flow path (65) is reduced. It becomes moderate and water temperature control becomes easy.

[0119]

Seventh Embodiment As shown in FIGS. 20 and 21, the seventh embodiment is different from the sixth embodiment in that the third opening (83)
a) In other words, instead of forming the main refrigerant inlet at the lower left corner of the supercooling heat transfer surface (51), it is provided at the lower center of the supercooling heat transfer surface (51).

-Operation- As a feature of the present invention, since the main refrigerant inflow passage (63a) is disposed at the center, the main refrigerant inflow passage (63a) flows from the main refrigerant inflow passage (63a) to the main refrigerant flow passage (66a). The refrigerant flows almost uniformly in the width direction of the heat transfer plates (P1, P2). After that, the refrigerant flows into the water channel (65)
Evaporates by exchanging heat with water flowing therethrough, and the evaporated refrigerant flows out of the main refrigerant outflow passage (64a). At this time, the main refrigerant outflow path (64
a) In the peripheral main refrigerant flow path (66a), since the refrigerant is in a gaseous state, the flow of the refrigerant is not greatly affected by the position of the main refrigerant outflow path (64a). That is, even if the main refrigerant outflow path (64a) is provided at the corner of the refrigerant flow path, it does not cause a refrigerant drift. On the other hand, the water flowing through the water flow path (65) flows at a substantially uniform flow velocity in the width direction and exchanges heat with the refrigerant in the refrigerant flow path, as in the sixth embodiment. As a result, the water temperature distribution in the width direction of the heat transfer plates (P1, P2) in the water flow path (65) becomes uniform.

The other structures and operations are the same as in the sixth embodiment.

-Effects of Seventh Embodiment- According to the present embodiment, the effects obtained in the fourth embodiment can be obtained in addition to the effects obtained in the sixth embodiment.

That is, by eliminating the non-uniform flow of the water flowing through the water flow path (65) and the refrigerant flowing through the main refrigerant flow path (66a), it is possible to correct the unevenness of the temperature distribution of the water and to supercool the heat medium. The state can be stabilized. Therefore, when the supercooled water is generated, the supercooling due to the temperature impact can be prevented from being eliminated, while the supercooling temperature can be lowered, and the ice generation efficiency can be improved.

[0124]

Other Embodiments of the Invention The above-described embodiments 1 to 7
In the above, the heat transfer plates (P1, P2) are integrally joined by brazing to form a plate heat exchanger, but may be joined by welding or sealed by a gasket.

[Brief description of the drawings]

FIG. 1 is a refrigerant circuit diagram and a water circuit diagram of a dynamic ice storage type air conditioner.

FIG. 2 is a water circulation circuit diagram of a dynamic ice storage air conditioner.

FIG. 3 is a perspective view of a plate heat exchanger according to the present invention.

FIG. 4 is an AA sectional view of the plate heat exchanger according to the present invention.

FIG. 5 is a front view of a first plate according to the first embodiment.

FIG. 6 is a front view of a second plate according to the first embodiment.

FIG. 7 is a BB cross-sectional view of the first plate in the first embodiment.

FIG. 8 is a front view of a first plate according to the second embodiment.

FIG. 9 is a front view of a second plate according to the second embodiment.

FIG. 10 is a front view of a first plate according to a third embodiment.

FIG. 11 is a front view of a second plate according to the third embodiment.

FIG. 12 is a front view of a first plate according to a modification of the third embodiment.

FIG. 13 is a front view of a second plate according to a modified example of the third embodiment.

FIG. 14 is a front view of a first plate according to a fourth embodiment.

FIG. 15 is a front view of a second plate according to the fourth embodiment.

FIG. 16 is a front view of a first plate according to the fifth embodiment.

FIG. 17 is a front view of a second plate according to the fifth embodiment.

FIG. 18 is a front view of a first plate according to the sixth embodiment.

FIG. 19 is a front view of a second plate according to the sixth embodiment.

FIG. 20 is a front view of a first plate according to the seventh embodiment.

FIG. 21 is a front view of a second plate according to the seventh embodiment.

FIG. 22 is an isotherm diagram of water in a conventional plate heat exchanger.

FIG. 23 is an isotherm diagram of water in the plate heat exchanger of the present invention.

FIG. 24 is an exploded perspective view of a conventional plate heat exchanger.

[Explanation of symbols]

 (P1) First plate (P2) Second plate (5A) Main body of heat exchanger (61) Water inflow path (Heat medium inflow path) (62) Water outflow path (Heat medium outflow path) (63a) Main refrigerant inflow path ( 63b) Sub refrigerant inflow path (64a) Main refrigerant outflow path (64b) Sub refrigerant outflow path (65) Water flow path (heat medium flow path) (66a) Main refrigerant flow path (66b) Sub refrigerant flow path (73) Inlet side Closed part (74) Exit side closed part

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-51-2052 (JP, A) JP-A-10-115442 (JP, A) JP-B-50-22503 (JP, B1) (58) Field (Int.Cl. ⁷ , DB name) F28F 3/08 301 F24F 5/00 102 F25C 1/00 F28D 9/02

Claims (6)

(57) [Claims] 1. A plurality of stacked heat transfer plates (P1, P2,
...), a heat medium flow path (65) through which the heat medium flows and a main refrigerant flow path (66a) through which the refrigerant flows are alternately formed, and heat exchange is performed so that the heat medium and the refrigerant perform heat exchange. Container body (5A)
The heat exchanger body (5A) penetrates each heat transfer plate (P1, P2,...) And has a heat medium flow path (65).
The heat medium inflow path (61) and the heat medium outflow path (62) communicating with the
The heat transfer plates (P1, P2, ...) are formed at both ends in the longitudinal direction and at the center in the width direction of the heat transfer plates (P1, P2, ...). P1, P2, ...) and the main refrigerant flow path (66
The main refrigerant inflow path (63a) and the main refrigerant outflow path (64a) communicating with the a) are both ends of the main refrigerant flow path (66a) in the refrigerant flow direction.
And the heat medium inflow path (61) and the heat medium outflow path (6
A plate heat exchanger characterized by being formed closer to the center in the longitudinal direction of the heat transfer plates (P1, P2,...) Than 2) . 2. A plurality of stacked heat transfer plates (P1, P2,
), The heat medium flow path (65) through which the heat medium flows and the refrigerant flow path through which the refrigerant flows are formed alternately, and the heat exchanger body (5A ), The refrigerant flow path corresponds to the upstream and downstream sides of the heat medium in the heat medium flow path (65), the sub-refrigerant flow path (66b) and the main refrigerant flow path (66a) in order Each heat transfer plate (P1, P2,...) Is formed in the heat exchanger body (5A).
Main refrigerant inflow passage penetrating through and communicating with the main refrigerant flow path (66a)
(63a) and a main refrigerant outflow path (64a) are formed at both ends of the main refrigerant flow path (66a) in the flow direction of the refrigerant, and the heat exchanger body (5A) Plate (P1, P2,…)
And a sub-refrigerant inflow passage (63b) communicating with the sub-refrigerant circuit
And the sub-refrigerant outflow passage (64b) are formed at both ends of the sub-refrigerant flow path (66b) in the flow direction of the refrigerant, while the heat exchanger body (5A) includes (P1, P2,…)
Through the heat medium inflow path (6) communicating with the heat medium flow path (65).
1) and the heat medium outlet channel (62) are connected to the heat transfer plates (P1, P2, ...).
Heat transfer plates at both ends in the longitudinal direction (P1, P2, ...)
A plate heat exchanger formed at a central portion in the width direction of the plate heat exchanger. 3. The plate type heat exchanger according to claim 1, wherein the main refrigerant inflow passage (63a) has a width corresponding to a width of the heat transfer plates (P1, P2,...).
A plate-type heat exchanger, which is provided at a central portion in a direction . 4. The plate type heat exchanger according to claim 1, wherein the width of the heat medium flow path (65) is set in the heat medium flow path (65) toward the heat medium outflow path (62). A plate-type heat exchanger, wherein an outlet-side closing portion (74) for blocking the flow of the heat medium so as to be narrow is formed corresponding to a peripheral portion of the main refrigerant outflow passage (64a). 5. The plate heat exchanger according to claim 4, wherein the width of the heat medium passage (65) in the heat medium passage (65) decreases toward the heat medium inflow passage (61). The plate type heat exchanger characterized in that the inlet-side closing portion (73) for blocking the flow of the heat medium is formed corresponding to the peripheral portion of the main refrigerant inflow passage (63a). 6. The plate heat exchanger according to claim 3, wherein the width of the heat medium passage (65) in the heat medium passage (65) decreases toward the heat medium outflow passage (62). The plate-type heat exchanger, wherein the outlet-side closing portion (74) for blocking the flow of the heat medium is formed corresponding to the peripheral portion of the main refrigerant outflow passage (64a).