Pipe material, piping member for air conditioner, and air conditioner

Abstract

This pipe material (1) has: an outer cylinder section (2); a plurality of partitions (3) that divide the inside of the outer cylinder section (2) into three or more cylinder internal spaces (4); a first cylinder internal space (41) that is surrounded by the outer cylinder section (2) and a first partition (31) from among the plurality of partitions (3); a second cylinder internal space (42) that is surrounded by the outer cylinder section (2) and a second partition (32) from among the plurality of partitions (3); and a third cylinder internal space (43) that is surrounded by the outer cylinder section (2) and the plurality of partitions (3). The first partition (31) is separated from the second partition (32).

Description

Pipe material, piping member for air conditioning device, and air conditioning device

[0001] The present invention relates to a pipe material, a piping member for an air conditioner, and an air conditioner.

[0002] Conventionally, temperature control systems, such as air conditioners, for controlling the temperature of an object by heat exchange with a heat transfer medium have been known. This type of system includes components including multiple heat exchangers and piping connecting the components. The piping used in temperature control systems is often a single pipe with a single flow path. However, using a single pipe to connect the components can lead to complex piping arrangements and cumbersome work for connecting the piping to the components. Furthermore, in applications where the space for arranging the components is extremely limited, such as automotive air conditioners, it is desirable to reduce the space required for piping arrangement.

[0003] In such cases, the piping connecting the components may be a parallel pipe formed by integrating two single pipes, or a double pipe having an inner pipe and an outer pipe that houses the inner pipe, in which two or more flow paths are provided in one pipe (for example, Patent Document 1).

[0004] Japanese Patent Application Laid-Open No. 2001-277842

[0005] The temperature control system is configured to control the temperature of an object by circulating a heat transfer medium at a temperature corresponding to the target temperature of the object through a pipe and exchanging heat between the heat transfer medium and the object in a heat exchanger. To achieve this function, it is necessary to make the temperature difference between the heat transfer medium flowing into the heat exchanger and the temperature of the object before the heat exchange relatively large.

[0006] However, the temperature of the heat transfer medium flowing out of the heat exchanger differs from the temperature of the heat transfer medium flowing into the heat exchanger due to heat exchange with the object. Therefore, when a heat exchanger is connected to other components using double pipes or parallel pipes, heat exchange occurs in the piping between the heat transfer medium flowing into the heat exchanger and the heat transfer medium flowing out of the heat exchanger, which can easily reduce the temperature difference between the heat transfer medium flowing into the heat exchanger and the object.

[0007] The present invention has been made in consideration of the above background, and aims to provide a pipe material that can reduce the space required for arranging the pipe material and suppress heat exchange within the pipe material, as well as a piping component for an air conditioning device and an air conditioning device made of this pipe material.

[0008] One aspect of the present invention is a pipe material having an outer tube portion, a plurality of partitions dividing the interior of the outer tube portion into three or more inner tube spaces, a first inner tube space surrounded by the outer tube portion and a first partition of the plurality of partitions, a second inner tube space surrounded by the outer tube portion and a second partition of the plurality of partitions, and a third inner tube space surrounded by the outer tube portion and the plurality of partitions, wherein the first partition is separated from the second partition.

[0009] The pipe has at least three internal spaces divided by partition walls, which makes it possible to easily reduce the space required for arranging the pipe.

[0010] Furthermore, among the in-cylinder spaces of the tubing, the first in-cylinder space is separated from the other in-cylinder spaces by a first partition wall, and the second in-cylinder space is separated from the other in-cylinder spaces by a second partition wall. The first partition wall is separated from the second partition wall. Therefore, even when substances at different temperatures are circulated through the first and second in-cylinder spaces, the tubing can avoid heat exchange between the substance in the first in-cylinder space and the substance in the second in-cylinder space via the partition wall.

[0011] Furthermore, a third intra-cylinder space is provided between the first intra-cylinder space and the second intra-cylinder space, and therefore, by suppressing heat conduction in the third intra-cylinder space, it is possible to suppress heat exchange between the substance in the first intra-cylinder space and the substance in the second intra-cylinder space via the third intra-cylinder space.

[0012] As described above, according to the above-mentioned aspects, it is possible to provide a pipe material that can reduce the space required to arrange the pipe material and suppress heat exchange within the pipe material, a piping component for an air conditioning device, and an air conditioning device equipped with this piping.

[0013] FIG. 1 is a side view of a pipe material in Example 1. FIG. 2 is a cross-sectional view taken along line II-II in FIG. 1. FIG. 3 is a cross-sectional view of a pipe material in Example 2, taken perpendicular to the extending direction of the pipe material. FIG. 4 is a cross-sectional view of a pipe material in Example 3, taken perpendicular to the extending direction of the pipe material. FIG. 5 is a graph showing the results of heat transfer analysis in an experimental example. FIG. 6 is an explanatory diagram showing the temperature distribution in a pipe in a steady state obtained by heat transfer analysis using structural model A in an experimental example. FIG. 7 is a cross-sectional view of a cross-section perpendicular to the extending direction of the pipe material in structural model C in an experimental example. FIG. 8 is a cross-sectional view of a cross-section perpendicular to the extending direction of the pipe material in structural model D in an experimental example. FIG. 9 is an explanatory diagram showing the temperature distribution in a pipe in a steady state obtained by heat transfer analysis using structural model C in an experimental example. FIG. 10 is a cross-sectional view of a cross-section perpendicular to the extending direction of the pipe material in structural model E in an experimental example. FIG. 11 is an explanatory diagram showing the schematic configuration of an air conditioning apparatus in Example 4.

[0014] (Pipe material) The pipe material has an outer tubular portion that forms its outer wall, and the outer tubular portion separates the inside and outside of the pipe material. The outer tubular portion may be tubular, and its specific shape may take various forms. For example, the outer tubular portion may have a cylindrical shape or a rectangular tubular shape. Furthermore, the cross-sectional shape of the outer tubular portion in a cross section perpendicular to the flow direction of the heat transfer medium may be a distorted circle, such as an oval or ellipse.

[0015] The outer tubular portion preferably has a cylindrical shape. In this case, the tubular material can be easily bent in various directions, which reduces restrictions on the arrangement of devices when connecting multiple devices with the tubular material. Furthermore, by making the outer tubular portion cylindrical, the pressure resistance of the outer tubular portion can be more easily increased. As a result, the pressure of the substance circulating in each tube space can be more easily increased.

[0016] The diameter of the outer tube portion may be set appropriately depending on the flow rate and flow velocity of the substance flowing through the tubing. For example, if the outer tube portion has a cylindrical shape, the outer diameter of the outer tube portion may be set appropriately within a range of 12 mm to 26 mm. The thickness of the outer tube portion may be set appropriately depending on the desired pressure resistance, etc. For example, if the outer tube portion has a cylindrical shape, the thickness of the outer tube portion may be set appropriately within a range of 1 mm to 3 mm.

[0017] A plurality of partition walls are provided within the outer tubular member, and these partition walls divide the interior of the outer tubular member into three or more internal spaces. The partition walls may be formed integrally with the outer tubular member, for example, by extrusion molding. Alternatively, the partition walls may be made of a separate member from the outer tubular member and joined to the inner surface of the outer tubular member via a joint such as brazing or adhesive. From the viewpoints of easier production of the pipe material and increasing the pressure resistance of the partition walls, it is preferable that the partition walls be formed integrally with the outer tubular member.

[0018] The specific shape of the partition wall may take various forms. For example, the partition wall may have a flat plate shape or may be curved so as to be convex in any direction in the thickness direction of the partition wall. The thickness of the partition wall may be appropriately set depending on the pressure resistance, etc. For example, the thickness of the partition wall may be appropriately set within the range of 1 mm or more and 3 mm or less.

[0019] The partition wall includes at least a first partition wall that separates the first intra-cylinder space from the other intra-cylinder spaces and a second partition wall that separates the second intra-cylinder space from the other intra-cylinder spaces. In addition to the first partition wall and the second partition wall, the partition wall may further include a third partition wall and a fourth partition wall.

[0020] The first partition portion is connected to the outer tubular portion at a first connecting portion. The number of first connecting portions is one or two. When the first partition portion is connected to the outer tubular portion at one first connecting portion, the first partition portion has, for example, a cylindrical shape including the first connecting portion. In this case, the space surrounded by the first partition portion becomes the first intra-tubular space. When the first partition portion is connected to the outer tubular portion at two first connecting portions, the shape of the first partition portion is, for example, a plate-like shape. In this case, the space surrounded by the first partition portion, the two first connecting portions, and the outer tubular portion becomes the first intra-tubular space.

[0021] The second partition portion is connected to the outer tubular portion at a second connecting portion. The number of second connecting portions is one or two. When the second partition portion is connected to the outer tubular portion at one second connecting portion, the second partition portion has, for example, a cylindrical shape including the second connecting portion. In this case, the space surrounded by the second partition portion becomes the second intra-tubular space. When the second partition portion is connected to the outer tubular portion at two second connecting portions, the shape of the second partition portion is, for example, a plate-like shape. In this case, the space surrounded by the second partition portion, the two second connecting portions, and the outer tubular portion becomes the second intra-tubular space.

[0022] The first partition is separated from the second partition. That is, when the pipe has only two partitions, the first partition and the second partition, the first partition and the second partition are each connected only to the outer tube and not to the other partition. Also, when the pipe has partitions other than the first partition and the second partition, the first partition and the second partition are not connected via the other partition.

[0023] By arranging the first partition and the second partition apart in this manner, thermal contact between the first partition and the second partition can be easily avoided, thereby suppressing heat exchange between the substance in the first cylinder space and the substance in the second cylinder space through the partition.

[0024] It is preferable that the minimum distance from the first connecting portion to the second connecting portion in a cross section perpendicular to the extension direction of the pipe be longer than the minimum distance from the first partition wall to the second partition wall. In this case, the first partition wall and the second partition wall are disposed relatively close to each other, which facilitates increasing the cross-sectional areas of the first and second internal spaces in a cross section perpendicular to the extension direction of the pipe. Furthermore, the length of the portion of the outer cylindrical portion facing the third internal space can be increased while ensuring the cross-sectional areas of the first and second internal spaces. As a result, heat exchange between a substance in the first internal space and a substance in the second internal space via the outer cylindrical portion can be suppressed.

[0025] Furthermore, the minimum distance from the first partition to the second partition is preferably 0.5 mm or more. By positioning the second partition at a distance of at least 0.5 mm from the first partition, the first partition and the second partition are more likely to be kept separated from each other even when the pipe is bent. As a result, thermal contact between the first partition and the second partition can be more easily avoided even when the pipe is bent. From the viewpoint of more reliably obtaining this effect, the minimum distance from the first partition to the second partition is more preferably 1 mm or more, even more preferably 1.5 mm or more, particularly preferably 2 mm or more, and most preferably 2.5 mm or more.

[0026] The first cylindrical space among the plurality of cylindrical spaces is a space surrounded by the outer cylindrical portion and the first partition wall. The specific shape of the first cylindrical space may be various. For example, the edge of the first cylindrical space in a cross section perpendicular to the extension direction of the pipe may have various shapes, such as a circle, a semicircle, an oval, a triangle, or a rectangle.

[0027] Preferably, the edge of the first internal space in a cross section perpendicular to the extension direction of the pipe, i.e., the flow direction of the substance flowing through the piping, is configured with a curve bulging outward from the first internal space, or a combination of a curve bulging outward from the first internal space and a straight line. By forming the curved portion of the edge of the first internal space in such a shape that bulges outward from the first internal space, the pressure resistance of the first partition wall can be more easily improved. Furthermore, in this case, the thickness of the first partition wall can be more easily reduced while maintaining the pressure resistance, thereby making the pipe more lightweight. To more reliably achieve this effect, the radius of curvature of the curved portion of the edge of the first internal space in a cross section perpendicular to the extension direction of the pipe is preferably greater than 0 mm, more preferably 0.5 mm or greater, even more preferably 1 mm or greater, particularly preferably 2 mm or greater, and most preferably 3 mm or greater.

[0028] On the other hand, the upper limit of the radius of curvature of the curved portion included in the edge of the first cylindrical space in the cross section may be equal to or less than the radius of curvature of the inner peripheral edge of the outer cylindrical portion.

[0029] The second internal space is defined by the outer cylindrical portion and the second partition wall. The specific shape of the second internal space can be various, similar to the first internal space. For example, the edge of the second internal space in a cross section perpendicular to the extension direction of the pipe can have various shapes, such as a circle, a semicircle, an oval, a triangle, or a rectangle.

[0030] It is preferable that the edge of the second internal space in a cross section perpendicular to the extension direction of the pipe be formed by a curve bulging outward from the second internal space, or by a curve bulging outward from the second internal space and a straight line. This makes it easier to improve the pressure resistance of the second partition wall. In addition, in this case, the thickness of the second partition wall can be more easily reduced while maintaining the pressure resistance, making it easier to reduce the weight of the pipe. From the viewpoint of more reliably achieving this effect, the radius of curvature of the curved portion of the edge of the second internal space in a cross section perpendicular to the extension direction of the pipe is preferably greater than 0 mm, more preferably 0.5 mm or more, even more preferably 1 mm or more, and particularly preferably 1.5 mm or more.

[0031] On the other hand, the upper limit of the radius of curvature of the curved portion included in the edge of the second cylinder space in the cross section may be equal to or less than the radius of curvature of the inner peripheral edge of the outer cylinder portion.

[0032] The third cylinder space is a space surrounded by the outer cylinder portion and the plurality of partitions, and faces both the first partition and the second partition. Therefore, by suppressing heat conduction in the third cylinder space, for example, by creating a vacuum in the third cylinder space or by filling it with a substance with low thermal conductivity, such as air or a heat insulating material, it is possible to suppress heat exchange between the substance in the first cylinder space and the substance in the second cylinder space via the first partition, the third cylinder space, and the second partition.

[0033] The outer cylindrical portion may have a thin-walled portion that is thinner than the other portions. In this case, the thin-walled portion is preferably located at a position facing the third cylindrical space. Because the thin-walled portion is thinner than the other portions, it has the property of being less likely to transmit heat. Therefore, by providing a thin-walled portion at the portion of the outer cylindrical portion facing the third cylindrical space, heat exchange between the substance in the first cylindrical space and the substance in the second cylindrical space via the outer cylindrical portion can be suppressed.

[0034] More specifically, the thin-walled portion may be provided in a part of the portion of the outer cylindrical portion facing the third cylindrical space. From the viewpoint of more effectively suppressing heat exchange between the substance in the first cylindrical space and the substance in the second cylindrical space, it is preferable that the thin-walled portion be provided over the entire portion of the outer cylindrical portion facing the third cylindrical space.

[0035] The pipe material may be made of metal or resin. From the viewpoint of increasing the pressure resistance strength of the outer tube portion and the partition wall portion, the pipe material is preferably made of metal. Furthermore, by making the pipe material from metal, the pipe material can be easily formed into a desired shape by bending.

[0036] From the viewpoint of easier manufacturing of the pipe material, the pipe material is preferably made of an extruded metal material.

[0037] The metal constituting the pipe material may be copper, copper alloy, aluminum, or aluminum alloy. From the viewpoint of more easily reducing the weight of the pipe material, the pipe material is preferably made of aluminum or an aluminum alloy. As the aluminum, for example, 1000 series aluminum may be used. Furthermore, as the aluminum alloy, for example, 2000 series aluminum alloy, 3000 series aluminum alloy, 4000 series aluminum alloy, 5000 series aluminum alloy, 6000 series aluminum alloy, 7000 series aluminum alloy, or 8000 series aluminum alloy may be used.

[0038] (Piping member for air conditioner) The pipe material is suitably used as a piping member for an air conditioner for connecting components of an air conditioner. The piping member for an air conditioner made of the pipe material has: a first flow path consisting of the first intra-cylinder space and through which a heat transfer medium flows; a second flow path consisting of the second intra-cylinder space and through which a heat transfer medium flows; and a heat insulating section consisting of the third intra-cylinder space and through which a heat transfer medium does not flow.

[0039] As described above, in the pipe material, the first partition wall and the second partition wall are spaced apart from each other, so that heat exchange between the substance in the first intra-cylinder space and the substance in the second intra-cylinder space through the partition wall can be avoided. Furthermore, because the third intra-cylinder space is interposed between the first intra-cylinder space and the second intra-cylinder space, heat conduction in the third intra-cylinder space can be suppressed, so that heat exchange between the substance in the first intra-cylinder space and the substance in the second intra-cylinder space through the first partition wall, the third intra-cylinder space, and the second partition wall can be suppressed.

[0040] Therefore, by using the first and second in-cylinder spaces in the pipe material as flow paths for the heat transfer medium, and using the third in-cylinder space as an insulating section through which the heat transfer medium does not flow, heat exchange between the heat transfer medium flowing through the first flow path and the heat transfer medium flowing through the second flow path can be suppressed.

[0041] The cross-sectional area of ​​the first flow path, i.e., the cross-sectional area of ​​the first flow path in a cross section perpendicular to the extension direction of the piping member, may be the same as the cross-sectional area of ​​the second flow path; however, it is preferable that the cross-sectional area of ​​the first flow path be larger than the cross-sectional area of ​​the second flow path. In condensers and evaporators of air conditioning systems, a heat transfer medium undergoes a phase change from gas to liquid or from liquid to gas. Furthermore, when such a phase change occurs, the volume of the heat transfer medium changes significantly. Therefore, if the cross-sectional area of ​​the first flow path is equal to the cross-sectional area of ​​the second flow path, the difference between the volumetric flow rate of the heat transfer medium in the first flow path and the volumetric flow rate of the heat transfer medium in the second flow path becomes significantly large, and in some cases, the pressure loss in the flow path through which the gas-phase heat transfer medium flows may become excessively high.

[0042] In response to this, by making the flow path cross-sectional area of ​​the first flow path larger than the flow path cross-sectional area of ​​the second flow path, and circulating a gas-phase heat transfer medium with a large volumetric flow rate through the first flow path and a liquid-phase heat transfer medium with a small volumetric flow rate through the second flow path, the difference in volumetric flow rate of the heat transfer medium in each flow path can be more easily reduced.

[0043] The specific configuration of the heat insulating section may take various forms. For example, the heat insulating section may be in a vacuum state. Alternatively, the heat insulating section may be filled with a substance having low thermal conductivity, such as air or a heat insulating material. From the viewpoint of further simplifying the configuration of the piping member, it is preferable that the heat insulating section be filled with air.

[0044] (Air Conditioning Apparatus) An air conditioning apparatus can be configured by appropriately connecting a compressor, a condenser, an evaporator, and a cooler using the piping member. More specifically, the air conditioning apparatus has: a compressor that compresses a gaseous heat transfer medium; a condenser that condenses the heat transfer medium compressed by the compressor; a cooler that cools the liquid heat transfer medium condensed by the condenser; an evaporator that evaporates the heat transfer medium cooled by the cooler; and piping that connects these devices, wherein the piping includes the piping member for an air conditioning apparatus of the above aspect.

[0045] The air conditioner may be configured, for example, as an automotive air conditioner that is mounted on an automobile, or as a stationary air conditioner that is used in ordinary homes, stores, offices, etc. Furthermore, the air conditioner may be configured, for example, to perform only cooling operation, or may be configured to be capable of performing both cooling operation and heating operation, like a heat pump air conditioner.

[0046] The air conditioning system is preferably configured as an automotive air conditioning system. As mentioned above, because a variety of devices are installed in a limited space in an automobile, the arrangement of the components in the automotive air conditioning system can be significantly restricted. In contrast, by configuring at least a portion of the piping from the piping member, the space required for arranging the piping can be easily reduced. Furthermore, even if the piping member is relatively long, the piping member can suppress heat exchange between the heat transfer media flowing within the piping member. Therefore, by using the piping member in an automotive air conditioning system, the effects of the piping member can be effectively utilized, restrictions on piping arrangement can be alleviated, and the energy consumed during operation of the air conditioning system can be expected to be further reduced.

[0047] The compressor in the air conditioner is configured to compress a gaseous heat transfer medium and increase the temperature of the heat transfer medium. The specific configuration of the compressor is not particularly limited, and an appropriate compressor can be appropriately selected from known compressors depending on the application of the air conditioner, the required performance, etc. The compressor may be, for example, a positive displacement compressor such as a reciprocating compressor, a screw compressor, a roots compressor, a rotary compressor, a vane compressor, or a scroll compressor, or may be a turbo compressor such as an axial compressor or a centrifugal compressor.

[0048] The condenser is configured to exchange heat between a high-temperature, high-pressure heat transfer medium compressed by the compressor and the atmosphere surrounding the condenser, thereby raising the temperature of the atmosphere surrounding the condenser and condensing the heat transfer medium. The specific form of the condenser is not particularly limited, and an appropriate heat exchanger can be selected from known heat exchangers depending on the application of the air conditioning system, the required performance, etc. For example, the condenser may be a fin-and-tube heat exchanger having a plurality of tubes through which the heat transfer medium flows and fins attached to these tubes.

[0049] The cooler is configured to be able to cool the liquid-phase heat transfer medium condensed in the condenser. The specific form of the cooler is not particularly limited, and various forms are possible. For example, the cooler may be configured to be able to cool the heat transfer medium by adiabatic expansion. For example, an expansion valve or a capillary tube can be used as this type of cooler. Furthermore, an ejector or the like can also be used as the cooler.

[0050] The evaporator is configured to exchange heat between the low-temperature heat transfer medium cooled by the cooler and the atmosphere surrounding the cooler, thereby lowering the temperature of the atmosphere surrounding the evaporator and evaporating the heat transfer medium. The specific form of the evaporator is not particularly limited, and an appropriate heat exchanger can be selected from known heat exchangers depending on the application of the air conditioning system, the required performance, etc. For example, the evaporator may be a fin-and-tube heat exchanger including a plurality of tubes through which the heat transfer medium flows and fins attached to these tubes.

[0051] The piping in the air conditioning apparatus may be made up of the piping members. Furthermore, the piping may include components other than the piping members, such as a single pipe or a pipe joint, in addition to the piping members.

[0052] Example 1 An example of the pipe material will be described with reference to Figures 1 and 2. As shown in Figures 1 and 2, the pipe material 1 of this example includes an outer tube portion 2, a plurality of partition wall portions 3 (31, 32) that divide the interior of the outer tube portion 2 into three or more inner-tube spaces 4 (41, 42, 43), a first inner-tube space 41 surrounded by the outer tube portion 2 and a first partition wall portion 31 of the plurality of partition wall portions 3, a second inner-tube space 42 surrounded by the outer tube portion 2 and a second partition wall portion 32 of the plurality of partition wall portions 3, and a third inner-tube space 43 surrounded by the outer tube portion 2 and the plurality of partition wall portions 3. The first partition wall portion 31 is spaced apart from the second partition wall portion 32.

[0053] The pipe material 1 in this example is made of an aluminum alloy having a chemical composition represented by alloy number A3003, and is integrally formed with an outer cylinder portion 2 and a partition wall portion 3. More specifically, the pipe material 1 is an extruded material made of an aluminum alloy.

[0054] 2, the outer cylinder 2 has a cylindrical shape, an outer diameter of 19.05 mm, and a thickness of 1.2 mm.

[0055] Two partitions 3, a first partition 31 and a second partition 32, are provided inside the outer cylinder 2, and these partitions 3 divide the inside of the outer cylinder 2 into three intra-cylinder spaces 4, a first intra-cylinder space 41, a second intra-cylinder space 42, and a third intra-cylinder space 43. The third intra-cylinder space 43 is disposed between the first intra-cylinder space 41 and the second intra-cylinder space 42.

[0056] More specifically, the first partition 31 is connected to the outer tube 2 at two first connecting portions 310 (310a, 310b). The first partition 31 has a first curved portion 311 connected to one of the two first connecting portions 310, the first connecting portion 310a, and having an arc-shaped cross section perpendicular to the extension direction of the pipe 1; a second curved portion 312 connected to the other first connecting portion 310b and having an arc-shaped cross section perpendicular to the extension direction of the pipe 1; and a first flat portion 313 connecting the first curved portion 311 and the second curved portion 312. The first curved portion 311 and the second curved portion 312 are symmetrical with respect to a line connecting the center of the first flat portion 313 in the width direction and the center of the outer tube 2. The thickness of the first partition 31 is 1.2 mm.

[0057] The first intra-tubular space 41 is surrounded by the first partition wall portion 31, the two first connecting portions 310, and the first portion 21 arranged between the two first connecting portions 310 in the outer tubular portion 2. The edge of the first intra-tubular space 41 in a cross section perpendicular to the extension direction of the pipe material 1 is composed of curves and straight lines that bulge outward from the first intra-tubular space 41. More specifically, of the contour 411 of the first intra-tubular space 41 in the cross section, the contour 411a of the portion facing the outer tubular portion 2 is composed of a curve that bulges outward from the first intra-tubular space 41.

[0058] Furthermore, of the contour 411 of the first internal space 41 in the cross section, a contour 411b of a portion facing the first curved portion 311 of the first partition wall portion 31 is formed by a curve that bulges outward from the first internal space 41. Similarly, of the contour 411 of the first internal space 41 in the cross section, a contour 411c of a portion facing the second curved portion 312 of the first partition wall portion 31 is formed by a curve that bulges outward from the first internal space 41. The curvature radii of the contours 411b and 411c are both 3 mm. Furthermore, of the contour 411 of the first internal space 41 in the cross section, a contour 411d of a portion facing the first flat plate portion 313 of the first partition wall portion 31 is formed by a straight line. The length of the contour 411d is 6.21 mm, and the maximum distance from the contour 411d to the contour 411a is 7 mm.

[0059] More specifically, the second partition portion 32 is connected to the outer tube portion 2 at two second connecting portions 320 (320a, 320b). The second partition portion 32 has a third curved portion 321 that is connected to one of the two second connecting portions 320, the second connecting portion 320a, and that has an arc-shaped cross section perpendicular to the extension direction of the pipe 1, a fourth curved portion 322 that is connected to the other second connecting portion 320b, and that has an arc-shaped cross section perpendicular to the extension direction of the pipe 1, and a second flat portion 323 that connects the third curved portion 321 and the fourth curved portion 322. The second partition portion 32 has a thickness of 1.6 mm.

[0060] The third curved portion 321 and the fourth curved portion 322 have shapes symmetrical with respect to a line connecting the center of the second flat plate portion 323 in the width direction and the center of the outer tube portion 2. The second flat plate portion 323 faces the first flat plate portion 313 and is positioned parallel to the first flat plate portion 313. The minimum distance from the first partition portion 31 to the second partition portion 32 in a cross section perpendicular to the extension direction of the pipe 1, i.e., the distance from the second flat plate portion 323 of the second partition portion 32 to the first flat plate portion 313 of the first partition portion 31, is 2.85 mm. The minimum distance from the first connecting portion 310 to the second connecting portion 320 in a cross section perpendicular to the extension direction of the pipe 1, i.e., the distance from the first connecting portion 310a to the second connecting portion 320b and the distance from the first connecting portion 310b to the second connecting portion 320a, are both 7.56 mm.

[0061] The second intra-tubular space 42 is surrounded by the second partition wall portion 32, the two second connecting portions 320, and the second portion 22 arranged between the two second connecting portions 320 in the outer tubular portion 2. The edge of the second intra-tubular space 42 in a cross section perpendicular to the extension direction of the pipe 1 is composed of straight lines and curves that bulge outward from the second intra-tubular space 42. More specifically, of the contour 421 of the second intra-tubular space 42 in the cross section, the contour 421a of the portion facing the outer tubular portion 2 is composed of a curve that bulges outward from the second intra-tubular space 42.

[0062] Furthermore, of the contour 421 of the second intra-cylinder space 42 in the cross section, a contour 421b of a portion facing the third curved portion 321 of the second partition wall portion 32 is formed by a curve that bulges outward from the second intra-cylinder space 42. Similarly, of the contour 421 of the second intra-cylinder space 42 in the cross section, a contour 421c of a portion facing the fourth curved portion 322 of the second partition wall portion 32 is formed by a curve that bulges outward from the second intra-cylinder space 42. The radii of curvature of contours 421b and 421c are both 1.5 mm. Of the contour 421 of the second intra-cylinder space 42 in the cross section, a contour 421d of a portion facing the second flat plate portion 323 of the second partition wall portion 32 is formed by a straight line. The length of contour 421d is 7.12 mm, and the maximum distance from contour 421d to contour 421a is 4 mm.

[0063] The third in-tube space 43 is surrounded by a third part 23 arranged between the first partition portion 31, the second partition portion 32 and the first connecting portion 310 and the second connecting portion 320 in the outer tube portion 2 of the pipe material 1, and is interposed between the first in-tube space 41 and the second in-tube space 42.

[0064] The pipe 1 of this example has at least three internal spaces 4 divided by partitions 3. Therefore, the space required for arranging the pipe 1 can be easily reduced.

[0065] Of the in-cylinder spaces 4 of the tubing 1, the first in-cylinder space 41 is separated from the other in-cylinder spaces 4 by the first partition wall portion 31, and the second in-cylinder space 42 is separated from the other in-cylinder spaces 4 by the second partition wall portion 32. The first partition wall portion 31 is separated from the second partition wall portion 32. Therefore, even when substances at different temperatures are circulated through the first in-cylinder space 41 and the second in-cylinder space 42, the tubing 1 can avoid heat exchange between the substance in the first in-cylinder space 41 and the substance in the second in-cylinder space 42 via the partition wall portion 3.

[0066] A third intra-cylinder space 43 is provided between the first intra-cylinder space 41 and the second intra-cylinder space 42. Therefore, by suppressing heat conduction in the third intra-cylinder space 43, it is possible to suppress heat exchange between the substance in the first intra-cylinder space 41 and the substance in the second intra-cylinder space 42 via the third intra-cylinder space 43.

[0067] The outer tubular portion 2 has a cylindrical shape. Therefore, the pipe material 1 can be easily bent in various directions, and when connecting multiple devices with the pipe material 1, restrictions on the arrangement of the devices can be reduced. Furthermore, by making the outer tubular portion 2 cylindrical, the pressure resistance of the outer tubular portion 2 can be more easily increased. As a result, the pressure of the substance that can flow through each of the intra-tubular spaces 4 can be more easily increased.

[0068] The edge of the first intra-tube space 41 in a cross section perpendicular to the extension direction of the pipe 1 is composed of straight lines and curves that bulge outward from the first intra-tube space 41, and the edge of the second intra-tube space 42 is composed of straight lines and curves that bulge outward from the second intra-tube space 42. This makes it easier to improve the pressure resistance of the first partition wall portion 31 and the second partition wall portion 32. In addition, the thicknesses of the first partition wall portion 31 and the second partition wall portion 32 can be more easily reduced while maintaining the pressure resistance, making it easier to reduce the weight of the pipe 1.

[0069] The minimum distance from the first connecting portion 310 to the second connecting portion 320 in a cross section perpendicular to the extension direction of the pipe 1 is longer than the minimum distance between the first partition 31 and the second partition 32. Therefore, the first partition 31 and the second partition 32 can be disposed relatively close to each other, and the cross-sectional areas of the first and second intra-cylinder spaces 41 and 42 in a cross section perpendicular to the extension direction of the pipe 1 can be easily increased. Furthermore, the cross-sectional areas of the first and second intra-cylinder spaces 41 and 42 can be ensured while the length of the third portion 23 of the outer cylindrical portion 2, i.e., the portion of the outer cylindrical portion 2 facing the third intra-cylinder space 43, can be increased. As a result, heat exchange between the substance in the first intra-cylinder space 41 and the substance in the second intra-cylinder space 42 via the third portion 23 of the outer cylindrical portion 2 can be suppressed.

[0070] Therefore, according to the pipe material 1 of this example, it is possible to avoid an increase in the space required for arranging the pipe material 1 and to suppress heat exchange within the pipe material 1.

[0071] (Example 2) In this example, an example of another aspect of the partition wall portion 3 will be described. Note that, among the reference numerals used in the examples and subsequent examples, the same reference numerals as those used in the previous examples indicate the same components as those in the previous examples, unless otherwise specified.

[0072] 3 , the pipe material 102 of this example has an outer tube portion 2, a plurality of partition wall portions 3 (33, 34) that divide the inside of the outer tube portion 2 into three or more inner tube spaces 4 (41, 42, 43), a first inner tube space 41 surrounded by the outer tube portion 2 and a first partition wall portion 33 of the plurality of partition wall portions 3, a second inner tube space 42 surrounded by the outer tube portion 2 and a second partition wall portion 34 of the plurality of partition wall portions 3, and a third inner tube space 43 surrounded by the outer tube portion 2 and the plurality of partition wall portions 3. In addition, the first partition wall portion 33 is separated from the second partition wall portion 34.

[0073] The first partition wall 33 in this example has a flat plate shape and is connected to the outer tubular portion 2 at two first connecting portions 330 (330a, 330b). The thickness of the first partition wall 33 is 1.2 mm.

[0074] The first internal cylinder space 41 is surrounded by a first partition portion 33, two first connection portions 330, and a first portion 21 arranged between the two first connection portions 330 in the outer cylinder portion 2.

[0075] In this example, the second partition wall portion 34 is connected to the outer tube portion 2 at two second connection portions 340 (340a, 340b) and has a flat plate shape. The thickness of the second partition wall portion 34 is 1.6 mm. The second partition wall portion 34 is also arranged parallel to the first partition wall portion 33. The minimum distance from the first partition wall portion 33 to the second partition wall portion 34 in a cross section perpendicular to the extension direction of the pipe material 102 is 4.2 mm.

[0076] The second cylinder space 42 is surrounded by the second partition wall portion 34, the two second connecting portions 340, and the second portion 22 arranged between the two second connecting portions 340 in the outer cylinder portion 2. The configuration of other parts of the pipe material 102 of this example is the same as that of the pipe material 1 of Example 1.

[0077] The pipe 102 of this example has at least three internal spaces 4 partitioned by partition walls 3. Therefore, the space required for arranging the pipe 102 can be easily reduced.

[0078] Of the in-cylinder spaces 4 of the tubing 102, the first in-cylinder space 41 is separated from the other in-cylinder spaces 4 by the first partition wall portion 33, and the second in-cylinder space 42 is separated from the other in-cylinder spaces 4 by the second partition wall portion 34. The first partition wall portion 33 is separated from the second partition wall portion 34. Therefore, even when substances at different temperatures are circulated through the first in-cylinder space 41 and the second in-cylinder space 42, the tubing 102 can avoid heat exchange between the substance in the first in-cylinder space 41 and the substance in the second in-cylinder space 42 via the partition wall portion 3.

[0079] A third intra-cylinder space 43 is provided between the first intra-cylinder space 41 and the second intra-cylinder space 42. Therefore, by suppressing heat conduction in the third intra-cylinder space 43, it is possible to suppress heat exchange between the substance in the first intra-cylinder space 41 and the substance in the second intra-cylinder space 42 via the third intra-cylinder space 43.

[0080] The outer tubular portion 2 has a cylindrical shape. Therefore, the pipe material 102 can be easily bent in various directions, and when connecting multiple devices with the pipe material 102, restrictions on the arrangement of the devices can be reduced. Furthermore, by making the outer tubular portion 2 cylindrical, the pressure resistance of the outer tubular portion 2 can be more easily increased. As a result, the pressure of the substance that can flow through each of the intra-tubular spaces 4 can be more easily increased.

[0081] (Example 3) This example illustrates an example of a pipe material 103 in which a thin-walled portion 231 is provided in the third portion 23 of the outer tube portion 2. As shown in Fig. 4 , the pipe material 103 of this example includes an outer tube portion 2, a plurality of partition wall portions 3 (31, 32) that divide the interior of the outer tube portion 2 into three or more inner-tube spaces 4 (41, 42, 43), a first inner-tube space 41 surrounded by the outer tube portion 2 and a first partition wall portion 31 of the plurality of partition wall portions 3, a second inner-tube space 42 surrounded by the outer tube portion 2 and a second partition wall portion 32 of the plurality of partition wall portions 3, and a third inner-tube space 43 surrounded by the outer tube portion 2 and the plurality of partition wall portions 3. In addition, the first partition wall portion 31 is separated from the second partition wall portion 32.

[0082] In this example, the outer tube portion 2 of the pipe material 103 has a cylindrical shape. The first partition wall portion 31 of the pipe material 103 is connected to the outer tube portion 2 at two first connecting portions 310 (310a, 310b). The first in-cylinder space 41 is surrounded by the first partition wall portion 31, the two first connecting portions 310, and the first portion 21 disposed between the two first connecting portions 310 of the outer tube portion 2.

[0083] Similarly, the second partition wall portion 32 in the pipe material 103 is connected to the outer tubular portion 2 at two second connecting portions 320 (320a, 320b). The second intra-tubular space 42 is surrounded by the second partition wall portion 32, the two second connecting portions 320, and the second portion 22 disposed between the two second connecting portions 320 in the outer tubular portion 2. The specific configurations of the first partition wall portion 31 and the second partition wall portion 32 are similar to those of the first partition wall portion 31 and the second partition wall portion 32 in Example 1.

[0084] In the pipe material 103, the third portion 23 of the outer tube portion 2, i.e., the portion located between the first connecting portion 310 and the second connecting portion 320, is provided with a thin-walled portion 231. In the pipe material 103 of this example, the thin-walled portion 231 is provided throughout the entire third portion 23, and the thickness of the third portion 23 is thinner than the first portion 21 and the second portion 22.

[0085] As in this example, by providing the thin-walled portion 231 in the outer tubular portion 2 at a position facing the third in-tubular space 43, it is possible to suppress heat exchange between the substance in the first in-tubular space 41 and the substance in the second in-tubular space 42 via the outer tubular portion 2. In addition, the pipe material 103 of this example can achieve the same effects as the pipe material 1 of Example 1.

[0086] (Experimental Example) In this example, a heat transfer analysis is performed assuming that heat transfer media of different temperatures are circulated through the first in-cylinder space 41 and the second in-cylinder space 42 in the pipe material 1 of Example 1 and the pipe material 102 of Example 2.

[0087] In this example, structural model A used for heat transfer analysis is a pipe having a length of 1000 mm. The cross-sectional shape of structural model A in a cross section perpendicular to the extension direction is the same as that of pipe material 1 in Example 1. Structural model B is a pipe having a length of 1000 mm. The cross-sectional shape of structural model B in a cross section perpendicular to the extension direction is the same as that of pipe material 102 in Example 2. The physical properties of the materials constituting the outer tube portion 2 and partition portion 3 in these structural models are the physical properties of an aluminum alloy.

[0088] Specific calculation conditions for the heat transfer analysis using structural model A and structural model B are as follows. First, a low-temperature, low-pressure heat transfer medium is circulated from the first end of each structural model to the first in-cylinder space 41, and a high-temperature, high-pressure heat transfer medium is circulated from the second end of the structural model to the second in-cylinder space 42. The third in-cylinder space 43 is maintained filled with air. Heat transfer analysis is performed under these conditions to determine the steady state of the heat transfer medium in each in-cylinder space 4. Then, the change in specific enthalpy of the low-temperature, low-pressure heat transfer medium in the steady state, and the temperatures at the inlet and outlet of each heat transfer medium are calculated.

[0089] Then, based on the value obtained by the heat transfer analysis, the thermal resistance R (unit: K / W) is calculated according to the following formula (1): R=Q LP / ΔT LMTD ...(1)

[0090] Here, Q in the formula (1) LP represents the amount of heat exchanged (unit: W). LP is the specific enthalpy change Δh of the low-temperature, low-pressure heat transfer medium LP It is calculated based on the following formula (2) using the heat transfer medium flow rate m (unit: kg / s) and the heat transfer fluid flow rate Q (unit: J / kg). LP = m Δh LP ...(2)

[0091] In addition, ΔT in the above formula (1) LMTD is the logarithmic mean temperature difference (unit: K) of the heat transfer medium. LMTD is the inlet temperature T of the low-temperature, low-pressure heat transfer medium LP,in (unit: K), outlet temperature T of low-temperature, low-pressure heat transfer mediumLP,out (unit: K), inlet temperature T of high-temperature and high-pressure heat transfer medium HP,in (unit: K) and the outlet temperature T of the high-temperature, high-pressure heat transfer medium HP,out (unit: K) and is calculated based on the following formula (3): LMTD = {(T HP,in -T LP,out )-(T HP,out -T LP,in )} / ln{(T HP,in -T LP,out )-(T HP,out -T LP,in ) ... (3)

[0092] The conditions of the heat transfer medium circulating in the first cylinder space 41 and the second cylinder space 42 were determined with reference to the conditions described in SAE J3094. The physical properties of the heat transfer medium were calculated using a refrigerant thermal property database (REFPROP Ver. 10.0, manufactured by the National Institute of Standards and Technology). Specific conditions of the heat transfer medium are shown in Table 1.

[0093]

[0094] The physical properties of the air filled in the third cylinder space 43 are as follows: Density: 1.204 kg / m 3 ・Viscosity: 1.81×10 -5 Pa·s Specific heat: 1006.64 J / (kg·K) Thermal conductivity: 0.0258 W / (m·K) Flow rate: 0 L / min

[0095] Table 2 shows the results of the heat transfer analysis using structural model A and structural model B. Fig. 5 shows a graph of the thermal resistance of structural model A and structural model B under each of conditions 1 to 3. The vertical axis of Fig. 5 represents the thermal resistance (unit: K / W) calculated based on the formula (1).

[0096] 6 shows the temperature distribution on a line connecting the center of the first flat plate portion 313, the center of the outer cylindrical portion 2, and the center of the second flat plate portion 323 at the center position in the longitudinal direction of the structural model A. The vertical axis of FIG. 6 represents the temperature (unit: °C) at each position, and the horizontal axis represents the relative position (unit: mm) on the line when the center of the outer cylindrical portion 2 is used as the reference. The absolute value of the relative position is the distance from the center of the outer cylindrical portion 2. For convenience, a relative position closer to the first inner-cylinder space 41 than the center of the outer cylindrical portion 2 is represented by adding a negative sign to the distance, and a relative position closer to the second inner-cylinder space 42 than the center of the outer cylindrical portion 2 is represented by adding a positive sign to the distance.

[0097] In this example, structural models C and D simulating double pipes, and structural model E in which an outer cylinder 2 is partitioned into two in-cylinder spaces 41 and 42 by a single partition wall 3, were prepared and compared with structural models A and B. Structural model C is a double pipe 9 having a length of 1000 mm, and as shown in FIG. 7 , it includes an inner pipe 91 and an outer pipe 92 that houses the inner pipe 91. The outer diameter of the inner pipe 91 is 12 mm, and the wall thickness of the inner pipe 91 is 1.2 mm. The cross-sectional area of ​​a flow path 911 formed inside the inner pipe 91 is approximately equal to the cross-sectional area of ​​the first in-cylinder space 41 in structural model A. The outer diameter of the outer pipe 92 is 15.8 mm, and the wall thickness of the outer pipe 92 is 1.2 mm. The cross-sectional area of ​​a flow path 921 formed between the inner pipe 91 and the outer pipe 92 is approximately equal to the cross-sectional area of ​​the second in-cylinder space 42 in structural model A.

[0098] Structural model D is a double-walled pipe 902 having a length of 1000 mm. As shown in FIG. 8 , it includes an inner pipe 93 and an outer pipe 94 that houses the inner pipe 93. Three support portions 95 are provided between the inner pipe 93 and the outer pipe 94. The outer diameter of the inner pipe 93 is 8.4 mm, and the wall thickness of the inner pipe 93 is 1.2 mm. The cross-sectional area of ​​a flow path 931 formed inside the inner pipe 93 is approximately equal to the cross-sectional area of ​​the flow path of the first in-cylinder space 41 in structural model A. The outer diameter of the outer pipe 94 is 15.6 mm, and the wall thickness of the outer pipe 94 is 1.2 mm. The thickness of the support portions 95 is 1.2 mm. The cross-sectional area of ​​a flow path 941 formed between the inner pipe 93 and the outer pipe 94 is approximately equal to the cross-sectional area of ​​the flow path of the second in-cylinder space 42 in structural model A.

[0099] The specific calculation conditions for the heat transfer analysis using structural models C and D are the same as those for the heat transfer analysis using structural model A, except that a low-temperature, low-pressure heat transfer medium is circulated from the first end of each structural model through flow paths 911 and 931 in inner pipes 91 and 93, and a high-temperature, high-pressure heat transfer medium is circulated from the second end of the structural model through flow paths 921 and 941 between the inner pipes 91 and 93 and the outer pipes 92 and 94. The results of the heat transfer analysis using structural models C and D are shown in Table 2 and FIG.

[0100] 9 shows the temperature distribution on a line passing through the center of the outer tube 92 at the center position in the longitudinal direction of the structural model C. The vertical axis of FIG. 9 represents the temperature (unit: °C) at each position, and the horizontal axis represents the relative position (unit: mm) on the line when the center of the outer tube 92 is used as the reference. The absolute value of the relative position is the distance from the center of the outer tube 92. For convenience, a relative position on the line that is distant from the center of the outer tube 92 in a first direction is represented by adding a positive sign to the distance, and a relative position that is distant in a second direction opposite to the first direction is represented by adding a negative sign to the distance.

[0101] Structural model E is a pipe 903 having a length of 1000 mm, and as shown in FIG. 10 , has a cylindrical outer tube portion 96 and a partition wall portion 98 that divides the interior of the outer tube portion 96 into two inner spaces 97, a first inner space 971 and a second inner space 972. The outer diameter of the outer tube portion 96 is 14.4 mm and a thickness of 1.2 mm. The partition wall portion 98 is flat and has a thickness of 1.0 mm. The cross-sectional area of ​​the first inner space 971 is approximately equal to the flow path cross-sectional area of ​​the first inner space 41 in structural model A. Furthermore, the cross-sectional area of ​​the second inner space 972 is approximately equal to the flow path cross-sectional area of ​​the second inner space 42 in structural model A.

[0102] The specific calculation conditions for the heat transfer analysis using structural model E are the same as those for the heat transfer analysis using structural model A, except that a low-temperature, low-pressure heat transfer medium is circulated from the first end of structural model E to the first intra-cylinder space 971, and a high-temperature, high-pressure heat transfer medium is circulated from the second end of structural model E to the second intra-cylinder space 972. The results of the heat transfer analysis using structural model E are shown in Table 2 and FIG.

[0103]

[0104] As shown in Table 2 and Fig. 5, when comparing thermal resistance under the same conditions, the thermal resistance of structural models A and B, which have the third intra-cylinder space 43, is higher than the thermal resistance of structural models C to E, which do not have the third intra-cylinder space 43. Furthermore, a comparison of Fig. 6 and Fig. 9 shows that when structural model A is used, the temperature difference between the high-temperature, high-pressure heat transfer medium and the low-temperature, low-pressure heat transfer medium can be made larger than when structural model C is used.

[0105] Therefore, from these results, it can be understood that by arranging the first partition portion 31 and the second partition portion 32 at a distance from each other and by providing a third intra-cylinder space 43 between the first intra-cylinder space 41 and the second intra-cylinder space 42, heat exchange between substances flowing within the piping 6 is suppressed.

[0106] Furthermore, as shown in Figure 5, a comparison between structural model A and structural model B shows that the thermal resistance can be further increased by arranging the first connection portion 310 and the second connection portion 320 so that the distance between them is greater than the minimum distance from the first partition portion 31 to the second partition portion 32.

[0107] Example 4 This example is an example of an air conditioner 5 including the tubing material 1 of Example 1. As shown in Figure 11, the air conditioner 5 of this example has a compressor 51 that compresses a gas phase heat transfer medium, a condenser 52 that condenses the heat transfer medium compressed by the compressor 51, a cooler 53 that cools the liquid phase heat transfer medium condensed by the condenser 52, an evaporator 54 that evaporates the heat transfer medium cooled by the cooler 53, and piping 6 that connects these devices. In addition, the piping 6 includes a piping member 61 made of the tubing material 1.

[0108] The piping 6 in the air conditioning apparatus 5 of this example includes one piping member 61 and six single pipes 62 (621 to 626). The piping member 61 includes a first flow path 611 formed by the first intra-cylinder space 41 of the pipe material 1 and through which the heat transfer medium flows, a second flow path 612 formed by the second intra-cylinder space 42 of the pipe material 1 and through which the heat transfer medium flows, and a heat insulating section 613 formed by the third intra-cylinder space 43 of the pipe material 1 and through which the heat transfer medium does not flow. The specific structure of the piping member 61 is the same as the structure of the pipe material 1 in Example 1. Note that, for convenience, the structure of the piping member 61 is depicted in a simplified form in FIG. 11 .

[0109] An inlet 611i of the first flow path 611 in the piping member 61 is connected to an outlet 54o of the evaporator 54 via a first single pipe 621 of the six single pipes 62. Furthermore, an outlet 611o of the first flow path 611 is connected to an inlet 51i of the compressor 51 via a second single pipe 622 of the six single pipes 62. Therefore, the gas-phase heat transfer medium flowing out of the evaporator 54 passes through the first single pipe 621, the first flow path 611 of the piping member 61, and the second single pipe 622, and is guided to the compressor 51.

[0110] An outlet 51o of the compressor 51 is connected to an inlet 52i of the condenser 52 via a third single pipe 623 of the six single pipes 62. Therefore, the heat transfer medium compressed in the compressor 51 is guided to the condenser 52 via the third single pipe 623.

[0111] The outlet 52o of the condenser 52 is connected to the inlet 612i of the second flow path 612 in the piping member 61 via a fourth single pipe 624 of the six single pipes 62. Furthermore, the outlet 612o of the second flow path 612 is connected to the inlet 53i of the cooler 53 via a fifth single pipe 625 of the six single pipes 62. Therefore, the liquid-phase heat transfer medium condensed in the condenser 52 is guided to the cooler 53 via the fourth single pipe 624, the second flow path 612 of the piping member 61, and the fifth single pipe 625. Note that the cooler 53 in this example is an expansion valve that cools the liquid-phase heat transfer medium by adiabatic expansion.

[0112] The outlet 53o of the cooler 53 is connected to the inlet 54i of the evaporator 54 via a sixth single pipe 626 of the six single pipes 62. Therefore, the liquid-phase heat transfer medium cooled in the cooler 53 is guided to the evaporator 54 via the sixth single pipe 626. In addition, the gas-phase heat transfer medium evaporated in the evaporator 54 flows out from the outlet 54o of the evaporator 54 to the first single pipe 621.

[0113] Both ends of the heat insulating portion 613 of the piping member 61 are open, and the heat insulating portion 613 is connected to the space outside the piping member 61. As a result, the heat insulating portion 613 is filled with air.

[0114] In the air conditioning device 5 of this example, a portion of the path of the heat transfer medium from the condenser 52 to the cooler 53 and a portion of the path of the heat transfer medium from the evaporator 54 to the compressor 51 are formed by the piping member 61. Therefore, the space required for arranging the piping 6 can be easily reduced.

[0115] Furthermore, the piping member 61 is made of a pipe material 1, and the first and second in-cylinder spaces 41, 42 of the pipe material 1 are used as flow paths for the heat transfer medium, and the third in-cylinder space 43 is used as a heat insulating section 613. Therefore, heat exchange between the heat transfer medium flowing through the first flow path 611 and the heat transfer medium flowing through the second flow path 612 can be suppressed.

[0116] Furthermore, the cross-sectional area of ​​the first flow path 611 in the piping member 61 is larger than the cross-sectional area of ​​the second flow path 612. Therefore, by circulating a gas-phase heat transfer medium through the first flow path 611 and a liquid-phase heat transfer medium through the second flow path 612, the difference in volumetric flow rate of the heat transfer medium in each flow path can be more easily reduced.

[0117] The above describes the aspects of the pipe material, piping components for air conditioning devices, and air conditioning devices based on examples and experimental examples, but the specific aspects of the pipe material, piping components for air conditioning devices, and air conditioning devices related to the present invention are not limited to the aspects of the examples and experimental examples, and the configuration can be changed as appropriate within the scope that does not detract from the intent of the present invention.

[0118] For example, while Example 1 illustrates an example of a pipe material having three intra-cylinder spaces, the pipe material may have four or more intra-cylinder spaces. In this case, for example, it is preferable to provide a partition wall separating each intra-cylinder space from the other intra-cylinder spaces at a position separated from the other partition walls. By arranging the partition walls in this manner and using the intra-cylinder spaces other than the third intra-cylinder space as a flow path for a heat transfer medium or the like, heat exchange within the pipe material can be suppressed, as with the pipe material of Example 1.

[0119] Furthermore, for example, in Example 2, an example was shown in which part of the path of the heat transfer medium from the condenser to the cooler and part of the path of the heat transfer medium from the evaporator to the compressor were formed by piping members, but the number and arrangement of the piping members are not limited to the form of Example 2, and various forms are possible as long as the heat transfer medium can be circulated among the components of the air conditioning system.

[0120] In addition, the pipe material may take the following forms (1) to (6), for example.

[0121] [1] A pipe material having an outer tube portion, a plurality of partition walls dividing the interior of the outer tube portion into three or more inner tube spaces, a first inner tube space surrounded by the outer tube portion and a first partition wall portion of the plurality of partition walls, a second inner tube space surrounded by the outer tube portion and a second partition wall portion of the plurality of partition walls, and a third inner tube space surrounded by the outer tube portion and the plurality of partition walls, wherein the first partition wall portion is separated from the second partition wall portion.

[0122] [2] The pipe material according to [1], wherein the outer tube portion has a cylindrical shape. [3] The pipe material according to [1] or [2], wherein, in a cross section perpendicular to the extension direction of the pipe material, an edge of the first internal space is formed by a curve bulging outward from the first internal space or a curve bulging outward from the first internal space and a straight line, and an edge of the second internal space is formed by a curve bulging outward from the second internal space or a curve bulging outward from the second internal space and a straight line.

[0123] [4] The pipe material according to any one of [1] to [3], wherein the outer tubular portion has a thin-walled portion in a part thereof that is thinner than other portions, and the thin-walled portion is positioned at a position facing the third internal space of the tubular portion. [5] The pipe material according to any one of [1] to [4], wherein the first partition wall portion is connected to the outer tubular portion at a first connecting portion, the second partition wall portion is connected to the outer tubular portion at a second connecting portion, and the minimum value of the distance from the first connecting portion to the second connecting portion in a cross section perpendicular to the extension direction of the pipe material is longer than the minimum value of the distance from the first partition wall portion to the second partition wall portion. [6] The pipe material according to any one of [1] to [5], wherein the pipe material is made of a metal extrusion material.

[0124] Furthermore, the air-conditioning apparatus piping member can take the following aspects [7] to [8], for example.

[0125] [7] A piping member for an air conditioner made of the piping material according to any one of [1] to [6], the piping member having: a first flow path consisting of the first intra-cylinder space and through which a heat transfer medium flows, a second flow path consisting of the second intra-cylinder space and through which the heat transfer medium flows, and a heat insulating section consisting of the third intra-cylinder space and through which the heat transfer medium does not flow. [8] The piping member for an air conditioner according to [7], wherein a flow path cross-sectional area of ​​the first flow path is larger than a flow path cross-sectional area of ​​the second flow path.

[0126] Furthermore, the air conditioning device may take the form of, for example, the following item [9].

[0127] [9] An air conditioning apparatus having: a compressor that compresses a gaseous heat transfer medium; a condenser that condenses the heat transfer medium compressed by the compressor; a cooler that cools the liquid phase heat transfer medium condensed by the condenser; an evaporator that evaporates the heat transfer medium cooled by the cooler; and piping that connects these devices, wherein the piping includes the piping component for an air conditioning apparatus described in [7] or [8].

Claims

1. A pipe material having an outer tube portion, a plurality of partition walls dividing the interior of the outer tube portion into three or more inner tube spaces, a first inner tube space surrounded by the outer tube portion and a first partition wall portion of the plurality of partition walls, a second inner tube space surrounded by the outer tube portion and a second partition wall portion of the plurality of partition walls, and a third inner tube space surrounded by the outer tube portion and the plurality of partition walls, wherein the first partition wall portion is spaced apart from the second partition wall portion.

2. The tubing of claim 1, wherein said outer tube portion has a cylindrical shape.

3. A pipe material as described in claim 1, wherein in a cross section perpendicular to the extension direction of the pipe material, the edge of the first intra-tubular space is composed of a curve that bulges outward from the first intra-tubular space, or a curve that bulges outward from the first intra-tubular space and a straight line, and the edge of the second intra-tubular space is composed of a curve that bulges outward from the second intra-tubular space, or a curve that bulges outward from the second intra-tubular space and a straight line.

4. A pipe material as described in claim 1, wherein the outer tube portion has a thin-walled portion in part thereof that is thinner than other portions, and the thin-walled portion is positioned facing the third internal tube space.

5. A pipe material as described in claim 1, wherein the first partition portion is connected to the outer tubular portion at a first connecting portion, the second partition portion is connected to the outer tubular portion at a second connecting portion, and the minimum value of the distance from the first connecting portion to the second connecting portion in a cross section perpendicular to the extension direction of the pipe material is longer than the minimum value of the distance from the first partition portion to the second partition portion.

6. The tubing of claim 1, wherein said tubing is constructed from a metal extrusion.

7. A piping component for an air conditioning system made of the tubing material according to any one of claims 1 to 6, comprising: a first flow path formed by the first in-cylinder space and through which a heat transfer medium flows; a second flow path formed by the second in-cylinder space and through which a heat transfer medium flows; and a heat insulating section formed by the third in-cylinder space and through which no heat transfer medium flows.

8. The piping member for an air conditioner according to claim 7, wherein the cross-sectional area of ​​the first flow path is larger than the cross-sectional area of ​​the second flow path.

9. An air conditioning apparatus having: a compressor that compresses a gaseous heat transfer medium; a condenser that condenses the heat transfer medium compressed by the compressor; a cooler that cools the liquid phase heat transfer medium condensed by the condenser; an evaporator that evaporates the heat transfer medium cooled by the cooler; and piping that connects these devices, wherein the piping includes the piping component for an air conditioning apparatus described in claim 7.

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