JP2008224165A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger capable of improving heat exchange efficiency by transmitting heat generated at a heat generating part of an apparatus, satisfactorily to a refrigerant regardless of the installed attitude of the apparatus. <P>SOLUTION: A condensation heat exchanger 21 applied to a Stirling refrigerating machine 10 generating heat from a cylindrical low temperature part 11, and exchanging heat by transmitting the heat generated from the lower temperature part 11 to a cooling refrigerant passing through by gravity, comprises a plurality of cooling fin members 211 of endless plate shape extended on the outer peripheral surface of the low temperature part 11 along an outer peripheral direction and erected in a form of being arranged every predetermined space along the axial direction of the low temperature part 11, and a cover member 212 covering the outer peripheral region of the low temperature part 11 including the cooling fin members 211 to form a cooling refrigerant passage for a cooling refrigerant to pass through on the outer peripheral surface of the low temperature part 11. The cooling fin members 211 are respectively erected in a form of inclining with respect an installation floor face P. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention is applied to equipment such as a Stirling refrigerator, for example, and relates to an improvement in a heat exchanger that performs heat exchange by transmitting cold heat generated in the Stirling refrigerator or high-temperature exhaust heat to a refrigerant that passes by gravity.

  Conventionally, a Stirling refrigerator is known as an example of a device that generates heat from a heat generation unit. A Stirling refrigerator is a self-cooling type refrigerator that does not have an external compressor, condenser, or the like, and is a heat generation unit that generates cold by compressing and expanding internal gas using a reciprocating compressor. It has a low temperature part and a high temperature part which is a heat generation part which generates high temperature exhaust heat. Here, a natural refrigerant such as helium gas is used as the internal gas, and since no chlorofluorocarbon gas is used, the Stirling refrigerator is friendly to the global environment. It is also well known that Stirling refrigerators are small and have high energy efficiency.

  Since such a Stirling refrigerator uses the refrigeration effect due to gas compression and expansion, there are restrictions on the structure of the compression / expansion space, and the areas of the low temperature part and the high temperature part, which are heat generation parts, are limited. Limited to a few parts. Therefore, there is a demand for a heat exchanger that efficiently exchanges heat (cold heat or high-temperature exhaust heat) generated in a heat generation unit of a Stirling refrigerator to perform heat exchange.

  As a heat exchanger for exchanging heat by transferring heat generated in the Stirling refrigerator to the refrigerant, a refrigerant flow path is provided inside an annular casing that is thermally connected to the heat generation part of the Stirling refrigerator. There is something. Such a heat exchanger is mainly applied to a Stirling refrigerator installed horizontally, i.e., a Stirling refrigerator installed in such a manner that the axial direction of the cylindrical heat generating portion is in the horizontal direction. It is erected along the direction orthogonal to the horizontal direction, that is, the vertical direction (see, for example, Patent Document 1).

  Moreover, as another example of the heat exchanger, there is one configured by winding a refrigerant pipe around the outer peripheral surface of the heat generating part of the Stirling refrigerator. Such a heat exchanger is generally a Stirling refrigerator installed vertically, that is, a Stirling refrigerator installed in such a manner that the axial direction of the cylindrical heat generating portion is perpendicular to the horizontal direction (vertical direction). This is mainly applied (for example, see Patent Document 2).

JP 2003-302117 A JP 2001-33139 A

  However, in the heat exchanger proposed in Patent Document 1 as described above, since the fin member is erected along the direction orthogonal to the horizontal direction, the Stirling refrigerator is placed vertically due to the problem of installation space. When installed in the above, the refrigerant does not flow smoothly, and as a result, the heat exchange efficiency may be reduced. Moreover, in the heat exchanger as proposed in Patent Document 2 as described above, since the refrigerant pipe is wound around the outer peripheral surface of the heat generating unit, the Stirling refrigeration is caused by the problem of installation space. Even if the machine is installed horizontally, it is thought that the refrigerant flows through the refrigerant pipe, but the refrigerant has a large pressure loss due to the small cross-sectional area of the refrigerant flow path. There is a risk that the efficiency may decrease.

  In view of the above circumstances, the present invention provides a heat exchanger that can improve heat exchange efficiency by transferring heat generated in a heat generation part of a device to a refrigerant satisfactorily regardless of the installation posture of the device. The purpose is to provide.

  In order to achieve the above object, a heat exchanger according to claim 1 of the present invention is applied to a device that generates heat from a cylindrical heat generating portion, and passes heat generated by the heat generating portion by gravity. In the heat exchanger for exchanging heat by transmitting to a refrigerant, each extends on the outer peripheral surface of the heat generating portion along the outer peripheral direction, and is arranged at predetermined intervals along the axial direction of the heat generating portion. A plurality of endless plate-like fin members erected in the form and a flow path for allowing the refrigerant to pass on the outer peripheral surface of the heat generating unit by covering the outer peripheral region of the heat generating unit including these fin members The fin member is erected in such a manner that it is inclined with respect to a horizontal plane.

  Moreover, the heat exchanger which concerns on Claim 2 of this invention is applied to the apparatus which generate | occur | produces heat from a cylindrical heat generation part, By transmitting the heat which generate | occur | produced from the said heat generation part to the refrigerant | coolant which passes by gravity, A cylindrical fin base member having an inner diameter that matches the outer diameter of the heat generating portion and arranged in such a manner that the inner peripheral surface is joined to the outer peripheral surface of the heat generating portion in a heat exchanger that performs heat exchange And a plurality of endless plate-like fin members that are provided on the outer peripheral surface of the fin base member so as to extend along the outer peripheral direction and are arranged at predetermined intervals along the axial direction of the fin base member. And a cover member that forms a flow path for allowing the refrigerant to pass on an outer peripheral surface of the fin base member by covering an outer peripheral area of the fin base member including these fin members, Against a horizontal plane Characterized in that is erected in a manner inclined.

  The heat exchanger according to claim 3 of the present invention is characterized in that, in the above-described claim 1 or 2, the fin member is formed of the same material as the heat generating portion.

  According to a fourth aspect of the present invention, in the heat exchanger according to the second or third aspect, the fin base member is formed of the same material as that of the heat generating portion.

  A heat exchanger according to claim 5 of the present invention is the heat exchanger according to any one of claims 1 to 4 described above, wherein the device is a Stirling refrigerator, and the heat generation unit is a low temperature unit that generates cold. It is characterized by being.

  Moreover, the heat exchanger which concerns on Claim 6 of this invention is the high temperature which the said apparatus is a Stirling refrigerator, and the said heat generation part generate | occur | produces high temperature waste heat in any one of Claims 1-4 mentioned above. It is a part.

  A heat exchanger according to a seventh aspect of the present invention is the heat exchanger according to any one of the first to sixth aspects described above, wherein the defining member for defining the width of the flow path is the fin member. It is characterized by being formed integrally with.

  The heat exchanger according to claim 8 of the present invention is characterized in that, in any one of the above-described claims 1 to 7, the refrigerant is carbon dioxide.

  According to the heat exchanger of the present invention, a plurality of endless plates are arranged in such a manner that each of the heat generating portions extends along the outer peripheral direction along the outer peripheral direction and is arranged at predetermined intervals along the axial direction of the heat generating portion. A fin-shaped fin member is erected, and the outer peripheral area of the heat generating portion including these fin members is covered with a cover member to form a flow path for the refrigerant to pass on the outer peripheral surface of the heat generating portion. By standing upright with respect to each horizontal plane, it is possible to allow the refrigerant to pass through the flow path well, and this allows the device to be installed vertically or horizontally. Regardless of the installation posture, it is possible to improve the heat exchange efficiency by favorably transferring the heat generated in the heat generating portion to the refrigerant.

  According to the heat exchanger of the present invention, the fin base member having an inner diameter that matches the outer diameter of the heat generating portion is disposed in such a manner that the inner peripheral surface is joined to the outer peripheral surface of the heat generating portion. A plurality of endless plate-like fin members are erected on the outer peripheral surface of the member so as to extend along the outer peripheral direction and are arranged at predetermined intervals along the axial direction of the fin base member. By covering the outer peripheral area of the fin base member including the cover member with the cover member, a flow path for the refrigerant to pass is formed on the outer peripheral surface of the fin base member, and the fin members are respectively erected in an inclined manner with respect to the horizontal plane. Therefore, it is possible to allow the refrigerant to pass through the flow path satisfactorily, and this is generated in the heat generation part regardless of whether the equipment is installed vertically or horizontally. Good heat transfer to refrigerant An effect that it is possible to improve the heat exchange efficiency by causing. In particular, the heat transfer area can be increased by the fin base member, whereby the number of fin members standing can be increased, and the heat exchange efficiency can be improved.

  Hereinafter, preferred embodiments of a heat exchanger according to the present invention will be described in detail with reference to the accompanying drawings. In the following, for convenience of explanation, a heat exchanger applied to a cooling device that cools a product accommodated in a vending machine will be described.

  FIG. 1 conceptually shows a cooling device to which a heat exchanger (condensation heat exchanger and heat radiation heat exchanger) according to an embodiment of the present invention is applied. In FIG. 1, the cooling device 1 includes a Stirling refrigerator 10, a cooling system pipe 20, and a heat radiation system pipe 30. The Stirling refrigerator 10 is installed vertically, and has a cylindrical low temperature portion 11 that generates cold heat when operated, and a cylindrical high temperature portion 12 that generates high temperature exhaust heat. Here, “installing vertically” means that the axial direction J of the low temperature part 11 and the axial direction J of the high temperature part 12 are orthogonal to the installation floor surface P as shown in FIG. More specifically, it means that the axial direction J of the low temperature part 11 and the high temperature part 12 when the installation floor surface P is a horizontal plane is the vertical direction. In the present embodiment, the installation floor surface P will be described as a horizontal plane.

  The cooling system pipe 20 transports cold heat to the cooling chamber 41 located at a predetermined distance from the Stirling refrigerator 10. Such a cooling system pipe 20 has a cooling refrigerant enclosed therein, and is configured by separately connecting a condensation heat exchanger 21 and an evaporating heat exchanger 22 by a liquid line 23 and a gas line 24. is there. Here, as the cooling refrigerant, for example, a gas (such as carbon dioxide) that is a gas at normal temperature and does not freeze with the cold heat from the low temperature portion 11 of the Stirling refrigerator 10 (an antifreeze refrigerant) is used.

  The condensation heat exchanger 21 is disposed on the outer peripheral surface of the low temperature portion 11 of the Stirling refrigerator 10 as shown in FIG. 3, and as shown in FIGS. 4 and 5, a plurality of cooling refrigerant flow paths R1 and The cooling refrigerant introduction path 213, the cooling refrigerant outlet path 214, the cooling refrigerant supply pipe 215, and the cooling refrigerant transfer pipe 216 are provided. Here, FIG. 3 to FIG. 5 are diagrams schematically showing an enlarged configuration of the condensation heat exchanger 21, respectively. FIG. 3 is a plan view of the heat exchanger as viewed from above, and FIG. FIG. 5 is a cross-sectional view of the condensation heat exchanger in FIG. 3 taken along the line AA, and FIG. 5 is a cross-sectional view of the condensation heat exchanger in FIG. The said condensation heat exchanger 21 is demonstrated using these figures suitably.

  The plurality of cooling refrigerant flow paths R1 extend on the outer peripheral surface of the low temperature part 11 along the outer peripheral direction of the low temperature part 11 and are juxtaposed along the axial direction J of the low temperature part 11. Is for passing the cooling refrigerant. Such a cooling refrigerant flow path R1 is configured by arranging a plurality of cooling fin members 211 and a cooling cover member 212 as follows. That is, a plurality of endless plate-like shapes are provided in such a manner that each extends along the outer peripheral surface of the low temperature portion 11 along the outer peripheral direction and is arranged at predetermined intervals along the axial direction J of the low temperature portion 11 (see FIG. 2). The cooling fin member 211 is erected, and the cooling cover member 212 is arranged in such a manner as to cover the outer peripheral area of the low temperature part 11 including the cooling fin member 211.

  Here, the number and interval of the cooling fin members 211 are determined in consideration of the heat transfer to the cooling refrigerant and the necessary amount of exchange heat. In addition, the inner end edge portion and the outer end edge portion of the cooling fin member 211 are spaced apart from each other with respect to the adjacent cooling fin member 211, that is, a spacer portion that regulates the width of the cooling refrigerant flow path R1 to a predetermined size. (Defining member) 2111 is integrally formed. Accordingly, the interval between the cooling fin members 211 is defined by the spacer portion 2111. And the cooling fin member 211 is standingly arranged in the aspect which inclines within the range which is not orthogonally crossed with respect to the axial direction J of the low temperature part 11, ie, it inclines with respect to the installation floor P (refer FIG. 2). It is erected in such a manner.

  Further, the shape of the cooling cover member 212 is not particularly limited as long as it covers the outer peripheral area of the low-temperature part 11, but in the present embodiment, a cylindrical cooling cover main body 2121 and two An annular cooling auxiliary cover 2122 is formed by welding. The cooling cover main body 2121 has a length in the axial direction J that is substantially the same as that of the low temperature portion 11, and an inner peripheral portion is disposed in contact with each outer peripheral portion of the cooling fin member 211. Thus, the cooling refrigerant flow path R1 is configured between the cooling fin members 211. The cooling auxiliary cover 2122 has an inner peripheral portion welded to each end (upper end and lower end) of the outer peripheral surface of the low temperature portion 11, and an outer peripheral portion is each end (upper end and lower end) of the cooling cover main body 2121. It is welded and provided in the inner peripheral part. Thereby, the cooling refrigerant flow path R1 is formed between each cooling auxiliary cover 2122 and the cooling fin member 211 erected on the uppermost side in the drawing or the cooling fin member 211 erected on the lowermost side. Composed.

  The cooling fin member 211 is made of a heat conductive material, and is made of the same material as the low temperature portion 11 such as copper, or a material that is not easily corroded with copper as the material of the low temperature portion 11. is there. On the other hand, the cooling cover member 212 (the cooling cover main body 2121 and the cooling auxiliary cover 2122) is formed of a material such as stainless steel from the viewpoint of strength and the like. The cooling refrigerant passing through the cooling refrigerant flow path R1 is cooled and condensed by the cold generated from the low temperature portion 11 when passing through the cooling refrigerant flow path R1.

  As shown in FIG. 4, the cooling refrigerant introduction path 213 extends along the axial direction J of the low temperature part 11 on a part of the condensation heat exchanger 21, for example, on the left side in FIG. This is for guiding the refrigerant to each cooling refrigerant flow path R1. Such a cooling refrigerant introduction path 213 is configured by forming introduction holes 211 a in the cooling fin members 211 along the axial direction J of the low temperature portion 11.

  As shown in FIG. 4, the cooling refrigerant lead-out path 214 extends along the axial direction J of the low temperature part 11 on a part of the condensation heat exchanger 21, for example, on the right side in FIG. The cooling refrigerant that has become a condensate after passing through is guided to the outside. Such a cooling refrigerant lead-out path 214 is configured by forming lead-out holes 211b in the cooling fin members 211 along the axial direction J of the low temperature portion 11.

  The cooling refrigerant supply pipe 215 passes through a through hole (not shown) formed in the upper cooling auxiliary cover 2122 in the drawing, and is arranged in such a manner that its tip is inserted into the cooling refrigerant introduction path 213. The cooling refrigerant supply pipe 215 is a cylindrical pipe for supplying a cooling refrigerant, and is formed of the same material (for example, copper) as the low temperature portion 11 and the cooling fin member 211. The tip of the cooling refrigerant supply pipe 215 has a semi-cylindrical shape with the low temperature portion 11 side cut away. That is, a notch 2151 is formed at the tip of the cooling refrigerant supply pipe 215 over the entire region. Further, although not clearly shown in the figure, a gas line 24 is connected to the base end portion of the cooling refrigerant supply pipe 215.

  The cooling refrigerant transfer pipe 216 passes through a through hole (not shown) formed in the cooling auxiliary cover 2122 on the lower side in the figure on the lower side of the low temperature portion 11, and its tip portion is inserted into the cooling refrigerant outlet path 214. It is arranged in the manner described above. The cooling refrigerant transfer pipe 216 is a cylindrical pipe for transferring the cooling refrigerant condensed through the cooling refrigerant flow path R1 (condensed liquid) toward the evaporating heat exchanger 22. The part 11 and the cooling fin member 211 are formed of the same material (for example, copper). The tip of cooling refrigerant transfer pipe 216 has a semi-cylindrical shape with the low temperature portion 11 side cut away. That is, a notch 2161 is formed at the tip of the cooling refrigerant transfer pipe 216 over the entire area. Further, although not clearly shown in the figure, a liquid line 23 is connected to the base end portion of the cooling refrigerant transfer pipe 216.

  The evaporative heat exchanger 22 is disposed in the cooling chamber 41, and more specifically, is accommodated in the evaporative heat exchanger accommodation box 42. The evaporation heat exchanger 22 has a meandering evaporation path 221. The evaporation path 221 is for passage of the cooling refrigerant. In such an evaporative heat exchanger 22, the details will be described later, but the cooling refrigerant passing through the evaporating path 221 is evaporated by the heat obtained from the outside into vapor. In other words, the air around the evaporative heat exchanger 22 is cooled because heat is taken away as the cooling refrigerant evaporates. Further, the evaporative heat exchanger 22 is disposed below the reference height of the low temperature part 11 of the Stirling refrigerator 10. A cooling fan 25 is provided at a predetermined location around the evaporative heat exchanger 22. The cooling fan 25 is for sending the air cooled by the evaporative heat exchanger 22.

  The liquid line 23 is a pipe line connecting the condensation heat exchanger 21 and the evaporative heat exchanger 22, and more specifically, the base end portion of the cooling refrigerant transfer pipe 216 constituting the condensation heat exchanger 21, and the evaporation heat. This is a pipe line connecting the inlet of the evaporation path 221 of the exchanger 22. The liquid line 23 is for moving the cooling refrigerant condensed in the condensation heat exchanger 21 from the condensation heat exchanger 21 to the evaporating heat exchanger 22.

  The gas line 24 is a pipe line that connects the condensation heat exchanger 21 and the evaporating heat exchanger 22 separately from the liquid line 23. More specifically, the gas line 24 is a cooling refrigerant supply pipe that constitutes the condensation heat exchanger 21. This is a pipe line that connects the base end portion of 215 and the outlet of the evaporation path 221 of the evaporation heat exchanger 22. The gas line 24 is for moving the cooling refrigerant evaporated in the evaporation heat exchanger 22 from the evaporation heat exchanger 22 to the condensation heat exchanger 21. Here, the gas line 24 is disposed above the liquid line 23. This is because the density of the cooling refrigerant passing through the gas line 24 is smaller than the density of the refrigerant passing through the liquid line 23.

  The heat dissipation system pipe 30 is for transporting high-temperature exhaust heat generated in the high-temperature part 12 of the Stirling refrigerator 10 to the outside. Such a heat radiating system pipe 30 has a heat radiating refrigerant sealed therein, and is configured by separately connecting a heat radiating heat exchanger 31 and an air heat exchanger 32 via a first line 33 and a second line 34. It is. Here, for example, carbon dioxide, water, and ammonia water are used as the heat radiation refrigerant. In the present embodiment, the heat radiation refrigerant will be described as carbon dioxide.

  The radiant heat exchanger 31 is disposed on the outer peripheral surface of the high temperature portion 12 of the Stirling refrigerator 10 as shown in FIG. 3, and as shown in FIGS. 6 and 7, a plurality of radiant refrigerant flow paths R 2 and The heat radiation refrigerant introduction path 313, the heat radiation refrigerant lead-out path 314, the heat radiation refrigerant supply pipe 315, and the heat radiation refrigerant transfer pipe 316 are provided. Here, FIG. 6 and FIG. 7 each schematically show an enlarged configuration of the condensing heat exchanger, and FIG. 6 is a cross-sectional view of the heat dissipation heat exchanger in FIG. FIG. 4 is a cross-sectional view of the radiant heat exchanger in FIG. 3 taken along the line CC. The said heat radiation heat exchanger 31 is demonstrated using these figures suitably.

  The plurality of heat-dissipating refrigerant channels R2 extend along the outer peripheral direction of the high-temperature portion 12 on the outer peripheral surface of the high-temperature portion 12 and are juxtaposed along the axial direction J of the high-temperature portion 12 (see FIG. 2). Each of them is for passing a heat-dissipating refrigerant. Such a heat radiating refrigerant channel R2 is configured by arranging a plurality of heat radiating fin members 311 and a heat radiating cover member 312 as follows. That is, a plurality of endless plate-like heat dissipating fin members 311 are provided on the outer peripheral surface of the high temperature portion 12 along the outer peripheral direction and arranged at predetermined intervals along the axial direction J of the high temperature portion 12. The radiating cover member 312 is arranged in a manner standing and covering the outer peripheral area of the high temperature portion 12 including these radiating fin members 311.

  Here, the number and interval of the heat dissipating fin members 311 are determined in consideration of heat transfer to the heat dissipating refrigerant and a necessary amount of exchange heat. In addition, the inner end edge portion and the outer end edge portion of the radiating fin member 311 have a spacer portion that regulates the distance between the adjacent radiating fin members 311, that is, the width of the radiating refrigerant flow path R <b> 2 to a predetermined size. (Defining member) 3111 is integrally formed. Therefore, the space between the heat radiating fin members 311 is defined by the spacer portion 3111. The radiating fin members 311 are erected in such a manner that each radiating fin member 311 is inclined within a range that is not orthogonal to the axial direction J of the high-temperature portion 12, that is, in an aspect that is inclined with respect to the installation floor P. It is set up.

  Further, the shape and the like of the heat dissipation cover member 312 are not particularly limited as long as they cover the outer peripheral area of the high temperature portion 12, but in the present embodiment, a cylindrical heat dissipation cover body 3121 and two An annular heat radiation auxiliary cover 3122 is formed by welding. The heat radiating cover main body 3121 has a length in the axial direction J that is substantially the same as that of the high temperature portion 12, and the inner peripheral portion is disposed in contact with each outer peripheral portion of the radiating fin member 311. Thereby, between the radiation fin members 311, the radiation refrigerant flow path R <b> 2 is configured. The heat radiation auxiliary cover 3122 has an inner peripheral portion welded to each end portion (upper end portion and lower end portion) of the outer peripheral surface of the high temperature portion 12, and an outer peripheral portion is each end portion (upper end portion and lower end portion) of the heat dissipation cover body 3121. It is welded and provided in the inner peripheral part. As a result, the radiating refrigerant flow path R2 is provided between each radiating auxiliary cover 3122 and the radiating fin member 311 erected on the uppermost side in the drawing or the radiating fin member 311 erected on the lowermost side. Composed.

  The heat radiating fin member 311 is formed of a heat conductive material, and is formed of a material which is not easily corroded with copper which is the same material as the high temperature portion 12 such as copper, or copper which is a material of the high temperature portion 12. is there. On the other hand, the heat radiating cover member 312 (the heat radiating cover main body 3121 and the heat radiating auxiliary cover 3122) is made of a material such as stainless steel from the viewpoint of strength and the like. And the refrigerant | coolant for thermal radiation which passes such a thermal radiation refrigerant flow path R2 will receive the high temperature waste heat which generate | occur | produced from the high temperature part 12, when passing this thermal radiation refrigerant flow path R2.

  As shown in FIG. 6, the radiant refrigerant introduction path 313 extends along the axial direction J of the high temperature portion 12 on a part of the radiant heat exchanger 31, for example, on the right side in FIG. This is for guiding the refrigerant to each heat radiation refrigerant flow path R2. Such a heat radiation refrigerant introduction path 313 is configured by forming an introduction hole 311 a along the axial direction J of the high temperature portion 12 in each of the heat radiation fin members 311.

  As shown in FIG. 6, the heat dissipation refrigerant lead-out path 314 extends along the axial direction J of the high temperature portion 12 on a part of the heat dissipation heat exchanger 31, for example, on the left side in FIG. The heat-dissipating refrigerant that has received the high-temperature exhaust heat after passing through is guided to the outside. Such a heat radiation refrigerant lead-out path 314 is configured by forming a lead-out hole 311 b along the axial direction J of the high-temperature portion 12 in each heat radiation fin member 311.

  The heat-dissipating refrigerant supply pipe 315 is arranged in such a manner that it penetrates a through-hole (not shown) formed in the heat-dissipating auxiliary cover 3122 on the upper side in the drawing, and its tip is inserted into the heat-dissipating refrigerant introduction path 313. The heat radiation refrigerant supply pipe 315 is a cylindrical pipe for supplying a heat radiation refrigerant, and is formed of the same material (for example, copper) as the high temperature portion 12 and the heat radiation fin member 311. Moreover, the front-end | tip part of the thermal radiation refrigerant | coolant supply pipe 315 has cut off the high temperature part 12 side, and has comprised the shape of the semi-cylinder. That is, a notch 3151 is formed at the tip of the heat radiating refrigerant supply pipe 315 over the entire region. Although not clearly shown in FIG. 6, the second line 34 is connected to the base end portion of the heat radiation refrigerant supply pipe 315.

  The heat dissipation refrigerant transfer pipe 316 passes through a through hole (not shown) formed in the heat dissipation auxiliary cover 3122 on the upper side in the drawing on the upper side of the high temperature portion 12, and its distal end portion is inserted into the heat dissipation refrigerant lead-out path 314. Arranged in a manner. The heat-dissipating refrigerant transfer pipe 316 is a cylindrical pipe for transferring the heat-dissipating refrigerant that has passed through the heat-dissipating refrigerant channel R2 and received high-temperature exhaust heat toward the air heat exchanger 32. The fin member 311 is formed of the same material (for example, copper). Moreover, the front-end | tip part of the thermal radiation transfer pipe 316 has cut off the high temperature part 12 side, and has comprised the semicylindrical form. That is, a notch 3161 is formed at the tip of the heat-dissipating refrigerant transfer pipe 316 over the entire area. Although not clearly shown in FIG. 6, the first line 33 is connected to the base end portion of the heat-dissipating refrigerant transfer pipe 316.

  The air heat exchanger 32 is disposed at a position separated from the Stirling refrigerator 10 by a predetermined distance. This air heat exchanger 32 has a meandering heat radiation path 321. The heat radiation path 321 is for the heat radiation refrigerant to pass through. In such an air heat exchanger 32, the high-temperature exhaust heat received by the heat-dissipating heat exchanger 31 when the heat-dissipating refrigerant passes through the heat-radiating path 321 is dissipated to the ambient air. Thereby, ambient air is heated by high temperature exhaust heat. In addition, the air heat exchanger 32 is disposed above the reference height of the high temperature part 12 of the Stirling refrigerator 10. A discharge fan 35 is provided at a predetermined location around the air heat exchanger 32. The discharge fan 35 is for discharging the air heated by the air heat exchanger 32 to the outside.

  The first line 33 is a pipe line connecting the heat radiation heat exchanger 31 and the air heat exchanger 32, and more specifically, the base end portion of the heat radiation refrigerant transfer pipe 316 constituting the heat radiation heat exchanger 31, and the air It is a pipe line connecting the inlet of the heat radiation path 321 of the heat exchanger 32. The first line 33 is for moving the heat-dissipating refrigerant that has received the high-temperature exhaust heat in the heat-dissipating heat exchanger 31 to the air heat exchanger 32.

  The second line 34 is a pipe line connecting the heat radiation heat exchanger 31 and the air heat exchanger 32 separately from the first line 33, and more specifically, the heat radiation refrigerant constituting the heat radiation heat exchanger 31. This is a pipe line that connects the base end of the supply pipe 315 and the outlet of the heat radiation path 321 of the air heat exchanger 32. The second line 34 is for moving the heat radiation refrigerant radiated by the air heat exchanger 32 to the heat radiation heat exchanger 31. Here, the second line 34 is located below the first line 33. This is because the density of the heat dissipating refrigerant passing through the second line 34 is greater than the density of the heat dissipating refrigerant passing through the first line 33.

  In the cooling system pipe 20, cold heat from the low temperature part 11 of the Stirling refrigerator 10 is transmitted to the cooling chamber 41 as follows. Due to the cold generated from the low temperature section 11, the cooling refrigerant passing through each cooling refrigerant flow path R1 of the condensation heat exchanger 21 is rapidly cooled to become a condensate, and moves downward due to its gravity. Thereafter, the cooling refrigerant that has become the condensate reaches the cooling refrigerant lead-out path 214, enters the cooling refrigerant transfer pipe 216 through the cooling refrigerant lead-out path 214, moves, and evaporates the heat exchanger 22 through the liquid line 23. Move up. In the evaporative heat exchanger 22, the cooling refrigerant evaporates to vapor by the heat of the air around the evaporative heat exchanger 22, that is, the air inside the cooling chamber 41 while passing through the evaporating path 221. That is, the air inside the cooling chamber 41 is cooled due to heat being taken away. The cooled air is sent out when the cooling fan 25 is driven, and the inside of the cooling chamber 41 is cooled. That is, cold heat generated in the low temperature part 11 of the Stirling refrigerator 10 is transmitted to the cooling chamber 41. By the way, the cooling refrigerant evaporated in the evaporative heat exchanger 22 into vapor reaches the cooling refrigerant supply pipe 215 through the gas line 24, and then moves to each cooling refrigerant flow path R1 through the cooling refrigerant introduction path 213. In the cooling refrigerant flow path R1, it becomes a condensate again and the above-described cycle is repeated.

  The cooling system pipe 20 is configured such that a cooling refrigerant circulates between the condensation heat exchanger 21 and the evaporating heat exchanger 22 through a liquid line 23 and a gas line 24 that are separately provided. This is called a siphon heat pipe.

  In the heat radiating system pipe 30, the high temperature exhaust heat from the high temperature part 12 of the Stirling refrigerator 10 is released to the outside as follows. The heat-dissipating refrigerant passing through each heat-dissipating refrigerant flow path R2 of the heat-dissipating heat exchanger 31 rises by receiving the high-temperature exhaust heat generated in the high-temperature portion 12, and then reaches the heat-dissipating refrigerant deriving path 314, where the heat-dissipating refrigerant is derived. The heat enters the inside of the heat-dissipating refrigerant transfer pipe 316 through the path 314 and moves to the air heat exchanger 32 through the first line 33. In the air heat exchanger 32, the heat radiation refrigerant radiates high-temperature exhaust heat to the ambient air of the air heat exchanger 32 while passing through the heat radiation path 321. That is, the ambient air around the air heat exchanger 32 is heated. The heated air is sent out by driving the discharge fan 35. By the way, the heat-dissipating refrigerant radiated by the air heat exchanger 32 reaches the heat-dissipating refrigerant supply pipe 315 through the second line 34, and then moves to each cooling refrigerant flow path R1 through the heat-dissipating refrigerant introduction path 313. The high-temperature exhaust heat is received again in the path R1, and the above-described cycle is repeated. Here, when the outside air temperature in summer or the like exceeds 30 ° C., carbon dioxide, which is a heat-dissipating refrigerant, circulates in a supercritical state.

  In the heat radiation system pipe 30, a heat radiation refrigerant circulates between the heat radiation heat exchanger 31 and the air heat exchanger 32 through a first line 33 and a second line 34 provided separately, and a loop. This is called a type thermosiphon heat pipe.

  In the condensation heat exchanger 21 that constitutes the cooling device 1 as described above, the cooling fin member 211 is erected in an aspect that is inclined within a range that is not orthogonal to the axial direction J of the low temperature portion 11. When the Stirling refrigerator 10 is installed from the vertical position to the horizontal position, that is, when the Stirling refrigerator 10 is installed on the installation floor surface P in such a manner that the axial direction J of the low temperature part 11 is horizontal, the cooling fin member 211 is installed on the installation floor surface P (horizontal plane) ) In an inclined manner. Therefore, it becomes possible to allow the refrigerant to pass through the cooling refrigerant flow path R1 satisfactorily, so that regardless of whether the Stirling refrigerator 10 is installed vertically or horizontally, regardless of the installation attitude of the Stirling refrigerator 10, The heat exchange efficiency can be improved by transmitting the cold heat generated in the low temperature part 11 to the refrigerant well. In particular, a plurality of cooling fin members 211 are arranged on the outer peripheral surface of the low temperature part 11 of the Stirling refrigerator 10 along the outer peripheral direction of the low temperature part 11 and at substantially equal intervals in the axial direction J of the low temperature part 11. Since the cooling cover member 212 is arranged in a manner to stand and cover the outer peripheral area of the low temperature part 11 including these cooling fin members 211, the cooling refrigerant flow path R1 is configured on the outer peripheral surface of the low temperature part 11. The cooling heat generated in the low temperature part 11 can be directly transmitted to the cooling refrigerant passing through the cooling refrigerant flow path R1. Thereby, generation | occurrence | production of the heat loss accompanying heat transfer can be reduced, and the transmission efficiency of the cold heat to the refrigerant | coolant for cooling can be improved.

  Further, according to the condensation heat exchanger 21, the cooling fin member 211 is formed of the same material as that of the low-temperature part 11 of the Stirling refrigerator 10, and therefore there is a possibility that a change with time due to the difference in material may occur between the two. In addition, there is no possibility that one of the materials will deteriorate due to electric corrosion or the like.

  Furthermore, according to the condensation heat exchanger 21, since the spacer portion 2111 defines the width of the cooling refrigerant flow path R1, the pressure of the cooling refrigerant passing through the cooling refrigerant flow path R1, that is, the inside of the cooling system pipe 20 There is no possibility that the width of the cooling refrigerant flow path R1 will change over time due to the pressure of the air. Thereby, the width | variety of each cooling refrigerant flow path R1 can be ensured substantially uniformly, As a result, it becomes possible to ensure the stable heat exchange efficiency.

  On the other hand, in the heat radiating heat exchanger 31, the radiating fin member 311 is erected in such a manner that the radiating fin member 311 is inclined within a range not orthogonal to the axial direction J of the high temperature portion 12, so When installed on the installation floor, that is, when installed on the installation floor P in such a manner that the axial direction J of the high temperature portion 12 is horizontal, the radiating fin member 311 stands in an aspect inclined with respect to the installation floor P (horizontal plane). Has been established. Therefore, it becomes possible to allow the refrigerant to pass through the heat-dissipating refrigerant flow path R2 satisfactorily, and regardless of whether the Stirling refrigerator 10 is installed vertically or horizontally, regardless of the installation attitude of the Stirling refrigerator 10, The heat exchange efficiency can be improved by transferring the cold generated in the high temperature part 12 to the refrigerant.

  Further, according to the heat dissipation heat exchanger 31, since the heat dissipation fin member 311 is formed of the same material as the high temperature portion 12 of the Stirling refrigerator 10, there is a possibility that a change with time due to the difference in material may occur between them. In addition, there is no possibility that one of the materials will deteriorate due to electric corrosion or the like.

  Furthermore, according to the heat dissipation heat exchanger 31, since the spacer 3111 defines the width of the heat dissipation refrigerant flow path R2, the pressure of the heat dissipation refrigerant passing through the heat dissipation refrigerant flow path R2, that is, the inside of the heat dissipation system pipe 30 is increased. There is no possibility that the width of the heat-dissipating refrigerant flow path R2 will change over time due to the sealing pressure. Thereby, the width | variety of each thermal radiation refrigerant flow path R2 can be ensured substantially uniformly, As a result, it becomes possible to ensure the stable heat exchange efficiency.

  The preferred embodiment of the present invention has been described above, but the present invention is not limited to this, and various modifications can be made. For example, as shown in FIG. 8, the condensing heat exchanger 21 has an inner diameter that matches the outer diameter of the low temperature portion 11 and is arranged in such a manner that the inner peripheral surface is joined to the outer peripheral surface of the low temperature portion 11. The cooling refrigerant flow path R1 may be configured by having a cylindrical fin base member 217 and by erecting the cooling fin member 211 on the outer peripheral surface of the fin base member 217. Here, it is preferable that the fin base member 217 is formed of the same material as that of the low temperature portion 11, similarly to the cooling fin member 211. According to such a configuration, the heat transfer area can be increased by the fin base member 217, whereby the number of cooling fin members 211 can be increased, and the heat exchange efficiency can be improved. .

  Further, as shown in FIG. 9, the heat dissipation heat exchanger 31 has an inner diameter that matches the outer diameter of the high temperature portion 12, and is disposed in such a manner that the inner peripheral surface is joined to the outer peripheral surface of the high temperature portion 12. The heat radiation refrigerant flow path R <b> 2 may be configured by having a cylindrical fin base member 317, and by placing a heat radiation fin member 311 upright on the outer peripheral surface of the fin base member 317. Here, the fin base member 317 is preferably formed of the same material as that of the high-temperature portion 12, similarly to the radiating fin member 311. According to such a configuration, the heat transfer area can be expanded by the fin base member 317, whereby the number of radiating fin members 311 can be increased, and the heat exchange efficiency can be improved. .

  In the above-described embodiment, the installation location of the refrigerant supply pipe and the refrigerant transfer pipe when the Stirling refrigerator 10 is installed vertically or horizontally is not particularly mentioned, but the installation locations of these pipes are: You may change suitably according to the installation attitude | position of the Stirling refrigerator 10. FIG.

  As described above, the heat exchanger according to the present invention is applied to equipment such as a Stirling refrigerator, for example, and is useful for transmitting cold heat generated in the Stirling refrigerator or high-temperature exhaust heat to the refrigerant.

It is the conceptual diagram which showed notionally the cooling device to which the heat exchanger (condensation heat exchanger and heat radiation heat exchanger) which is embodiment of this invention is applied. It is the side view which expanded and showed the Stirling refrigerator shown in FIG. It is the top view which looked at the heat exchanger from upper direction. It is the sectional view on the AA line of the condensation heat exchanger in FIG. It is CC sectional view taken on the line of the condensation heat exchanger in FIG. It is the BB sectional view taken on the line of the heat dissipation heat exchanger in FIG. It is CC sectional view taken on the line of the thermal radiation heat exchanger in FIG. It is sectional drawing which showed the modification of the condensation heat exchanger. It is sectional drawing which showed the modification of the thermal radiation heat exchanger.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Stirling refrigerator 11 Low temperature part 12 High temperature part 20 Cooling system piping 21 Condensing heat exchanger 211 Cooling fin member 2111 Spacer part 212 Cooling cover member 2121 Cooling cover body 2122 Cooling auxiliary cover 213 Cooling refrigerant introduction path 214 Cooling refrigerant lead-out path 215 Cooling Refrigerant supply pipe 2152 Notch 216 Cooling refrigerant transfer pipe 2162 Notch 22 Evaporation heat exchanger 23 Liquid line 24 Gas line 30 Heat dissipating system pipe 31 Heat dissipating heat exchanger 311 Heat dissipating fin member 3111 Spacer part 312 Heat dissipating cover member 3121 Heat dissipating cover main body 3122 Heat dissipation auxiliary cover 313 Heat dissipation refrigerant introduction path 314 Heat dissipation refrigerant lead-out path 315 Heat dissipation refrigerant supply pipe 316 Heat dissipation refrigerant transfer pipe R1 Cooling refrigerant flow path R2 Heat dissipation refrigerant flow path

Claims (8)

In a heat exchanger that is applied to a device that generates heat from a cylindrical heat generation unit and performs heat exchange by transferring heat generated by the heat generation unit to a refrigerant that passes by gravity,
A plurality of endless plate-like fin members each extending on the outer peripheral surface of the heat generating portion along the outer peripheral direction and standing in a manner arranged at predetermined intervals along the axial direction of the heat generating portion;
A cover member that forms a flow path for allowing the refrigerant to pass on an outer peripheral surface of the heat generating unit by covering an outer peripheral region of the heat generating unit including these fin members;
Each of the fin members is erected in such a manner as to be inclined with respect to a horizontal plane. In a heat exchanger that is applied to a device that generates heat from a cylindrical heat generation unit and performs heat exchange by transferring heat generated by the heat generation unit to a refrigerant that passes by gravity,
A cylindrical fin base member having an inner diameter that matches the outer diameter of the heat generating portion, and disposed in such a manner that the inner peripheral surface is joined to the outer peripheral surface of the heat generating portion;
A plurality of endless plate-like fin members each extending on the outer peripheral surface of the fin base member along the outer peripheral direction and erected in a state of being arranged at predetermined intervals along the axial direction of the fin base member;
A cover member that forms a flow path for the refrigerant to pass on the outer peripheral surface of the fin base member by covering an outer peripheral area of the fin base member including these fin members;
Each of the fin members is erected in such a manner as to be inclined with respect to a horizontal plane.   The heat exchanger according to claim 1 or 2, wherein the fin member is formed of the same material as the heat generating unit.   4. The heat exchanger according to claim 2, wherein the fin base member is formed of the same material as that of the heat generation unit.   The heat exchanger according to any one of claims 1 to 4, wherein the device is a Stirling refrigerator, and the heat generation unit is a low-temperature unit that generates cold.   The heat exchanger according to any one of claims 1 to 4, wherein the device is a Stirling refrigerator, and the heat generation unit is a high-temperature unit that generates high-temperature exhaust heat.   The heat exchanger according to any one of claims 1 to 6, wherein a defining member for defining the width of the flow path is formed integrally with each of the fin members. .   The heat exchanger according to any one of claims 1 to 7, wherein the refrigerant is carbon dioxide.

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