KR20090029891A - Double Tube Internal Heat Exchanger - Google Patents

Abstract

The present invention relates to a double-tube type internal heat exchanger, and more particularly, by installing separate connectors connected to inlet and outlet pipes at both ends of the external pipe so as to enlarge the flow path of the refrigerant flowing into or out of the external pipe. In addition, the present invention relates to a double-pipe internal heat exchanger capable of minimizing pressure loss of the refrigerant flowing into or out of the external tube and uniformly distributing a flow rate of the refrigerant flowing through each spiral high pressure flow path of the external tube.

Accordingly, the present invention is coupled to the inner tube 110, 110a and the outer peripheral surface of the inner tube 110, 110a to form a low pressure flow path 111 so that the refrigerant of low temperature and low pressure flows in high temperature and high pressure. Outer pipes 120 and 120a forming the high pressure flow passage 121 so that the coolant flows therein, and inlet / outlet pipes 125 for introducing / exhausting high-temperature and high-pressure refrigerant to the outer pipes 120 and 120a. 126, the double tube type internal heat exchanger for mutual heat exchange between the refrigerant flowing through the inner tube (110, 110a) and the refrigerant flowing through the outer tube (120, 120a), the outer tube (120, 120a) and The connector 130 may be installed between the inlet and outlet pipes 125 and 126 so as to enlarge a flow path of the refrigerant flowing into or out of the outer tube 120 and 120a.

Description

Dual pipe type internal heat exchanger

The present invention relates to a double-tube type internal heat exchanger, and more particularly, by installing separate connectors connected to inlet and outlet pipes at both ends of the external pipe so as to enlarge the flow path of the refrigerant flowing into or out of the external pipe. In addition, the present invention relates to a double-pipe internal heat exchanger capable of minimizing pressure loss of the refrigerant flowing into or out of the external tube and uniformly distributing a flow rate of the refrigerant flowing through each spiral high pressure flow path of the external tube.

The vehicle air conditioner is a vehicle interior that is installed for the purpose of securing the driver's front and rear view by removing the frost from the windshield or heating in the summer or winter, or during the rain or winter season. Such an air conditioning apparatus is usually provided with a heating system and a cooling system at the same time, thereby cooling, heating, or ventilating the interior of a vehicle by selectively introducing outside air or bet, heating or cooling the air, and then blowing the air into the interior of the vehicle.

In general, a cooling system of such an air conditioner has a compressor (1) for compressing and delivering a refrigerant as shown in FIG. 1, and a condenser (condenser) for condensing a high-pressure refrigerant from the compressor (1). 2) an expansion valve 3 for condensing the liquefied refrigerant condensed in the condenser 2, and a low pressure liquid refrigerant condensed by the expansion valve 3 is blown to the vehicle interior. It consists of a refrigeration cycle consisting of an evaporator (4) connected to the refrigerant pipe (5) to cool the air discharged to the room by the endothermic action of the latent heat of the refrigerant by evaporating by heat exchange with the air. Cool the inside of the car through the circulation process.

When the cooling switch (not shown) of the vehicle air conditioner is turned on, the compressor 1 first drives the engine power and sucks and compresses the low-temperature, low-pressure gaseous refrigerant to the condenser 2 in a high-temperature, high-pressure gas state. The condenser 2 exchanges the gaseous refrigerant with outside air to condense it into a liquid of high temperature and high pressure. Subsequently, the liquid refrigerant discharged from the condenser 2 in the state of high temperature and high pressure rapidly expands by the throttling action of the expansion valve 3 and is sent to the evaporator 4 in the low temperature low pressure wet state, and the evaporator 4 is The refrigerant is heat-exchanged with the air blower (not shown) blowing into the vehicle interior. Accordingly, the refrigerant is evaporated from the evaporator 4, discharged into a gas state at low temperature and low pressure, and then sucked back into the compressor 1 to recycle the refrigeration cycle as described above. In the above refrigerant circulation process, the cooling of the vehicle interior is cooled by latent heat of evaporation of the liquid refrigerant circulating in the evaporator 4 while the air blown by the blower (not shown) passes through the evaporator 4 as described above. It is made by discharging the inside of the vehicle in the cold state.

Meanwhile, a receiver dryer (not shown) is provided between the condenser 2 and the expansion valve 3 to separate the refrigerant in the gas phase and the liquid phase so that only the liquid refrigerant can be supplied to the expansion valve 3. .

As described above, the cooling efficiency of the air conditioner that provides cooling through the refrigerating cycle is determined by various factors. Among them, the subcooling of the high-pressure refrigerant immediately before being throttled by the expansion valve 3 and the evaporator 4 The superheat degree of the low pressure refrigerant discharged from the gas can affect the refrigerant fluidity, the amount of pressure drop in the evaporator 4, the superheated region of the evaporator 4 (partial region of the refrigerant outlet side of the evaporator), and the volumetric efficiency of the compressor 1, respectively. It has a significant influence on the cooling efficiency of the air conditioning system.

For example, if the subcooling of the refrigerant before the condensation increases, the specific volume of the refrigerant is reduced, the refrigerant flow is stabilized, and the refrigerant pressure drop in the evaporator 4 is reduced, so that the cooling efficiency of the air conditioner is increased, and the power of the compressor 1 is increased. Consumption is reduced. On the other hand, if the superheat degree of the low pressure refrigerant discharged from the evaporator 4 is not properly maintained, the relatively high temperature evaporator 4 is set such that the refrigerant can be completely vaporized to prevent the refrigerant 1 from entering the compressor 1. Since the overheating zone of) must be enlarged, the cooling performance of the air conditioner is reduced.

Therefore, the vehicle air conditioners generally increase the cooling performance if the supercooling degree of the refrigerant before being throttled and the superheating degree of the refrigerant discharged from the evaporator 4 are maintained.

Accordingly, in order to improve the cooling performance of the vehicle air conditioner, the supercooling of the high temperature and high pressure liquid refrigerant throttled by the expansion valve 3 before entering the evaporator 4 and the degree of superheat of the refrigerant discharged from the evaporator 4 are achieved. Various attempts have been made to optimize the bar, and as shown in FIG. 2, the high temperature and high pressure liquid refrigerant flowing into the expansion valve 3 and the low temperature low pressure gas phase refrigerant discharged from the evaporator 4 are illustrated in FIG. 2. The internal heat exchanger 10 which supercools the high-temperature high-pressure liquid refrigerant before throttling and optimizes the superheat degree of the low-pressure refrigerant discharged | emitted from the evaporator 4 by mutually exchanging heat exchanger is mainly used.

The internal heat exchanger (10) exchanges heat between the high temperature and high pressure liquid refrigerant before being throttled by the expansion valve (3) and the low temperature and low pressure gas phase refrigerant discharged from the evaporator (4), thereby preventing the flow of the refrigerant flowing into the evaporator (4). It stabilizes and reduces the amount of refrigerant pressure drop in the evaporator 4, and the refrigerant can be completely vaporized to prevent the introduction of the liquid refrigerant into the compressor 1 so that the temperature of the evaporator 4 is relatively high. It is possible to reduce the time).

Therefore, when the internal heat exchanger 10 is employed in the cooling system as shown in FIG. 2, the specific volume of the refrigerant flowing into the evaporator 4 is reduced, so that the amount of refrigerant pressure drop in the evaporator 4 is reduced, so that the evaporator 4 is reduced. The refrigerant flow in each cooling tube can be stabilized, and the refrigerant flowing into the compressor 1 can be superheated after being discharged from the evaporator 4, so that the temperature is relatively high, thereby reducing the cooling performance of the air conditioning system. The overheating area of the evaporator 4, which is a factor, can be reduced, which can greatly increase the cooling efficiency of the air conditioner. As a result, the compressor 1, the condenser 2, and the evaporator 4 can be made efficient, contributing to the high efficiency and miniaturization of the air conditioning apparatus.

3 is a view illustrating an example of the internal heat exchanger 10. As shown in the drawing, the internal heat exchanger 10 includes an inner tube 20 through which a low temperature low pressure refrigerant flows, and an outer circumferential surface of the inner tube 20. Coupled to the double tube structure in the high temperature and high pressure refrigerant flows made of an outer tube (30).

In addition, the inner tube 20 is formed of a spiral pipe so as to minimize a change in the flow path area when bending, and the outer tube 30 is formed of a circular pipe.

In addition, the inlet and outlet pipes 31 and 32 are coupled to both end portions of the outer tube 30 to allow the refrigerant to flow in and out.

Here, the inlet pipe 31 is a refrigerant pipe connecting the condenser 2 and the outer tube 30, and the outlet pipe 32 is a refrigerant connecting the outer tube 30 and the expansion valve (3). It is a pipe.

In addition, the inner tube 20 is formed by helically forming a specific portion of the refrigerant pipe connecting the compressor 1 in the evaporator (4).

On the other hand, the outer tube 30 is fitted in close contact with the outer peripheral surface of the inner tube 20 and both ends are welded to the outer peripheral surface of the inner tube (20).

Therefore, the high temperature and high pressure liquid refrigerant discharged from the condenser 2 is introduced into the outer tube 30 through the inlet pipe 31, and the refrigerant introduced into the outer tube 30 is the outer tube 30. And flows along the plurality of spiral high pressure flow passages 33 formed between the inner tube 20 and the expansion pipe 3 through the outlet pipe 32.

In addition, the low-temperature low-pressure gaseous refrigerant discharged from the evaporator 4 passes through the low-pressure flow path in the inner tube 20, and passes through the refrigerant passing through the inner tube 20 and the outer tube 30. The refrigerants are exchanged with each other.

Thereafter, the refrigerant passing through the inner tube 20 flows into the compressor 1.

However, the double tube internal heat exchanger 10 in which the inner tube 20 is formed of a spiral pipe and the outer tube 30 is formed of a circular pipe as described above is connected to the inlet and outlet pipes 31 and 32. As the flow path of the outer tube 30 side of the site is narrow, the pressure loss of the refrigerant flowing into or out of the outer tube 30 through the inlet and outlet pipes 31 and 32 increases, and at the same time, each spiral high pressure channel ( There is also a problem that the distribution of the refrigerant flow rate flowing through 33 is not uniform.

An object of the present invention for solving the above problems is to install a separate connector connected to the inlet and outlet pipes at both ends of the outer tube to enlarge the flow path of the refrigerant flowing into or out of the outer tube, the outer observation The present invention provides a double-tube internal heat exchanger capable of minimizing the pressure loss of the refrigerant flowing into or out of the reactor and uniformly distributing the flow rate of the refrigerant flowing through each spiral high pressure flow path of the external pipe.

In order to achieve the above object, the present invention provides an inner tube for forming a low pressure passage so that a low temperature and low pressure refrigerant flows, and a high pressure passage for combining a double tube structure with an outer circumferential surface of the inner tube and flowing a high temperature and high pressure refrigerant. In the double tube type internal heat exchanger for heat exchange between the refrigerant flowing through the inner tube and the refrigerant flowing through the outer tube consisting of an outer tube, and an inlet and an outlet pipe for introducing and discharging a high temperature and high pressure refrigerant into the outer tube. A connector is installed between the outer tube and the inlet and outlet pipes to enlarge a flow path of the refrigerant flowing into or out of the outer tube.

The present invention, by installing a separate connector connected to the inlet and outlet pipes at both ends of the outer tube to expand the flow path of the refrigerant flowing into or out of the outer tube, the refrigerant flowing into or out of the outer tube In addition to minimizing pressure loss, the flow rate distribution of the refrigerant flowing through the respective spiral high-pressure flow paths of the outer tube can be uniform, thereby improving the performance of the internal heat exchanger.

Hereinafter, the present invention will be described in detail with reference to the accompanying drawings.

Repeated description of the same construction and operation as in the prior art will be omitted.

4 is a block diagram showing a case in which a double tube internal heat exchanger according to the present invention is installed in a cooling system, FIG. 5 is a perspective view showing a double tube internal heat exchanger according to the present invention, and FIG. 6 is a double tube internal heat exchanger according to the present invention. It is sectional drawing which shows group, FIG. 7 is AA sectional drawing in FIG.

First, the vehicle cooling system to which the double tube internal heat exchanger 100 according to the present invention is applied includes a compressor 1, a condenser 2, a double tube internal heat exchanger 100, an expansion valve 3, an evaporator 4, The double tube internal heat exchanger 100 and the compressor 1 are sequentially connected to the refrigerant pipe to circulate the refrigerant.

In addition, the double tube internal heat exchanger (100) has an inner tube (110) for forming a low pressure flow path (111) so that the low temperature low pressure refrigerant discharged from the evaporator (4), and a double tube on the outer peripheral surface of the inner tube (110) The outer pipe 120 is coupled to the structure and forms a high-pressure flow passage 121 so that the high-temperature high-pressure refrigerant discharged from the condenser 2 flows.

Accordingly, by mutually heat-exchanging the refrigerant flowing out of the condenser 2 to the expansion valve 3 and the refrigerant flowing out of the evaporator 4 and flowing to the compressor 1 in the double tube internal heat exchanger 100, The refrigerant flowing into the expansion valve 3 is supercooled, and the superheat degree of the refrigerant flowing into the compressor 1 is appropriately increased.

In addition, the inner tube 110 is a refrigerant pipe installed to connect the evaporator 4 and the compressor 1 is used as the inner tube 110, in this case, the inner tube 110, the internal heat exchanger 100 The spiral portion 112 is formed at a specific portion to be configured.

The spiral portion 112 of the inner tube 110 is formed by forming a predetermined length of a specific portion of the inner tube 110 in the form of a spiral pipe.

In addition, the outer tube 120 is formed in the shape of a circular pipe is inserted into the outside of the inner tube 110 and its length is formed longer than the length of the spiral portion 112 of the inner tube (110).

At this time, both ends of the outer tube 120 is concentrically sealed to the outer circumferential surface of the inner tube 110 by welding or the like.

Then, the outer surface of the spiral portion 112 of the inner tube 110 is in close contact with the inner circumferential surface of the outer tube 120, so that between the spiral portion 112 of the inner tube 110 and the outer tube 120. In the three spiral high-pressure flow passage 121 is formed, the three spiral high-pressure flow passage 121 is not in communication with each other in an independent state.

Here, it is most preferable to form three spiral high pressure passages 121 formed by the spiral portion 112 of the inner tube 110, but may be formed less than three or more than three. However, when the number of the spiral high pressure flow passages 121 is less than three, the heat exchange performance is lowered, and when the number is more than three, the production of the spiral pipe becomes difficult.

In addition, the inlet and outlet pipes 125 and 126 are provided at both ends of the outer tube 120 so that the high temperature and high pressure refrigerant discharged from the condenser 2 is introduced into the outer tube 120 and passed through the outer tube 120. Is installed, in this case, between the outer tube 120 and the inlet, outlet pipes 125, 126 connector 130 to enlarge the flow path of the refrigerant flowing into or out of the outer tube 120 side Is installed.

The connector 130 is formed at one end of the connection portion 131 through which the inlet and outlet pipes 125 and 126 are connected inward, and at the other end thereof by welding or the like on the outer circumferential surface of the outer tube 120. An expansion tube 132 to be joined is formed.

At this time, when the connector 130 is bonded to the outer circumferential surface of the outer tube 120, it is preferable that the spiral portion 112 of the inner tube 110 is bonded to the unformed position.

In addition, the inner diameter of the expansion pipe 132 is preferably formed to be larger than the inner diameter of the inlet, outlet pipes 125, 126.

In addition, the inlet and outlet pipes 125 and 126 are joined by welding in a state of being connected to the connection part 131 of the connector 130.

On the other hand, the inlet pipe 125 is a refrigerant pipe connecting the inlet 121 and the condenser 2, the outlet pipe 126 is connected to the outlet 122 and the expansion valve (3). Is a refrigerant pipe.

As such, by installing a separate connector 130 in the outer pipe 120 to which the inlet and outlet pipes 125 and 126 are connected, the refrigerant flow path flowing in and out of the outer pipe 120 is expanded. The cross-sectional area of the inlet side and the outlet side of the outer tube 120 is increased so that the refrigerant flows into the outer tube 120 through the inlet pipe 125 or the refrigerant introduced into the outer tube 120 after heat exchange. When the outlet pipe 126 is discharged to minimize the pressure loss of the refrigerant.

In addition, the flow path distribution of the refrigerant flowing through the three spiral high-pressure flow paths 121 formed inside the outer pipe 120 by increasing the cross-sectional area of the inlet and outlet side flow paths of the outer pipe 120 through the connector 130. To make it as uniform as possible.

8 is a perspective view showing a double tube internal heat exchanger according to another embodiment of the present invention, Figure 9 is a cross-sectional view showing a double tube internal heat exchanger according to another embodiment of the present invention, as shown, the inner tube (110a) The connector 130 is similarly installed in the double tube internal heat exchanger formed in the shape of the circular pipe and the external pipe 120a formed in the spiral pipe shape.

The connector 130 is joined to the outer circumferential surface of both ends of the outer tube (120a) by welding, etc. At this time, the connector 130 is coupled to the side in which the spiral portion 122 is not formed in the outer tube (120a). .

In addition, the inlet and outlet pipes 125 and 126 are connected to the connector 130 coupled to both ends of the outer tube 120a.

Hereinafter, the operation of the double tube internal heat exchanger 100 according to the present invention will be described.

First, the high temperature / high pressure gaseous refrigerant compressed by the compressor 1 is discharged into the condenser 2, and the gaseous refrigerant introduced into the condenser 2 is condensed through heat exchange with external air. After the phase change to a high-pressure liquid refrigerant, it is introduced into the outer tube 120 of the internal heat exchanger 100 through the inlet pipe 125 and the connector 130.

The high temperature / high pressure refrigerant introduced into the outer tube 120 is discharged from the evaporator 4 in the process of being uniformly distributed to each spiral high pressure passage 121 in the outer tube 120 and flows through the inner tube 110. After mutual heat exchange with the low-temperature / low-pressure refrigerant flowing through the low pressure flow path 111 of the), it is introduced into the expansion valve (3) through the connector 130 and the outlet pipe 126 to be decompressed / expanded.

The refrigerant depressurized / expanded by the expansion valve (3) enters the evaporator (4) after being in a low / low pressure atomization state, and the refrigerant introduced into the evaporator (4) exchanges heat with air blown to the vehicle interior to evaporate. At the same time, the air blown into the vehicle interior is cooled by an endothermic action caused by latent heat of evaporation of the refrigerant.

Thereafter, the low temperature / low pressure refrigerant discharged from the evaporator 4 flows through the low pressure passage 111 of the inner tube 110 of the internal heat exchanger 100, and the spiral high pressure passage of the outer tube 120 ( After performing heat exchange with the high temperature / high pressure refrigerant flowing through 121, the compressor 1 is introduced.

As described above, in the double tube internal heat exchanger 100 of the present invention, the high temperature and high pressure refrigerant discharged from the condenser 2 flows into the spiral high pressure passage 121 of the outer tube 120, and the inner side in the opposite direction to the inner side of the double tube type internal heat exchanger 100. As the low pressure flow path 111 of the pipe 110 flows through the low temperature low pressure refrigerant discharged from the evaporator 4, the performance of the cooling system is improved through mutual heat exchange.

1 is a configuration diagram showing a general vehicle cooling system

2 is a block diagram showing a case in which an internal heat exchanger is installed in a general vehicle cooling system;

3 is a cross-sectional view showing an example of a conventional internal heat exchanger;

4 is a block diagram showing a case in which a double tube internal heat exchanger according to the present invention is installed in a cooling system;

5 is a perspective view showing a double tube internal heat exchanger according to the present invention;

6 is a cross-sectional view showing a double tube internal heat exchanger according to the present invention;

7 is a cross-sectional view taken along the line A-A in FIG.

8 is a perspective view showing a double tube internal heat exchanger according to another embodiment of the present invention;

9 is a cross-sectional view showing a double tube internal heat exchanger according to another embodiment of the present invention.

<Code Description of Main Parts of Drawing>

100: internal heat exchanger 110, 110a: inner tube

111: low pressure flow path 112: spiral portion

120,120a: outer tube 121: high pressure flow path

125: inlet pipe 126: outlet pipe

130: connector 131: connection part

132: expansion tube

Claims (5)

Inner pipes 110 and 110a forming the low pressure flow path 111 so that the low-temperature low-pressure refrigerant flows, and coupled to the outer peripheral surface of the inner pipes 110 and 110a in a double pipe structure, so that the high-temperature high-pressure refrigerant flows It consists of an outer tube (120) (120a) to form a high-pressure flow path 121, and the inlet and outlet pipes (125, 126) for introducing / discharging a high-temperature high-pressure refrigerant to the outer tube (120, 120a) side In the double tube type internal heat exchanger for mutual heat exchange between the refrigerant flowing through the inner tube (110, 110a) and the refrigerant flowing through the outer tube (120, 120a), The connector 130 between the outer tube 120 and 120a and the inlet and outlet pipes 125 and 126 to enlarge the flow path of the refrigerant flowing into or out of the outer tube 120 and 120a. Double tube internal heat exchanger, characterized in that is installed. The method of claim 1, The connector 130 includes a connection part 131 to which the inlet and outlet pipes 125 and 126 are connected, and an expansion part 132 coupled to an outer circumferential surface of the outer tube 120 and 120a. Double tube internal heat exchanger. The method of claim 1, Any one of the inner tube (110) (110a) and the outer tube (120 (120a)) is provided with a spiral portion (112, 122) formed in a spiral to form the high-pressure flow path 121 in a spiral Double tube internal heat exchanger, characterized in that. The method of claim 3, wherein The inner tube 110 is formed with a spiral portion 112 forming three spiral high-pressure flow path 121, The outer tube 120 is a double tube internal heat exchanger, characterized in that formed in the shape of a circular pipe. The method of claim 1, Both ends of the outer tube (120) (120a) is concentric with the double tube type internal heat exchanger, characterized in that bonded to the inner tube (110) (110a).

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