KR102086378B1 - Cooling system for vehicle - Google Patents

Abstract

The present invention provides a compressor for compressing a refrigerant, a condenser for condensing the refrigerant discharged from the compressor, an expansion valve for expanding the refrigerant discharged from the condenser, and an evaporator for evaporating the refrigerant discharged from the expansion valve through heat exchange with the outside and the outside. A refrigeration system comprising: a sub-expansion line for bypassing a part of the refrigerant discharged from the condenser and supplying it to the compressor, a sub-expansion valve provided in the sub-expansion line, and a condenser and an expansion valve, and discharged from the condenser. And a first heat exchanger configured to exchange heat between the first refrigerant and the second refrigerant expanded by the sub-expansion valve, wherein the first heat exchanger includes: a high-pressure flow path through which the first refrigerant flows and a sub-flow through which the second refrigerant flows; Provided is a vehicle cooling system, each of which is a double pipe in which expansion passages are formed.
Therefore, through the heat exchange with the sub-expanded refrigerant, it is possible to secure sufficient sub-cooling even with a low flow rate refrigerant, improve efficiency, and reduce the sub-cooling area in the condenser to increase the size and capacity of the condenser. There is no need to facilitate design and manufacturability, and the cost can be reduced by reducing the amount of refrigerant filling, thereby ensuring economical and sufficient supercooling degree.

Description

Cooling system for vehicle

The present invention relates to a vehicle cooling system, and more particularly, to a vehicle cooling system capable of securing sufficient sub-cooling to improve the cooling performance of an air conditioner as well as reducing the amount of refrigerant filling by reducing the sub-cooling area in the condenser. It is about.

In general, a vehicle is provided with a cooling and heating system to control the temperature inside the vehicle. A dual cooling system includes a compressor that compresses a refrigerant in a gas state, a condenser that condenses the compressed refrigerant into a liquid state by condensing it into a liquid state, and a condensed refrigerant. It is configured to include an expander for reducing the pressure and the evaporator for evaporating the expanded refrigerant with the surroundings to vaporize the gas. In the present invention, such a cooling system is called a normal system.

On the other hand, in order to improve the efficiency of the cooling system, by increasing the supercooling degree of the refrigerant by heat exchange between the low-temperature low-pressure refrigerant flowing from the evaporator to the compressor and the high-temperature and high-pressure refrigerant flowing from the condenser to the expansion valve, A supercooling system has been developed to improve the COP (Coefficient of performance) of the cooling system, reduce the power consumption of the compressor, and improve the overall fuel economy of the vehicle. The liquid subcooling system of patent 2011-0060281 has been disclosed.

However, the liquid subcooling system, which is a vehicle cooling system of the related art, has a problem that it is difficult to secure sufficient supercooling degree because the superheat degree is limited without considering only the subcooling degree.

In addition, since the conventional normal system increases the subcooling area of the condenser and secures the supercooling degree, the condenser also needs to increase its size and capacity correspondingly.

According to the present invention, a sufficient sub-cooling is ensured through heat exchange of the refrigerant, and the residence time of the refrigerant is extended by guiding the flow of the refrigerant flowing along the high pressure flow path formed on the outer circumferential side of the inner tube in a spiral direction through the spiral groove. In addition, the heat exchange between the refrigerants is improved, improving the cooling performance, avoiding the increase in the size and capacity of the condenser, as well as easy to apply in a constrained layout (Lay-out), can reduce the amount of refrigerant filling An object of the present invention is to provide a cooling system for a vehicle capable of securing a sufficient degree of supercooling.

According to an aspect of the present invention, the present invention provides a compressor for compressing a refrigerant, a condenser for condensing the refrigerant discharged from the compressor, an expansion valve for expanding the refrigerant discharged from the condenser, and a refrigerant discharged from the expansion valve. A refrigeration system comprising an evaporator for evaporating through heat exchange with the outside and the outside, comprising: a sub-expansion line for bypassing a part of the refrigerant discharged from the condenser and supplying it to the compressor; and a sub-expansion valve provided in the sub-expansion line; And a first refrigerant disposed between the condenser and the expansion valve, the first refrigerant discharged from the condenser, a second refrigerant expanded by the sub expansion valve, and a third refrigerant discharged from the evaporator and supplied to the compressor. And a second heat exchanger configured to heat exchange, wherein the second heat exchanger is a high pressure oil through which the first refrigerant flows. And a triple tube formed with a sub expansion channel through which the second refrigerant flows and a suction channel through which the third refrigerant flows, wherein the sub expansion valve is an orifice having a diameter of 0.1 mm to 1.0 mm in the expansion diameter. The sub-expansion line is branched from the outlet side of the second heat exchange part between the second heat exchange part and the expansion valve, and the second heat exchange part has a sixth pipe in which a plurality of ribs protrude into an inner wall in a tubular shape, and The seventh tube is inserted into the sixth tube and the sub-expansion flow path is formed between the sixth pipe and the high-pressure flow path is formed therein, and the suction tube is inserted into the seventh pipe. Including an inner tube formed with a flow path, the inner tube is called a vehicle cooling system that is a spiral tube formed with a spiral groove on the outer peripheral side.

delete

delete

delete

delete

delete

delete

delete

The vehicle cooling system according to the present invention provides the following effects.

First, a sufficient subcool can be secured even with a low flow rate refrigerant through heat exchange with the sub-expanded refrigerant, and the spiral flows through the groove of the refrigerant flowing along the high pressure flow path formed on the outer circumferential side of the inner tube. By inducing it to extend the residence time of the refrigerant and it is possible to improve the heat exchange efficiency between the refrigerant.

Second, it is possible to reduce the sub-cooling area in the condenser, it is not necessary to increase the size and capacity of the condenser can facilitate the design and manufacturing.

Third, it is possible to reduce the cost, such as to reduce the amount of refrigerant filling is economical, it is possible to ensure a sufficient degree of subcooling.

1 is a configuration diagram schematically showing the configuration of a vehicle cooling system according to a first embodiment of the present invention.
FIG. 2 is a schematic diagram illustrating a configuration of a vehicle cooling system according to another exemplary embodiment of the sub-expansion line of FIG. 1.
Figure 3 is a schematic diagram showing the configuration of a vehicle cooling system according to a second embodiment of the present invention.
4 is a configuration diagram schematically showing the configuration of a vehicle cooling system according to another embodiment of the sub-expansion line of FIG.
5 is a front view illustrating the heat exchanger of FIG. 3.
6 to 8 are graphs showing performance by the vehicle cooling system of FIG. 3.
9 is a perspective view illustrating a structure of the subcooling part of FIG. 3.
10 is a cross-sectional view of the subcooling part of FIG. 9.
11 is a perspective view illustrating a structure according to another embodiment of the subcooling part of FIG. 3.
12 is a cross-sectional view of the subcooling part of FIG. 11.
13 is a perspective view illustrating a structure according to another embodiment of the subcooling part of FIG. 3.
14 is a cross-sectional view of the subcooling part of FIG. 13.

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

First, referring to FIG. 1, a vehicle cooling system 910 according to an exemplary embodiment of the present invention includes a compressor 100 for compressing a refrigerant, a condenser 200 for condensing the refrigerant discharged from the compressor 100, and And an expansion valve 300 for expanding the refrigerant discharged from the condenser 200 and an evaporator 400 for evaporating the refrigerant discharged from the expansion valve 300 through heat exchange with outside air. The expansion line 510, the surf expansion valve 600, and the first heat exchange part 700 are included.

Here, the compressor 100, the condenser 200, the expansion valve 300 and the evaporator 400 is a compressor, condenser, expansion valve and the evaporator and its configuration and operation in the known cooling system, so detailed description thereof will be omitted. In the following, only the configuration that is roughly differentiated will be described. In addition, although not shown, the condenser 200 may be provided with a receiver dryer is integrally provided or installed in a separate position.

The sub-expansion line 510 is a line for bypassing a portion of the high-temperature, high-pressure refrigerant discharged from the condenser 200 and supplying it to the compressor 100, and the condenser 200 and the first heat exchange part 700. Branched at the outlet side of the condenser 200 between the sub expansion valve 600.

The sub expansion valve 600 is provided in the sub expansion line 510 to expand a refrigerant flowing through the sub expansion line 510.

Here, the sub-expansion valve 600, it is preferable to apply an electromagnetic expansion valve or orifice (Orifice), but other configurations can be applied if the above object can be achieved.

The first heat exchange part 700 is disposed between the condenser 200 and the expansion valve 300, the surf expansion line 510 passes through, and is discharged from the condenser 200 to discharge the expansion valve 300. The first refrigerant of the high temperature and high pressure flowing in the) and the second refrigerant expanded by the sub expansion valve 600 serves to heat exchange with each other.

The first heat exchange part 700 may not only improve the supercooling degree (subcool) of the refrigerant discharged from the condenser 200, but also improve the performance of the expansion valve 300, as well as the inlet side of the evaporator 400. By lowering the enthalpy of can be obtained the effect of improving the performance of the evaporator (400).

On the other hand, the first heat exchange unit 700 is a double pipe for forming a flow path through which the first refrigerant and the second refrigerant flows, respectively, the first refrigerant and the second refrigerant can exchange heat with each other or The plate heat exchanger may be applied, and the double tube or plate heat exchanger is similar in structure to a known double tube and plate heat exchanger, and thus detailed description thereof will be omitted.

Referring to FIG. 2, unlike the vehicle cooling system 920, the sub-expansion line 520 may include the first heat exchanger between the first heat exchanger 700 and the expansion valve 300. 700) Branched at the exit side. Another embodiment of such a sub-expansion line 520 may be applied in response to the layout of the vehicle, the performance and fuel economy characteristics of the system.

As described above, the vehicle cooling system 910 and 920 includes a sub expansion system including the sub expansion lines 510 and 520, the sub expansion valve 600, and the first heat exchange part 700. Since the first refrigerant of high temperature and high pressure discharged from the outlet of the condenser 200 is exchanged with the second refrigerant of low pressure sub-expanded by the sub expansion valve 600, sufficient sub-cooling can be ensured even at a low flow rate. It can improve the performance of the whole cooling system.

Meanwhile, the normal system including only the compressor 100, the condenser 200, the expansion valve 300, and the evaporator 400 of FIG. 1 has a structure in which the supercooling degree is secured in the condenser 200. Another embodiment of the present invention described below has a structure of a sub-expansion system that further increases the subcooling as a method of further increasing the subcooling than the above-described normal system.

3, the vehicle cooling system 930 according to another embodiment of the present invention, the vehicle cooling system 930 is the compressor 100, the condenser 200, the expansion valve 300 In the cooling system including the evaporator 400, the sub expansion line 530, the sub expansion valve 600, and the second heat exchanger 800 are included. Here, the compressor 100, the condenser 200, the expansion valve 300, the evaporator 400, the sub expansion line 530, and the sub expansion valve 600 correspond to the configuration of FIG. 1. Detailed description will be omitted.

The second heat exchange part 800 constitutes a sub-expansion system and is disposed between the condenser 200 and the expansion valve 300, and the sub-expansion line 530 passes through and discharges from the condenser 200. The high-pressure first refrigerant 10 (see FIG. 5) and the second refrigerant 20 expanded by the sub-expansion valve 600 exchange heat with each other, and are discharged from the evaporator 400 and the compressor ( As the low-pressure third refrigerant 30 supplied to 100 passes, the first refrigerant 10, the second refrigerant 20, and the third refrigerant serve to exchange heat with each other.

The second heat exchange part 800 is a triple tube or plate heat exchanger having a flow path through which the first refrigerant 10, the second refrigerant 20, and the third refrigerant 30 flow, respectively. can do.

On the other hand, referring to Figure 4, the vehicle cooling system 940, unlike in Figure 3, the sub-expansion line 540 is the second heat exchange between the second heat exchange unit 800 and the expansion valve 300 In the case of branching at the outlet side of the part 800, another embodiment of such a sub-expansion line 540 may also be applied accordingly after grasping the layout of the vehicle and the performance and fuel economy characteristics of the system.

FIG. 5 is a view illustrating the second heat exchange part 800 in the vehicle cooling system 930 of FIG. 3, wherein a triple tube is applied to the second heat exchange part 800. First, the sub-expansion line 530 is branched from the outlet of the condenser 200 and flows into the second heat exchange part 800 via the orifice 600. In this case, reference numeral 531 denotes a branch where the sub-expansion line 530 is branched.

Here, the second heat exchange part 800 of the triple pipe includes a high pressure flow path through which the first refrigerant 10 flows, a sub expansion flow path through which the second refrigerant 20 flows, and the third refrigerant. Suction flow paths through which 30 flow are formed, respectively.

6 to 8 are graphs of evaluation results of the vehicle cooling system 930 to which the sub-expansion system of FIG. 3 is applied. Referring to the drawings, first, the graphs are the electronic expansion valve (EEV) to the second heat exchange unit 800. Is a graph showing cooling performance, required power, and COP according to the sub-expansion opening amount of the electromagnetic expansion valve.

Referring to the drawings, the appropriate subexpansion opening amount of the electromagnetic expansion valve is about 5 to 20, and when it is applied to the orifice, the diameter corresponding to the sub expansion opening amount of the electromagnetic expansion valve is preferably 0.1 mm to 1.0 mm. Do. This is because when the diameter is less than 0.1 mm or when the diameter exceeds 1.0 mm, as well as the performance and efficiency are reduced, as well as the power required increases as shown in the figure. On the other hand, the expansion diameter of the orifice can be appropriately selected in accordance with the degree to reduce the power consumption or to increase the performance according to the characteristics of each system.

On the other hand, the relationship between the refrigerant flow rate of the sub-expansion lines (510, 520, 530, 540) and the main flow rate branched from the outlet of the condenser 200 is correlated with the heat exchange amount through the sub-expansion, and heat exchange at a low flow rate to form a sufficient sub-cool If so, the smaller diameter of the orifice is better. Meanwhile, as described above, the vehicle cooling systems 910, 920, 930, and 940 that bypass the refrigerant of the condenser 200 and use the cooling heat to obtain the supercooling degree of the outlet of the condenser 200 by bypass heat, but the condenser 200 In order to obtain an effect of expanding a portion of the refrigerant in the first heat exchange part 700 or the second heat exchange part 800 to have a greater effect than the refrigerant flow rate, the first heat exchange part 700 or the second heat exchange part ( An appropriate value of the size of the 800 and the refrigerant flow rate of the sub-expansion lines 510, 520, 530, and 540 to be bypassed should be set.

Thus, referring to the appropriate criteria with reference to Figure 1, as shown in Equation 1, the heat exchange through the first heat exchange unit 700 for the mass flow rate (m) of the refrigerant flowing through the vehicle cooling system 910 The ratio of the mass flow rate m _y of the refrigerant flowing into the evaporator 400 is the difference between the enthalpy h ₇ at the outlet end of the evaporator 400 and the enthalpy h ₆ at the inlet end of the evaporator 400 in the sub-expansion system. The enthalpy (h ₆ ') of the inlet end of the evaporator 400 is greater than the difference in the enthalpy (h ₇ ') of the outlet end of the evaporator 400 in the normal cooling system for a large effect can be obtained.

Equation 1

On the other hand, while the appropriate criterion of the refrigerant flow rate according to Equation 1 is shown with reference to the vehicle cooling system 910 of FIG. 1, in addition to the vehicle cooling system 910 of FIG. 1, the vehicle cooling system of FIGS. 2 to 4 ( 920, 930, and 940 may be applied in the same concept.

Hereinafter, the second heat exchangers 810, 820, and 830 will be described with reference to FIGS. 9 through 14.

First, referring to FIGS. 9 and 10, the second heat exchange part 810 is a triple tube integrated extrusion pipe structure, which includes a first pipe 801, a second pipe 802, and a third pipe 803. ) And ribs 8001.

The first pipe 801 is disposed in the outermost in a tubular shape, the second pipe 802 is radially spaced apart inside the first pipe 801, the first pipe The sub-expansion flow path 1 is formed between the inner wall of 801.

The third pipe 803 is radially spaced inside the second pipe 802 so that the high pressure flow path 2 is formed between the second pipe 802 and the inner wall of the third pipe 802. The suction passage 3 is formed in the suction passage 3.

The rib 8001 is disposed between the first pipe 801 and the second pipe 802 and between the second pipe 802 and the third pipe 803, respectively. One pipe 801 and the second pipe 802 and the third pipe 803 are integrally connected to each other.

11 and 12, the second heat exchange part 820 includes a double pipe 806 and an inner pipe 808 inserted into the double pipe 806.

The double pipe 806 is disposed between the fourth pipe 804 and the inner wall of the fourth pipe 804 radially spaced apart from the inner side of the fourth pipe 804. A fifth pipe 805 having an expansion flow path 1 formed therein and a high pressure flow path 2 formed therein; and a fourth pipe 804 disposed between the fourth pipe 804 and the fifth pipe 805. ) And a plurality of ribs (8001) for integrally connecting the fifth pipe (805) with each other is a double pipe integrated compression pipe structure.

The inner tube 808 is inserted into the fifth tube 805, and the suction passage 3 is formed therein, and a detailed description thereof will be described later.

Referring to FIGS. 13 and 14, the second heat exchange part 830 includes a sixth pipe 8302, a seventh pipe 807, and the inner pipe 808. It has a detachable structure.

The sixth pipe (8062) has a tubular shape and a plurality of ribs (8061) protruding in the longitudinal direction to the inner wall. Here, the height of the ribs 8081 can be varied depending on the design of the sub-expansion flow path (1). In addition, the ribs 8081 can be spiraled depending on the processing method.

The seventh pipe 807 is inserted into the sixth pipe 8082 in a tubular shape to form the sub-expansion flow path 1 between the sixth pipe 8082 and the high pressure flow path therein. (2) is formed.

On the other hand, the inner tube 808 is preferably applied to the spiral type tube with the spiral grooves 8801 formed on the outer peripheral side. This is to extend the residence time of the refrigerant and improve heat exchange efficiency between the refrigerant by guiding the flow of the refrigerant flowing along the high pressure flow path 2 formed on the outer circumferential side of the inner tube 808 in a spiral direction.

Although the present invention has been described with reference to the embodiments illustrated in the drawings, this is merely exemplary, and it will be understood by those skilled in the art that various modifications and equivalent other embodiments are possible. Therefore, the true technical protection scope of the present invention will be defined by the technical spirit of the appended claims.

1 ... sub expansion passage 2 ... high pressure passage
3. Suction euro 100 ... Compressor
200 ... condenser 300 ... expansion valve
400 ... evaporator 510,520,530,540 ... sub-expansion line
600 ... sub expansion valve 700 ... first heat exchange part
800,810,820,830 ... The 2nd Heat Exchange Part 801 ... The 1st Hall
802 ... Hall 2 803 ... Hall 3
804 ... Building 4 805 ... Building 5
806 ... double tube 808 ... inner tube
8001,8061 ... Rib 8081 ... Spiral Home
910,920,930,940 ... Car Cooling System

Claims (11)

delete A compressor for compressing the refrigerant, a condenser for condensing the refrigerant discharged from the compressor, an expansion valve for expanding the refrigerant discharged from the condenser, and an evaporator for evaporating the refrigerant discharged from the expansion valve through heat exchange with the outside and the outside In the refrigeration system comprising,
A sub-expansion line for bypassing a part of the refrigerant discharged from the condenser and supplying it to the compressor;
A sub expansion valve provided in the sub expansion line;
A heat exchanger disposed between the condenser and the expansion valve to exchange the first refrigerant discharged from the condenser, the second refrigerant expanded by the sub-expansion valve, and the third refrigerant discharged from the evaporator and supplied to the compressor To include a second heat exchanger,
The second heat exchange part is a triple tube in which a high pressure flow path through which the first refrigerant flows, a sub-expansion flow path through which the second refrigerant flows, and a suction flow path through which the third refrigerant flows are formed, respectively.
The sub expansion valve is an orifice having an diameter of the expansion diameter of 0.1 mm to 1.0 mm,
The sub expansion line,
Branched at the outlet side of the second heat exchange part between the second heat exchange part and the expansion valve,
The second heat exchange unit,
A sixth tube in which a plurality of ribs protrude into the inner wall in a tubular shape,
A seventh tube inserted into the sixth tube to form the sub-expansion passage between the sixth tube and the high pressure passage formed therein;
And an inner tube inserted into the seventh tube and having the suction passage formed therein, wherein the inner tube is a spiral tube having a spiral groove formed on an outer circumferential side thereof. delete delete delete delete delete delete delete delete delete

Images