JP2008002771A - Component for refrigerating cycle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a component for a refrigerating cycle capable of improving mounting performance to a vehicle with small space by simplifying a piping composition carrying a high pressure coolant between an expansion valve and an internal heat exchanger, and carrying out compactification. <P>SOLUTION: The component for a refrigerating cycle is arranged between a gas cooler and an evaporator for a vapor compression type refrigerating cycle, and The component for a refrigerating cycle controls a pressure of the coolant flowing into the evaporator on the basis of a temperature of the coolant flowing out from the gas cooler, and is provided with the expansion valve 4 controlling a pressure of the high pressure coolant flowing from the gas cooler to the evaporator, and the internal heat exchanger 9 provided so as to protrude outward from the expansion valve 4 and carrying out heat exchange between the high pressure coolant and a low pressure coolant flowing from an accumulator to a compressor to cool the high pressure coolant. A pair of opening ends 33a, 33b of the internal heat exchanger 9 is directly connected to openings 23b, 23c opened in a wall part of the expansion valve 4 in correspondence to each of the pair of the opening ends 33a, 33b. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a refrigeration cycle component that is disposed between a gas cooler and an evaporator of a vapor compression refrigeration cycle and controls the pressure of the refrigerant flowing into the evaporator based on the temperature of the refrigerant flowing out of the gas cooler.

  Generally, components for a refrigeration cycle used as an air conditioner are arranged between a gas cooler and an evaporator that are components of a vapor compression refrigeration cycle. This refrigeration cycle component has a pressure control valve that functions to control the pressure of the refrigerant flowing into the evaporator based on the temperature of the refrigerant flowing out of the gas cooler, and a function of cooling the refrigerant flowing into the evaporator by heat exchange. And an internal heat exchanger to exhibit. As this type of component for a refrigeration cycle, those disclosed in Patent Documents 1 and 2 are known as an example.

  The pressure control valve disclosed in Patent Documents 1 and 2 moves the valve body integrally formed on the back side of the diaphragm by displacing the diaphragm with the pressure of the refrigerant, and opens and closes the valve opening provided in the case It has a structure to do. The valve body is provided at a position where the valve opening can be freely opened and closed within the case. On the surface side of the diaphragm, a sealed space is formed between the diaphragm and the lid, and a gas as a refrigerant is sealed in the sealed space with a predetermined pressure, and the tip of the valve element is brought into contact with the valve port. it can.

  The contact force of the valve body with respect to the valve opening corresponds to the total force of the force of the gas sealed in the sealed space deforming the diaphragm and the spring force of the coil spring. A refrigerant having an arbitrary temperature flows into the case from the gas cooler side, and the pressure of the refrigerant is controlled based on the temperature of the refrigerant detected on the outlet side of the gas cooler. When the pressure exceeds the value, the valve body is pushed up to open, and the refrigerant flows out to the evaporator via the pressure control valve.

Further, the internal heat exchangers disclosed in Patent Documents 1 and 2 improve the efficiency of the evaporator by reducing the enthalpy of the refrigerant flowing into the evaporator when CO ₂ is used as the refrigerant, and improve the efficiency of the evaporator. The enthalpy of the refrigerant flowing into the machine is increased to improve the efficiency of the compressor. Thereby, the operating efficiency (COP) of the refrigeration cycle is increased.

JP 2000-179959 A JP 2002-206823 A

  However, in the configuration of the refrigeration cycle component of Patent Document 1, since the high-pressure pipe of the internal heat exchanger is connected to the pressure control valve via the intermediate member, the number of components increases and the manufacturing is complicated. There was a problem of becoming. Further, there is a problem that it is difficult to closely contact the contact surface between the intermediate member and the expansion valve and the contact surface between the intermediate member and the internal heat exchanger without any gaps.

  Patent Document 2 discloses a refrigeration cycle component in which a pressure reducing device having a function as a pressure control valve is fixed to an accumulator tank, and an internal heat exchanger is fixed to the pressure reducing device. That is, the accumulator tank, the pressure reducing device, and the internal heat exchanger are integrated. However, this refrigeration cycle component may be unsuitable for a limited mounting environment such as a vehicle or a chassis of an air conditioner because the structure is enlarged.

Therefore, in view of the above points, the present invention can simplify the piping configuration in which the high-pressure refrigerant flows between the expansion valve and the internal heat exchanger, thereby reducing the size and reducing the space of the vehicle. An object of the present invention is to provide a component for a refrigeration cycle that can be easily mounted on a battery.
It is another object of the present invention to provide a refrigeration cycle component that can reliably prevent refrigerant leakage between the expansion valve and the internal heat exchanger and has high quality reliability.

  In order to achieve the above-mentioned object, the invention according to claim 1 is arranged between a gas cooler and an evaporator of a vapor compression refrigeration cycle, and enters the evaporator based on a temperature of a refrigerant flowing out of the gas cooler. In the refrigeration cycle component for controlling the pressure of the refrigerant, an expansion valve for controlling the pressure of the high-pressure refrigerant flowing from the gas cooler to the evaporator, and an outlet from the expansion valve are provided, and the high-pressure refrigerant is supplied from the accumulator to the compressor. An internal heat exchanger that cools the high-pressure refrigerant by exchanging heat with the low-pressure refrigerant flowing to the internal heat exchanger, and the pair of open end portions of the internal heat exchanger are respectively connected to the pair of open end portions. Correspondingly, it is directly connected to an opening formed in the wall of the expansion valve.

  The invention according to claim 2 is the refrigeration cycle component according to claim 1, wherein the internal heat exchanger has a U shape extending from one opening end to the other opening end in order to flow the high-pressure refrigerant. It has a passage that folds in a turn and extends.

  According to a third aspect of the present invention, in the refrigeration cycle component according to the first or second aspect, the pair of opening end portions are connected to the opening portions by brazing.

  According to a fourth aspect of the present invention, in the refrigeration cycle component according to any one of the first to third aspects, a flow path that penetrates the inside of the expansion valve from one side wall to the other side wall is formed. The open end of the flow path formed on one side wall is a refrigerant inlet through which the high-pressure refrigerant flows from the gas cooler side, and the open end of the flow path formed on the other side wall is the refrigerant inlet The high-pressure refrigerant flowing out of the refrigerant flows out to the internal heat exchanger side.

  According to a fifth aspect of the present invention, in the refrigeration cycle component according to any one of the second to fourth aspects, the passage is formed by a flat tube, and the low-pressure refrigerant flows outside the tube. A low pressure tube is attached.

  As described above, according to the first aspect of the present invention, in the refrigeration cycle component including the expansion valve and the internal heat exchanger, the pair of open end portions of the internal heat exchanger has the pair of open end portions. The intermediate member for the joint can be made unnecessary between the expansion valve and the internal heat exchanger by being directly connected to the opening formed in the wall portion of the expansion valve corresponding to each. . As a direct connection method, various methods such as press fitting, brazing, and welding can be employed. Therefore, the piping configuration through which the high-pressure refrigerant flows can be simplified, the size can be reduced, and the mounting property in a vehicle having a small space can be improved. Moreover, refrigerant leakage can be reliably prevented between the expansion valve and the internal heat exchanger, and the quality reliability as an air conditioner can be enhanced.

  According to the invention described in claim 2, the high-pressure refrigerant flows through a passage that extends in a U-turn shape from one opening end portion to the other opening end portion, so that the medium exists outside the passage. It is possible to exchange heat between the two. By using a refrigerant having a temperature lower than that of the high-pressure refrigerant as the medium, the temperature of the high-pressure refrigerant can be lowered while the high-pressure refrigerant flows from one side to the other in the passage.

  According to the third aspect of the present invention, since the pair of opening end portions of the passage are connected to the opening portion by brazing, the wall portion of the expansion valve can be configured with a simple structure without using an intermediate member for the joint. It is possible to connect the passage directly. Moreover, it can prevent reliably that a refrigerant | coolant leaks from a connection part.

  According to the invention of claim 4, the refrigerant inlet into which the high-pressure refrigerant flows from the gas cooler side and the refrigerant outlet from which the high-pressure refrigerant flowing out from the refrigerant inlet flows out to the internal heat exchanger side are expanded. Since it is formed at both ends of the flow path penetrating the inside of the valve, this flow path can be manufactured by extruding (forging) the expansion valve. For this reason, compared with the case where the flow path through which the high-pressure refrigerant flows is manufactured by drilling, manufacturing is facilitated, productivity is increased, and manufacturing can be performed at low cost.

  According to the fifth aspect of the invention, since the low-pressure tube that allows the low-pressure refrigerant to flow is provided on the flat tube, the degree of freedom increases in the direction of taking out the low-pressure refrigerant, and the mountability of the components for the refrigeration cycle is improved. It can be improved. Further, since the radius of the bent portion of the tube can be increased, the pressure loss of the bent portion of the refrigerant can be reduced, and the high-pressure refrigerant can be efficiently cooled without impairing the performance of the refrigeration cycle.

Hereinafter, an embodiment of a refrigeration cycle component according to the present invention will be described with reference to the drawings. FIG. 1 is a diagram for explaining a vapor compression refrigeration cycle (supercritical refrigeration cycle) in which CO ₂ is circulated as a refrigerant. In FIG. 1, reference numeral 2 denotes a compressor (compressor) that sucks and compresses refrigerant (CO ₂ ), and reference numeral 3 denotes a gas cooler (heat radiator) that cools the high-pressure refrigerant compressed by the compressor 2. An expansion valve (pressure control valve) 4 that controls the refrigerant pressure based on the refrigerant temperature on the outlet side of the gas cooler 3 is disposed on the outlet side of the gas cooler 3. The expansion valve 4 also functions as a decompressor that decompresses high-pressure refrigerant. The expansion valve 4 is connected to a temperature sensing portion 6 provided in the refrigerant passage on the outlet side of the gas cooler 3, and the valve opening degree is controlled by a change in internal pressure based on the refrigerant temperature of the gas sealed in the temperature sensing portion 6. It is like that.

  Reference numeral 7 denotes an evaporator (evaporator) that evaporates the gas-liquid two-phase refrigerant decompressed by the expansion valve 4, and reference numeral 8 separates the gas-phase refrigerant and the liquid-phase refrigerant, and the excess refrigerant in the refrigeration cycle. It is an accumulator that stores temporarily. Reference numeral 9 denotes an internal heat exchanger that is provided on the front side of the expansion valve 4 and exchanges heat between the high-temperature and high-pressure refrigerant that flows from the gas cooler 3 to the expansion valve 4 and the low-temperature and low-pressure refrigerant that returns from the accumulator 8 to the compressor 2. . The compressor 2, the gas cooler 3, the internal heat exchanger 9, the expansion valve 4, the evaporator 7 and the accumulator 8 are connected by a refrigerant passage 5 to form a closed circuit. The expansion valve 4 and the internal heat exchanger 9 constitute a refrigeration cycle component 10 according to the present invention.

  Next, a first embodiment of the refrigeration cycle component 10 according to the present invention will be described with reference to FIGS. The refrigeration cycle component 10 of the present embodiment is provided to control the pressure of the high-pressure refrigerant flowing from the gas cooler 3 to the evaporator 7, and to be led out from the expansion valve 4. The high-pressure refrigerant is supplied from the accumulator 8 to the compressor. And an internal heat exchanger 9 that cools the high-pressure refrigerant by exchanging heat with the low-pressure refrigerant flowing into the refrigerant.

  The expansion valve 4 includes a block 15 as a housing in which a refrigerant passage is formed, a valve support 16 provided in the block 15, a valve body 17 movably accommodated in the valve support 16, a valve It comprises a cover 18 that forms a sealed space of gas sealed between a diaphragm 19 integrally formed at the upper end of the body 17.

  The block 15 has a quadrangular prism shape in appearance, and adjacent side walls are orthogonal to each other. In the block 15, the second opening formed in the side wall 22b on the other side is filled with the high-pressure refrigerant flowing in from the first opening (refrigerant inlet) 23a on the gas cooler 3 side formed in the side wall 22a on the one side. (Refrigerant outlet) First straight flow path 24 that flows out from 23b and flows to internal heat exchanger 9, and the side wall on the other side of the refrigerant that is folded in a U-turn shape inside pipe 33 of internal heat exchanger 9 A second flow path 25 that flows into the block 15 from the third opening 23c formed in 22b and flows out to the evaporator 7 side from the fourth opening 23d formed in the side wall 22a on one side, respectively. Is formed. Further, a support accommodating portion 27 that receives the valve support 16 from the upper wall side is formed in a direction (vertical direction) crossing the first flow path 24 and the second flow path 25.

  Like this embodiment, the opening part 23a into which a high pressure refrigerant | coolant flows in from the gas cooler 3 side is provided in one side wall 22a of the block 15 (expansion valve 4), and internal heat is provided in the other side wall 22b of the block 15 (expansion valve 4). By providing the opening 23b through which the high-pressure refrigerant flows out to the exchanger 9 side, the first flow path 24 can be formed through the block 15 by extrusion (forging). Specifically, each block as an intermediate product can be obtained by forming a through-hole in a long block material by extrusion and cutting the block material to a predetermined dimension by cutting. For this reason, compared with the case where the 1st flow path 24 is manufactured to each block by drilling, manufacture of a block becomes easy, productivity increases, and it can manufacture at low cost.

  In the present embodiment, the opening 23d provided on one side wall 22a of the block 15 (expansion valve 4) and the opening 23c provided on the other side wall 22b of the block 15 (expansion valve 4) are arranged vertically. The second flow path 25 is formed by drilling from two directions because it is shifted from each other and not positioned on a straight line, but the second flow path is changed by changing the shape of the valve port. Extrusion processing can also be applied by making 25 a straight line. When both the flow paths 24 and 25 are formed by extrusion, the production of the block 15 can be further enhanced.

  In the first flow path 24, the heat of the high-pressure refrigerant on the outlet side of the gas cooler 3 is transmitted to the temperature sensing unit 6 formed in the upper part of the valve body 17. The second flow path 25 is provided with a valve port 38 that is opened and closed by the distal end portion 42 of the valve body 17. The flow rate and pressure of the refrigerant flowing through the second flow path 25 are adjusted by opening and closing the valve port 38 by the distal end portion 42 of the valve body 17. The support accommodating portion 27 has a closed wall 27a on the lower side and an opening 27b on the upper side, and is formed in a cylindrical shape.

  The valve support 16 is inserted into the support housing portion 27, and the inner surface of the support housing portion 27 and the valve support 16 are sealed by seal members 30 a and 30 c provided on the inner wall of the support housing portion 27 and the wall portion of the valve support 16. No gap is formed between the outer surface. The inner surface of the valve support 16 and the valve body 17 are sealed by a seal member 30b.

  One end 33a (open end) of the pipe 33 of the internal heat exchanger 9 is press-fitted into the second opening 23b of the first flow path 24 and brazed so that the refrigerant does not leak from the gap. As a result, the gap is sealed liquid-tight. Similarly, the other end 33b (opening end) of the pipe 33 is press-fitted into the third opening 23c of the second flow path 25, and the gap is closed liquid-tightly by brazing. ing. For this reason, it is prevented that the 1st flow path 24 and the 2nd flow path 25 connect in the state which the expansion valve 4 is functioning, and a refrigerant | coolant does not leak from one side to the other.

  The valve support 16 has a cylindrical portion 35 a formed in a shape substantially corresponding to the support housing portion 27 on one side in the axial direction, and a flange portion 35 b fixed to the upper surface of the block 15 on the other side. A threaded portion is formed on the base side of the tubular portion 35a, and the threaded portion of the tubular portion 35a is used as the threaded portion of the support accommodating portion 27 in a state where the gasket 36 is sandwiched between the flange portion 35b and the wall portion of the block 15. The valve support 17 is fixed to the block 15 by screwing. A through hole 37 is formed in the axial center of the valve support 16 so as to penetrate from one end to the other end in the axial direction. A lower end opening of the through hole 37 serves as a valve port 38. The cylinder portion 35a has a refrigerant that is in heat exchange with the first communication hole 40a that communicates with the first flow path 24 in the direction orthogonal to the through hole 37, the fourth opening portion 23d, and the valve port 38. A second communication hole 40b is formed. The high-pressure refrigerant flows from the block 15 side to the internal heat exchanger 9 side through the first communication hole 40a, and flows from the internal heat exchanger 9 side to the floc 15 side through the second communication hole 40b. The flange portion 35 b is for defining the insertion depth of the valve support 16 with respect to the support housing portion 27 and fixing the valve support 16 to the block 15.

  The valve body 17 has a rod shape, and the valve support 16 is configured such that the base portion 41 located on the upper side is welded and fixed to the back surface of the diaphragm 19 and the tip portion 42 located on the lower side closes the valve port 38 in an openable and closable manner. It is arranged. The base portion 41 has a flange shape, and engages with a notch portion 35c of the flange portion 35b of the valve support 16 so as to be displaceable in the axial direction. The valve body 17 can be displaced together with the diaphragm 19 by an amount corresponding to the gap dimension between the base portion 41 and the notch portion 35c. An annular gap communicating with the first flow path 24 is formed between the outer surface of the rod-shaped portion of the valve body 17 and the inner surface of the valve support 16. For this reason, the high-pressure refrigerant flowing in from the first opening 23a flows into the annular gap through the first flow path 24, and at the same time, the heat of the high-pressure refrigerant is transmitted to the refrigerant in the temperature sensing unit 6. The pressure of the refrigerant acts on the diaphragm 19.

  On the upper side of the rod-like portion of the valve body 17, a sealed space 11 b is formed between the back surface of the diaphragm 19. The sealed space 11b communicates with the sealed space 11a formed between the surface of the diaphragm 19 and the cover 18, so that the sealed space is widened and the accuracy of the temperature sensing unit 6 is improved.

  Since the lower part of the rod-like part of the valve body 17 is in slidable contact with the inner surface of the valve support 16 via the seal member 30b in a liquid-tight state, the first flow path 24 and the second flow path 25 are provided. The refrigerant does not leak from one side to the other.

  The cover 18 forms a sealed space 11 a with the diaphragm 19 provided on the upper surface of the valve support 16. At the center of the cover 18, an enclosure tube 43 for enclosing the refrigerant at a predetermined pressure in the sealed space 11a is provided. The diaphragm 19 and the cover 18 that form the sealed space 11 a and the sealed space 11 b that are in communication with each other are constituent elements that constitute the temperature sensing unit 6 of the expansion valve 4.

  The diaphragm 19 is in the form of a thin film made of stainless steel, and is deformed and displaced according to the pressure difference between the inside and outside of the sealed spaces 11a and 11b. The peripheral edge of the diaphragm 19 is fixed by being sandwiched between the upper surface of the flange portion 35b of the valve support 16 and the lower surface of the cover 18, and the center portion can be deformed and displaced.

  The internal heat exchanger 9 has a pipe (passage) 33 that is integrally formed by extrusion and is folded and extended in a U-turn shape. The cross-sectional shape of the pipe 33 is a double pipe as shown in FIG. 7, and a high-temperature and high-pressure refrigerant flows through a center hole 34a formed at the center of the pipe 33, and a plurality of pipes 33 formed around the center hole 34a. The low-temperature and low-pressure refrigerant flows in the reverse direction through the peripheral hole 34b. For this reason, the high-temperature and high-pressure refrigerant flowing through the center hole 34a is heat-exchanged and cooled by the low-temperature and low-pressure refrigerant flowing through the peripheral hole 34b. Thereby, the enthalpy of the refrigerant flowing into the evaporator 7 can be reduced, the enthalpy difference on both sides of the evaporator 7 is increased, the cooling efficiency of the evaporator 7 is increased, and the load on the compressor 2 can be reduced. ing.

  As for the pipe 33, the outer peripheral part is removed in the edge part side. A joint member 45 for connecting the low-pressure refrigerant flowing through the peripheral hole 34b to the refrigerant passage is provided in the removed portion. As described above, the pair of open end portions 33a and 33b of the pipe 33 from which the peripheral hole 34b has been removed are press-fitted into the second opening portion 23b and the third opening portion 23c of the block 15 of the expansion valve 4, and then soldered. Connect directly.

  As described above, according to the present embodiment, by directly connecting the end portion of the pipe 33 to the block 15 of the expansion valve 4, the expansion valve 4, the internal heat exchanger 9, and the like can be used without using an intermediate member. It is possible to reliably prevent refrigerant leakage between the two. Since an intermediate member can be made unnecessary, the piping configuration of the internal heat exchanger 9 through which the refrigerant flows can be simplified. Moreover, the shift | offset | difference in the edge part of the U-shaped pipe 33 can be absorbed, and an assembly can be performed easily. Further, it is possible to provide a product that can reduce internal stress generated during pipe connection and maintain reliability over a long period of time.

  Next, a second embodiment of a refrigeration cycle component will be described with reference to FIG. In the present embodiment, a low-pressure flat tube 33B through which low-pressure refrigerant flows is provided on the flat tube 33A of the internal heat exchanger 9A through which high-pressure refrigerant flows, and the valve body 17A is closed by the adjustment coil spring 50. It is different from the first embodiment in that it is urged to. FIG. 8 shows a flat tube cross-sectional structure in which a plurality of holes 51a and 51b are formed inside. In the drawing, a low-pressure flat tube 33B through which the low-pressure refrigerant flows is located on the upper side, and a flat tube 33A through which the high-pressure refrigerant flows is located on the lower side. The upper and lower tubes 33A and 33B are bonded to each other, and heat transfer between the high-temperature refrigerant and the low-temperature refrigerant is performed through the bonded portion.

  As shown in FIG. 5, a plurality of passages arranged in a horizontal row are narrowed at both ends (only one end is shown in FIG. 5) of the flat tube 33A through which the high-pressure refrigerant flows to concentrate the passages into one. Tube cap 47 is provided. That is, the tube cap 47 has one end 47a on the flat tube 33A side having a wide opening (large opening) and the other end 47b on the side connected to the openings 23b and 23c formed on the wall portion of the block 15 having a narrow opening (small opening). ). The connection between the one end 47a of the tube cap 47 and the flat tube 33A and the connection between the other end 47b of the tube cap 47 and the openings 23b and 23c of the block 15 are performed by brazing so that the refrigerant does not leak from the connection portion. .

  At both ends of the low-pressure flat tube 33B, joint members 45A for connecting the low-pressure refrigerant to the refrigerant passage are provided. The connection between the tube 33B and the joint member 45A is preferably performed by press-fitting and brazing in order to reliably prevent the refrigerant from leaking.

  As in the present embodiment, the same effect as that of the first embodiment can be obtained by adding the low pressure tube 33B that allows the low pressure refrigerant to flow on the flat tube 33A. Since the low-pressure tube for flowing the low-pressure refrigerant is attached on the outer surface of the flat tube, the degree of freedom increases in the direction of taking out the low-pressure refrigerant, and the mountability can be improved. Furthermore, since the radius of the bent portion of the tube can be increased, the pressure loss of the refrigerant in the bent portion can be suppressed to a low level, and the high-pressure refrigerant can be efficiently cooled without impairing the performance of the refrigeration cycle.

  Further, by providing the adjustment coil spring 50, the valve closing force of the valve body 17A can be arbitrarily adjusted, and the application range of the expansion valve 4A can be expanded. Since the other components are the same as those in the first embodiment, a duplicate description will be omitted.

  Next, a third embodiment of a refrigeration cycle component will be described with reference to FIG. In the present embodiment, the internal structure of the expansion valve 4B is simplified, and the valve port 38B formed in the block 15A is directly closed by the valve body 17B instead of the cassette type as in the first and second embodiments. It was made like. Thus, even if the internal structure of the expansion valve 4B is different, the pipe 33 of the internal heat exchanger 9 can be directly connected to the wall of the block.

  In addition, this invention is not limited to the said embodiment, In the range which does not deviate from the main point of this invention, it can deform | transform and implement variously. For example, in the present embodiment, the expansion valves 4, 4 A, 4 B and the internal heat exchangers 9, 9 A, 9 B are connected by brazing after press-fitting, but can also be directly connected by brazing. It is possible to connect by other methods than attaching. Here, the direct connection between the pair of opening end portions 33a and 33b of the internal heat exchanger and the pair of opening portions 23b and 23c formed in the wall portion of the block 15 of the expansion valve 4 cannot be disassembled. Provided by the connection. This direct connection can be provided by a connection obtained by melting and then solidifying the metal again, such as brazing or welding using a hot flame or electrical discharge. This direct connection can also be provided by non-disassembling connections that cannot be disassembled without the use of special tools. The expansion valve 4 has a configuration in which both a high-pressure passage and a valve passage are formed in one block 15. For this reason, a pair of connections can be connected by a common connection process.

  In the present embodiment, the first side wall 22a of the block 15 is provided with a first opening 23a through which the high-pressure refrigerant flows from the gas cooler 3 side and a fourth opening 23d through which the refrigerant heat-exchanged to the evaporator side flows out. The second side wall 22b of the block 15 is provided with a second opening 23b through which the high-pressure refrigerant flows out toward the internal heat exchanger 9 and a third opening 23c through which the heat-exchanged refrigerant flows into the block 15. However, in the present invention, the positions of the first to fourth openings 23a are not limited to the aspect of the present embodiment, and can be provided at arbitrary positions. For example, the first opening 23a and the second opening 23b are provided on the adjacent side walls of the block 15 so that the first flow path 24 in the block 15 through which the high-pressure refrigerant flows is bent at a right angle, and heat exchange is performed. The third opening 23c and the fourth opening 23d may be provided on the adjacent side wall of the block 15 so that the second flow path 25 in the block 15 through which the refrigerant flows is bent at a right angle. As described above, by changing the positions of the first to fourth openings 23a, it is possible to increase the degree of freedom in the layout of the components for the refrigeration cycle, and it is possible to improve the component mountability.

It is a figure explaining the vapor compression refrigerating cycle which circulates CO2 as a refrigerant | coolant. It is sectional drawing of the components for refrigeration cycles of the 1st Embodiment of this invention used for the refrigeration cycle shown in FIG. FIG. 3 is an exploded cross-sectional view of the refrigeration cycle component shown in FIG. 2. It is sectional drawing of the components for refrigerating cycles of the 2nd Embodiment of this invention used for the refrigerating cycle shown in FIG. It is a top view of the tube cap shown in FIG. It is sectional drawing of the components for refrigeration cycles of the 3rd Embodiment of this invention used for the refrigeration cycle shown in FIG. It is sectional drawing of the pipe of the internal heat exchanger shown in FIG. It is sectional drawing of the tube of the internal heat exchanger shown in FIG.

Explanation of symbols

2 Compressor 3 Gas cooler 4 Expansion valve 7 Evaporator 9 Heat exchanger 10 Heat cycle component 15 Block 22a One side wall 22b Other side wall 23a First opening 23b Second opening 23c Third opening 23d Second 4 opening 33 pipe 33A tube 33a, 33b opening end

Claims (5)

Based on the temperature of the refrigerant that is disposed between the gas cooler (3) and the evaporator (7) of the vapor compression refrigeration cycle and flows out of the gas cooler (3), the pressure of the refrigerant flowing into the evaporator (7) is reduced. In refrigeration cycle parts to be controlled,
An expansion valve (4) for controlling the pressure of the high-pressure refrigerant flowing from the gas cooler (3) to the evaporator (7);
Internal heat that is provided so as to lead out from the expansion valve (4) and exchanges heat with the low-pressure refrigerant flowing from the accumulator (8) to the compressor (2) to cool the high-pressure refrigerant. An exchanger (9, 9A, 9B),
A pair of open end portions (33a, 33b) of the internal heat exchanger (9, 9A, 9B) correspond to each of the pair of open end portions (33a, 33b), and the wall of the expansion valve (4). A component for a refrigeration cycle, characterized in that it is directly connected to the opening (23b, 23c) formed in the opening.   The internal heat exchanger (9, 9A, 9B) is provided with a passage (33) extending in a U-turn shape from one open end (33a) to the other open end (33b). Item for refrigeration cycle according to Item 1.   The component for a refrigeration cycle according to claim 1 or 2, wherein the pair of opening end portions (33a, 33b) are connected to the opening portions (23b, 23c) by brazing.   A flow path (24) is formed through the expansion valve (4) from one side wall (22a) to the other side wall (22b), and the flow path (24) formed on one side wall (22a). Is the refrigerant inlet (23a) through which the high-pressure refrigerant flows from the gas cooler (3) side, and the open end of the flow path (24) formed in the other side wall (22b) is the refrigerant flow. The refrigeration cycle according to any one of claims 1 to 3, wherein the high-pressure refrigerant flowing out from the inlet (23a) is a refrigerant outlet (23c) flowing out toward the internal heat exchanger (9, 9A, 9B). Parts.   The refrigeration cycle according to any one of claims 2 to 4, wherein the passage (33) is formed of a flat tube, and a low-pressure tube 33B through which the low-pressure refrigerant flows is attached to the outside of the tube. parts.

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