JP2009257742A - Refrigerating device and manufacturing method therefor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a refrigerating device and its manufacturing method, capable of suppressing pressure loss, in a refrigerating cycle that utilizes a refrigerant of 0 ozone depletion potential. <P>SOLUTION: An air-conditioning device 1 comprises a refrigerant circuit 10, and a single refrigerant composed of a refrigerant, represented by a molecular formula: C<SB>3</SB>H<SB>m</SB>F<SB>n</SB>(m=1-5, n=1-5 and m+n=6), and having a single double bond in the molecular structure, or a refrigerant mixture including the refrigerant. An evaporator 350 has a heat transfer tube 351, in which the inside diameter at an outlet side, in the flowing direction of a working refrigerant, is set larger than the inside diameter at the inlet side. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a refrigeration apparatus and a method for manufacturing the refrigeration apparatus.

  Conventionally, chlorofluorohydrocarbons, fluorohydrocarbons, azeotropic compositions thereof, and the like are known as heat media (refrigerants) used in the refrigeration cycle. As these refrigerants, for example, R-11 (trichloromonofluoromethane), R-22 (monochlorodifluoromethane), R502 (R-22 + chloropentafluoroethane) and the like are mainly used.

  However, it has been pointed out that the destruction of the ozone layer has a negative impact on the global ecosystem, and there is an international agreement that the use of refrigerants with high risk of destroying the ozone layer is restricted. .

  On the other hand, as described in Patent Document 1 (Japanese Patent Laid-Open No. 4-110388) shown below, the applicant, even if leaked into the atmosphere from the refrigeration cycle, the ozone layer depletion coefficient (ODP: Ozone) A refrigerant having a Depletion Potential) of 0 and capable of exhibiting the same ability as a refrigerant conventionally used in a refrigeration cycle has been devised. Specifically, the refrigerant | coolant which does not contain a chlorine atom and a bromine atom is proposed.

By the way, as a refrigerant which is a refrigerant having an ozone depletion coefficient of 0, it is represented by a molecular formula: C ₃ H _m F _n (where m = 1 to 5, n = 1 to 5, and m + n = 6), and A single refrigerant composed of a refrigerant having one double bond in the molecular structure or a mixed refrigerant containing this refrigerant can be used. However, in the case where this refrigerant is used in a refrigeration apparatus, no consideration has yet been given to a technique that can suppress the pressure loss to a low level.

The present invention has been made in view of the above, an object of the present invention, there is provided a ozone depletion is 0, molecular formula: C ₃ H _m F _n (where, m = 1 to 5, n = 1 to 5 and m + n = 6) and a pressure in a refrigeration cycle using a single refrigerant composed of a refrigerant having one double bond in the molecular structure or a mixed refrigerant containing this refrigerant An object of the present invention is to provide a refrigeration apparatus and a method for manufacturing the refrigeration apparatus that can reduce loss.

The refrigeration apparatus of the first invention includes a refrigerant circuit and a working refrigerant. The refrigerant circuit has at least a compression mechanism, a condenser, an expansion mechanism, and an evaporator. The working refrigerant is expressed by a molecular formula: C ₃ H _m F _n (where m = 1 to 5, n = 1 to 5, and m + n = 6) in which a refrigeration cycle is performed by circulating in the refrigerant circuit. And either a single refrigerant composed of a refrigerant having one double bond in the molecular structure, or a mixed refrigerant containing the refrigerant. The evaporator has a heat transfer tube through which the working refrigerant flows and whose inner diameter on the outlet side is larger than the inner diameter on the inlet side in the flow direction of the working refrigerant.

  In this refrigeration apparatus, a working refrigerant having an ozone depletion coefficient of 0 can be used. Further, this refrigeration apparatus has an evaporator with an inner diameter on the outlet side where a large amount of the gas component of the working refrigerant is present larger than an inner diameter of the inlet side where the liquid component of the working refrigerant is present. The inner diameter of the heat transfer tube can be increased corresponding to the increase in the specific volume of the working refrigerant flowing inside. For this reason, the pressure loss which arises in the part which a pressure loss tends to produce in an evaporator can be reduced. Thereby, even when the ozone layer depletion coefficient is set to 0 using the working refrigerant, the pressure loss in the evaporator can be kept small.

  In the refrigeration apparatus of the second invention, in the refrigeration apparatus of the first invention, the evaporator further has a heat radiation fin having a through hole for allowing the heat transfer tube to penetrate in the plate thickness direction. An evaporator is obtained by sticking the outer surface of a heat exchanger tube and the through-hole of a radiation fin by expanding a heat exchanger tube. The heat transfer tube is larger on the inlet side in the flow direction of the working refrigerant on the outlet side than on the expanded side.

  In this refrigeration apparatus, the pressure loss of the working refrigerant in the evaporator can be effectively reduced by changing the degree of expansion of the heat transfer tube between the inlet side and the outlet side.

  In the refrigeration apparatus of the third invention, in the refrigeration apparatus of the first invention or the second invention, the heat transfer tube has an uneven shape provided so as to extend along the inner surface in a direction not parallel to the flow direction of the working refrigerant. Have.

  In this refrigeration apparatus, since the surface area per unit area inside the heat transfer tube can be increased, the heat exchange efficiency can be increased.

  In the refrigeration apparatus of the fourth invention, in the refrigeration apparatus of the third invention, the inner diameter of the heat transfer tube is a value twice the shortest distance between the convex portion of the concavo-convex shape and the axis of the heat transfer tube.

  In this refrigeration apparatus, the difference in the inner diameter can be easily ensured by the pipe expansion using the pipe expansion tool from the inside of the heat transfer tube.

  In the refrigeration apparatus of the fifth invention, in the refrigeration apparatus of the third invention or the fourth invention, the surface perpendicular to the axial direction of the heat transfer tube and the direction in which the uneven shape of the heat transfer tube extends along the inner surface The smaller one of the angles formed by the two is larger on the outlet side than on the inlet side in the flow direction of the working refrigerant.

  In this refrigeration apparatus, the pressure loss that the working refrigerant flowing in the heat transfer tube receives due to the uneven shape is reduced as the flow direction of the working refrigerant and the direction in which the uneven shape extends are closer to each other. For this reason, pressure loss can be more effectively suppressed on the outlet side of the evaporator than on the inlet side.

  In the refrigeration apparatus of the sixth invention, in the refrigeration apparatus of any one of the third to fifth inventions, the difference in height of the uneven shape in the radial direction of the heat transfer tube is greater than the outlet side in the flow direction of the working refrigerant in the heat transfer tube. The side is bigger.

  In this refrigeration apparatus, the pressure loss that the working refrigerant flowing in the heat transfer tube receives due to the uneven shape is reduced as the height difference of the uneven shape is smaller. For this reason, pressure loss can be more effectively suppressed on the outlet side of the evaporator than on the inlet side.

The refrigeration apparatus of the seventh invention includes a refrigerant circuit and a working refrigerant. The refrigerant circuit has at least a compression mechanism, a condenser, an expansion mechanism, and an evaporator. The working refrigerant is expressed by a molecular formula: C ₃ H _m F _n (where m = 1 to 5, n = 1 to 5, and m + n = 6) in which a refrigeration cycle is performed by circulating in the refrigerant circuit. And either a single refrigerant composed of a refrigerant having one double bond in the molecular structure, or a mixed refrigerant containing the refrigerant. The evaporator has a heat transfer tube in which a working refrigerant flows and an uneven shape extending in a direction not parallel to the flow direction of the working refrigerant is provided on the inner surface. The resistance caused by the uneven shape of the heat transfer tube with respect to the flow of the working refrigerant is larger on the inlet side of the evaporator in the direction of flow of the working refrigerant than on the outlet side.

  In this refrigeration apparatus, a working refrigerant having an ozone depletion coefficient of 0 can be used. Moreover, since this refrigeration apparatus employ | adopts uneven | corrugated shape on the inner surface of a heat exchanger tube, since the surface area per unit area inside a heat exchanger tube can be increased, the heat exchange efficiency can be raised. In addition, among the evaporators, the resistance on the outlet side where the gas component of the working refrigerant exists is made smaller than the resistance on the inlet side where the liquid component of the working refrigerant exists, so that the working refrigerant flowing in the evaporator Corresponding to the increase in the specific volume, the resistance of the heat transfer tube can be reduced. For this reason, the pressure loss which arises in the part which a pressure loss tends to produce in an evaporator can be reduced. Thereby, even when the ozone layer depletion coefficient is set to 0 using the working refrigerant, it is possible to reduce the pressure loss in the evaporator while increasing the heat exchange efficiency.

  In the refrigeration apparatus of the eighth invention, in the refrigeration apparatus of the seventh invention, of the angles formed by the surface perpendicular to the axial direction of the heat transfer tube and the direction in which the uneven shape of the heat transfer tube extends along the inner surface Is smaller on the outlet side than on the inlet side in the flow direction of the working refrigerant.

  In this refrigeration apparatus, the pressure loss that the working refrigerant flowing in the heat transfer tube receives due to the uneven shape is reduced as the flow direction of the working refrigerant and the direction in which the uneven shape extends are closer to each other. For this reason, pressure loss can be more effectively suppressed on the outlet side of the evaporator than on the inlet side.

  In the refrigeration apparatus of the ninth invention, in the refrigeration apparatus of the seventh or eighth invention, the difference in height of the uneven shape in the radial direction of the heat transfer tube is greater on the inlet side than on the outlet side in the flow direction of the working refrigerant in the heat transfer tube. Is big.

  In this refrigeration apparatus, the pressure loss that the working refrigerant flowing in the heat transfer tube receives due to the uneven shape is reduced as the height difference of the uneven shape is smaller. For this reason, pressure loss can be more effectively suppressed on the outlet side of the evaporator than on the inlet side.

  In the refrigeration apparatus according to the tenth aspect, in the refrigeration apparatus according to any one of the seventh to ninth aspects, the outer diameters of the heat transfer tubes are substantially equal.

  In this refrigeration apparatus, heat transfer tubes having substantially the same outer diameter can be used, so that the air flow passing through the outer surface of the heat transfer tube can be reduced by the location of the evaporator.

  In the refrigeration apparatus according to the eleventh aspect, in the refrigeration apparatus according to any one of the seventh to ninth aspects, the evaporator uses a heat transfer tube having the same shape and the same size, and the degree of expansion on the outlet side in the flow direction of the working refrigerant. Is larger than the degree of expansion on the inlet side.

  In this refrigeration apparatus, heat transfer tubes having the same shape and the same dimensions can be used, so that the manufacturing cost can be reduced.

  In a refrigeration apparatus according to a twelfth aspect of the present invention, in the refrigeration apparatus according to any one of the third to sixth aspects and the seventh to eleventh aspects, the heat transfer tube is a seam tube.

  In this refrigeration apparatus, the evaporator can be easily manufactured even in the case where both the portion having the uneven shape and the portion not having the uneven shape are provided in the heat transfer tube.

  In the refrigeration apparatus of the thirteenth invention, in the refrigeration apparatus of any one of the third to sixth inventions and the seventh to twelfth inventions, the heat transfer tube has the working refrigerant from the horizontal one end side of the evaporator in the horizontal direction, etc. It is arranged to flow only toward the end side.

  In this refrigeration apparatus, the working refrigerant flows in one direction in the evaporator and is not provided with a turn. For this reason, it becomes possible to reduce the part by which the direction of the working refrigerant which flows through the inside of a heat exchanger tube is changed abruptly.

  In a refrigeration apparatus according to a fourteenth aspect, in the refrigeration apparatus according to any one of the third to sixth aspects and the seventh to thirteenth aspects, the heat transfer tube has an axial direction of 90 degrees or less in the vicinity of the inlet side of the evaporator. It has an acute angle bent portion bent at an angle, and does not have a portion bent at an angle of 90 degrees or less in the vicinity of the outlet side of the evaporator.

  In this refrigeration apparatus, the heat transfer tube in the vicinity of the inlet side of the evaporator has an acute angle bent portion bent at an angle of 90 degrees or less, so the evaporator can be made compact so as to correspond to the installation space. . In the vicinity of the inlet side of the evaporator, the working refrigerant exists in a liquid state or a gas-liquid two-phase state, so even if it is bent at an angle of 90 degrees or less, it exists in a gas single-phase state. In comparison, the pressure loss can be kept small. In addition, since the heat transfer tube near the outlet of the evaporator does not have a portion bent at an angle of 90 degrees or less, pressure loss caused by abrupt bending of the traveling direction of the working refrigerant in the gas state is unlikely to occur. Can be. As a result, the evaporator can be made compact while keeping the pressure loss in the evaporator small.

The refrigeration apparatus of the fifteenth aspect of the invention is a molecular circuit: C ₃ H _m F _{n in which a} refrigeration cycle is performed by circulating in the refrigerant circuit and a refrigerant circuit having at least a compressor, a condenser, an expansion mechanism, and an evaporator. (However, m = 1 to 5, n = 1 to 5, and m + n = 6) and includes a single refrigerant composed of a refrigerant having one double bond in the molecular structure or a refrigerant. A working refrigerant that is one of the mixed refrigerants. The evaporator has a larger pipe diameter on the outlet side than on the inlet side in the refrigerant flow direction when functioning as an evaporator.

  In this refrigeration apparatus, the pressure loss of the evaporator can be reduced.

A refrigeration apparatus according to a sixteenth aspect of the present invention has a refrigerant circuit having at least a compressor, a condenser, an expansion mechanism, and an evaporator, and a refrigeration cycle performed by circulating the refrigerant circuit. Molecular formula: C ₃ H _m F _n (However, m = 1 to 5, n = 1 to 5, and m + n = 6) and includes a single refrigerant composed of a refrigerant having one double bond in the molecular structure or a refrigerant. A working refrigerant that is one of the mixed refrigerants. In the evaporator, the concave and convex grooves on the inner side of the pipe are deeper on the inlet side in the refrigerant flow direction when functioning as an evaporator than on the outlet side.

  In this refrigeration apparatus, the pressure loss of the evaporator can be reduced.

According to a seventeenth aspect of the present invention, there is provided a method of manufacturing a refrigeration apparatus. A refrigerant circuit having an evaporator obtained by increasing the degree of expansion of the gas, and a refrigeration cycle is performed by circulating in the refrigerant circuit. Molecular formula: C ₃ H _m F _n (where m = 1 to 5, n = 1 -5 and m + n = 6), and a working refrigerant that is either a single refrigerant composed of a refrigerant having one double bond in the molecular structure or a mixed refrigerant containing a refrigerant. I have.

  In this method for manufacturing a refrigeration apparatus, a refrigeration apparatus having an evaporator that can reduce pressure loss can be easily manufactured.

The refrigeration apparatus of the eighteenth aspect of the invention is a molecular circuit: C ₃ H _m F _{n in which a} refrigeration cycle is performed by circulating in the refrigerant circuit and a refrigerant circuit having at least a compressor, a condenser, an expansion mechanism, and an evaporator. (However, m = 1 to 5, n = 1 to 5, and m + n = 6) and includes a single refrigerant composed of a refrigerant having one double bond in the molecular structure or a refrigerant. A working refrigerant that is one of the mixed refrigerants. The evaporator has a substantially quadrangular prism shape that is divided into approximately equal halves.

  In this refrigeration apparatus, the pressure loss of the evaporator can be reduced.

The refrigeration apparatus of the nineteenth aspect of the invention is a molecular circuit: C ₃ H _m F _{n in which a} refrigeration cycle is performed by circulating in the refrigerant circuit and a refrigerant circuit having at least a compressor, a condenser, an expansion mechanism, and an evaporator. (However, m = 1 to 5, n = 1 to 5, and m + n = 6) and includes a single refrigerant composed of a refrigerant having one double bond in the molecular structure or a refrigerant. A working refrigerant that is one of the mixed refrigerants. The evaporator does not have a portion where the bending angle of the heat transfer tube is less than 90 degrees from the inlet to the outlet.

  In this refrigeration apparatus, the pressure loss of the evaporator can be reduced.

The refrigeration apparatus according to the twentieth aspect of the present invention is a molecular circuit: C ₃ H _m F _{n in which a} refrigeration cycle is performed by circulating through the refrigerant circuit having at least a compressor, a condenser, an expansion mechanism, and an evaporator. (However, m = 1 to 5, n = 1 to 5, and m + n = 6) and includes a single refrigerant composed of a refrigerant having one double bond in the molecular structure or a refrigerant. A working refrigerant that is one of the mixed refrigerants. The evaporator has a heat transfer tube which is a seam tube.

  In this refrigeration apparatus, even if a seam pipe is adopted by using a low-pressure refrigerant, refrigerant leakage hardly occurs.

A refrigeration apparatus according to a twenty-first aspect of the present invention includes a refrigerant circuit having at least a compressor, a condenser, an expansion mechanism, and an evaporator, and a refrigeration cycle performed by circulating the refrigerant circuit. Molecular formula: C ₃ H _m F _n (However, m = 1 to 5, n = 1 to 5, and m + n = 6) and includes a single refrigerant composed of a refrigerant having one double bond in the molecular structure or a refrigerant. A working refrigerant that is one of the mixed refrigerants. The evaporator has a heat transfer tube which is a seam tube having a non-uniform uneven shape on the inner surface side.

  In this refrigeration apparatus, the heat transfer coefficient can be improved by making the uneven shape of the inner surface of the seam tube non-uniform.

  In a refrigeration apparatus according to a twenty-second invention, in the refrigeration apparatus according to any one of the first to twenty-first inventions, the working refrigerant is a single refrigerant made of 2,3,3,3-tetrafluoro-1-propene.

  In this refrigeration apparatus, the ozone depletion coefficient can be set to 0, and the operation in the refrigeration cycle can be made favorable.

  In the refrigeration apparatus of the 23rd invention, in any of the refrigeration apparatuses of the 1st invention to the 21st invention, the working refrigerant is a mixed refrigerant of 2,3,3,3-tetrafluoro-1-propene and difluoromethane, or , 2,3,3,3-tetrafluoro-1-propene and pentafluoroethane mixed refrigerant.

  In this refrigeration apparatus, the ozone depletion coefficient is set to 0, and the operation in the refrigeration cycle can be improved even if the refrigerant temperature tends to change during the phase change.

The method for manufacturing a refrigeration apparatus according to the twenty-fourth aspect includes the following steps. In the first step, a first tube expansion tool for expanding the evaporator inlet side of the heat transfer tube provided in the evaporator, and a second tube expansion tool having a tube expansion target inner diameter value larger than that of the first tube expansion tool and expanding the evaporator outlet side To obtain an evaporator. In the second step, a refrigerant circuit is obtained by connecting at least the evaporator, the compression mechanism, the condenser, and the expansion mechanism obtained in the first step. In the third step, the molecular formula: C ₃ H _m F _n (where m = 1 to 5, n) is used to cause the refrigerant circuit obtained in the second step to circulate in the refrigerant circuit to perform a refrigeration cycle. = 1-5 and m + n = 6), and a working refrigerant that is one of a single refrigerant composed of a refrigerant having one double bond in the molecular structure and a mixed refrigerant containing the refrigerant. Fill.

  In the refrigeration apparatus obtained by the manufacturing method of the refrigeration apparatus, a working refrigerant having an ozone layer depletion coefficient of 0 can be used. Further, in the refrigeration apparatus obtained by the method for manufacturing the refrigeration apparatus, the expansion side of the heat transfer tube included in the evaporator is changed between the inlet side and the outlet side, whereby the outlet side on which a large amount of the gas component of the working refrigerant exists. Is made larger than the inner diameter on the inlet side where a large amount of liquid component of the working refrigerant exists. For this reason, the inner diameter of the heat transfer tube can be increased in response to an increase in the specific volume of the working refrigerant flowing in the evaporator, and the pressure loss of the working refrigerant in the evaporator can be effectively reduced. . Thereby, even when the ozone layer depletion coefficient is set to 0 using the above working refrigerant, the pressure loss of the working refrigerant in the evaporator is changed by changing the extent of expansion of the heat transfer tube between the inlet side and the outlet side. Can be effectively reduced.

The manufacturing method of the refrigeration apparatus of the 25th invention includes the following steps. In the first step, a heat transfer tube having the same shape and the same size with an uneven shape extending on the inner surface extending in a direction not parallel to the flow direction of the working refrigerant is prepared, and the flow of the working refrigerant due to the uneven shape of the heat transfer tube is prepared. The evaporator is obtained by processing so that the resistance is larger on the inlet side of the evaporator in the flow direction of the working refrigerant than on the outlet side. In the second step, a refrigerant circuit is obtained by connecting at least the evaporator, the compression mechanism, the condenser, and the expansion mechanism obtained in the first step. In the third step, the molecular formula: C ₃ H _m F _n (where m = 1 to 5, n) is used to cause the refrigerant circuit obtained in the second step to circulate in the refrigerant circuit to perform a refrigeration cycle. = 1-5 and m + n = 6), and a working refrigerant that is one of a single refrigerant composed of a refrigerant having one double bond in the molecular structure and a mixed refrigerant containing the refrigerant. Fill.

  In the refrigeration apparatus obtained by the manufacturing method of the refrigeration apparatus, a working refrigerant having an ozone layer depletion coefficient of 0 can be used. Moreover, in the refrigeration apparatus obtained by the manufacturing method of this refrigeration apparatus, the uneven | corrugated shape is employ | adopted on the inner surface of the heat exchanger tube which the evaporator has. For this reason, the surface area per unit area inside a heat exchanger tube can be increased, and the heat exchange efficiency can be raised. In addition, among the evaporators, the resistance on the outlet side where the gas component of the working refrigerant exists is made smaller than the resistance on the inlet side where the liquid component of the working refrigerant exists, so that the working refrigerant flowing in the evaporator Corresponding to the increase in the specific volume, the resistance of the heat transfer tube can be reduced. For this reason, the pressure loss which arises in the part which a pressure loss tends to produce in an evaporator can be reduced. In addition, the types of heat transfer tubes prepared in the first step can be unified. Thereby, even when the ozone layer depletion coefficient is set to 0 using the above working refrigerant, a refrigeration apparatus capable of suppressing the pressure loss in the evaporator small while increasing the heat exchange efficiency is inexpensive. It becomes possible to manufacture.

  In the refrigeration apparatus of the first invention, even when the ozone layer depletion coefficient is 0, the pressure loss in the evaporator can be kept small.

  In the refrigeration apparatus of the second invention, the pressure loss of the working refrigerant in the evaporator can be effectively reduced.

  In the refrigeration apparatus of the third invention, the heat exchange efficiency can be increased.

  In the refrigeration apparatus according to the fourth aspect of the present invention, the difference in the inner diameter can be easily ensured by the pipe expansion using the pipe expansion tool from the inside of the heat transfer tube.

  In the refrigeration apparatus of the fifth aspect of the invention, the pressure loss can be suppressed more effectively on the outlet side of the evaporator than on the inlet side.

  In the refrigeration apparatus of the sixth aspect of the invention, the pressure loss can be suppressed more effectively on the outlet side of the evaporator than on the inlet side.

  In the refrigeration apparatus according to the seventh aspect of the invention, even when the ozone layer depletion coefficient is 0, the pressure loss in the evaporator can be kept small while increasing the heat exchange efficiency.

  In the refrigeration apparatus of the eighth aspect of the invention, the pressure loss can be suppressed more effectively on the outlet side of the evaporator than on the inlet side.

  In the refrigeration apparatus of the ninth aspect of the invention, the pressure loss can be more effectively suppressed on the outlet side of the evaporator than on the inlet side.

  In the refrigeration apparatus according to the tenth aspect of the present invention, the air flow passing through the outer surface of the heat transfer tube can reduce the distance due to the location of the evaporator.

  In the refrigeration apparatus according to the eleventh aspect of the invention, the manufacturing cost can be kept small.

  In the refrigeration apparatus according to the twelfth aspect of the invention, the evaporator can be easily manufactured even when both the portion having the uneven shape and the portion not having the uneven shape are provided.

  In the refrigeration apparatus according to the thirteenth aspect, it is possible to reduce the portion where the direction of the working refrigerant flowing in the heat transfer tube is suddenly changed.

  In the refrigeration apparatus according to the fourteenth aspect, the evaporator can be made compact while keeping the pressure loss in the evaporator small.

  In the refrigeration apparatus according to the fifteenth aspect, the pressure loss of the evaporator can be reduced.

  In the refrigeration apparatus according to the sixteenth aspect of the present invention, the pressure loss of the evaporator can be reduced.

  In the refrigeration apparatus manufacturing method according to the seventeenth aspect of the present invention, it is possible to easily manufacture a refrigeration apparatus having an evaporator that can reduce pressure loss.

  In the refrigeration apparatus according to the eighteenth aspect of the invention, the pressure loss of the evaporator can be reduced.

  In the refrigeration apparatus according to the nineteenth aspect, the pressure loss of the evaporator can be reduced.

  In the refrigeration apparatus of the twentieth invention, even if a seam pipe is adopted by using a low-pressure refrigerant, refrigerant leakage hardly occurs.

  In the refrigeration apparatus of the twenty-first invention, the heat transfer coefficient can be improved by making the uneven shape of the inner surface of the seam tube non-uniform.

  In the refrigeration apparatus of the twenty-second invention, the ozone depletion coefficient can be set to 0, and the operation in the refrigeration cycle can be made favorable.

  In the refrigeration apparatus according to the twenty-third aspect, the ozone depletion coefficient is set to 0, and the operation in the refrigeration cycle can be improved even if the refrigerant temperature tends to change during the phase change.

  In the method for manufacturing a refrigeration apparatus according to the twenty-fourth aspect of the present invention, even when the ozone layer depletion coefficient is 0, by changing the extent of expansion of the heat transfer tube between the inlet side and the outlet side, the working refrigerant in the evaporator Pressure loss can be effectively reduced.

  In the method for manufacturing a refrigeration apparatus according to the twenty-fifth aspect of the present invention, there is provided a refrigeration apparatus capable of reducing the pressure loss in the evaporator while increasing the heat exchange efficiency even when the ozone depletion coefficient is 0. It can be manufactured at low cost.

The figure which shows the example of the refrigerant circuit which can apply this invention. The ph diagram which shows the example of the refrigerating cycle of the single refrigerant | coolant of this invention. The Ts diagram which shows the example of the refrigerating cycle of the single refrigerant | coolant of this invention. The figure which shows the example of the refrigerant circuit which can apply this invention. The figure which shows the example of the refrigerant circuit which can apply this invention. The figure which shows the example of the refrigerant circuit which can apply this invention. The figure which shows the example of the refrigerant circuit which can apply this invention. The figure which shows the example of the refrigerant circuit which can apply this invention. The figure which shows the example of the refrigerant circuit which can apply this invention. The figure which shows the example of the refrigerant circuit which can apply this invention. The figure which shows the example of the refrigerant circuit which can apply this invention. The figure which shows the example of the refrigerant circuit which can apply this invention. The figure which shows the example of the refrigerant circuit which can apply this invention. The figure which shows the example of the refrigerant circuit which can apply this invention. The figure which shows the heat exchanger tube of 1st Embodiment. The figure which shows the heat exchanger tube of the modification of 1st Embodiment. The figure which shows the conventional heat exchanger. The figure which shows the heat exchanger of the modification of 1st Embodiment. The figure which shows the conventional heat exchanger. The figure which shows the heat exchanger of the modification of 1st Embodiment. The figure which shows the conventional heat exchanger tube material. The figure which shows the heat exchanger tube material of 2nd Embodiment. The figure which shows the heat exchanger tube material of 2nd Embodiment. The figure which shows the heat exchanger tube of the modification of 2nd Embodiment. The figure which shows the evaporator of 3rd Embodiment. The figure which shows the evaporator of the modification (1) of 3rd Embodiment. The figure which shows the evaporator of the modification (2) of 3rd Embodiment. The figure which shows the evaporator of the modification (3) of 3rd Embodiment. The figure which shows the evaporator of the modification (4) of 3rd Embodiment. The figure which shows the evaporator of the modification (5) of 3rd Embodiment. The figure which shows the evaporator of the modification (6) of 3rd Embodiment. The figure which shows the evaporator of the modification (7) of 3rd Embodiment. The figure which shows the heat exchanger tube cross section of the modification (7) of 3rd Embodiment. The figure which shows the heat exchanger tube cross section of the modification (8) of 3rd Embodiment. The figure which shows the heat exchanger tube cross section of the modification (9) of 3rd Embodiment. The figure which shows the evaporator of the modification (11) of 3rd Embodiment. The figure which shows the evaporator of the modification (12) of 3rd Embodiment. The figure which shows the example of the heat exchanger tube prepared in the modification (13) of 3rd Embodiment. The figure which shows the manufacture example of the evaporator in the modification (13) of 3rd Embodiment. The figure which shows the example of the evaporator obtained in the modification (13) of 3rd Embodiment. The figure which shows the refrigerating cycle of the modification (14) of 3rd Embodiment. The figure which shows the refrigerating cycle of the modification (15) of 3rd Embodiment.

  Hereinafter, a plurality of embodiments will be described as examples of embodiments of the present invention.

  As long as there is no contradiction with each other, embodiments described below can adopt embodiments in which different embodiments are freely combined, and embodiments by this combination are also included in the present invention. In addition, as this combination, it is more preferable to employ a combination that exhibits not only individual effects but also synergistic effects.

<1> Example of refrigeration cycle Hereinafter, before showing an example of an embodiment of the present invention, an example of a refrigeration cycle to which the present invention is applied will be described.

  In addition, the refrigeration cycle shown below shows the example of the refrigeration cycle to which this invention is applied, Comprising: The refrigeration cycle which can apply this invention is not limited to the following refrigeration cycles.

  In the following description, the heat exchanger indicated by member number 4 means an outdoor heat exchanger installed in a space other than the air-conditioned space such as outdoors, and the heat exchanger indicated by member number 6 It means an indoor heat exchanger installed in an air-conditioned space such as a room.

(1-A) Cooling Application Refrigeration Cycle FIG. 1 shows an example of a refrigerant circuit 10A included in an air conditioner 1 that performs a cooling-only refrigeration cycle.

  The refrigerant circuit 10 includes a compressor 2, a condenser 4 installed outdoors, an expansion valve 5, and an evaporator 6 installed indoors in this order, and the refrigerant circulates in the interior. Perform a refrigeration cycle. The compressor 2 is driven by a motor 2a.

  Here, the refrigerant that operates in the refrigerant circuit 10A may be a single refrigerant or a mixed refrigerant.

  As such a refrigerant, for example, a single refrigerant made of HFO-1234yf (2,3,3,3-tetrafluoro-1-propene) can be used.

In place of this refrigerant, for example, the molecular formula: C ₃ H _m F _n (where m = 1 to 5, n = 1 to 5, and m + n = 6) is used, and two in the molecular structure. A single refrigerant composed of a refrigerant having one double bond can be used. For example, HFO-1225ye (1,2,3,3,3-pentafluoro-1-propene, chemical formula: CF ₃ —CF═CHF), HFO-1234ze (1,3,3,3-tetrafluoro-1- Propene, chemical formula: CF ₃ —CH═CHF), HFO-1234ye (1,2,3,3-tetrafluoro-1-propene, chemical formula: CHF ₂ —CF═CHF), HFO-1243zf (3, 3, 3 - trifluoro-1-propene, chemical _{formula: CF 3 -CH = CH 2)} , 1,2,2- trifluoro-1-propene (chemical _{formula: CH 3 -CF = CF 2)} , 2- fluoro-1-propene (Chemical formula: CH ₃ —CF═CH ₂ ) or the like can be used.

  Moreover, you may use the mixed refrigerant | coolant containing the above-mentioned refrigerant | coolant. For example, there is a mixed refrigerant of HFO-1234yf (2,3,3,3-tetrafluoro-1-propene) and HFC-32 (difluoromethane). Here, as a composition of this mixed refrigerant, the ratio of HFO-1234yf is 70% by mass or more and 94% by mass or less, and the ratio of HFC-32 is 6% by mass or more and 30% by mass or less, preferably HFO-1234yf. The proportion is 77% by mass or more and 87% by mass or less, and the proportion of HFC-32 is preferably 13% by mass or more and 23% by mass or less. More preferably, the proportion of HFO-1234yf is 77% by mass or more and 79% by mass or less. Is preferably 21% by mass to 23% by mass (for example, a mixed refrigerant of 78% by mass of HFO-1234yf and 22% by mass of HFC-32). Further, there is a mixed refrigerant of HFO-1234yf (2,3,3,3-tetrafluoro-1-propene) and HFC-125 (pentafluoroethane). Here, the composition of the mixed refrigerant is such that the ratio of HFO-1234yf is 90% by mass or less and the ratio of HFC-125 is 10% by mass or more, preferably, the ratio of HFO-1234yf is 80% by mass or more and 90% by mass. %, The ratio of HFC-125 is preferably 10% by mass or more and 20% by mass or less. In addition, other HFC refrigerants such as HFC-134 (1,1,2,2-tetrafluoroethane), HFC-134a (1,1,1,2-tetrafluoroethane), HFC-143a (1, 1,1-trifluoroethane), HFC-152a (1,1-difluoroethane), HFC-161 (fluoroethane), HFC-227ea (1,1,1,2,3,3,3-heptafluoropropane) HFC-236ea (1,1,1,2,3,3-hexafluoropropane), HFC-236fa (1,1,1,3,3,3-hexafluoropropane), HFC-365mfc (1,1 , 1,3,3-pentafluorobutane) or the like may be used. In addition, other refrigerants such as hydrocarbons, not HFC refrigerants, such as methane, ethane, propane, propene, butane, isobutane, pentane, 2-methylbutane, cyclopentane, dimethyl ether, bis-trifluoromethyl-sulfide, A mixed refrigerant with carbon dioxide, helium or the like may be used.

Further, refrigerants represented by molecular formula: C ₃ H _m F _n (where m = 1 to 5, n = 1 to 5 and m + n = 6) and having one double bond in the molecular structure Or a molecular formula: C ₃ H _m F _n (where m = 1 to 5, n = 1 to 5, and m + n = 6), and a double bond in the molecular structure And other refrigerants such as the above-mentioned HFC refrigerants and hydrocarbons, the molecular formula: C ₃ H _m F _n (where m = 1 to 5, n = 1 to 5, and m + n = 6), and a mixed refrigerant composed of three or more components including at least one refrigerant having one double bond in the molecular structure may be used. For example, there is a mixed refrigerant of HFO-1234yf, HFC-32, and HFC-125 (for example, a mixed refrigerant of 52% by weight of HFO-1234yf, 23% by mass of HFC-32, and 25% by weight of HFC-125). .

  In the refrigerant circuit 10A filled with the above refrigerant, the refrigerant discharged from the compressor 2 is condensed in the condenser to become liquid refrigerant, and the liquid refrigerant is decompressed by the expansion valve 5 and becomes gas refrigerant through the evaporator. The refrigeration cycle is executed by returning to the compressor 2.

  FIG. 2 is a ph diagram when the refrigeration cycle is performed using HFO-1234yf (2,3,3,3-tetrafluoro-1-propene) as a single refrigerant in the refrigerant circuit 10A. Show. FIG. 3 is a Ts diagram when the refrigeration cycle is performed using HFO-1234yf (2,3,3,3-tetrafluoro-1-propene) as a single refrigerant in the refrigerant circuit 10A. Show.

  In the cooling-only refrigeration cycle, the refrigerant circulates in the order of A → B → C → D → A in the portion indicated by points A to D in the refrigerant circuit 10A in FIG. 2 and 3 are the same in that the refrigerant circulates in the order of A → B → C → D → A.

  The behavior of the refrigerant shown in FIG. 2 and FIG. 3 is an example when used in the cooling-only refrigeration cycle, and points A, B, C, and D are points in the cooling-only refrigeration cycle shown in FIG. Show. In the drawings showing other refrigerant circuits, the points A, B, C, D,... Are shown, but these are not the same state but different ones. It shows the points based on the circuit.

(1-B) Heating-only refrigeration cycle FIG. 4 shows an example of the refrigerant circuit 10B of the air-conditioning apparatus 1 that performs the heating-only refrigeration cycle. As the refrigerant used here, any one of the single refrigerant and the mixed refrigerant exemplified as the refrigerant used in the above-described cooling-only refrigeration cycle can be used.

  Here, the discharge side of the compressor 2 is connected to a condenser 6 installed indoors. Further, the refrigerant evaporated in the evaporator 4 installed outdoors is sucked into the compressor 2.

  The refrigerant circuit 10A is provided with a temperature sensor 4a capable of detecting the temperature in the vicinity of the evaporator 4 installed outdoors, and a control unit 4b for controlling the operation of the refrigerant circuit 10A. This control part 4b performs control which stops the driving | operation in the refrigerant circuit 10B, when the temperature which the temperature sensor 4a detects becomes below the atmospheric pressure equivalent temperature of a refrigerant | coolant. Thereby, the situation where frost formation to the evaporator 4 installed outdoors can be avoided.

(1-C) Cooling / heating switching refrigeration cycle FIG. 5 shows an example of a refrigerant circuit 10C of the air-conditioning apparatus 1 that performs the cooling / heating switching refrigeration cycle. As the refrigerant used here, any one of the single refrigerant and the mixed refrigerant exemplified as the refrigerant used in the above-described cooling-only refrigeration cycle can be used.

  Here, there is a four-way switching valve 3 for switching the four connection objects of the discharge side, the suction side, the indoor heat exchanger (condenser, evaporator), and the outdoor heat exchanger (evaporator, condenser) of the compressor 2. Is provided. Other configurations are the same as those of the refrigerant circuit 10A described above.

  In the four-way switching valve 3 shown in FIG. 5, the connection state when the cooling operation is performed is indicated by a solid line, and the connection state when the heating operation is performed is indicated by a dotted line.

(1-D) Accumulator refrigeration cycle FIG. 6 shows an example of a refrigerant circuit 10D of the air conditioner 1 that performs the accumulator refrigeration cycle. As the refrigerant used here, any one of the single refrigerant and the mixed refrigerant exemplified as the refrigerant used in the above-described cooling-only refrigeration cycle can be used.

  Here, an accumulator 7 is provided between the four-way switching valve 3 and the suction side of the compressor 2. In this accumulator refrigeration cycle, the risk of liquid compression occurring in the compressor 2 is reduced. Other configurations are the same as those of the refrigerant circuit 10C described above.

(1-E) Receiver Refrigeration Cycle FIG. 7 shows an example of the refrigerant circuit 10E included in the air conditioner 1 that performs the receiver refrigeration cycle. As the refrigerant used here, any one of the single refrigerant and the mixed refrigerant exemplified as the refrigerant used in the above-described cooling-only refrigeration cycle can be used.

  Here, a receiver 8 is provided between the outdoor heat exchanger 4 (condenser and evaporator) and the expansion valve 5. In this receiver refrigeration cycle, the receiver 8 can absorb the change in the amount of circulating refrigerant corresponding to the load fluctuation around the refrigerant circuit 10D. Other configurations are the same as those of the refrigerant circuit 10A described above.

(1-F) Liquid Gas Heat Exchanger Refrigeration Cycle FIG. 8 shows an example of the refrigerant circuit 10F included in the air conditioner 1 that performs the liquid gas heat exchanger refrigeration cycle. As the refrigerant used here, any one of the single refrigerant and the mixed refrigerant exemplified as the refrigerant used in the above-described cooling-only refrigeration cycle can be used.

  Here, the part through which the liquid refrigerant from the outdoor heat exchanger 4 (condenser) to the expansion valve 5 passes, the part through which the gas refrigerant from the indoor heat exchanger 6 to the suction side of the compressor 2 passes, A liquid gas heat exchange circuit 9 having a liquid gas heat exchanger 9a for performing heat exchange between the two is provided. Here, it is possible to avoid the liquid compression by increasing the circulation amount of the liquid refrigerant to improve the refrigerating capacity and applying appropriate superheat to the refrigerant sucked in the compressor 2. Other configurations are the same as those of the refrigerant circuit 10A described above.

(1-G) Supercooling Refrigeration Cycle FIG. 9 shows an example of a refrigerant circuit 10G included in the air conditioner 1 that performs the supercooling refrigeration cycle. As the refrigerant used here, any one of the single refrigerant and the mixed refrigerant exemplified as the refrigerant used in the above-described cooling-only refrigeration cycle can be used.

  Here, a subcooling circuit 11 is provided in which a part of the refrigerant decompressed in the expansion valve 5 is branched and returned to the suction side of the compressor 2. The supercooling circuit 11 is provided with a supercooling expansion valve 11b that depressurizes the branched refrigerant. And the supercooling circuit 11 has the supercooling heat exchanger 11a which heat-exchanges between the refrigerant | coolant branched and pressure-reduced by the supercooling expansion valve 11b, and the refrigerant | coolant which goes to the evaporator 6 without branching. Yes. Since the enthalpy of the refrigerant going to the evaporator 6 can be further reduced in this way, the coefficient of performance (COP) can be improved. Other configurations are the same as those of the refrigerant circuit 10C described above.

(1-H) Oil Separation Refrigeration Cycle FIG. 10 shows an example of the refrigerant circuit 10H included in the air conditioner 1 that performs the oil separation refrigeration cycle. As the refrigerant used here, any one of the single refrigerant and the mixed refrigerant exemplified as the refrigerant used in the above-described cooling-only refrigeration cycle can be used.

  Here, an oil separation circuit 12 is provided for returning a circuit branched from the discharge side of the compressor 2 to the four-way switching valve 3 to the suction side of the compressor 2. The oil separation circuit 12 is provided with an oil separator 12a that separates the refrigeration oil from the discharged refrigerant, a filter 12b that passes the refrigeration oil recovered in the oil separator 12a, and a capillary tube 12c that decompresses the oil. Thereby, exhaustion of refrigerating machine oil due to an increase in the temperature of the discharged refrigerant can be avoided. Other configurations are the same as those of the refrigerant circuit 10C described above.

(1-I) Hot gas bypass refrigeration cycle FIG. 11 shows an example of the refrigerant circuit 10I of the air conditioner 1 that performs the hot gas bypass refrigeration cycle. As the refrigerant used here, any one of the single refrigerant and the mixed refrigerant exemplified as the refrigerant used in the above-described cooling-only refrigeration cycle can be used.

  The refrigerant circuit 10I is provided with a hot gas bypass circuit 13 that mixes a part of the gas refrigerant discharged from the compressor 2 in the refrigerant circuit 10I with the refrigerant passing through the expansion valve 5 and going to the evaporator 6. ing. The hot gas bypass circuit 13 is provided with a hot gas bypass expansion valve 13 a that can adjust the bypass amount of the refrigerant discharged from the compressor 2. By adjusting the flow rate by the hot gas bypass expansion valve 13a, the state of the refrigerant sucked by the compressor 2 can be stabilized even when the load on the evaporator 6 is reduced. Other configurations are the same as those of the refrigerant circuit 10C described above.

(1-J) Two-stage compression refrigeration cycle FIG. 12 shows an example of the refrigerant circuit 10J of the air conditioner 1 that performs the two-stage compression refrigeration cycle. As the refrigerant used here, any one of the single refrigerant and the mixed refrigerant exemplified as the refrigerant used in the above-described cooling-only refrigeration cycle can be used.

  The refrigerant circuit 10J is provided with a two-stage compression circuit 14 that compresses the refrigerant in two stages using a two-stage compression type compressor as the compressor 2. The two-stage compression circuit 14 is condensed by a low-stage compressor, an intermediate cooler 14a for cooling the refrigerant discharged from the low-stage compressor, a receiver 14b for collecting the refrigerant flowing out of the intermediate cooler 14a, and the condenser 4. There are provided an expansion valve 5a for depressurizing the refrigerant toward the receiver 14b, a high stage compressor for sucking and compressing the gas refrigerant accumulated in the receiver 14b, and an expansion valve 5b for depressurizing the refrigerant toward the evaporator 6 from the receiver 14b. ing. The refrigerant cooled by the intermediate cooler 1a accumulates in the receiver 14b. Further, the refrigerant condensed by the condenser 4 and decompressed by the expansion valve 5a also accumulates in the receiver 14b and is mixed with the refrigerant cooled by the intermediate cooler 14a. The gas refrigerant in the receiver 14b is sucked into the high-stage compressor, but since the sucked refrigerant is cooled, an excessive temperature rise in the high-stage discharge pipe can be prevented, and deterioration and depletion of the refrigerator oil can be prevented. Can be prevented. Moreover, the pressure ratio per stage can be reduced. Other configurations are the same as those of the refrigerant circuit 10C described above.

(1-K) Multi Refrigeration Cycle FIG. 13 shows an example of the refrigerant circuit 10K included in the air conditioner 1 that performs the multi refrigeration cycle. As the refrigerant used here, any one of the single refrigerant and the mixed refrigerant exemplified as the refrigerant used in the above-described cooling-only refrigeration cycle can be used.

  The refrigerant circuit 10K is provided with a plurality of evaporators 6 installed indoors and a multi-refrigerant circuit 15 installed in parallel. Other configurations are the same as those of the refrigerant circuit 10C described above.

(1-L) Steam Bypass Refrigeration Cycle FIG. 14 shows an example of a refrigerant circuit 10L included in the air conditioner 1 that performs the steam refrigeration cycle. As the refrigerant used here, any one of the single refrigerant and the mixed refrigerant exemplified as the refrigerant used in the above-described cooling-only refrigeration cycle can be used.

  The refrigerant circuit 10L includes an accumulator 17b that separates the refrigerant that has been condensed by the condenser 6 and decompressed by the expansion valve 5 and before flowing into the evaporator 4 into a gas refrigerant and a liquid refrigerant. The evaporator 4 that evaporates only the liquid refrigerant excluding the gas refrigerant out of the refrigerant, the expansion valve 17a that depressurizes the gas refrigerant among the refrigerant in the accumulator 17b, and the flow of the refrigerant decompressed by the expansion valve 17a There is provided a steam bypass circuit 17 provided with a check valve 17c that allows only the flow toward the suction side. Here, since the gas refrigerant is removed from the refrigerant flowing into the evaporator 4, it is possible to reduce the gas refrigerant that does not contribute to heat exchange with the air or the like in the evaporator 4, which is a particular problem when the refrigerant is used. Thus, the pressure loss in the evaporator 4 can be reduced. Other configurations are the same as those of the refrigerant circuit 10C described above.

  In addition to this, the vapor bypass circuit 17 is arranged in the same way as the accumulator 17b in the portion where the pressure loss due to the evaporated refrigerant becomes remarkable in the middle of the evaporator 4 to evaporate. The gas refrigerant may be extracted from the middle of the vessel 4. In this case, the gas refrigerant after being evaporated in the evaporator 4 can be extracted, and the pressure loss in the evaporator 4 can be reduced more effectively.

<2> First Embodiment <2-1> Heat Transfer Tube Shape of Heat Exchanger The heat transfer tube of the first embodiment described below is one of (1-A) to (1-L) described above as an example of a refrigeration cycle. It can be applied to any refrigeration cycle.

  As the heat transfer tube of the first embodiment, an evaporator 50A can be employed as shown in FIG.

  In this evaporator 50A, the tube diameter of the heat transfer tube on the outlet side from which the refrigerant in the gas state flows out is larger than the tube diameter of the heat transfer tube on the inlet side into which the liquid refrigerant or the gas-liquid two-phase refrigerant flows. Is formed. As a result, when any one of the single refrigerant and the mixed refrigerant exemplified in the column (1-A) having a large specific volume is employed, the pressure changes due to the phase change from the liquid refrigerant to the gas refrigerant in the evaporator. Even if the loss increases, the diameter of the pressure loss increases because the pipe diameter is widened at that portion. Here, a thin heat transfer tube is connected by a thin U-shaped tube at the end, and a configuration in which the tube diameter of the outlet is larger than the inlet is adopted in the U-shaped tube used for a portion that transitions to a thick heat transfer tube.

  Here, in which part of the evaporator 50A the diameter of the heat transfer tube is increased is determined by the balance between the elimination of the pressure loss and the reduction of the heat exchange amount by reducing the flow velocity.

<2-2> Modification of First Embodiment (1)
As shown in FIG. 16, a heat transfer tube 50 </ b> B having a portion in which the diameter of the evaporator gradually increases from the liquid refrigerant side toward the gas refrigerant side may be adopted as a part of the heat transfer tube of the evaporator.

(2)
Inside the heat transfer tube of the evaporator, a groove shape deeper on the liquid refrigerant side than on the gas refrigerant side may be provided, so that pressure loss due to the gas refrigerant may be reduced. Here, the gas refrigerant side may have a structure in which the peak height of the inner surface of the heat transfer tube is made lower, the number of grooves, the twist angle is made smaller, etc. than the liquid refrigerant side.

(3)
As a method of manufacturing the evaporator according to the modified example (2), when the heat transfer tube having a uniform groove shape is expanded from the inside, the extent of the expansion on the gas refrigerant side is larger than that on the liquid refrigerant side. Thus, the groove shape on the gas refrigerant side may be crushed and manufactured. In this way, the pressure loss can be reduced by smoothing the inner surface of the heat transfer tube on the gas refrigerant side.

(4)
Conventionally, as shown in FIG. 17, in an indoor heat exchanger 960 of a four-direction blowout ceiling embedded type indoor unit that sucks room air from the center by a centrifugal blower and blows it in a radial direction, an input pipe 962 and a path A long piping path structure is adopted in which the heat transfer tube at the end is folded back from 963 through the U-shaped tube to reach the outlet piping 964. For this reason, when any one of the single refrigerant and the mixed refrigerant exemplified in the column (1-A) having a large specific volume is used, the pressure loss becomes more remarkable.

  On the other hand, in this modified example, as shown in FIG. 18, an indoor heat exchanger 60 is employed in which a substantially quadrangular prism shape is divided into two substantially equally so as to be L-shaped. The indoor heat exchanger 60 includes a first divided indoor heat exchanger 61, a second divided indoor heat exchanger 62, an inflow pipe 68, inflow paths 64 and 65, branch pipes 66 and 67, and outflow pipes 68 and 69. ing. The liquid refrigerant or the gas-liquid two-phase refrigerant flowing through the inflow pipe 68 is divided into inflow paths 66 and 67. The refrigerant branched in the inflow path 66 passes through the second branch indoor heat exchanger 62 through the branch pipe 66 and then flows in the outflow pipe 68 as a refrigerant in a gas state. The refrigerant branched in the inflow path 67 passes through the first branch indoor heat exchanger 61 through the branch pipe 67 and then flows through the outflow pipe 69. The gas refrigerant flowing through the outflow pipe 68 and the gas refrigerant flowing through the outflow pipe 69 then merge. Thereby, even if it is a case where any one of the single refrigerant | coolant and mixed refrigerant which were illustrated in the column of the said (1-A) is used as a working refrigerant, each piping path | route can be shortened and pressure loss is reduced. Can be made.

(5)
Conventionally, as shown in FIG. 19, the refrigerant is divided into a plurality of flow dividers 971 by the heat exchanger 970 and flows into the respective heat transfer tubes 972, and each flow path has a so-called hairpin shape. It flows back at the U-shaped tube 973 portion of the pipe. For this reason, the path is long and pressure loss becomes a problem.

  On the other hand, as shown in FIG. 20, like the heat exchanger 70, the refrigerant | coolant flow divided | segmented by the flow divider 71 is each guide | induced to each heat exchanger tube 72, and it is only to one direction toward the header 73 in an other end. It may be configured to flow. In this case, since a folded portion such as a U-shaped tube is not provided, pressure loss can be reduced.

<3> Second Embodiment <3-1> Welded Heat Transfer Tube The heat transfer tube of the second embodiment described below is any one of the refrigeration cycles (1-A) to (1-L) described above as an example of the refrigeration cycle. It can also be applied. And the heat exchanger tube of 2nd Embodiment is the single refrigerant | coolant and mixed refrigerant which were illustrated in the column of said (1-A) in the refrigeration cycle in any one of (1-A)-(1-L) mentioned above. Any of the above can be employed as a heat transfer tube in a refrigeration apparatus that is used as a working refrigerant.

  Conventionally, a seamless tube having an inner surface shape as shown in FIG. 21 is adopted, and the one that increases the surface area of the inner surface of the heat transfer tube and increases the heat exchange performance while preventing refrigerant leakage from the heat transfer tube is used. It has been.

  On the other hand, in the heat transfer tube of the second embodiment, the inner surface shape as shown in FIG. 22 is used together with either the single refrigerant or the mixed refrigerant exemplified in the section (1-A). It is possible to employ a seam pipe having a cylindrical shape by welding. Since the refrigerant employed here has a high boiling point and tends to have a low evaporation pressure, the risk of refrigerant leakage as in the conventional R-410A can be reduced. For this reason, a seam tube can be adopted as the heat transfer tube.

  Moreover, since the uneven | corrugated uneven | corrugated shape is provided in the inside of this heat exchanger tube instead of the groove | channel which repeats the same shape at fixed intervals, reduction of the pressure loss in a pipe | tube can be suppressed effectively.

<3-2> Modified example of the second embodiment (1)
A pipe 81 having a trapezoidal shape instead of a rectangle as shown in FIG. 23 may be used, and a seam pipe 82 having different pipe diameters at one end and the other end as shown in FIG. 24 may be used. By adopting the thicker side of the seam pipe 82 on the gas refrigerant side of the evaporator, the pressure loss of the refrigerant can be reduced.

(2)
The inner surface shape of the seam tube may be a welded tube having a non-uniform uneven shape, instead of a spiral grooved tube having a groove with the same shape at regular intervals. Thereby, a heat transfer rate can also be improved.

<4> Third Embodiment <4-1> Heat Transfer Tube Shape of Heat Exchanger The heat transfer tube of the third embodiment described below is one of (1-A) to (1-L) described above as an example of a refrigeration cycle. It can be applied to any refrigeration cycle.

  The heat transfer tube 351 of the third embodiment constitutes a part of the evaporator 350 as shown in FIG.

  In this evaporator 350, when functioning as a refrigerant evaporator, the refrigerant flows in the direction indicated by the arrow, and the diameter of the heat transfer pipe 351 on the inlet side into which liquid refrigerant or refrigerant in a gas-liquid two-phase state flows is determined. Also, it is formed so that the diameter of the heat transfer tube 351 on the outlet side from which the refrigerant in the gas state flows out becomes larger. In FIG. 25, the heat transfer tube 351 of the evaporator 350 is formed between the substantially U-shaped folded portions so that only the inner diameter increases without changing the outer diameter as it advances in the refrigerant flow direction. Has been. As shown in FIG. 25, the heat transfer tube 351 has an outer diameter L2 larger than the outer diameter L1, and is formed so that the outer diameter of the heat transfer tube 351 increases every time it passes through the folded portion. ing. Thereby, since the outer diameter of the heat transfer tube 351 is not changed between the substantially U-shaped folded portions, the size of the through-hole portion is changed for each radiating fin 352 when the evaporator 350 is manufactured. It can be manufactured by preparing a plurality of heat radiation fins 352 having the same shape. Thereby, in the evaporator 350, manufacturing cost can be reduced, suppressing a pressure loss small.

<4-2> Modification of Third Embodiment (1)
The heat transfer tube 351a of the modification (1) of the third embodiment constitutes a part of the evaporator 350A as shown in FIG.

  In this evaporator 350A, like the evaporator 350 of the third embodiment, when it functions as a refrigerant evaporator, the refrigerant flows in the direction indicated by the arrow, and the liquid refrigerant or the gas-liquid two-phase refrigerant is The tube diameter of the outlet heat transfer tube 351a from which the refrigerant in the gas state flows out is larger than the tube diameter of the inlet heat transfer tube 351a. In FIG. 26, the heat transfer tube 351a of the evaporator 350A is formed such that only the inner diameter increases without changing the outer diameter as it proceeds in the refrigerant flow direction between the substantially U-shaped folded portions. Has been. And as this heat exchanger tube 351a is shown in FIG. 26, the outer diameter La of an entrance side and an exit side becomes a common magnitude | size. Thereby, not only the outer diameter of the heat transfer tube 351a does not change between the substantially U-shaped folded portions, but also the inner diameter of the through-hole formed in one radiating fin 352a can be made common. it can. Thereby, when manufacturing the evaporator 350A, it is not necessary to change the size of the through hole portion for each heat radiating fin 352a, and the inner diameter of the through hole formed in one heat radiating fin 352a is made common. Therefore, all the through holes of the radiating fins 352a can have a common inner diameter. Thereby, in the evaporator 350A, the manufacturing cost of the radiation fin 352a can be reduced while suppressing the pressure loss to be small.

(2)
As shown in FIG. 27, the heat transfer tube 351b of the modification (2) of the third embodiment constitutes a part of the evaporator 350B.

  In this evaporator 350B, like the evaporator 350 of the third embodiment, when functioning as a refrigerant evaporator, the refrigerant flows in the direction indicated by the arrow, and the liquid refrigerant or the gas-liquid two-phase refrigerant is The tube diameter of the heat transfer tube 351b on the outlet side from which the refrigerant in the gas state flows out is larger than the tube diameter of the heat transfer tube 351b on the inlet side into which it flows. In FIG. 27, the heat transfer tube 351b of the evaporator 350B has an outer diameter that gradually increases in the direction of refrigerant flow between the substantially U-shaped folded portions, and the inner diameter also gradually increases. Is formed. As shown in FIG. 27, the heat transfer tube 351b is formed such that the outer diameter L4 is larger than the outer diameter L3 on the inlet side, and the outer diameter L6 is larger than the outer diameter L5. . Here, the outer diameter L4 of the inlet of the substantially U-shaped folded portion is formed to be equal to the outer diameter L5 of the outlet, but the outer diameter L5 is formed to be larger than the outer diameter L4. May be. Thereby, in the evaporator 350B, the material cost of the heat transfer tube 351b can be reduced by reducing the thickness of the heat transfer tube 351b while keeping the pressure loss small.

(3)
As shown in FIG. 28, the heat transfer tube 351c of the modification (3) of the third embodiment constitutes a part of the evaporator 350C, and an uneven shape Wc is formed on the inner surface of the heat transfer tube 351 of the evaporator 350. It has been made. In this case, since the contact area between the refrigerant and the inner surface of the heat transfer tube 351c increases, the effective heat exchange area can be increased. Even when the inner diameter of the heat transfer tube 351c is defined as twice the shortest distance between the peak portion of the concavo-convex shape Wc and the shaft portion of the heat transfer tube 351c, the evaporator 350C has an outlet from the refrigerant inlet side. Since the inner diameter can be increased toward the side, the effect of reducing the pressure loss of the refrigerant is also obtained.

(4)
As shown in FIG. 29, the heat transfer tube 351d of the modification (4) of the third embodiment constitutes a part of the evaporator 350D, and an uneven shape Wd is formed on the inner surface of the heat transfer tube 351a of the evaporator 350A. It has been made. In this case, since the contact area between the refrigerant and the inner surface of the heat transfer tube 351d increases, the effective heat exchange area can be increased. Even when the inner diameter of the heat transfer tube 351d is defined as twice the shortest distance between the peak portion of the concavo-convex shape Wd and the shaft portion of the heat transfer tube 351d, the evaporator 350D has an outlet from the refrigerant inlet side. Since the inner diameter can be increased toward the side, the effect of reducing the pressure loss of the refrigerant is also obtained.

(5)
The heat transfer tube 351e of the modification (5) of the third embodiment constitutes a part of the evaporator 350E as shown in FIG. 30, and the uneven shape We is formed on the inner surface of the heat transfer tube 351b of the evaporator 350B. It has been made. In this case, since the contact area between the refrigerant and the inner surface of the heat transfer tube 351e increases, the effective heat exchange area can be increased. Even when the inner diameter of the heat transfer tube 351e is defined as twice the shortest distance between the peak portion of the concavo-convex shape We and the shaft portion of the heat transfer tube 351e, the evaporator 350E has an outlet from the refrigerant inlet side. Since the inner diameter can be increased toward the side, the effect of reducing the pressure loss of the refrigerant is also obtained.

(6)
As shown in FIG. 31, the heat transfer tube 351f of the modification (6) of the third embodiment constitutes a part of the evaporator 350F and has an uneven shape Wf on the inner surface.

  In this evaporator 350F, similarly to the evaporator 350 of the third embodiment, when functioning as a refrigerant evaporator, the refrigerant flows in the direction indicated by the arrow, and the liquid refrigerant or the gas-liquid two-phase refrigerant flows. The unevenness height difference of the uneven shape Wf of the outlet heat transfer tube 351f from which the refrigerant in the gas state flows is smaller than the uneven height difference of the uneven shape Wf of the heat transfer tube 351f on the inlet side. Yes. In FIG. 31, the heat transfer tube 351f of the evaporator 350F has only the uneven height difference of the uneven shape Wf without changing the outer diameter as it proceeds in the refrigerant flow direction between the substantially U-shaped folded portions. Is formed to gradually shrink. For this reason, in the evaporator 350F, the pressure loss which a refrigerant | coolant receives as it goes to an exit side from an entrance side is restrained small. And as this heat exchanger tube 351f is shown in FIG. 31, the outer diameter Lf of an entrance side and an exit side becomes a common magnitude | size. Thereby, not only the outer diameter of the heat transfer tube 351f does not change between the substantially U-shaped folded portions, but also the inner diameter of the through-hole formed in one radiating fin 352f can be made common. it can. Thereby, when manufacturing the evaporator 350F, it is not necessary to change the size of the through-hole portion for each heat radiating fin 352f, and the inner diameter of the through-hole formed in one heat radiating fin 352f is made common. Therefore, all the through holes of the radiating fins 352f can have a common inner diameter. Thereby, in the evaporator 350F, the manufacturing cost of the radiation fin 352f can be reduced while suppressing the pressure loss to be small.

(7)
As shown in FIG. 32, the heat transfer tube 351g of the modification (7) of the third embodiment constitutes a part of the evaporator 350G and has an uneven shape Wg on the inner surface. FIG. 33 shows a cross-sectional view in which the crests of the concavo-convex shape Wg are connected by a one-dot chain line. In the heat transfer tube 351g, the concavo-convex shape Wg is formed to extend perpendicular to the flow direction of the refrigerant.

  In this evaporator 350G, like the evaporator 350 of the third embodiment, when functioning as a refrigerant evaporator, the refrigerant flows in the direction indicated by the arrow, and the liquid refrigerant or the gas-liquid two-phase refrigerant is The uneven unit shape width in the refrigerant flow direction of the concavo-convex shape Wg of the outlet side heat transfer tube 351g from which the refrigerant in the gas state flows out is larger than the concavo-convex unit shape width in the refrigerant flow direction of the concavo-convex shape Wg of the inlet heat transfer tube 351g. Is formed to be larger. Note that the uneven height difference of the uneven shape Wg is unified to the same height difference in any part. In FIG. 32, the heat transfer tube 351g of the evaporator 350G has an uneven shape Wg in the refrigerant flow direction without changing its outer diameter as it proceeds in the refrigerant flow direction between the substantially U-shaped folded portions. Only the concavo-convex unit shape width is formed so as to gradually increase. For this reason, in the evaporator 350G, the pressure loss which a refrigerant | coolant receives as it goes to an exit side from an entrance side is restrained small. And as this heat exchanger tube 351g is shown in FIG. 32, the outer diameter Lg of an entrance side and an exit side becomes a common magnitude | size. Thereby, not only the outer diameter of the heat transfer tube 351g does not change between the substantially U-shaped folded portions, but also the inner diameter of the through-hole formed in one heat radiating fin 352g can be made common. it can. Thereby, when manufacturing the evaporator 350G, it is not necessary to change the size of the through hole portion for each heat radiation fin 352g, and the inner diameter of the through hole formed in one heat radiation fin 352g is made common. Therefore, all the through holes of the radiating fins 352g can have a common inner diameter. Thereby, in the evaporator 350G, the manufacturing cost of the radiation fin 352g can be reduced while suppressing the pressure loss to be small.

(8)
As shown in FIG. 34, the heat transfer tube 351h of the modification (8) of the third embodiment has an uneven shape Wh. FIG. 34 is a cross-sectional view showing the peak portions of the concavo-convex shape Wh connected by a one-dot chain line. In the heat transfer tube 351h, the concavo-convex shape Wh is formed so as to extend along the inner surface while extending so as to be twisted with respect to the flow direction of the refrigerant. The uneven shape Wh is formed so that the uneven height difference is constant. The uneven shape Wh gradually increases as the smaller one of the angles formed by the surface perpendicular to the axial direction of the heat transfer tube 351h and the direction in which the uneven shape Wh extends as it goes in the refrigerant flow direction. It is formed to become. As a result, the pressure loss can be effectively reduced as the refrigerant flows in the direction of the refrigerant flow, and the heat exchange efficiency on the upstream side can be improved.

(9)
As shown in FIG. 35, the heat transfer tube 351i of the modification (9) of the third embodiment has an uneven shape Wi on the inner surface. FIG. 35 is a cross-sectional view showing the peak portions of the concavo-convex shape Wi connected by a one-dot chain line. In the heat transfer tube 351i, the concavo-convex shape Wi is formed along the inner surface while extending so as to be twisted with respect to the flow direction of the refrigerant. The concavo-convex shape Wi is formed so that the concavo-convex height difference becomes smaller as the refrigerant flows in the direction of the refrigerant flow. The uneven shape Wi gradually increases as the smaller one of the angles formed by the surface perpendicular to the axial direction of the heat transfer tube 351i and the direction in which the uneven shape Wi extends as the refrigerant flows in the direction of the refrigerant flow. It is formed to become. As a result, the pressure loss can be effectively reduced as the refrigerant flows in the direction of the refrigerant flow, and the heat exchange efficiency on the upstream side can be improved. And not only adjustment of the uneven | corrugated unit shape width | variety in a refrigerant | coolant flow direction but not only adjustment of the uneven | corrugated height difference in a refrigerant | coolant flow direction but also with respect to the direction where the uneven | corrugated shape Wi in a refrigerant | coolant flow direction is extended, and the axial direction of the heat exchanger tube 351i The three values can be adjusted by adjusting the smaller one of the angles formed by the vertical surface, and the degree of suppression of these pressure losses and improvement of heat exchange efficiency are meticulously determined. Can be designed.

(10)
About the heat exchanger tube of the said 3rd Embodiment and each modification of 3rd Embodiment, it is a part which contacts a radiation fin, Comprising: About the part which has an uneven | corrugated shape in an inner surface, or the internal diameter of an inner surface differs May use a seam tube and use a seamless tube for other parts. In this way, the evaporator may be obtained by collecting and welding parts that have been subdivided to such an extent that partial uneven shape processing, tube expansion processing, and the like are possible. Since the refrigerant used in the third embodiment and each modification of the third embodiment has a lower refrigerant pressure than the conventional 410A and the like, it is assumed that a welding point is formed in the refrigerant circuit. However, the problem of refrigerant leakage is less likely to occur.

(11)
The heat transfer tube 351j of the modification (11) of the third embodiment constitutes a part of the evaporator 350J as shown in FIG.

  When this heat transfer tube 351j functions as an evaporator as shown by an arrow in FIG. 36, the refrigerant is allowed to flow from one end side in the horizontal direction of the evaporator 350J while diverting the refrigerant through the path 354, and the horizontal direction of the evaporator 350J. It extends so that the refrigerant can be guided so as to flow out from the other end side and join the refrigerant through the path 355. Here, the folding by passing the hairpin-shaped U-shaped tube like the conventional evaporator does not occur. For this reason, since the part which a refrigerant | coolant folds back 180 degree | times is not provided, the pressure loss can be suppressed.

(12)
The heat transfer tube 351k of the modification (12) of the third embodiment constitutes a part of the evaporator 350K as shown in FIG.

  When the heat transfer tube 351k functions as an evaporator as shown by an arrow in FIG. 37, the refrigerant is allowed to flow from one end side in the horizontal direction of the evaporator 350K while being diverted through the path 354, and the horizontal direction of the evaporator 350K. It extends so that the refrigerant can be guided so as to flow out from the other end side and join the refrigerant through the path 356. Here, the folding by passing the hairpin-shaped U-shaped tube like the conventional evaporator does not occur. For this reason, since the part which a refrigerant | coolant folds back 180 degree | times is not provided, the pressure loss can be suppressed. Further, the heat transfer tube 351k has a bent portion of less than 90 degrees on the inlet side flowing into the evaporator 350K, but has a bent portion of less than 90 degrees on the outlet side flowing out of the evaporator 350K. Absent. Furthermore, the heat transfer tube 351k passing through the evaporator 350K is formed such that the bending angle and the bending frequency are lower on the outlet side than on the inlet side. As a result, the inlet side can be made compact by appropriately adopting a bent shape in consideration of the installation space, and the pressure loss can be more effectively reduced on the outlet side.

(13)
The heat transfer tube provided with the uneven shape shown in the modifications (6), (7), (8), and (9) of the third embodiment can be manufactured as follows, for example.

  For example, as shown in FIG. 38, heat transfer tubes f1 and f2 having the same uneven shape are prepared. Specifically, the concavo-convex shape is transferred by pressing the steel material stretched on a plane with a roller having a concavo-convex shape. And the heat exchanger tubes f1 and f2 are obtained by winding the steel material in which the uneven | corrugated shape was transferred in the cylinder shape. Here, the heat transfer tubes f1 and f2 have the same outer diameter, inner diameter, uneven height difference, and uneven unit shape width, and can be mass-produced at low cost. A plurality of heat radiation fins f5 are stacked on the heat transfer tubes f1 and f2 prepared in this way. In this state, the heat transfer tubes f1 and f2 and the radiation fins f5 are still in contact with each other and are not firmly fixed to each other.

  And as shown in FIG. 39, tube expansion heads S1 and S2 having different inclination angles are prepared, and among the heat transfer tubes f1 and f2, the tube expansion rate can be further increased. The tube expansion is performed by the tube expansion head S1, which is the larger one of the tube expansion heads S1 and S2. Further, in both of the heat transfer tubes f1 and f2, the tube expansion heads S1 and S2 are inserted and expanded from the downstream side in the refrigerant flow direction to the upstream side, respectively. At this time, the mountain portion of the uneven shape is appropriately crushed. The degree to which the ridges of the concavo-convex shape are crushed by the expansion heads S1 and S2 is set to be larger on the downstream side of the refrigerant flow. Then, in agreement with the fact that the heat transfer tubes f1 and f2 are expanded by the tube expansion heads S1 and S2, the outer diameters of the heat transfer tubes f1 and f2 are slightly increased, and the inner sides of the through holes of the radiation fins f5 are crimped. In this state, the heat transfer tubes f1 and f2 and the radiation fins f5 are firmly fixed.

  As described above, an evaporator as shown in FIG. 40 is obtained, and a refrigeration cycle is configured by connecting a compressor, a radiator, an expansion valve, and the like thereto. And the single refrigerant | coolant which consists of HFO-1234yf (2,3,3,3-tetrafluoro-1-propene) mentioned above in the refrigeration cycle comprised in this way, HFO-1234yf (2,3,3, 3-tetrafluoro-1-propene) and HFC-32 (difluoromethane) mixed refrigerant, and HFO-1234yf (2,3,3,3-tetrafluoro-1-propene) and HFC-125 (pentafluoro) A refrigerant selected from a refrigerant mixed with ethane) is charged.

(14)
As shown in FIG. 41, in the liquid gas heat exchanger 9a employed in the refrigerant circuit 10F of the air conditioner 1 that performs the liquid gas heat exchanger refrigeration cycle, a refrigerant in a liquid state or a gas-liquid two-phase state is present. In the refrigeration cycle formed so that the wet side pipe 391 that passes through and the dry side pipe 392 through which the gaseous refrigerant passes, the dry side pipe 392 includes the third embodiment and the modification example (1). The shape and structure described in (13) may be applied. That is, not only in the evaporator of the refrigerant, but also in order to reduce the pressure loss in the gas side passage of the liquid gas heat exchanger 9a, the downstream side pressure loss of the dry side pipe 392 is the upstream side pressure loss. You may make it employ | adopt the shape which becomes smaller than this. For example, as described above, the pressure loss may be reduced by making the inner diameter on the outlet side of the dry side pipe 392 larger than the inner diameter on the inlet side of the dry side pipe 392. Further, as described above, the pressure loss due to the uneven shape on the outlet side of the dry side tube 392 may be suppressed to be smaller than the pressure loss due to the uneven shape on the inlet side of the dry side tube 392.

(15)
As shown in FIG. 42, the main flow path side pipe 311 and the branch flow path side pipe 312 pass through the supercooling circuit 11 employed in the refrigerant circuit 10G of the air conditioning apparatus 1 that performs the supercooling refrigeration cycle. In the refrigeration cycle formed as described above, the shape and structure described in the third embodiment and the modifications (1) to (13) may be applied to the branch channel side pipe 312. That is, in addition to applying to the evaporator of the refrigerant, in order to reduce the pressure loss in the branch passage side pipe 312 of the supercooling circuit 11, the branch passage is about Wanhan 312 and the downstream pressure loss is on the upstream side. A shape that becomes smaller than the pressure loss may be adopted. For example, as described above, the pressure loss can be reduced by setting the branch flow path so that the inner diameter on the outlet side of the Waghan 312 is larger than the inner diameter on the inlet side of the Waghan 312. May be. Further, as described above, the pressure loss due to the uneven shape on the outlet side of the branch flow channel side pipe 312 may be suppressed smaller than the pressure loss due to the uneven shape on the inlet side of the branch flow channel side pipe 312.

<5> Reference Embodiment In the modification (13) of the third embodiment, the method for manufacturing the refrigeration apparatus filled with the refrigerant containing HFO-1234yf and the like has been described as an example.

  As a reference embodiment, the following method for manufacturing a refrigeration apparatus is also conceivable.

  In the first step, a first tube expansion tool for expanding the evaporator inlet side of the heat transfer tube provided in the evaporator, and a tube expansion target inner diameter value larger than that of the first tube expansion tool and expanding the evaporator outlet side of the second tube. An evaporator is obtained using a tube expansion tool.

  In the second step, a refrigerant circuit is obtained by connecting at least the evaporator, the compression mechanism, the condenser, and the expansion mechanism obtained in the first step.

  In a 3rd process, the refrigerant | coolant circuit obtained by the said 2nd process is filled with the working refrigerant | coolant for performing a refrigerating cycle by circulating the inside of the said refrigerant circuit.

  Instead of the first step, the following steps may be performed. That is, a heat transfer tube having the same shape and the same size with an uneven shape extending on the inner surface extending in a direction not parallel to the flow direction of the working refrigerant is prepared, and the flow of the working refrigerant due to the uneven shape of the heat transfer tube The evaporator may be obtained by processing so that the resistance is larger on the inlet side of the evaporator in the flow direction of the working refrigerant than on the outlet side.

If the present invention is used, the ozone depletion coefficient is 0, and the molecular formula is C ₃ H _m F _n (where m = 1 to 5, n = 1 to 5, and m + n = 6), And since the pressure loss in the refrigerating cycle using the single refrigerant | coolant which consists of a refrigerant | coolant which has one double bond in molecular structure, or the mixed refrigerant | coolant containing this refrigerant | coolant can be suppressed small, especially an air conditioner etc. It can be applied to the refrigeration cycle.

1 Refrigeration equipment 2 Compressor (compression mechanism)
3 Four-way selector valve 4 Evaporator, condenser, outdoor heat exchanger 5 Expansion valve (expansion mechanism)
6 Condenser, Evaporator, Indoor Heat Exchanger 350 Evaporator 351 Heat Transfer Tube f1, f2 Heat Transfer Tube f5 Radiation Fin S1 Tube Expansion Head (Second Tube Expansion Tool)
S2 Tube expansion head (first tube expansion tool)

JP-A-4-110388

Claims (25)

A refrigerant circuit (10) having at least a compression mechanism (2), a condenser (4, 6), an expansion mechanism (5), and an evaporator (6, 4);
The refrigeration cycle is performed by circulating the refrigerant circuit (10), and is represented by the molecular formula: C ₃ H _m F _n (where m = 1 to 5, n = 1 to 5, and m + n = 6). And a single refrigerant composed of a refrigerant having one double bond in the molecular structure, and a working refrigerant that is one of the mixed refrigerants containing the refrigerant,
With
The evaporator (6, 350) has a heat transfer tube (351) through which the working refrigerant flows and whose inner diameter on the outlet side is larger than the inner diameter on the inlet side in the flow direction of the working refrigerant.
Refrigeration equipment (1). The evaporator further includes a heat dissipating fin (352) having a through hole for penetrating the heat transfer tube in the plate thickness direction,
The evaporator is obtained by closely contacting the outer surface of the heat transfer tube and the through hole of the radiating fin by expanding the heat transfer tube.
The heat transfer tube is larger in the direction of expansion on the outlet side than in the direction of expansion on the inlet side in the flow direction of the working refrigerant,
The refrigeration apparatus (1) according to claim 1. The heat transfer tubes (351c, 351d, 351e...) Are provided with an uneven shape (Wc, Wd, We...) Provided so as to extend along the inner surface in a direction not parallel to the flow direction of the working refrigerant. have,
The refrigeration apparatus (1) according to claim 1 or 2. The inner diameter of the heat transfer tube is a value twice the shortest distance between the convex portion of the concavo-convex shape and the axis of the heat transfer tube.
The refrigeration apparatus (1) according to claim 3. The smaller one of the angles formed by the surface perpendicular to the axial direction of the heat transfer tube (351i) and the direction in which the uneven shape of the heat transfer tube extends along the inner surface is the working refrigerant. The outlet side is larger than the inlet side in the flow direction of
The refrigeration apparatus (1) according to claim 3 or 4. The height difference of the uneven shape in the radial direction of the heat transfer tube (351f) is larger on the inlet side than on the outlet side in the flow direction of the working refrigerant of the heat transfer tube (351f).
The refrigeration apparatus (1) according to any one of claims 3 to 5. A refrigerant circuit (10) having at least a compression mechanism (2), a condenser (4, 6), an expansion mechanism (5), and an evaporator (6, 4);
The refrigeration cycle is performed by circulating the refrigerant circuit (10), and is represented by the molecular formula: C ₃ H _m F _n (where m = 1 to 5, n = 1 to 5, and m + n = 6). And a single refrigerant composed of a refrigerant having one double bond in the molecular structure, and a working refrigerant that is one of the mixed refrigerants containing the refrigerant,
With
The evaporator (6, 350F) has a heat transfer tube (351f) in which the working refrigerant flows inside, and an uneven shape extending in a direction not parallel to the flow direction of the working refrigerant is provided on the inner surface. And
The resistance caused by the uneven shape of the heat transfer tube with respect to the flow of the working refrigerant is larger on the inlet side of the evaporator in the flow direction of the working refrigerant than on the outlet side,
Refrigeration equipment (1). The smaller one of the angles formed by the surface perpendicular to the axial direction of the heat transfer tube (351h) and the direction in which the uneven shape of the heat transfer tube extends along the inner surface is the working refrigerant. The outlet side is larger than the inlet side in the flow direction of
The refrigeration apparatus (1) according to claim 7. The height difference of the uneven shape in the radial direction of the heat transfer tubes (351f, 351g) is larger on the inlet side than on the outlet side in the flow direction of the working refrigerant of the heat transfer tube,
The refrigeration apparatus (1) according to claim 7 or 8. The outer diameters of the heat transfer tubes (351f, 351g) are substantially equal.
The refrigeration apparatus (1) according to any one of claims 7 to 9. The evaporator is obtained by using the heat transfer tubes having the same shape and the same size, and making the extent of expansion on the outlet side in the flow direction of the working refrigerant larger than the extent of expansion on the inlet side.
The refrigeration apparatus (1) according to any one of claims 7 to 9. The heat transfer tube is a seam tube.
The refrigeration apparatus (1) according to any one of claims 3 to 6 and 7 to 11. The heat transfer tube (351j) is arranged so that the working refrigerant flows only from one horizontal end to the other horizontal end of the evaporator.
The refrigeration apparatus (1) according to any one of claims 3 to 6 and 7 to 12. The heat transfer tube (351k) has an acute angle bent portion bent in the axial direction at an angle of 90 degrees or less near the inlet side of the evaporator, and 90 degrees or less near the outlet side of the evaporator. Does not have a part folded at an angle of
The refrigeration apparatus (1) according to any one of claims 3 to 6 and 7 to 13. A refrigerant circuit (10) having at least a compressor (2), a condenser (4, 6), an expansion mechanism (5), and an evaporator (6, 4);
The refrigeration cycle is performed by circulating the refrigerant circuit (10), and is represented by the molecular formula: C ₃ H _m F _n (where m = 1 to 5, n = 1 to 5, and m + n = 6). A working refrigerant that is either a single refrigerant composed of a refrigerant having one double bond in the molecular structure or a mixed refrigerant containing the refrigerant;
With
The evaporator has a larger tube diameter on the outlet side than the inlet side in the refrigerant flow direction when functioning as an evaporator,
Refrigeration equipment (1). A refrigerant circuit (10) having at least a compressor (2), a condenser (4, 6), an expansion mechanism (5), and an evaporator (6, 4);
The refrigeration cycle is performed by circulating the refrigerant circuit (10), and is represented by the molecular formula: C ₃ H _m F _n (where m = 1 to 5, n = 1 to 5, and m + n = 6). A working refrigerant that is either a single refrigerant composed of a refrigerant having one double bond in the molecular structure or a mixed refrigerant containing the refrigerant;
With
The evaporator has an uneven groove on the inside of the tube deeper on the inlet side in the refrigerant flow direction when functioning as an evaporator than on the outlet side,
Refrigeration equipment (1). At least the compressor (2), the condenser (4, 6), the expansion mechanism (5), and the outlet side rather than the inlet side when expanding the heat transfer tube provided with a uniform uneven shape on the inner surface side from the inside A refrigerant circuit (10) having the evaporator (6, 4) obtained by increasing the degree of expansion of
The refrigeration cycle is performed by circulating the refrigerant circuit (10), and is represented by the molecular formula: C ₃ H _m F _n (where m = 1 to 5, n = 1 to 5, and m + n = 6). A working refrigerant that is either a single refrigerant composed of a refrigerant having one double bond in the molecular structure or a mixed refrigerant containing the refrigerant;
The manufacturing method of the freezing apparatus (1) provided with. A refrigerant circuit (10) having at least a compressor (2), a condenser (4, 6), an expansion mechanism (5), and an evaporator (6, 4);
The refrigeration cycle is performed by circulating the refrigerant circuit (10), and is represented by the molecular formula: C ₃ H _m F _n (where m = 1 to 5, n = 1 to 5, and m + n = 6). A working refrigerant that is either a single refrigerant composed of a refrigerant having one double bond in the molecular structure or a mixed refrigerant containing the refrigerant;
With
The evaporator has a substantially quadrangular prism shape divided into approximately equal halves,
Refrigeration equipment (1). A refrigerant circuit (10) having at least a compressor (2), a condenser (4, 6), an expansion mechanism (5), and an evaporator (6, 4);
The refrigeration cycle is performed by circulating the refrigerant circuit (10), and is represented by the molecular formula: C ₃ H _m F _n (where m = 1 to 5, n = 1 to 5, and m + n = 6). A working refrigerant that is either a single refrigerant composed of a refrigerant having one double bond in the molecular structure or a mixed refrigerant containing the refrigerant;
With
The evaporator does not have a portion where the bending angle of the heat transfer tube is less than 90 degrees from the inlet to the outlet.
Refrigeration equipment (1). A refrigerant circuit (10) having at least a compressor (2), a condenser (4, 6), an expansion mechanism (5), and an evaporator (6, 4);
The refrigeration cycle is performed by circulating the refrigerant circuit (10), and is represented by the molecular formula: C ₃ H _m F _n (where m = 1 to 5, n = 1 to 5, and m + n = 6). A working refrigerant that is either a single refrigerant composed of a refrigerant having one double bond in the molecular structure or a mixed refrigerant containing the refrigerant;
With
The evaporator has a heat transfer tube which is a seam tube.
Refrigeration equipment (1). A refrigerant circuit (10) having at least a compressor (2), a condenser (4, 6), an expansion mechanism (5), and an evaporator (6, 4);
The refrigeration cycle is performed by circulating the refrigerant circuit (10), and is represented by the molecular formula: C ₃ H _m F _n (where m = 1 to 5, n = 1 to 5, and m + n = 6). A working refrigerant that is either a single refrigerant composed of a refrigerant having one double bond in the molecular structure or a mixed refrigerant containing the refrigerant;
With
The evaporator has a heat transfer tube which is a seam tube having a non-uniform uneven shape on the inner surface side.
Refrigeration equipment (1). The working refrigerant is a single refrigerant composed of 2,3,3,3-tetrafluoro-1-propene,
The refrigeration apparatus (1) according to any one of claims 1 to 21. The working refrigerant is a mixed refrigerant of 2,3,3,3-tetrafluoro-1-propene and difluoromethane, or a mixture of 2,3,3,3-tetrafluoro-1-propene and pentafluoroethane. A refrigerant,
The refrigeration apparatus (1) according to any one of claims 1 to 21. A first tube expansion tool (S2) for expanding the evaporator inlet side of the heat transfer tubes (f1, f2) provided in the evaporator, and a tube expansion target inner diameter value is larger than that of the first tube expansion tool, and the evaporator outlet side is expanded. A first step of obtaining an evaporator using a second tube expansion tool (S1),
A second step of obtaining a refrigerant circuit (10) by connecting at least the evaporator, the compression mechanism (2), the condenser (4, 6), and the expansion mechanism (5) obtained in the first step. When,
Molecular formula: C ₃ H _m F _n (where m = 1) for causing the refrigerant circuit (10) obtained in the second step to perform a refrigeration cycle by circulating in the refrigerant circuit (10). -5, n = 1 to 5, and m + n = 6), and any one of a single refrigerant composed of a refrigerant having one double bond in the molecular structure, and a mixed refrigerant containing the refrigerant A third step of filling the working refrigerant,
The manufacturing method of the freezing apparatus (1) provided with. Prepared are heat transfer tubes (f1, f2) having the same shape and the same size with uneven shapes extending on the inner surface extending in a direction not parallel to the flow direction of the working refrigerant, and the working refrigerant according to the uneven shapes of the heat transfer tubes A first step of obtaining an evaporator by processing such that the resistance to the flow of the working refrigerant is larger on the inlet side of the evaporator in the flow direction of the working refrigerant than on the outlet side;
A second step of obtaining a refrigerant circuit (10) by connecting at least the evaporator, the compression mechanism (2), the condenser (4, 6), and the expansion mechanism (5) obtained in the first step. When,
Molecular formula: C ₃ H _m F _n (where m = 1) for causing the refrigerant circuit (10) obtained in the second step to perform a refrigeration cycle by circulating in the refrigerant circuit (10). -5, n = 1 to 5, and m + n = 6), and any one of a single refrigerant composed of a refrigerant having one double bond in the molecular structure, and a mixed refrigerant containing the refrigerant A third step of filling the working refrigerant,
The manufacturing method of the freezing apparatus (1) provided with.

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