KR102711202B1 - Heat exchanger - Google Patents

Abstract

The present invention provides a heat exchanger including a condenser and an evaporator through which refrigerant moves, an internal heat exchanger for heat-exchanging the refrigerant passing through the condenser and the refrigerant passing through the evaporator, and an accumulator for separating the refrigerant discharged from the evaporator into gas and liquid, wherein the internal heat exchanger is disposed inside the accumulator.

Description

Heat exchanger

The invention relates to a heat exchanger. More specifically, it relates to a heat exchanger for controlling the subcooling of a refrigerant before it is throttled by an expansion valve and the superheating of a refrigerant discharged from an evaporator.

A typical vehicle cooling system, as shown in Fig. 1, is composed of a compressor (1) that compresses and discharges a refrigerant, a condenser (2) that condenses the high-pressure refrigerant discharged from the compressor (1), an expansion valve (3) that condenses the refrigerant condensed and liquefied in the condenser (2), and an evaporator (4) that cools the air discharged into the interior by absorbing heat due to the latent heat of vaporization of the refrigerant by evaporating the low-pressure liquid refrigerant discharged from the expansion valve (3) through heat exchange with air blown into the interior of the vehicle, thereby forming a refrigeration cycle in which the interior of the vehicle is cooled through the following refrigerant circulation process.

When the vehicle cooling system is operated, the compressor (1) is first driven to suck and compress low-temperature and low-pressure gaseous refrigerant and send it to the condenser (2) in a high-temperature and high-pressure gaseous state, and the condenser (2) condenses the gaseous refrigerant into a low-temperature and high-pressure liquid by exchanging heat with the outside air. Then, the liquid refrigerant sent from the condenser (2) in a low-temperature and high-pressure state is rapidly expanded by the throttle action of the expansion valve (3) and sent to the evaporator (4) in a low-temperature and low-pressure saturated state, and the evaporator (4) exchanges heat with the air blown into the vehicle interior by the blower. Accordingly, the refrigerant evaporates in the evaporator (4) and is discharged in a low-temperature and low-pressure gaseous state and is sucked back into the compressor (1) to recirculate the refrigeration cycle as described above.

In the refrigerant circulation process, cooling of the vehicle interior is achieved by, as described above, cooling of the air blown by the blower through the evaporator (4) by the latent heat of vaporization of the liquid refrigerant circulating within the evaporator (4) and then discharging it into the vehicle interior in a cooled state.

The cooling efficiency of the cooling system as described above is determined by various factors, among which, the degree of subcooling of the high-pressure refrigerant just before being throttled by the expansion valve (3) and the degree of superheating of the low-pressure refrigerant discharged from the evaporator (4) affect the fluidity of the refrigerant, the pressure drop in the evaporator (4), the superheated area of the evaporator (4) (a portion of the refrigerant discharge port side of the evaporator), and the volumetric efficiency of the compressor (1), which significantly affect the cooling efficiency. For example, if the degree of subcooling of the refrigerant before being throttled increases, the specific volume of the refrigerant decreases, thereby stabilizing the refrigerant flow and reducing the refrigerant pressure drop in the evaporator (4), thereby increasing the cooling efficiency of the air conditioning system and reducing the power consumption of the compressor (1).

On the other hand, if the superheat of the low-pressure refrigerant discharged from the evaporator (4) is not maintained appropriately, the relatively high temperature superheat area of the evaporator (4) that is set to allow the refrigerant to completely vaporize must be expanded to prevent the liquid refrigerant from flowing into the compressor (1), thereby reducing the cooling performance of the air conditioning system.

Accordingly, research is ongoing into vehicle cooling systems to maintain the subcooling of the refrigerant before it is throttled by the expansion valve (3) and the superheating of the refrigerant discharged from the evaporator (4).

Republic of Korea Publication No. 10-2015-0069354.

The invention aims to control the subcooling of the refrigerant before it is throttled by the expansion valve and the superheating of the refrigerant discharged from the evaporator.

The problems to be solved by the present invention are not limited to the problems mentioned above, and other problems not mentioned herein will be clearly understood by those skilled in the art from the description below.

An embodiment of the present invention provides a heat exchanger including a condenser and an evaporator through which a refrigerant moves; an internal heat exchanger for heat-exchanging the refrigerant passing through the condenser and the refrigerant passing through the evaporator; and an accumulator for separating the refrigerant discharged from the evaporator into gas and liquid, wherein the internal heat exchanger is disposed inside the accumulator.

Preferably, the condenser may include a pair of first header tanks arranged to face each other, a plurality of first tubes connected between the first header tanks, and a first housing surrounding the first tubes, and the evaporator may include a pair of second header tanks arranged to face each other, a plurality of second tubes connected between the second header tanks, and a second housing surrounding the second tubes.

Preferably, the first header tank and the second header tank, which are arranged in the same direction, may be characterized in that they share one header tank.

Preferably, at least one of the condenser and the evaporator may be characterized by having a two-row arrangement structure.

Preferably, the internal heat exchanger may include a first discharge pipe connected to the first header tank to discharge the refrigerant and pass through the accumulator, and the first discharge pipe may be characterized in that it contacts and exchanges heat with the refrigerant discharged through a second discharge pipe connected to the second header tank.

Preferably, the second discharge pipe may be characterized in that it is positioned above the first discharge pipe.

Preferably, the first discharge pipe may be characterized by branching into a plurality of pipe structures to increase the heat exchange area with the refrigerant discharged from the second discharge pipe.

Preferably, the first discharge pipe may be characterized by having a tubular structure to increase the heat exchange area with the refrigerant discharged from the second discharge pipe.

Preferably, the accumulator may be characterized in that a compartment for receiving refrigerant discharged from the second discharge pipe is provided inside the accumulator.

Preferably, the accumulator, the condenser, and the evaporator may be formed integrally.

According to an embodiment, the cooling efficiency can be increased by controlling the subcooling degree of the refrigerant before being throttled by the expansion valve and the superheating degree of the refrigerant discharged from the evaporator.

In addition, by arranging the internal heat exchanger inside the accumulator, it is possible to increase heat exchange efficiency while minimizing the space occupied by the component.

In addition, it has the effect of reducing the risk of refrigerant leakage and simplifying assembly by reducing the number of connections between each component.

The various advantageous and beneficial effects of the present invention are not limited to the above-described contents, and will be more easily understood in the course of explaining specific embodiments of the present invention.

Figure 1 is a structural diagram of a typical vehicle cooling system.
Figure 2 is a structural diagram of a vehicle cooling system in which an embodiment of the present invention is used.
Figure 3 is a structural diagram of a heat exchanger according to an embodiment of the present invention.
Fig. 4 is a first embodiment of an internal heat exchanger, which is a component of Fig. 3.
Fig. 5 is a second embodiment of an internal heat exchanger, which is a component of Fig. 3.
Fig. 6 is a third embodiment of an internal heat exchanger, which is a component of Fig. 3.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the attached drawings.

However, the technical idea of the present invention is not limited to some of the embodiments described, but can be implemented in various different forms, and within the scope of the technical idea of the present invention, one or more of the components between the embodiments can be selectively combined or substituted for use.

In addition, terms (including technical and scientific terms) used in the embodiments of the present invention can be interpreted as having a meaning that can be generally understood by a person of ordinary skill in the technical field to which the present invention belongs, unless explicitly and specifically defined and described, and terms that are commonly used, such as terms defined in a dictionary, can be interpreted in consideration of the contextual meaning of the relevant technology.

Additionally, the terms used in the embodiments of the present invention are for the purpose of describing the embodiments and are not intended to limit the present invention.

In this specification, the singular may also include the plural unless specifically stated otherwise in the phrase, and when it is described as “A and/or at least one (or more) of B, C”, it may include one or more of all combinations that can be combined with A, B, C.

Additionally, in describing components of embodiments of the present invention, terms such as first, second, A, B, (a), (b), etc. may be used.

These terms are only intended to distinguish one component from another and are not intended to limit the nature, order, or sequence of the component.

In addition, when a component is described as being “connected,” “coupled,” or “connected” to another component, it may include not only cases where the component is directly connected, coupled, or connected to the other component, but also cases where the component is “connected,” “coupled,” or “connected” by another component between the component and the other component.

In addition, when described as being formed or arranged “above or below” each component, above or below includes not only the case where the two components are in direct contact with each other, but also the case where one or more other components are formed or arranged between the two components. In addition, when expressed as “above or below,” it can include the meaning of the downward direction as well as the upward direction based on one component.

Hereinafter, embodiments will be described in detail with reference to the attached drawings. Regardless of the drawing symbols, identical or corresponding components will be given the same reference numbers and redundant descriptions thereof will be omitted.

FIGS. 2 to 6 clearly illustrate only the main features in order to conceptually clearly understand the present invention, and as a result, various modifications of the drawings are expected, and the scope of the present invention need not be limited by specific shapes illustrated in the drawings.

Figure 2 is a structural diagram of a vehicle cooling system in which an embodiment of the present invention is used.

Referring to FIG. 2, the structure of a vehicle cooling system in which an embodiment of the present invention is used may include a heat exchanger having a condenser (100), an evaporator (200), and an accumulator (300), an expansion valve (500), and a compressor.

At this time, an internal heat exchanger may be provided inside the accumulator (300) in which the refrigerant passing through the condenser (100) and the refrigerant passing through the evaporator (200) exchange heat during the circulation process. The internal heat exchanger is arranged inside the accumulator (300) where separation of gas and liquid occurs, and aims to increase cooling efficiency by controlling the degree of subcooling of the refrigerant before being throttled by the expansion valve (500) and the degree of superheating of the refrigerant discharged from the evaporator (200).

These vehicle heat exchange systems have a basic structure in which refrigerant circulates through a condenser (100), an expansion valve (500), an evaporator (200), and a compression unit (600).

The condenser (100) condenses the high-temperature, high-pressure gaseous refrigerant discharged from the compression unit (600) into a low-temperature, high-pressure liquid by exchanging heat with an external heat source and sends it toward the expansion valve (500). In addition, the condenser (100) separates the gaseous refrigerant and the liquid refrigerant in a gas-liquid separator so that only the liquid refrigerant can be supplied toward the expansion valve (500). In one embodiment, the condenser (100) may use a water-cooling structure.

The expansion valve (500) rapidly expands the low-temperature, high-pressure liquid refrigerant discharged from the condenser (100) using a throttle action to create a low-temperature, low-pressure, saturated state and sends it to the evaporator (200). Here, the expansion valve (500) may be formed with an expansion path having an orifice to expand the refrigerant flowing from the condenser (100) toward the evaporator (200), and may be provided with a flow rate control means to control the degree of opening of the orifice to control the flow rate of the refrigerant flowing from the condenser (100) toward the evaporator (200).

The evaporator (200) cools the air being blown into the interior by heat absorption due to the latent heat of vaporization of the refrigerant by exchanging heat between the low-pressure liquid refrigerant condensed in the expansion valve (500) and the air being blown into the interior of the vehicle, thereby evaporating the liquid refrigerant. Then, the low-temperature and low-pressure gaseous refrigerant evaporated in the evaporator (200) is again sucked and compressed through the compression unit (600) to become a high-temperature and high-pressure gaseous state and sent to the condenser (100), and the cycle described above is repeated. At this time, the evaporator (200) may use a water-cooling structure.

The compression unit (600) can be driven by receiving power from a motor or engine as a power source, and can suck in and compress the low-temperature, low-pressure gaseous refrigerant discharged from the evaporator (200) to create a high-temperature, high-pressure gaseous state and send it to the condensation unit (100).

In this way, the refrigerant circulates through the condenser (100), expansion valve (500), evaporator (200), and compression unit (600).

The accumulator (300) can separate the refrigerant moving to the compression unit (600) into gaseous and liquid refrigerant and supply them to the compression unit (600). An internal heat exchanger (400), which is a component of the present invention, is arranged inside the accumulator (300) to control the subcooling degree of the refrigerant before being throttled by the expansion valve (500) and the superheating degree of the refrigerant discharged from the evaporator (200).

The structure of the accumulator (300) equipped with an internal heat exchanger is described again below.

Hereinafter, the condenser (100) and the evaporator (200) will be described based on a water-cooling structure.

Figure 3 is a structural diagram of a heat exchanger according to an embodiment of the present invention.

Referring to FIG. 3, the heat exchanger of the present invention may include a condenser (100), an evaporator (200), an internal heat exchanger, and an accumulator (300).

The condenser (100) may include a pair of first header tanks (110) arranged facing each other, a plurality of first tubes, and a housing.

The first header tanks (110) are provided as a pair and can form a path through which the high temperature and high pressure gaseous refrigerant compressed in the compression unit (600) moves. The first header tank (110) can form a path through which the refrigerant can move by brazing the header and the tank. The pair of first header tanks (110) are arranged to face each other, and a plurality of insertion holes for inserting the first tube can be formed on one side of the first header tank (110).

A plurality of first tubes (not shown) may be formed in an elongated shape, and a plurality of paths may be formed inside for the refrigerant to move. The first tubes may be inserted into the insertion holes of the first header tanks (110) that are arranged to face each other, and may be connected to the paths of the first header tanks (110). Since the shape and arrangement structure of the first tubes correspond to a known configuration, a detailed description thereof will be omitted.

The first housing (120) can form a passage for cooling water to move in a condenser (100) that operates in a water-cooled manner. The first housing (120) is provided with a structure that surrounds a plurality of tubes and fins arranged inside, and can form a cooling water movement passage that can move in the space between the first tube and the first tube (230).

In one embodiment, the first housing (120) may have a pair of plate-shaped structures that are joined to the sides of a plurality of first tubes. The first housing (120) may be joined to both sides of the first tubes through brazing welding to form a coolant passage in the space between the first tubes arranged above and below.

The evaporator (200) may include a pair of second header tanks (210), a plurality of second tubes arranged to connect the second header tanks (210), and a second housing (220).

The second header tank (210) is provided as a pair and can form a path through which low-pressure liquid refrigerant reduced by the expansion valve (500) moves.

The second header tank (210) can form a passage through which the refrigerant can move by brazing the header and the tank. A pair of second header tanks (210) are arranged to face each other, and a plurality of insertion holes for inserting a second tube (not shown) can be formed on one side of the second header tank (210).

In one embodiment, the second tube may be formed in a long shape, and a plurality of paths for the refrigerant to move may be formed inside. The second tube may be inserted into each of the insertion holes of the second header tank (210) that are arranged to face each other, and may be connected to the paths of the second header tank (210).

The second housing (220) can form a passage for the cooling water to move in the evaporator (200). The second housing (220) is provided with a structure that surrounds a plurality of second tubes and second fins, and can form a second cooling water movement passage that can move between the second tubes and the space between the second tubes.

Additionally, the first header tank (110) of the condenser (100) and the second header tank (210) of the evaporator (200) may be provided with a connected structure.

The first header tank (110) and the second header tank (210) provided as a pair may be provided in a structure in which each of the first header tank (110) and the second header tank (210) positioned in the same direction shares one header tank. In this case, the first header tank (110) and the second header tank (210) may be provided in a form in which the interior is partitioned using a baffle.

Through this connection structure, the number of connections between each component can be reduced, which has the effect of reducing the risk of refrigerant leakage.

In addition, at least one of the condenser (100) and the evaporator (200) may have a two-row arrangement structure. Through such a two-row arrangement structure, the condensation efficiency or evaporation efficiency can be increased.

The accumulator (300) can be formed integrally with the condenser (100) and the evaporator (200). The accumulator (300) can be formed integrally with the condenser (100) and the evaporator (200) through brazing welding, thereby reducing the number of parts for moving the refrigerant and preventing the refrigerant from leaking from the connecting portion.

The internal heat exchanger is placed inside the accumulator (300) and can perform heat exchange between the refrigerant that has passed through the condenser (100) and the refrigerant that has passed through the evaporator (200).

The structure of an accumulator (300) in which an internal heat exchanger (400) is arranged is described below.

Fig. 4 is a first embodiment of an internal heat exchanger (400), which is a component of Fig. 3.

The accumulator (300) includes a third housing (310) that forms a space in which the refrigerant supplied from the evaporator (200) can be separated into gas and liquid.

A second discharge pipe (420) into which refrigerant discharged from the evaporator (200) flows may be arranged in the third housing (310). The outlet refrigerant (L1) flowing in through the second discharge pipe (420) is separated into gas and liquid inside the accumulator (300), and the low-temperature refrigerant (G) of the gas moves to the compression unit (600) through the outlet (330) formed at the upper portion of the third housing (310).

At this time, a first discharge pipe (410) into which refrigerant discharged from the condenser (100) flows may be connected to the third housing (310). However, the first discharge pipe (410) may be provided with a structure that penetrates the third housing (310) to prevent the refrigerant discharged through the second discharge pipe (420) from being mixed with the refrigerant discharged through the first discharge pipe (410).

The refrigerant discharged through the second discharge pipe (420) is stored in the third housing (310), and the first discharge pipe (410) is arranged to pass through the stored refrigerant. At this time, the refrigerant moving through the first discharge pipe (410) can exchange heat with the refrigerant stored in the second discharge pipe (420) through the heat conduction of the first discharge pipe (410).

Fig. 5 is a second embodiment of an internal heat exchanger (400), which is a component of Fig. 3.

Referring to FIG. 5, the second discharge pipe (420) may be positioned higher than the first discharge pipe (410).

The internal heat exchanger (400) performs heat exchange between the refrigerant flowing into the accumulator (300) through the second discharge pipe (420) and the refrigerant moving through the first discharge pipe (410). At this time, the second discharge pipe (420) is positioned above the first discharge pipe (410) to increase the contact area and contact time between the refrigerant flowing in through the second discharge pipe (420) and the first discharge pipe (410), thereby increasing the heat exchange efficiency.

Fig. 6 is a third embodiment of an internal heat exchanger (400), which is a component of Fig. 3.

Referring to FIG. 6, the first discharge pipe (410) can change its pipe structure to increase its contact area with the refrigerant discharged from the second discharge pipe (420).

The first discharge pipe (410) has a structure that branches into multiple pipe structures to increase the heat exchange area with the refrigerant discharged from the second discharge pipe (420).

The first discharge pipe (410) has a tubular structure so as to increase the heat exchange area between the outer surface of the first discharge pipe (410) and the refrigerant discharged from the second discharge pipe (420).

The purpose of changing the structure of the first discharge pipe (410) is to increase the contact surface area of the limited capacity refrigerant.

In addition, a compartment (350) for receiving refrigerant discharged from the second discharge pipe (420) may be provided inside the accumulator (300). The compartment (350) may increase heat exchange efficiency by allowing the refrigerant discharged from the second discharge pipe (420) to exchange heat with the first discharge pipe (410) at the closest location.

Hereinafter, embodiments of the present invention will be described in detail with reference to the attached drawings.

The above description is merely an illustrative description of the technical idea of the present invention, and those skilled in the art will appreciate that various modifications, changes, and substitutions may be made without departing from the essential characteristics of the present invention. Accordingly, the embodiments disclosed in the present invention and the accompanying drawings are not intended to limit the technical idea of the present invention but to explain it, and the scope of the technical idea of the present invention is not limited by these embodiments and the accompanying drawings. The protection scope of the present invention should be interpreted by the following claims, and all technical ideas within a scope equivalent thereto should be interpreted as being included in the scope of the rights of the present invention.

100 : Condenser
110; 1st header tank
120 : 1st Housing
200 : Evaporation section
210: 2nd Header Tank
220: Second Housing
300 : Accumulator
310: 3rd Housing
330 : Exit
350 : Compartment
400 : Internal heat exchanger
410: 1st discharge pipe
420: 2nd discharge pipe
500 : Expansion valve
600 : Compression section

Claims (10)

A condenser and an evaporator through which the refrigerant moves;
An internal heat exchanger that exchanges heat between the refrigerant passing through the condenser and the refrigerant passing through the evaporator; and
An accumulator that separates the refrigerant discharged from the above evaporator into gas and liquid;
Including,
The above internal heat exchanger is characterized in that it is placed inside the accumulator,
The above condenser comprises a pair of first header tanks arranged to face each other, a plurality of first tubes connected between the first header tanks, and a first housing surrounding the first tubes.
A heat exchanger characterized in that the evaporator comprises a pair of second header tanks arranged to face each other, a plurality of second tubes connected between the second header tanks, and a second housing surrounding the second tubes. delete In the first paragraph,
A heat exchanger, characterized in that the first header tank and the second header tank, which are arranged in the same direction, share one header tank. In the first paragraph,
A heat exchanger characterized in that at least one of the condensing section and the evaporating section has a two-row arrangement structure. In the first paragraph,
The above internal heat exchanger is connected to the first header tank and includes a first discharge pipe that discharges refrigerant and passes through the accumulator.
A heat exchanger characterized in that the first discharge pipe exchanges heat by coming into contact with the refrigerant discharged through the second discharge pipe connected to the second header tank. In clause 5,
A heat exchanger, characterized in that the second discharge pipe is positioned above the first discharge pipe. In clause 5,
A heat exchanger characterized in that the first discharge pipe branches into a plurality of pipe structures to increase the heat exchange area with the refrigerant discharged from the second discharge pipe. In clause 5,
A heat exchanger characterized in that the first discharge pipe has a tubular structure to increase the heat exchange area with the refrigerant discharged from the second discharge pipe. In clause 5,
A heat exchanger characterized in that a compartment for receiving refrigerant discharged from the second discharge pipe is provided inside the accumulator. In the first paragraph,
A heat exchanger characterized in that the accumulator, the condenser, and the evaporator are formed integrally.

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