JP2001021234A - Cooler - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the heat-exchange function of a cooler by performing supercooling of a refrigerant with high efficiency without needing a surplus installation space and to save energy by reducing a power load loaded on a compressor. SOLUTION: This cooler comprises a compressor to compress a refrigerant; a condenser to condense the compressed refrigerant; an expansion valve 5 to perform heat insulation and expansion of a condensed refrigerant; and an evaporator 6 to perform evaporation of an expand refrigerant. In this case, the cooler is provided with an internal heat-exchanger 7 to effect heat-exchange between a refrigerant before an inflow of it to the expansion valve 5 and a refrigerant after a flow of it through the evaporator 6, and the internal heat-exchanger 7 is situated in a state to be formed integrally with the evaporator.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

TECHNICAL FIELD The present invention relates to a cooling device used in a heat exchange cycle of a vehicle or the like.

[0002]

2. Description of the Related Art Conventionally, a cooling device used for a vehicle includes a compressor, a condenser, a liquid receiver, an expansion valve, and an evaporator, and these devices are connected by piping to form one heat exchange cycle. Is composed.

FIG. 10 is a diagram showing a schematic configuration of a conventional cooling device 20. As shown in FIG.
A compressor 21 for compressing the refrigerant to a high temperature and a high pressure, a condenser 22 for condensing the compressed refrigerant, a liquid receiver 23 for separating the condensed refrigerant into gas and liquid and temporarily storing the liquid refrigerant therein, An expansion valve 24 for adiabatically expanding the refrigerant, and an evaporator 25 for exchanging heat between the adiabatic expanded refrigerant and the outside air to release cool air are provided. The refrigerant flowing through the evaporator 25 flows into the compressor 21 again, and the cooling system circulates through a heat exchange cycle via a pipe 26 connecting each device.

FIG. 11 shows a conventional cooling device 27 including a sub heat exchanger 28 for supercooling (subcooling) a refrigerant after flowing through a condenser.

The sub heat exchanger 28 includes, for example, the condenser 22
For example, the refrigerant that has been heat-exchanged with the outside air in the condenser 22 is once passed through the receiver to separate the refrigerant into gas and liquid, and then passed through the sub heat exchanger 28 again. It is configured to flow and exchange heat with outside air to supercool the refrigerant.

In this way, the sub-heat exchanger 28 is in a state of supercooling of the refrigerant, and in this state, adiabatic expansion of the expansion valve is performed.

[0007] Since the refrigerant adiabatically expands in a supercooled state, it is possible to improve the heat exchange efficiency of the entire heat exchange cycle.

Further, since the refrigerant is adiabatically expanded in a low temperature state supercooled by the expansion valve, the work of the expansion valve 24 and the evaporator 25 during the adiabatic expansion affected by the temperature difference is reduced, and the heat is reduced. It is possible to improve the heat exchange efficiency (cooling efficiency) of the entire exchange cycle.

For example, in the invention described in Japanese Patent Application Laid-Open No. H10-62021, heat exchange between the refrigerant flowing through the receiver and the refrigerant flowing through the evaporator is performed in the cooling device described above. It is equipped with a sub heat exchanger. That is, this sub heat exchanger is provided with a pipe through which the refrigerant flowing out of the evaporator flows in the receiver, and a relatively high-temperature refrigerant flowing or temporarily stored in the receiver and the evaporator. Heat exchange of the flowing relatively low-temperature refrigerant is performed.

In the invention described in Japanese Patent Application Laid-Open No. 6-185831, a heat exchanger is provided between an expansion valve and an evaporator, and one or more throttles are provided between the heat exchangers. The pressure of the flowing refrigerant is regulated, and the refrigerant flows substantially evenly through the branched refrigerant flow path inside the evaporator, thereby improving the heat exchange function of the evaporator.

[0011]

However, Japanese Patent Application Laid-Open No.
In the case of the invention described in JP-A-62021, it is necessary to separately provide the sub heat exchanger as described above, which complicates the configuration of the cooling device and increases the size of the cooling device itself. A problem arises when installing in

In the invention described in Japanese Patent Application Laid-Open No. 6-185831, heat exchange between the refrigerant ejected from the pressure reducing valve and the refrigerant flowing out of the evaporator is performed. Since adiabatic compression is performed in the compressor as it is, there is a problem that power consumption of the compressor cannot be reduced.

On the other hand, when the refrigerant is supercooled (subcooled) in the sub heat exchanger 28, the refrigerant flowing through the evaporator 25 is conceptualized in the compressor 21 so that the refrigerant has a predetermined high temperature and high pressure. It is necessary to be in a state of superheat (superheat) on the higher temperature side than before. However, when the refrigerant enters a superheat state, the power load applied to the compressor 21 increases, and the energy consumption in the compressor 21 increases.

Therefore, in view of the above problems, the present invention provides:
It does not require extra installation space, efficiently supercools the refrigerant, improves the heat exchange function of the cooling device, reduces the power load on the compressor, and saves energy. It is an object to provide a cooling device.

[0015]

According to a first aspect of the present invention, there is provided a compressor for compressing a refrigerant, a condenser for condensing the compressed refrigerant, and an expansion valve for adiabatically expanding the condensed refrigerant. And a cooling device provided with an evaporator for evaporating the expanded refrigerant, wherein the cooling device performs a heat exchanger on the refrigerant before flowing into the expansion valve and the refrigerant after flowing through the evaporator. The cooling device includes an internal heat exchanger, and the internal heat exchanger is provided integrally with the evaporator.

As described above, when the internal heat exchanger for exchanging heat between the refrigerant flowing through the condenser and the refrigerant flowing through the evaporator is provided, in this internal heat exchanger, the expansion valve is provided. The supercooling (subcooling) of the refrigerant before flowing in is performed, and the heat exchange efficiency of the cooling device can be improved.

On the other hand, the refrigerant after flowing through the evaporator exchanges heat with the refrigerant before flowing into the expansion valve, and flows into the compressor in a state where the temperature is increased. Increases the specific volume of the refrigerant, that is, flows into the compressor in a state where the density of the refrigerant is reduced,
In a state where the density of the refrigerant is reduced, the impossibility of power to be applied to the compressor for setting the refrigerant to a predetermined high temperature and high pressure is reduced, and energy can be saved.

Further, since the internal heat exchanger of this embodiment is provided integrally with the evaporator, the heat exchange efficiency can be improved and the energy consumption of the compressor can be improved without increasing the installation space of the entire cooling device as described above. Reduction can be achieved.

Therefore, for example, even when the cooling device of the present invention is mounted on a vehicle body or the like having a limited installation space, the installation space can be prevented from being enlarged by providing the internal heat exchanger, and the heat exchange efficiency can be reduced. And energy saving can be achieved.

According to a second aspect of the present invention, in the first aspect of the invention, the internal heat exchanger includes a plurality of first flow paths through which the refrigerant before flowing into the expansion valve flows. ,
A plurality of second flow paths through which the refrigerant flows after flowing through the evaporator were provided, and the flow paths were formed such that the first flow paths and the second flow paths were alternately adjacent to each other. It is provided with a plurality of refrigerant flow paths alternately flowing adjacently.

As described above, the internal heat exchanger has the first refrigerant flow path through which the refrigerant before flowing into the expansion valve flows and the second refrigerant flow path through which the refrigerant flowing out of the evaporator flows. Because it is provided adjacently, sufficient heat exchange is performed between the refrigerant flowing through the first refrigerant flow path and the refrigerant flowing through the second refrigerant flow path, before the refrigerant flows into the expansion valve. In addition to bringing the refrigerant into a desired supercooled state, the temperature of the refrigerant before flowing into the compressor is increased, the degree of superheat of the refrigerant is suppressed, and the power load applied to the compressor can be reduced.

According to a third aspect of the present invention, in the first aspect, the internal heat exchanger is formed by using a plurality of core plates constituting a plurality of refrigerant flow paths. The coolant flow path formed by joining a plurality of core plates together has a honeycomb-shaped cross section. As described above, the internal heat exchanger is formed by abutting a plurality of core plates. When the tops of the protrusions of the other core plate are joined to each other, a first refrigerant flow path is formed in which the two recesses are abutted symmetrically.

When the bottom surface of the concave portion of the first core plate and the bottom surface of the concave portion of the third plate are in contact with each other, the convex portion of the first core plate and the convex portion of the third core plate are contacted. A second refrigerant flow path is formed at the second position.

Therefore, by contacting the plurality of core plates provided with the concave and convex portions, for example, the first refrigerant flow path through which the refrigerant flowing out of the condenser flows and the second refrigerant flow out of the evaporator flow A coolant channel having a honeycomb shape in cross section, in which the flowing second coolant channels are alternately adjacent, is formed.

In the internal heat exchanger, when the first refrigerant flow path and the second refrigerant flow path are alternately adjacent to each other and the cross sections of the first and second refrigerant flow paths are formed in a honeycomb shape, The heat exchange between the refrigerant flowing through the first refrigerant flow path and the refrigerant flowing through the second refrigerant flow path is efficiently performed via the core plate that constitutes the flow path. The cooling state can be set, and the degree of superheat of the refrigerant can be suppressed, so that the heat exchange efficiency of the entire cooling device can be improved.

[0026]

BEST MODE FOR CARRYING OUT THE INVENTION

FIG. 1 is a diagram showing a schematic configuration of the cooling device of the present embodiment.

As shown in FIG. 1, the cooling device 1 of the present embodiment comprises:
A compressor 2 for compressing the refrigerant, a condenser 3 for exchanging heat between the compressed refrigerant and the outside air to condense the refrigerant, and a liquid receiver for temporarily separating the condensed gas into a liquid medium and temporarily storing a liquid medium therein. The apparatus includes a vessel 4, an expansion valve 5 for adiabatically expanding the liquid medium condensed in the condenser 3, and an evaporator 6 for evaporating the expanded refrigerant. Each of the devices is connected by a pipe 8 that allows the refrigerant to flow therein and communicates with each device.

The cooling device 1 includes an internal heat exchanger 7 for exchanging heat between the refrigerant flowing through the condenser 3 and the liquid receiver 4 and the refrigerant flowing through the evaporator 6. The internal heat exchanger 7 is provided integrally with the evaporator 6 and the expansion valve 5.

FIG. 2 is a perspective view showing a schematic configuration of an evaporator 10 provided integrally with the above-mentioned internal heat exchanger 7, expansion valve 5 and evaporator 6. FIG. 3 is an exploded view showing a schematic structure of a connection structure for connecting the internal heat exchanger 7, the expansion valve 5, and the evaporator 6.

As shown in FIG. 2 or FIG. 3, in the evaporator 10 of this embodiment, the internal heat exchanger 7 and the evaporator 6 are integrally joined via the expansion valve 5. For example, the internal heat exchanger 7
The internal heat exchanger 7 is connected to the expansion valve 5 via connecting portions 7a and 7b, and is connected to a connector 11 having a pipe 8a communicating with the condenser 3 and a pipe 8b communicating with the compressor 2. Then, the expansion valve 5 is connected to the evaporator 6 via the connecting portion 6a of the evaporator 6.

As shown in FIG. 2, the evaporator 6 includes a plurality of tubes 61, fins 62 mounted between the plurality of tubes 61, and a tank 6 for distributing the refrigerant to each tube 61.
3,64.

Next, the structure of the internal heat exchanger 7 will be described in detail.

FIG. 4 is a view showing a plurality of core plates 70 constituting the internal heat exchanger 7.

The core plate 70 has a plurality of concave portions 71 and convex portions 72 on the plate. In addition, four communication holes 73a, 73b, 73c, 73 are provided above and below the core plate.
d is drilled. Around the core plate 70, a flat contact portion 74 that is in contact with another core plate is formed.

Above and below the core plate 70, the ends of the core plate 70 are bifurcated, and the contact ends 75, 7 are formed with contact surfaces that contact the contact portions of the other core plates 70.
6 are formed.

As shown in FIG. 4, the contact surfaces of the contact portions 74 and the contact ends 75 and 76 of one core plate and the other core plate are joined to each other. The flat portions at the tops of the portions 72 are joined to form a first coolant flow path 100 between the recesses 71 of the two core plates.

The arrows in FIG. 4 indicate the flow direction of the refrigerant flowing through the first refrigerant flow path 100.

Further, 70 contact ends 7 of one core plate 7
5, 76, the bottom portion of the contact portion 74 and the concave portion 73 and the bottom portion of the contact portion 75, 76, the contact portion 74 and the concave portion 73 of another core plate 70 are joined together. The second coolant flow path 101 is formed between the projections 72 of the other core plate.

FIG. 5 shows a plurality of core plates 70 as in FIG. 4, and the arrows in FIG. 5 indicate the flow of the refrigerant flowing through the second refrigerant flow path 101 formed between the convex portions 72, 72. Indicates the direction of flow.

FIG. 6 is a perspective view showing a cross section in a state where a plurality of core plates 70 are in contact with each other.

As shown in FIG. 6, when the abutting end of the core plate 70, the bottom surface of the abutting recess 71, and the flat portion of the top of the projection 72 abut, a plurality of honeycombs having a honeycomb cross section are formed. First and second refrigerant flow paths 100 and 101 are formed.

The arrows in FIG. 6 indicate the first and second refrigerant flow paths 1.
It is an arrow showing the flowing direction of the refrigerant flowing through 00 and 101.

FIG. 7 is a cross-sectional view of the internal heat exchanger 7 showing a refrigerant flow path 100 through which the refrigerant flowing through the condenser 3 and the liquid receiver 4 flows, and FIG. It is sectional drawing of the internal heat exchanger 7 which shows the refrigerant | coolant flow path 101 which the flowing refrigerant | coolant flows.

As shown in FIGS. 7 and 8, side plates 77 and 78 are in contact with both ends of the plurality of core plates 70.

FIG. 7 shows the first refrigerant flow path 100. The refrigerant flows downward from the communication hole 73a of the core plate 70 through the refrigerant flow path 100 formed between the recesses 71, 71 of the two core plates, and the communication passage 79 connects the communication holes 73d, 73d. And again, the refrigerant flow path 100
Flow upward. The refrigerant repeats the above-described flow, and flows out of the communication hole 73a of the core plate 70 at the outermost end to flow toward another device.

FIG. 8 is a cross-sectional view showing the second refrigerant flow passage 101. The refrigerant flows from the communication holes 78d formed in the side plate 78 through the core plate 70 and the side plate 7 through the communication holes 78d.
8 and flows through the refrigerant flow path 102 between
Through the communication passage 79 formed between the communication holes 73b, 73b, and the two core plates 70,
70, flows downward between the second refrigerant flow paths 101 formed between the convex portions 72, 72, and flows through the connection path 79 connecting the communication holes 73c, 73c of the two core plates 70, Again, the refrigerant flows upward in the refrigerant flow path 101. The refrigerant repeats the above-described flow, and finally, the core plate
0, flows through the flow path 103 between the side plates 77, and flows from the communication hole 77b formed in the side plate 77 to another device.

As described above, the first and second refrigerant flow paths 10
When 0, 101 is formed in an adjacent cross-sectional honeycomb shape, for example, the refrigerant flowing out of the condenser 3 and the liquid receiver 4 flows through the first refrigerant flow path 100, and If the refrigerant flowing out of the evaporator 6 is configured to flow through the refrigerant flow path 101, the relatively high-temperature refrigerant flowing through the first refrigerant flow path 100 and the second refrigerant flow path The flowing relatively low-temperature refrigerant exchanges heat through the core plate,
It is possible to improve the heat exchange efficiency and reduce the power load on the compressor 2.

FIG. 9 is a diagram showing the state of the refrigerant in the cooling device 1.

As shown in FIG. 9, the refrigerant is adiabatically compressed to a high temperature and a high pressure in the compressor 2 (between AB in FIG. 9).
Next, heat exchange with the outside air is performed in the condenser 3, and gas-liquid separation is performed in the liquid receiver 4 (between B and C in FIG. 9). here,
In the internal heat exchanger 7, the refrigerant flowing out of the condenser 3 and the liquid receiver 4 and flowing through the first refrigerant flow path 100 and the refrigerant flowing out of the evaporator 6 and flowing through the second refrigerant flow path 101. When heat exchange with the refrigerant is performed, the refrigerant flowing through the first refrigerant flow path is supercooled and moves from point C to point c in FIG. 9 toward the low enthalpy side, and the refrigerant is supercooled. The refrigerant becomes a liquid refrigerant and flows through the expansion valve 5.

When the refrigerant is in a liquid state by supercooling, evaporation and vaporization of the low-pressure and low-temperature refrigerant (between cd in FIG. 9) due to adiabatic expansion by the expansion valve 5 is improved, and the cooling effect is improved.

Further, when the refrigerant is supercooled, the compressor is adiabatically compressed to a predetermined high temperature and high pressure, so that the degree of superheat of the refrigerant increases. That is, the adiabatic compression performed in the state shown between AB in FIG. 9 is performed on the high enthalpy side shown between a and b in FIG. 9, the power load on the compressor increases, and the energy Consumption will increase.

In this example, in the internal heat exchanger 7,
Since heat exchange between the refrigerant flowing out of the evaporator 6 and the refrigerant flowing out of the condenser 3 and the liquid receiver 4 is performed, the temperature of the refrigerant flowing into the compressor 2 increases.

As described above, when the refrigerant temperature rises, the specific volume of the refrigerant becomes large, that is, the density becomes small on the Moliere line X diagram shown in FIG. 9, and the refrigerant is insulated in a low density state. Since the compressor is compressed, the power load on the compressor is reduced, and energy can be saved.

That is, supercooling of the refrigerant (cd in FIG. 9)
) To improve the heat exchange efficiency, suppress the degree of superheat of the refrigerant (between a and b in FIG. 9), and reduce the power load on the compressor 2. Further, in the cooling device provided with the internal heat exchanger 7, since the internal heat exchanger 7 is provided integrally with the evaporator 6 and the expansion valve 5, the above-mentioned effect can be obtained without increasing the installation space.

The internal heat exchanger 7 of the present embodiment is
Since the first refrigerant flow path 100 through which the refrigerant flowing out of the liquid receiver 4 flows and the second refrigerant flow path 101 through which the refrigerant flowing out of the evaporator 6 flows are alternately adjacent to each other, the number is small. Desired heat exchange efficiency can be obtained in the space.

In the internal heat exchanger 7 of this embodiment, the first refrigerant flow paths 100 and the second refrigerant flow paths 101 are formed in a honeycomb shape in which the cross sections are alternately adjacent to each other, but the cross-sectional shape is limited to the honeycomb shape. Not something.

[0058]

As described above, the present invention provides a compressor for compressing a refrigerant, a condenser for condensing the compressed refrigerant, an expansion valve for performing adiabatic expansion of the condensed refrigerant, and an expanded valve. In a cooling device provided with an evaporator that evaporates the refrigerant, the cooling device is an internal heat exchanger that performs heat exchange between the refrigerant before flowing into an expansion valve and the refrigerant after flowing through the evaporator. Wherein the internal heat exchanger is a cooling device provided integrally with an evaporator.

As described above, when the internal heat exchanger for exchanging heat between the refrigerant flowing through the condenser and the refrigerant flowing through the evaporator is provided, in this internal heat exchanger, the expansion valve is connected to the expansion valve. The supercooling (subcooling) of the refrigerant before flowing in is performed, and the heat exchange efficiency of the cooling device can be improved.

On the other hand, the refrigerant after flowing through the evaporator exchanges heat with the refrigerant before flowing into the expansion valve, and flows into the compressor in a state where the temperature is increased. Increases the specific volume of the refrigerant, that is, flows into the compressor in a state where the density of the refrigerant is reduced,
In a state where the density of the refrigerant is reduced, the impossibility of power to be applied to the compressor for setting the refrigerant to a predetermined high temperature and high pressure is reduced, and energy can be saved.

Further, since the internal heat exchanger of this embodiment is provided integrally with the evaporator, the heat exchange efficiency is improved and the energy consumption of the compressor is reduced without increasing the installation space of the entire cooling device as described above. Reduction can be achieved.

Therefore, for example, even when the cooling device of the present invention is mounted on a vehicle body or the like having a limited installation space, the installation space is prevented from being enlarged by providing the internal heat exchanger, and the heat exchange efficiency is reduced. And energy saving can be achieved. The internal heat exchanger is configured such that the first refrigerant flow path through which the refrigerant flowing out of the condenser and the liquid receiver flows and the second refrigerant flow path flowing out of the evaporator flow alternately and adjacently. Constitute. For example, the plurality of first and second refrigerant flow paths are formed so that the cross-sectional shape becomes a honeycomb shape.
As described above, when the first and second refrigerant channels are provided so as to be alternately adjacent to each other, the first and second refrigerant channels flow through the core plate that forms the refrigerant channel. Since heat exchange between the refrigerants is performed, the refrigerant is supercooled, and the temperature of the refrigerant before flowing into the compressor is increased, so that the power load applied to the compressor can be reduced. further,
When the cross-sectional shape of the refrigerant flow path is a honeycomb shape, when the first and second refrigerant flow paths are provided adjacent to each other, the installation space can be reduced, and the first refrigerant flow is provided via the core plate. Since the heat exchange between the refrigerant flowing through the passage and the refrigerant flowing through the second refrigerant flow passage is efficiently performed, the refrigerant can be brought into a desired supercooled state, and the degree of superheat of the refrigerant can be reduced. In this way, it is possible to improve the heat exchange efficiency of the entire cooling device. In this manner, when the refrigerant flow path of the internal heat exchanger is configured, it is possible to efficiently perform heat exchange between the refrigerants having different temperature differences without forming an extra refrigerant flow path. Without increasing, it is possible to improve the efficiency of the cooling cycle and save energy.

[0063]

[Brief description of the drawings]

FIG. 1 is a diagram showing a schematic configuration of a cooling device according to a specific example of the present invention.

FIG. 2 is a view showing a device in which an internal heat exchanger, an expansion valve, and an evaporator are integrated according to a specific example of the present invention.

FIG. 3 is an exploded view showing a connection structure when an internal heat exchanger, an expansion valve, and an evaporator are integrated according to a specific example of the present invention.

FIG. 4 is a view showing a core plate constituting an internal heat exchanger according to a specific example of the present invention and showing a flowing direction of a refrigerant flowing between recesses of the core plate.

FIG. 5 is a view showing a core plate constituting an internal heat exchanger according to a specific example of the present invention, and showing a flowing direction of a refrigerant flowing between convex portions of the core plate.

FIG. 6 is a perspective view showing a cross-sectional shape of an internal heat exchanger formed using a plurality of core plates according to a specific example of the present invention.

FIG. 7 is a cross-sectional view showing a first refrigerant flow path of an internal heat exchanger according to a specific example of the present invention.

FIG. 8 is a cross-sectional view showing a second refrigerant flow path of the internal heat exchanger according to a specific example of the present invention.

FIG. 9 is a diagram showing a state of a refrigerant flowing through a cooling device according to a specific example of the present invention.

FIG. 10 is a diagram showing a schematic configuration of a cooling device according to a conventional example.

11 is a diagram showing a state change of a refrigerant flowing through the cooling device shown in FIG. 10 according to a conventional example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Cooling apparatus 2 Compressor 3 Condenser 4 Liquid receiver 5 Expansion valve 6 Evaporator 6a Connection part 7 Internal heat exchanger 7a Connection part 7b Connection part 8 Pipe 8a Pipe 8b Pipe 9 Sub heat exchanger 10 Evaporator 11 Connector 20 Cooling device 21 Compressor 22 Condenser 23 Receiver 24 Expansion valve 25 Evaporator 26 Piping 27 Cooling device 28 Sub heat exchanger 61 Tube 62 Fin 63 Tank 64 Tank 70 Core plate 71 Concave portion 72 Convex portion 73a Communication hole 73b Communication hole 73c communication hole 73d communication hole 74 contact part 75 contact end part 76 contact end part 77 side plate 78 side plate 79 communication path 100 refrigerant flow path 101 refrigerant flow path 102 refrigerant flow path 103 refrigerant flow path

Continued on the front page (72) Inventor Muneo Sakurada 39, Higashihara, Chiyo-ji, Odai-gun, Osato-gun, Saitama Pref. (72) Kunihiko Nishishita 39, Higashihara, Chiyo, Odai-gun, Osato-gun, Saitama

Claims (3)

[Claims] 1. A compressor for compressing a refrigerant, a condenser for condensing the compressed refrigerant, an expansion valve for performing adiabatic expansion of the condensed refrigerant, and an evaporator for evaporating the expanded refrigerant. In the cooling device, the cooling device includes an internal heat exchanger that exchanges heat between the refrigerant before flowing into the expansion valve and the refrigerant after flowing through the evaporator, and the internal heat exchanger includes an evaporator. A cooling device characterized by being provided integrally with the cooling device. 2. The internal heat exchanger includes a plurality of first flow paths through which the refrigerant before flowing into the expansion valve flows, and a plurality of second flow paths through which the refrigerant flows through the evaporator. 2. The cooling device according to claim 1, wherein the flow path is formed such that the first flow path and the second flow path are alternately adjacent to each other. 3. 3. The internal heat exchanger is formed by using a plurality of core plates constituting a plurality of refrigerant flow paths, and is formed by joining a plurality of core plates to each other. 3. The cooling device according to claim 1, wherein a cross section of the refrigerant flow path has a honeycomb shape. 4.