JP6149203B1 - Heat exchanger and hydrogen gas cooling device - Google Patents

Abstract

It is possible to reduce the size without causing a decrease in heat exchange efficiency or an increase in manufacturing cost. SOLUTION: Heat transfer coils 50o, 50i, a container body 40 in which each of the heat transfer coils 50o, 50i is accommodated, a fluid branch part for branching a hydrogen gas flow path into a plurality of flow paths, and each flow path. And a heat transfer coil 50o, 50i is provided for each flow path, and the heat transfer coils 50o, 50i are arranged in such a manner that the winding axis direction of the tube winding parts 51o, 51i is a container. Along the tube length direction of the body 40, the tubes 40 are accommodated in the container body 40 along the tube length direction, and a part of the tube winding portion 51o in the heat transfer coil 50oa is a tube in the heat transfer coil 50ob. A non-overlapping portion that does not overlap with the body winding portion 51o in the tube length direction or a part of the tube winding portion 51i in the heat transfer coil 50id is a tube length with respect to the tube winding portion 51i in the heat transfer coil 50ic. Non-overlapping parts that do not overlap in direction occur Are sea urchin placed. [Selection] Figure 9

Description

  The present invention relates to a heat exchanger configured to be able to exchange heat between a first heat exchange target fluid and a second heat exchange target fluid, and hydrogen as the first heat exchange target fluid including such a heat exchanger. The present invention relates to a hydrogen gas cooling device configured to be capable of cooling hydrogen gas by mutually exchanging heat between a gas and a heat transfer fluid as a second heat exchange target fluid.

  As this type of heat exchanger, the invention of a heat exchanger for cooling hydrogen gas is disclosed in the following patent document. This heat exchanger was disposed along the axial direction of the container, penetrating the center of the lid, a cylindrical container with a bottom filled with brine, a disk-shaped lid that closes the upper opening of the container Rotating shaft, a plurality of axial flow type propellers attached to the rotating shaft, spiral first and second hydrogen gas cooling pipes arranged in two upper and lower stages, and both hydrogen gas cooling pipes And a plurality of brine cooling refrigerant pipes arranged along the axial direction of the container around (outside) the cooling of the brine by heat exchange between the refrigerant in each refrigerant pipe and the brine in the container, The hydrogen gas can be cooled by heat exchange between the hydrogen gas in both hydrogen gas cooling pipes and the brine around the hydrogen gas cooling pipes (inside the container).

  In this case, when cooling the hydrogen gas using this heat exchanger, first, the rotating shaft is rotated by an air motor to rotate the propeller, thereby causing the brine to flow in the container. At this time, the brine in the container is raised inside the container through the inside of the first hydrogen gas cooling pipe and the second hydrogen gas cooling pipe, and passes through the outside of the refrigerant pipe from above the first hydrogen gas cooling pipe. After the inside of the container is lowered, the brine is circulated in the container by flowing again into the second hydrogen gas cooling pipe from below the second hydrogen gas cooling pipe. Next, the brine in the container is cooled by supplying the refrigerant into the refrigerant pipe by causing the brine pipe for cooling the brine to function as an evaporator of the refrigeration cycle while continuing the circulation of the brine in the container.

  On the other hand, when filling a fuel tank of an automobile with hydrogen gas, hydrogen gas from a hydrogen gas supply source is supplied to the first hydrogen gas cooling pipe and the second hydrogen gas cooling pipe. At this time, the supplied hydrogen gas is cooled by heat exchange with the brine around both hydrogen gas cooling pipes while rising in the first hydrogen gas cooling pipe and the second hydrogen gas cooling pipe. As a result, the hydrogen gas whose temperature has dropped is supplied to the fuel tank via the filling pipe and filled.

Japanese Patent No. 5809268 (page 4-6, Fig. 1-3)

  However, the heat exchanger disclosed in the above patent document has the following problems. That is, in the above heat exchanger, the hydrogen gas that is allowed to pass through the first hydrogen gas cooling pipe and the second hydrogen gas cooling pipe, and the periphery of both hydrogen gas cooling pipes by the rotation of the propeller (the tubular body is spirally wound). A configuration is adopted in which the hydrogen gas is cooled by heat exchange with the brine that raises the inner circumferential side of the tubular body winding portion that is raised. For this reason, in the heat exchanger disclosed in the above-mentioned patent document, a propeller for flowing brine in the container and a rotating shaft for rotating the propeller are essential. In addition to the difficulty of downsizing the heat exchanger, there is a problem in that the manufacturing cost of the heat exchanger is rising due to the component cost and assembly cost of the propeller and the rotating shaft.

  In the above heat exchanger, compressed air needs to be continuously supplied to the air motor for rotating the propeller (rotating shaft) during the process of cooling the hydrogen gas. There is a problem that the running cost is increased by the amount of electric power consumed by the air generator (air compressor). In this case, the same problem occurs when an electric motor is used instead of the air motor. Furthermore, in the above heat exchanger, it is necessary to arrange a sealing member so that the brine does not flow out from the gap between the rotating shaft and the lid, and the manufacturing cost of the heat exchanger is reduced due to the component cost. In addition to the further increase in the price, it is necessary to periodically replace the sealing member before the brine leaks due to deterioration of the sealing member that is always in contact with the brine, resulting in a problem that the running cost is further increased.

  Furthermore, in the above heat exchanger, a configuration is adopted in which a process for cooling the brine in the container in the container is executed in parallel with the process for cooling the hydrogen gas by the brine stored in the container. For this reason, in the above heat exchanger, when a large amount of hydrogen gas is cooled, the temperature of the brine stored in the container is continuously increased. It may be difficult to maintain everything at a sufficiently low temperature that can be suitably cooled.

  In view of these problems, the applicant has prototyped a hydrogen gas cooling apparatus in which the configuration of the hydrogen gas cooling facility using the heat exchanger disclosed in the above-mentioned patent document is improved. In the hydrogen gas cooling device prototyped by the applicant, the propeller, the rotating shaft, and the refrigerant pipe for cooling the brine are excluded from the heat exchanger, and the brine cooled by the cooling device configured separately from the heat exchanger is heated. The structure which introduce | transduces in a container from the bottom part of the container in an exchanger, and cools the hydrogen gas in both hydrogen gas cooling pipes by heat exchange with this brine is employ | adopted. In this case, in the hydrogen gas cooling device prototyped by the applicant, the brine that has risen in temperature due to heat exchange with the hydrogen gas is pushed up into the brine that is sequentially introduced into the heat exchanger (container) and rises in the vessel. And the structure discharged | emitted from the discharge port provided in the upper part of the container, returned to the cooling device, and cooled again is employ | adopted.

  According to the hydrogen gas cooling device (heat exchanger) having such a configuration, as a result of being able to configure the heat exchanger with a container that is small enough to accommodate the propeller, the rotating shaft, the refrigerant pipe, and the like, It becomes possible to reduce the size of the gas cooling device. Moreover, the manufacturing cost of the heat exchanger can be sufficiently reduced by reducing the component cost and the assembly cost, and the replacement work of the sealing member is not required, and it is not necessary to supply compressed air during operation. In addition, the running cost can be sufficiently reduced. In this case, in the heat exchanger prototyped by the applicant, the tube winding portions (coil portions) of both hydrogen gas cooling pipes are wound with equal windings in the same manner as the heat exchanger disclosed in the above patent document. It is formed in a spiral shape in plan view so as to have a diameter. Further, in the heat exchanger prototyped by the applicant, in the same manner as the heat exchanger disclosed in the above-mentioned patent document, the entire tubular body winding portion of both hydrogen gas cooling pipes is overlapped in plan view. It is arranged to become.

  Therefore, in this heat exchanger, when the hydrogen gas is cooled, the brine that is moved from the bottom of the container toward the top of the container is the lowermost part of the tube winding portion of the second hydrogen gas cooling pipe that is disposed below. As a result of abutting in the moving direction (upward) with respect to the tube body, the brine and the hydrogen gas are suitably heat-exchanged at the lowermost part of the tube body winding portion of the second hydrogen gas cooling tube. However, the brine that has moved upward from the lowermost part of the second hydrogen gas cooling pipe (tubular winding part) will be pushed upward by the brine that is sequentially introduced into the container, and will proceed straight upward in the container. Therefore, both the pipes other than the lowermost pipe in the pipe winding part of the second hydrogen gas cooling pipe and the pipes of the pipe winding part of the second hydrogen gas cooling pipe are brought into contact with each other. There is a risk of passing through the inside of the tube winding part and reaching the uppermost part of the container.

  For this reason, in the heat exchanger prototyped by the applicant, brine and hydrogen gas are used rather than the heat exchanger in which the brine is swirled by the rotation of the propeller as in the heat exchanger disclosed in the above-mentioned patent document. The heat exchange efficiency of the hydrogen gas and brine may be sufficiently cooled so that the hydrogen gas and brine flow path lengths are sufficiently long (the effective area for heat exchange is sufficiently wide). There is a need. As a result, the heat exchanger prototyped by the applicant has a current situation that it is difficult to further downsize the heat exchanger without reducing the cooling efficiency of hydrogen gas, and this can be improved. preferable.

  The present invention has been made in view of such problems, and provides a heat exchanger and a hydrogen gas cooling device that can be miniaturized without causing an increase in manufacturing cost and running cost and a decrease in heat exchange efficiency. The main purpose.

In order to achieve the above object, the heat exchanger according to claim 1 includes a heat transfer coil having a tube winding portion in which a tube capable of passing the first heat exchange target fluid is spirally wound; And a container body in which the heat transfer coil is accommodated and capable of passing the second heat exchange target fluid, and the first heat exchange target fluid and the second heat exchange target fluid are A heat exchanger configured to be capable of exchanging heat with each other in a container body, wherein the fluid branch section branches the flow path of the first heat exchange target fluid into N (N is a natural number of 2 or more) flow paths. And a fluid merging section that merges the N flow paths, and the heat transfer coils are disposed for the N flow paths, respectively, and each of the heat transfer coils includes the tube winding section. The winding shapes of the pipes are non-circular, and the winding diameters of the maximum diameter portion of the tubular body winding portion are not equal to each other. Is configured so as, together with the winding axis direction of the tube winding portion is accommodated in the container body side by side along the tube length direction so as to extend along the respective tubular length direction of the container body, wherein A part of the tubular body winding portion in one of the two adjacent heat transfer coils in the tubular length direction is in the tubular length direction with respect to the tubular body winding portion in the other of the two adjacent heat transfer coils. The non-overlapping parts that do not overlap are arranged so as to occur at least one place , and when viewed along the tube length direction of the container body, the tube winding part in one of the two adjacent heat transfer coils The virtual line along the radial direction of the maximum diameter part and the virtual line along the radial direction of the maximum diameter part of the tube winding part in the other of the two adjacent heat transfer coils intersect with each other. By arranging both heat transfer coils, The overlapping portion is provided.

The heat exchanger of claim 2, in the heat exchanger according to claim 1 Symbol placement, N = 3 or more of said heat transfer coil is accommodated in the container body side by side along the tube length direction, the non Of the two adjacent heat transfer coils provided with the overlapping portion, the tube winding part of the heat transfer coil on the downstream side in the moving direction of the second heat exchange target fluid, and the heat transfer on the downstream side It arrange | positions so that the said tube winding part of the said heat-transfer coil arrange | positioned along with the downstream further of the coil may overlap in the said cylinder length direction, and the said non-overlapping part may not arise.

The heat exchanger according to claim 3 is the heat exchanger according to claim 1 or 2 , wherein N = 3 or more of the heat transfer coils are accommodated in the container along the cylinder length direction, Of the two adjacent heat transfer coils provided with non-overlapping portions, the tube winding part of the heat transfer coil on the upstream side in the moving direction of the second heat exchange target fluid, and the upstream side heat transfer coil It arrange | positions so that the said tube winding part of the said heat-transfer coil arrange | positioned along with the further upstream of the thermal coil may overlap in the said cylinder length direction, and the said non-overlapping part may not arise.

The heat exchanger according to claim 4 is the heat exchanger according to any one of claims 1 to 3 , wherein the outer heat transfer coil as the heat transfer coil and the inner side of the outer heat transfer coil are arranged. Inner heat transfer coils as heat transfer coils are provided for each of the N flow paths, and each of the outer heat transfer coils is arranged so that there is at least one non-overlapping part, and the non-overlapping part The inner heat transfer coils are arranged so that there is at least one point.

A heat exchanger according to a fifth aspect is the heat exchanger according to any one of the first to fourth aspects, wherein the N flow paths are configured to have the same flow path length.

The heat exchanger according to claim 6 is the heat exchanger according to any one of claims 1 to 5 , wherein an ejector is attached to a fluid introduction part for introducing the second heat exchange target fluid into the container body. .

The heat exchanger according to claim 7 is the heat exchanger according to any one of claims 1 to 6 , wherein hydrogen gas as the first heat exchange target fluid and a heat medium as the second heat exchange target fluid. The liquid is configured to be able to exchange heat with each other.

A hydrogen gas cooling device according to an eighth aspect includes the heat exchanger according to the seventh aspect and a refrigeration circuit that cools the heat medium liquid, and the heat medium liquid cooled by the refrigeration circuit and the hydrogen gas. The hydrogen gas can be cooled by exchanging heat with each other in the heat exchanger.

  In the heat exchanger according to claim 1, the heat transfer coils are accommodated in the container body side by side along the tube length direction so that the winding axis direction of the tube winding portion is along the tube length direction of the container body. And a non-overlapping part in which a part of the tube winding part in one of the two heat transfer coils adjacent in the cylinder length direction does not overlap in the cylinder length direction with respect to the tube winding part in the other heat transfer coil Each heat transfer coil is arranged so that at least one occurs.

  Therefore, according to the heat exchanger of the first aspect, the second heat exchange target fluid that is going to advance straight along the cylinder length direction of the container body comes into contact with the non-overlapping portion, so that the first in the non-overlapping portion. The result is that not only heat exchange with the fluid subject to heat exchange can be suitably performed, but also the movement direction of the fluid subject to second heat exchange is deflected from the cylinder length direction of the container body by abutting against the non-overlapping portion, resulting in turbulent flow The second heat exchange target fluid can be suitably brought into contact with not only the most upstream tube in the tube winding part but also each tube downstream of the most upstream tube. Since heat exchange with the first heat exchange target fluid in the tubular body winding portion can be performed favorably, heat exchange with the first heat exchange target fluid in the tubular body winding portion can be performed more preferably. As a result, the heat exchange efficiency between the first heat exchange target fluid and the second heat exchange target fluid can be sufficiently increased without providing a propeller or the like that causes a rise in parts cost or assembly cost or requires a large container body. Since the manufacturing cost can be improved, the manufacturing cost can be sufficiently reduced and the size can be sufficiently reduced. Further, since a power source for rotating the propeller is not necessary, the running cost can be sufficiently reduced.

Further, in the heat exchanger according to claim 1 , each heat transfer is performed so that the winding shapes of the tube winding portions are equal non-circular shapes and the winding diameters of the maximum diameter portions of the tube winding portions are equal to each other. A virtual line along the radial direction of the maximum diameter portion of the tube winding portion in one of the two adjacent heat transfer coils, when the coil is configured and viewed along the tube length direction of the container body, Both heat transfer coils are arranged and non-overlapping portions are provided so that a virtual line along the radial direction of the maximum diameter portion of the tubular body winding portion in the other heat transfer coil intersects.

Therefore, according to the heat exchanger according to claim 1 , non-overlapping portions are formed only by using heat transfer coils having the same winding shape and winding diameter of the tube winding portion and changing their arrangement angles. Therefore, the manufacturing cost can be further reduced as compared with a configuration in which a plurality of types of heat transfer coils having different winding shapes and winding diameters of the tube winding part are produced to generate a non-overlapping part. it can.

Furthermore, in the heat exchanger according to claim 2 , the tubular body winding portion of the heat transfer coil on the downstream side in the moving direction of the second heat exchange target fluid among the two heat transfer coils provided with the non-overlapping portion; The heat transfer coils are arranged so that the tube winding portions of the heat transfer coils arranged side by side on the downstream side of the heat transfer coils on the downstream side overlap with each other in the cylinder length direction so that no non-overlapping portions are generated. ing.

Therefore, according to the heat exchanger according to claim 2, it is possible to sufficiently increase the flow rate of the second heat exchange target fluid that has decreased in the non-overlapping portion provided on the upstream side. Since the amount of the second heat exchange target fluid that is allowed to exchange heat with the first heat exchange target fluid can be sufficiently increased, the first heat exchange target fluid and the pipe winding portion of the downstream heat transfer coil A situation in which the heat exchange efficiency with the second heat exchange target fluid is lowered can be suitably avoided.

Furthermore, in the heat exchanger according to claim 3 , the tube winding part of the upstream heat transfer coil in the moving direction of the second heat exchange target fluid of the two heat transfer coils provided with the non-overlapping part; The heat transfer coils are arranged so that the tube winding portions of the heat transfer coils arranged side by side on the upstream side of the heat transfer coil on the upstream side overlap with each other in the tube length direction so that a non-overlapping portion does not occur. ing.

Therefore, according to the heat exchanger according to claim 3 , the second heat exchange target fluid is flowed at a sufficient flow rate with respect to the tube winding part of the heat transfer coil in which the flow rate decreases due to the presence of the non-overlapping part. Since it can be made to flow in, it can avoid suitably the situation where the heat exchange efficiency of the 1st heat exchange object fluid and the 2nd heat exchange object fluid falls in the tube winding part of the upstream heat transfer coil. .

Further, according to the heat exchanger of claim 4 , each outer heat transfer coil is provided with an outer heat transfer coil and an inner heat transfer coil for each of the N flow paths, and at least one non-overlapping portion exists. In addition to arranging the coils, each inner heat transfer coil is arranged so that there is at least one non-overlapping part, so that only one of the outer heat transfer coil and the inner heat transfer coil is arranged for each flow path. Compared to the configuration described above, the flow path length of the first heat exchange target fluid in the container is sufficiently long, so that the heat exchange processing time between the second heat exchange target fluid and the first heat exchange target fluid is sufficient. Therefore, heat exchange between the first heat exchange target fluid and the second heat exchange target fluid can be performed more suitably.

Furthermore, according to the heat exchanger according to claim 5 , since the N flow paths are configured so that the flow path lengths are equal to each other, the flow path lengths of the respective flow paths are different from each other. There is a time difference in the time for the heat exchange target fluid to reach the fluid junction, and this causes a change in the discharge amount per unit time of the first heat exchange target fluid from the heat exchanger. By equalizing the flow path lengths of the flow paths, the time until the first heat exchange target fluid passes through each flow path and reaches the fluid junction is equalized. The discharge amount can be kept constant from the start of discharge until the discharge is completed.

Further, according to the heat exchanger of the sixth aspect , the ejector is attached to the fluid introduction part, so that the second heat is not contained in the container body without providing a propeller for stirring and a power source for rotating the propeller. Since the turbulent flow can be generated simply by ejecting the exchange target fluid, the second heat exchange target fluid advances straight around the heat transfer coil without causing an increase in manufacturing cost or running cost. The situation of passing through the part can be preferably avoided, whereby the first heat exchange target fluid and the second heat exchange target fluid can be favorably exchanged in the heat transfer coil.

Moreover, in the heat exchanger of Claim 7 , it is comprised so that heat exchange between the hydrogen gas as a 1st heat exchange object fluid and the heat-medium liquid as a 2nd heat exchange object fluid is mutually possible. The hydrogen gas cooling device according to claim 8 includes the heat exchanger according to claim 7 and a refrigeration circuit for cooling the heat transfer fluid, and heats the heat transfer fluid and hydrogen gas cooled by the refrigeration circuit. In the exchanger, the hydrogen gas can be cooled by exchanging heat with each other. Therefore, according to the heat exchanger of Claim 7 , and the hydrogen gas cooling device of Claim 8 , the supply cost of the hydrogen gas with respect to the supply object can be reduced sufficiently.

It is a block diagram which shows the structure of the hydrogen gas supply system 100 which concerns on embodiment of this invention. It is side surface sectional drawing of the heat exchanger 30 for hydrogen gas cooling which concerns on embodiment of this invention. It is the external view which looked at the heat exchanger 30 for hydrogen gas cooling which concerns on embodiment of this invention from upper direction. It is the external view which looked at the upper part of the heat exchanger 30 for hydrogen gas cooling which concerns on embodiment of this invention from the side. It is a side view of outer side heat-transfer coil 50oa-50od and inner side heat-transfer coil 50ia-50id in the heat exchanger 30 for hydrogen gas cooling which concerns on embodiment of this invention. It is a top view of outer side heat transfer coils 50oa-50od and inner side heat transfer coils 50ia-50id in the heat exchanger 30 for hydrogen gas cooling which concerns on embodiment of this invention. It is explanatory drawing for demonstrating hydrogen gas flow path L50a-L50d in the heat exchanger 30 for hydrogen gas cooling which concerns on embodiment of this invention. It is explanatory drawing for demonstrating arrangement | positioning of the outer side heat transfer coils 50oa-50od and the inner side heat transfer coils 50ia-50id in the container body 40 of the heat exchanger 30 for hydrogen gas cooling which concerns on embodiment of this invention. Explanation for explaining the positional relationship between the outer heat transfer coil 50ob and the inner heat transfer coil 50ic, and the outer heat transfer coil 50oa and the inner heat transfer coil 50id of the heat exchanger 30 for cooling hydrogen gas according to the embodiment of the present invention. FIG. Explanation for explaining the positional relationship between the outer heat transfer coil 50od and the inner heat transfer coil 50ia, the outer heat transfer coil 50oc, and the inner heat transfer coil 50ib of the heat exchanger 30 for cooling hydrogen gas according to the embodiment of the present invention. FIG. Description for explaining the positional relationship among the outer heat transfer coil 50oa and the inner heat transfer coil 50id, the outer heat transfer coil 50od, and the inner heat transfer coil 50ia of the hydrogen gas cooling heat exchanger 30 according to the embodiment of the present invention. FIG. It is side surface sectional drawing of the ejection nozzle 43a vicinity in the heat exchanger 30 for hydrogen gas cooling which concerns on embodiment of this invention.

  Hereinafter, embodiments of a heat exchanger and a hydrogen gas cooling device will be described with reference to the accompanying drawings.

  First, configurations of the heat exchanger 30 for cooling hydrogen gas and the hydrogen gas cooling device 1 will be described with reference to the accompanying drawings.

  A hydrogen gas supply system 100 shown in FIG. 1 is a facility for a hydrogen gas station that supplies hydrogen gas to an air supply target X such as a hydrogen gas fuel cell vehicle, and includes a hydrogen gas cooling device 1, a gas tank 2, and a dispenser. 3 and so on. In the figure, in order to facilitate understanding of the hydrogen gas cooling device 1, regarding the components other than the hydrogen gas cooling device 1 in the hydrogen gas supply system 100, the gas tank 2, the dispenser 3, and the hydrogen gas pipes 4a to 4a. Only 4c is shown, and the other components are not shown.

  The hydrogen gas cooling device 1 is an example of a “hydrogen gas cooling device”, and includes a refrigeration circuit 11, a brine tank 12, brine pipes 13a to 13d, liquid feed pumps 14a and 14b, a temperature sensor 15, a control unit 16, and hydrogen gas. A cooling heat exchanger 30 is provided, and brine that is an example of a “heat medium liquid” as a “second heat exchange target fluid” is cooled, and the cooled brine is supplied to the hydrogen gas cooling heat exchanger 30. Thus, the hydrogen gas can be cooled by heat exchange between hydrogen gas and brine, which is an example of the “first heat exchange target fluid”.

  The refrigeration circuit 11 is a unitary refrigeration circuit that is an example of a “refrigeration circuit”, and includes a compressor 21, a condenser 22, an expansion valve 23, and an evaporator 24. As will be described later, It is comprised so that a brine can be cooled by heat exchange with the brine as a "heat medium liquid". In this case, in the hydrogen gas cooling device 1 of this example, as an example, the pressure sensor 25 that detects the discharge pressure of the refrigerant from the compressor 21 and outputs the sensor signal S25 connects the compressor 21 and the condenser 22. It is arrange | positioned at refrigerant | coolant piping. The actual refrigeration circuit 11 includes various components such as various refrigerant bypass circuits, a reheat circuit, and a lubricating oil pipe that returns the lubricating oil discharged from the compressor 21 together with the chlorofluorocarbon to the compressor 21. However, in order to facilitate understanding of the hydrogen gas cooling device 1, illustration and description of these components are omitted.

  As will be described later, the brine tank 12 is configured to be capable of storing brine that is cooled by the refrigeration circuit 11 (evaporator 24) and supplied to the heat exchanger 30 for cooling hydrogen gas. The brine pipes 13a and 13b connect the evaporator 24 of the refrigeration circuit 11 and the brine tank 12 to each other. In this case, in the hydrogen gas cooling device 1 of this example, the brine in the brine tank 12 is supplied to the evaporator 24 via the brine pipe 13a and cooled, and then guided to the brine tank 12 via the brine pipe 13b. Thus, a configuration in which the brine is circulated between the brine tank 12 and the evaporator 24 is employed. The brine pipes 13c and 13d connect the brine tank 12 and the hydrogen gas cooling heat exchanger 30 to each other. In this case, in the hydrogen gas cooling device 1 of the present example, the brine in the brine tank 12 is supplied to the hydrogen gas cooling heat exchanger 30 via the brine pipe 13c and heat-exchanged with hydrogen, and then the brine pipe 13d. The brine is circulated between the brine tank 12 and the hydrogen gas cooling heat exchanger 30 by being guided to the brine tank 12 via the.

  The liquid feed pump 14 a pumps the brine in the brine tank 12 toward the evaporator 24 under the control of the control unit 16. In this case, in the hydrogen gas cooling device 1 of this example, the liquid feed pump 14a pumps the brine in the brine tank 12 to the evaporator 24, so that the brine in the evaporator 24 (brine cooled in the evaporator 24). Is adopted that is guided to the brine tank 12. The liquid feed pump 14 b pressure-feeds the brine in the brine tank 12 toward the hydrogen gas cooling heat exchanger 30 according to the control of the control unit 16. In this case, in the hydrogen gas cooling device 1 of this example, the liquid feed pump 14b pressure-feeds the brine in the brine tank 12 to the hydrogen gas cooling heat exchanger 30, thereby the brine in the hydrogen gas cooling heat exchanger 30. Is adopted that is guided to the brine tank 12.

  Instead of the configuration of the hydrogen gas cooling device 1 described above, for example, the brine in the “liquid storage tank (brine tank)” is supplied to the refrigeration circuit 11 (evaporator 24) and cooled, and then the hydrogen gas cooling heat is supplied. While supplying hydrogen directly to the exchanger 30 to cool the hydrogen gas, it is also possible to arrange a “liquid storage tank” so as to collect the brine whose temperature has been raised by the cooling of the hydrogen gas in the “liquid storage tank” (not shown). ) In addition, when used in an environment where there is no possibility of continuously cooling a large amount of hydrogen gas, that is, an environment where it is not necessary to provide a large amount of brine, a “storage tank (brine tank)” is not required. A configuration in which brine is directly circulated between the refrigeration circuit 11 (evaporator 24) and the hydrogen gas cooling heat exchanger 30 can also be employed (not shown).

  For example, the temperature sensor 15 is disposed in the brine pipe 13c for supplying the brine in the brine tank 12 to the hydrogen gas cooling heat exchanger 30, and the temperature of the brine in the brine pipe 13c (that is, hydrogen). The temperature of the brine that is heat exchanged with the gas) is detected and a sensor signal S15 is output.

  The control unit 16 comprehensively controls the hydrogen gas cooling device 1. Specifically, the control unit 16 switches the compressor 21 of the refrigeration circuit 11 in accordance with a sensor signal S25 from the pressure sensor 25 or the like when performing a brine cooling process for cooling the brine by the refrigeration circuit 11 (evaporator 24). The refrigerant is controlled to compress an amount of refrigerant necessary and sufficient for cooling the brine, and the expansion valve 23 is controlled to supply the evaporator 24 with an amount of refrigerant necessary and sufficient for cooling the brine.

  Further, the control unit 16 controls the liquid feed pump 14 a in parallel with the brine cooling process by the refrigeration circuit 11, thereby circulating the brine between the brine tank 12 and the evaporator 24, so that the brine in the brine tank 12 is Is maintained at a specified temperature (a temperature suitable for cooling hydrogen gas). The control unit 16 is moved from the gas tank 2 toward the dispenser 3 by controlling the liquid feed pump 14b to circulate the brine between the brine tank 12 and the hydrogen gas cooling heat exchanger 30. The hydrogen gas is cooled by heat exchange with brine in the hydrogen gas cooling heat exchanger 30.

  On the other hand, the heat exchanger 30 for cooling the hydrogen gas is an example of a “heat exchanger” and is connected to the dispenser 3 through the hydrogen gas pipe 4b and to the air supply target X through the hydrogen gas pipe 4c. And connected to the brine tank 12 through the brine pipes 13c and 13d, and hydrogen gas that flows from the gas tank 2 through the hydrogen gas pipe 4a and the dispenser 3 toward the supply target X is supplied to the brine. It cools to the temperature prescribed | regulated previously by heat exchange (as an example, the temperature within the temperature range of -33 degreeC--40 degreeC). In this example, an example in which the hydrogen gas cooling heat exchanger 30 is provided as a constituent element of the hydrogen gas cooling device 1 will be described. However, the hydrogen gas cooling heat exchanger 30 is an external device that is a “hydrogen gas cooling device”. It can also be used by connecting to.

  As shown in FIG. 2, the hydrogen gas cooling heat exchanger 30 includes a container body 40, outer heat transfer coils 50 oa to 50 od, and inner heat transfer coils 50 ia to 50 id (hereinafter, “outer heat transfer coils 50 oa to 50 od”). It is also referred to as “outer heat transfer coil 50o” when not distinguished, and also referred to as “inner heat transfer coil 50i” when “inner heat transfer coils 50ia to 50id” are not distinguished.

  The container body 40 corresponds to a “container body”, and as an example, a cylindrical tubular portion 41, a lid portion 42 b that closes a lower end portion of the tubular portion 41, and an upper end portion of the tubular portion 41 are closed. A lid introduction part 43 (an example of a “fluid introduction part”) for introducing brine into the heat exchange process space S formed by the lid part 42t, the cylindrical part 41 and the lid parts 42b and 42t, and the heat exchange process space S A brine discharge section 44 (fluid discharge section) for discharging brine from the heat exchanger, a speed increasing shaft 45 for increasing the flow rate of the brine in the heat exchange processing space S, and a hydrogen gas introduction section 46 for introducing hydrogen gas. And a hydrogen gas discharge portion 47 for discharging hydrogen gas.

  In this case, the main body part of the container body including the brine introduction part 43 and the brine discharge part 44 in the container body 40 and the tubular part 41 and the cover parts 42b and 42t are covered with a heat insulating material (not shown). Insulated against outside air. Moreover, as shown in FIG. 3, in the lid part 42t, the outer coil connection part 60oai-60odi which can connect the hydrogen gas inflow side edge part in outer heat transfer coil 50oa-50od, and outer heat transfer coil 50oa-50od. Outer coil connection portions 60 oa to 60 odo that can connect the hydrogen gas discharge side end portions are provided, and inner coil connection portions 60 ia to 60 idi that can connect the hydrogen gas inflow side end portions of the inner heat transfer coils 50 ia to 50 id, Inner coil connection portions 60 ia to 60 id that can connect the hydrogen gas discharge side ends of the inner heat transfer coils 50 ia to 50 id are provided.

  As shown in FIGS. 3 and 4, the outer coil connecting portion 60oai is connected to the hydrogen gas introducing portion 46 via a hydrogen gas pipe 61ba, and the outer coil connecting portion 60obi is connected to hydrogen gas via a hydrogen gas pipe 61bb. Connected to the introduction part 46, the outer coil connection part 60oci is connected to the hydrogen gas introduction part 46 via the hydrogen gas pipe 61bc, and the outer coil connection part 60odi is connected to the hydrogen gas introduction part via the hydrogen gas pipes 61ad, 61ba. 46. In the following description, when the hydrogen gas pipes 61ad, 61ba, 61bb, 61bc are not distinguished, they are also referred to as “hydrogen gas pipes 61”.

  Further, the outer coil connection portion 60oao is connected to the inner coil connection portion 60iai via the hydrogen gas pipe 62aa, and the outer coil connection portion 60obo is connected to the inner coil connection portion 60ibi via the hydrogen gas pipe 62bb. The connection part 60oco is connected to the inner coil connection part 60ici via the hydrogen gas pipe 62cc, and the outer coil connection part 60odo is connected to the inner coil connection part 60idi via the hydrogen gas pipe 62dd. In the following description, when the hydrogen gas pipes 62aa, 62bb, 62cc, and 62dd are not distinguished, they are also referred to as “hydrogen gas pipes 62”.

  The inner coil connection portion 60iao is connected to the hydrogen gas discharge portion 47 via the hydrogen gas pipes 63ad and 63db, and the inner coil connection portion 60ibo is connected to the hydrogen gas discharge portion 47 via the hydrogen gas pipe 63bb. The inner coil connection part 60ico is connected to the hydrogen gas discharge part 47 via a hydrogen gas pipe 63cb, and the inner coil connection part 60ido is connected to the hydrogen gas discharge part 47 via a hydrogen gas pipe 63db. In the following description, when the hydrogen gas pipes 63ad, 63bb, 63cb, and 63db are not distinguished, they are also referred to as “hydrogen gas pipes 63”.

Further, as shown in FIG. 2, the brine is diffused in the radial direction of the cylindrical portion 41 while blowing the brine upward toward the upper side of the container body 40 at the end portion in the heat exchange processing space S in the brine introduction portion 43. The ejection nozzle 43a for making it attach is attached. In this case, the ejection nozzle 43a is an example of an “ejector”, and in the hydrogen gas cooling heat exchanger 30 of this example, the brine is introduced so as to be positioned in the center of the cylindrical portion 41 of the container body 40 in plan view. part 43 that is attached to (the end of the brine pipe constituting the brine inlet portion 43).

  The brine introduction unit 43 is connected to the brine discharge port of the brine tank 12 through the brine pipe 13c, and the brine discharge unit 44 is connected to the brine inlet of the brine tank 12 through the brine pipe 13d. It is connected to the. Thereby, in the hydrogen gas cooling heat exchanger 30 of the present example, the brine supplied via the brine pipe 13c is ejected from the ejection nozzle 43a of the brine introduction part 43 into the heat exchange treatment space S, and the container body 40 After being moved in the direction of arrow A (an example of the “movement direction of the second heat exchange target fluid”) in the heat exchange processing space S, and then flows into the brine tank 12 from the brine discharge portion 44 via the brine pipe 13d. Be made. Further, the hydrogen gas introduction unit 46 is connected to the dispenser 3 through the hydrogen gas pipe 4b, and the hydrogen gas discharge unit 47 is connected to the air supply target X through the hydrogen gas pipe 4c. .

  The outer heat transfer coil 50 o and the inner heat transfer coil 50 i correspond to “heat transfer coils”, are accommodated in the container body 40, and are connected to the hydrogen gas introduction part 46 and the hydrogen gas discharge part 47. In this case, in the hydrogen gas cooling heat exchanger 30 of this example, N = 4 “outer heat transfer coils” of the outer heat transfer coils 50 oa to 50 od and the inner heat transfer coil disposed inside the outer heat transfer coil 50 o. A total of eight “heat transfer coils” including N = 4 “inner heat transfer coils” of the heat coils 50 ia to 50 id are configured to cool the hydrogen gas. As shown in FIGS. 5 and 6, each outer heat transfer coil 50o includes a tube winding portion 51o in which a tube capable of passing hydrogen gas is spirally wound, and each inner heat transfer coil. 50i includes a tubular body winding portion 51i in which a tubular body capable of passing hydrogen gas is spirally wound.

  Furthermore, each outer heat transfer coil 50o has a non-circular shape (in this example, a rounded substantially square shape) in which the winding shapes of the tube winding portions 51o are equal to each other, and the maximum in each tube winding portion 51o. The winding diameters of the diameter portions (diameters along the alternate long and short dash lines L1 and L2 shown in FIG. 6) are configured to be equal to each other. Each inner heat transfer coil 50i is formed in a non-circular shape (in this example, a rounded substantially square shape) in which the winding shapes of the tube winding portions 51i are equal to each other, and each tube winding portion. The winding diameter (the diameter in the direction along the alternate long and short dash lines L1 and L2) of the maximum diameter portion in 51o is equal to each other and smaller than the winding diameter of the maximum diameter portion of each of the tubular body winding portions 51o. It is configured.

  Furthermore, in the heat exchanger 30 for cooling a hydrogen gas of this example, as shown in FIG. 2, each outer transmission is performed such that the winding axis direction of each tube winding part 51 o is along the tube length direction of the container body 40. Thermal coils 50o are accommodated in the container body 40 side by side. In the hydrogen gas cooling heat exchanger 30 of this example, each inner heat transfer coil 50i is connected to the container body 40 so that the winding axis direction of each tube winding portion 51i is along the tube length direction of the container body 40. They are housed side by side. In this case, in the hydrogen gas cooling heat exchanger 30 of this example, the inside of the tube winding part 51o of each outer heat transfer coil 50o and the inside of the tube winding part 51i of each inner heat transfer coil 50i are indicated by the arrow B. Each of the outer heat transfer coils 50o and each of the inner heat transfer coils 50i is moved in the direction (the direction opposite to the direction of the arrow A in which the brine moves in the container body 40). It is connected to the gas discharge part 47.

  Further, in the hydrogen gas cooling heat exchanger 30 of the present example, as described above, each outer power transmission to each outer coil connection part 60oai to 60odi connected to the hydrogen gas introduction part 46 via each hydrogen gas pipe 61. The hydrogen gas inflow side ends of the thermal coil 50o are connected to the outer coil connection portions 60oao to 60odo connected to the inner coil connection portions 60iai to 60idi via the hydrogen gas pipes 62, respectively. 50o hydrogen gas discharge side end portions are respectively connected to the inner coil connection portions 60iai to 60idi, and hydrogen gas inflow end portions of the inner heat transfer coils 50i are respectively connected to the hydrogen gas exhaust pipes 63 through the hydrogen gas pipes 63. The hydrogen gas discharge side end portions of the respective inner heat transfer coils 50i are respectively connected to the inner coil connection portions 60ia to 60ido connected to the discharge portion 47. It is connected.

  Thereby, in the heat exchanger 30 for cooling hydrogen gas of this example, the hydrogen gas introduced into the hydrogen gas introduction part 46 through the hydrogen gas pipe 4b is four in the hydrogen gas flow paths L50a to L50d shown in FIG. Are discharged from the hydrogen gas discharge section 47 to the hydrogen gas pipe 4c (an example of a configuration in which N = 4 “flow paths” are provided). In the hydrogen gas cooling heat exchanger 30, each of the hydrogen gas pipes 61 corresponds to a “fluid branch part”, and each of the hydrogen gas pipes 63 corresponds to a “fluid merging part”.

  In this case, the hydrogen gas flow path L50a extends from the hydrogen gas introduction portion 46 to the hydrogen gas piping 61ba, the outer coil connection portion 60oai, the outer heat transfer coil 50oa, the outer coil connection portion 60oao, the hydrogen gas piping 62aa, and the inner coil connection portion 60iai. The inner heat transfer coil 50ia, the inner coil connection portion 60iao, and the hydrogen gas pipes 63ad and 63db are configured to reach the hydrogen gas discharge portion 47. Further, the hydrogen gas flow path L50b extends from the hydrogen gas introduction part 46 to the hydrogen gas pipe 61bb, the outer coil connection part 60obi, the outer heat transfer coil 50ob, the outer coil connection part 60obo, the hydrogen gas pipe 62bb, the inner coil connection part 60ibi, It is configured to reach the hydrogen gas discharge part 47 via the inner heat transfer coil 50ib, the inner coil connection part 60ibo, and the hydrogen gas pipe 63bb.

  Further, the hydrogen gas flow path L50c extends from the hydrogen gas introduction part 46 to the hydrogen gas pipe 61bc, the outer coil connection part 60oci, the outer heat transfer coil 50oc, the outer coil connection part 60oco, the hydrogen gas pipe 62cc, the inner coil connection part 60ici, It is configured to reach the hydrogen gas discharge part 47 via the inner heat transfer coil 50ic, the inner coil connection part 60ico, and the hydrogen gas pipe 63cb. Further, the hydrogen gas flow path L50d extends from the hydrogen gas introduction part 46 to the hydrogen gas pipes 61ba and 61ad, the outer coil connection part 60odi, the outer heat transfer coil 50od, the outer coil connection part 60odo, the hydrogen gas pipe 62dd, and the inner coil connection part. 60 idi, the inner heat transfer coil 50 id, the inner coil connection part 60 ido, and the hydrogen gas pipe 63 db are configured to reach the hydrogen gas discharge part 47.

  Further, in the heat exchanger 30 for cooling hydrogen gas of this example, as shown in FIG. 2, the outer heat transfer coil 50ob and the inner heat transfer coil 50ic are arranged at the lowermost portion of the container body 40, and the outer heat transfer is arranged above the outer heat transfer coil 50ic. The coil 50oa and the inner heat transfer coil 50id are arranged, the outer heat transfer coil 50od and the inner heat transfer coil 50ia are arranged above it, and the outer heat transfer coil 50oc and the inner heat transfer coil 50ib are arranged above it, By adjusting the pipe length of each of the hydrogen gas pipes 61, 62, 63, as shown in FIG. 7, the flow path length from the hydrogen gas introduction part 46 to the hydrogen gas discharge part 47 of the hydrogen gas flow path L50a, and the hydrogen gas The length of the flow path from the hydrogen gas introduction part 46 to the hydrogen gas discharge part 47 of the flow path L50b and the distance from the hydrogen gas introduction part 46 to the hydrogen gas discharge part 47 of the hydrogen gas flow path L50c And pathlength, and the flow path length from the hydrogen gas inlet 46 of the hydrogen gas flow path L50d until hydrogen gas discharge portion 47 is configured to be equal to each other.

  In this case, in the heat exchanger 30 for cooling hydrogen gas of this example, the outer heat transfer coil 50ob and the inner heat transfer coil 50ic disposed at the lowermost part of the container body 40 are connected to the container body 40 as shown in FIG. When viewed from above along the tube length direction, the alternate long and short dash lines L1 and L2 along the radial direction of the maximum diameter portion in the tube winding portion 51o of the outer heat transfer coil 50ob and the tube body of the inner heat transfer coil 50ic. The alternate long and short dash lines L3 and L4 along the radial direction of the maximum diameter portion of the winding portion 51i intersect at an angle of 45 degrees, and the winding center of the tube winding portion 51o and the winding of the tube winding portion 51i The outer heat transfer coil 50ob and the inner heat transfer coil 50ic are arranged so that the center is concentric with the center of the container body 40 (tubular portion 41).

  Further, in the heat exchanger 30 for cooling hydrogen gas of this example, the outer heat transfer coil 50oa and the inner heat transfer coil 50id disposed above the outer heat transfer coil 50ob and the inner heat transfer coil 50ic are connected to the cylinder of the container body 40. When viewed from above along the long direction, the alternate long and short dash lines L3 and L4 along the radial direction of the maximum diameter portion of the tube winding portion 51o of the outer heat transfer coil 50oa and the tube winding of the inner heat transfer coil 50id. The alternate long and short dash lines L1 and L2 along the radial direction of the maximum diameter portion of the turning portion 51i intersect at an angle of 45 degrees, and the winding center of the tube winding portion 51o and the winding center of the tube winding portion 51i The outer heat transfer coil 50oa and the inner heat transfer coil 50id are arranged so that they are concentric at the center of the container body 40 (tubular portion 41).

  Furthermore, in the hydrogen gas cooling heat exchanger 30 of the present example, the outer heat transfer coil 50od and the inner heat transfer coil 50ia disposed above the outer heat transfer coil 50oa and the inner heat transfer coil 50id are connected to the cylinder of the container body 40. When viewed from above along the long direction, the alternate long and short dash lines L3 and L4 along the radial direction of the maximum diameter portion of the tube winding portion 51o of the outer heat transfer coil 50od and the tube winding of the inner heat transfer coil 50ia. The alternate long and short dash lines L1 and L2 along the radial direction of the maximum diameter portion of the turning portion 51i intersect at an angle of 45 degrees, and the winding center of the tube winding portion 51o and the winding center of the tube winding portion 51i The outer heat transfer coil 50od and the inner heat transfer coil 50ia are arranged so that they are concentric at the center of the container body 40 (tubular portion 41).

  In the hydrogen gas cooling heat exchanger 30 of this example, the outer heat transfer coil 50oc and the inner heat transfer coil 50ib disposed above the outer heat transfer coil 50od and the inner heat transfer coil 50ia are connected to the cylinder of the container body 40. When viewed from above along the long direction, the alternate long and short dash lines L1 and L2 along the radial direction of the maximum diameter portion in the tube winding portion 51o of the outer heat transfer coil 50oc and the tube winding of the inner heat transfer coil 50ib. The alternate long and short dash lines L3 and L4 along the radial direction of the maximum diameter portion of the turning portion 51i intersect at an angle of 45 degrees, and the winding center of the tube winding portion 51o and the winding center of the tube winding portion 51i The outer heat transfer coil 50oc and the inner heat transfer coil 50ib are arranged so that they are concentric with each other at the center of the container body 40 (tubular portion 41).

  Although different from the hydrogen gas cooling heat exchanger 30 of the present example, a “virtual line” along the radial direction of the maximum diameter portion in the tube winding portion 51o of the outer heat transfer coil 50o and its outer heat transfer. The “virtual line” along the radial direction of the maximum diameter portion of the tubular body winding portion 51i of the inner heat transfer coil 50i disposed inside the thermal coil 50o intersects at an arbitrary angle other than 45 degrees. It can also be configured. Moreover, the "imaginary line" along the radial direction of the largest diameter part in the tube winding part 51o of the outer heat transfer coil 50o, and the tube of the inner heat transfer coil 50i disposed inside the outer heat transfer coil 50o. It can also be configured such that the “virtual line” along the radial direction of the maximum diameter portion in the body winding portion 51i matches (does not intersect).

  Furthermore, in the heat exchanger 30 for cooling hydrogen gas of this example, as shown in FIG. 9, the outer heat transfer coils 50 obs and 50 oa (an example of “two heat transfer coils adjacent in the cylinder length direction”) are used as the container body 40. Of the tube winding part 51o in the outer heat transfer coil 50ob (an example of "one of two adjacent heat transfer coils") and the outer heat transfer when viewed from above along the tube length direction The winding center of the tube winding portion 51o in the coil 50oa (an example of “the other of the two adjacent heat transfer coils”) is concentric at the center of the cylindrical portion 41, and the tube winding of the outer heat transfer coil 50ob. The alternate long and short dash lines L1 and L2 (an example of “imaginary line along the radial direction”) along the radial direction of the maximum diameter portion at the turning portion 51o and the maximum diameter portion at the tube winding portion 51o of the outer heat transfer coil 50oa. Dash-dot lines L3 and L4 along the radial direction The tube winding portion 51o of the outer heat transfer coil 50ob and the tube winding portion 51o of the outer heat transfer coil 50oa so that the “an imaginary line along the radial direction” intersects at an angle of 45 degrees. Are arranged side by side in the tube length direction of the container body 40.

  Thereby, in the hydrogen gas cooling heat exchanger 30 of this example, the tube winding part 51o in the outer heat transfer coil 50ob and the tube winding part 51o in the outer heat transfer coil 50oa are the tube length of the container body 40. “Overlapping part (a part of the circumferential direction of the tubular body constituting one tubular body winding part 51o is in the tube length direction with respect to the tubular body constituting the other tubular body winding part 51o”. "The overlapping portion)" and the "non-overlapping portion (a portion of the tubular body constituting the one tubular body winding portion 51o in the circumferential direction is the other tubular body winding portion 51o) that does not overlap in the tube length direction" The portion that does not overlap in the cylinder length direction) ”is generated. Specifically, as shown in FIG. 9, the tube winding portions 51o and 51o of the outer heat transfer coils 50ob and 50oa are provided with “overlapping portions” and “non-overlapping portions” alternately to form eight portions. The “overlapping portion” and eight “non-overlapping portions” are generated.

  Moreover, in the heat exchanger 30 for cooling hydrogen gas of this example, as shown in FIG. 9, inner heat transfer coils 50ic and 50id (another example of “two heat transfer coils adjacent in the cylinder length direction”) are used as containers. When viewed from above along the cylinder length direction of the body 40, the winding center of the tubular body winding portion 51i in the inner heat transfer coil 50ic (another example of "one of two adjacent heat transfer coils") The winding center of the tube winding part 51i in the inner heat transfer coil 50id (another example of "the other of the two adjacent heat transfer coils") is concentric at the center of the tubular part 41, and the inner heat transfer Dotted lines L3 and L4 (an example of “imaginary line along the radial direction”) along the radial direction of the maximum diameter portion in the tubular winding portion 51i of the coil 50ic, and the tubular winding portion of the inner heat transfer coil 50id An alternate long and short dash line along the radial direction of the maximum diameter portion in 51i 1 and L2 (an example of a “imaginary line along the radial direction”) intersect with each other at an angle of 45 degrees, the tube winding portion 51i of the inner heat transfer coil 50ic, and the tube body of the inner heat transfer coil 50id. Winding portions 51 i are arranged side by side in the tube length direction of the container body 40.

  Thereby, in the heat exchanger 30 for cooling hydrogen gas of this example, the tube winding part 51i in the inner heat transfer coil 50ic and the tube winding part 51i in the inner heat transfer coil 50id are the tube length of the container body 40. "Overlapping part (a part of the circumferential direction of the tubular body constituting one tubular body winding part 51i is in the tube length direction with respect to the tubular body constituting the other tubular body winding part 51i". "The overlapping portion)" and "the non-overlapping portion (the portion of the tubular body constituting one tubular body winding portion 51i is part of the other tubular body winding portion 51i) that does not overlap in the tube length direction" The portion that does not overlap in the cylinder length direction) ”is generated. Specifically, as shown in FIG. 9, the tube winding portions 51i and 51i of the inner heat transfer coils 50ic and 50id are continuously overlapped along the circumferential direction of the tube winding portions 51i and 51i. Part "and eight" non-overlapping parts (a part on the outer peripheral side and a part on the inner peripheral side in the winding diameter direction of the pipe constituting one pipe winding part 51i are the other pipes. " In this state, a portion that does not overlap with the tubular body constituting the winding portion 51i) is generated.

  Furthermore, in the heat exchanger 30 for cooling hydrogen gas of this example, as shown in FIG. 10, outer heat transfer coils 50od, 50oc (another example of “two heat transfer coils adjacent in the cylinder length direction”) are used as containers. When viewed from above along the tube length direction of the body 40, the winding center of the tubular body winding portion 51o in the outer heat transfer coil 50od (another example of “one of two adjacent heat transfer coils”) The winding center of the tube winding part 51o in the outer heat transfer coil 50oc (an example of “the other of the two adjacent heat transfer coils”) is concentric at the center of the tubular part 41, and the outer heat transfer coil 50od. Dotted lines L3 and L4 (another example of “imaginary line along the radial direction”) along the radial direction of the maximum diameter portion of the tubular winding portion 51o of the tubular winding portion of the outer heat transfer coil 50oc One point along the radial direction of the maximum diameter part at 51o The tube winding part 51o of the outer heat transfer coil 50od and the outer heat transfer coil 50oc so that the lines L1 and L2 (another example of the “imaginary line along the radial direction”) intersect at an angle of 45 degrees. Tube winding parts 51o are arranged side by side in the tube length direction of the container body 40.

  Thereby, in the heat exchanger 30 for cooling hydrogen gas of this example, the tube winding part 51o in the outer heat transfer coil 50od and the tube winding part 51o in the outer heat transfer coil 50oc are the tube length of the container body 40. In this state, an “overlapping portion” that is a portion overlapping in the direction and a “non-overlapping portion” that is a portion not overlapping in the cylinder length direction are generated. Specifically, as shown in FIG. 10, the tube winding portions 51o and 51o of the outer heat transfer coils 50od and 50oc are provided with “overlapping portions” and “non-overlapping portions” alternately to form eight portions. The “overlapping portion” and eight “non-overlapping portions” are generated.

  Further, in the heat exchanger 30 for cooling hydrogen gas of the present example, as shown in FIG. 10, inner heat transfer coils 50 ia and 50 ib (another example of “two heat transfer coils adjacent in the cylinder length direction”) are used as containers. When viewed from above along the cylinder length direction of the body 40, the winding center of the tubular body winding portion 51i in the inner heat transfer coil 50ia (another example of “one of two adjacent heat transfer coils”) The winding center of the tubular body winding portion 51i in the inner heat transfer coil 50ib (another example of "the other of the two adjacent heat transfer coils") is concentric at the center of the tubular portion 41, and the inner heat transfer Dotted lines L1 and L2 (another example of “imaginary line along the radial direction”) along the radial direction of the maximum diameter portion in the tubular body winding portion 51i of the coil 50ia and the tubular body winding of the inner heat transfer coil 50ib. Along the radial direction of the maximum diameter portion in the turning portion 51i The tubular body winding portion 51i of the inner heat transfer coil 50ia and the inner heat transfer coil 50ib so that the chain lines L3 and L4 (another example of the “imaginary line along the radial direction”) intersect at an angle of 45 degrees. Tube winding parts 51i are arranged side by side in the tube length direction of the container body 40.

  Thereby, in the heat exchanger 30 for cooling the hydrogen gas of this example, the tube winding part 51i in the inner heat transfer coil 50ia and the tube winding part 51i in the inner heat transfer coil 50ib are the tube length of the container body 40. In this state, an “overlapping portion” that is a portion overlapping in the direction and a “non-overlapping portion” that is a portion not overlapping in the cylinder length direction are generated. Specifically, as shown in FIG. 10, the tube winding portions 51 i and 51 i of the inner heat transfer coils 50 ia and 50 ib are continuously overlapped along the circumferential direction of both the tube winding portions 51 i and 51 i. "Parts" are provided, and eight "non-overlapping parts" are generated.

  Although different from the hydrogen gas cooling heat exchanger 30 of the present example, regarding the two outer heat transfer coils 50o and 50o that generate the “non-overlapping portion”, the maximum diameter portion in one tubular body winding portion 51o The “virtual line” along the radial direction of the tube and the “virtual line” along the radial direction of the maximum diameter portion of the other tubular body winding portion 51o intersect at an arbitrary angle other than 45 degrees. You can also. Similarly, with respect to the two inner heat transfer coils 50i and 50i that generate the “non-overlapping portion”, the “virtual line” along the radial direction of the maximum diameter portion in one tube winding portion 51i and the other tube The “virtual line” along the radial direction of the maximum diameter portion of the body winding portion 51i may be configured to intersect at an arbitrary angle other than 45 degrees.

  Further, in the hydrogen gas cooling heat exchanger 30 of this example, the movement direction of the brine in the container body 40 of the outer heat transfer coils 50od, 50oc provided with the “non-overlapping portion” (arrow A shown in FIG. 2). The outer heat transfer coil 50od disposed on the upstream side of the outer heat transfer coil 50od and the outer side disposed adjacent to the upstream side of the outer heat transfer coil 50od (adjacent in the cylinder length direction of the container body 40). When the heat transfer coil 50oa is viewed from above along the tube length direction of the container body 40, as shown in FIG. 11, the winding center of the tube winding portion 51o in the outer heat transfer coil 50oa and the outer transfer One point along the radial direction of the maximum diameter portion of the tubular body winding portion 51o of the outer heat transfer coil 50oa, which is concentric with the winding center of the tubular body winding portion 51o in the thermal coil 50od at the center of the tubular portion 41. Chain lines L3 and L4 and outside The tube winding part 51o of the outer heat transfer coil 50oa and the outer heat transfer so that the alternate long and short dash lines L3 and L4 along the radial direction of the maximum diameter part of the tube winding part 51o of the heat transfer coil 50od coincide with each other. The tubular body winding part 51o of the coil 50od is arranged side by side in the tube length direction of the container body 40.

  Thereby, in the heat exchanger 30 for cooling hydrogen gas of this example, the tube winding part 51o in the outer heat transfer coil 50oa and the tube winding part 51o in the outer heat transfer coil 50od are in the cylinder length direction of the container body 40. In FIG. 2, no “non-overlapping portion” is formed.

  Further, in the heat exchanger 30 for cooling hydrogen gas of this example, the movement direction of the brine in the container body 40 among the inner heat transfer coils 50ia and 50ib provided with the “non-overlapping portion” (arrow A shown in FIG. 2). The inner heat transfer coil 50ia disposed on the upstream side of the inner heat transfer coil 50ia and the inner side disposed adjacent to the upstream side of the inner heat transfer coil 50ia (adjacent in the cylinder length direction of the container body 40). When the heat transfer coil 50id is viewed from above along the cylinder length direction of the container body 40, as shown in FIG. 11, the winding center of the tube winding portion 51i in the inner heat transfer coil 50id and the inner transfer One point along the radial direction of the maximum diameter portion of the tubular body winding portion 51i of the inner heat transfer coil 50id is concentric with the winding center of the tubular body winding portion 51i in the thermal coil 50ia at the center of the tubular portion 41. Chain lines L1, L2 and inside The tube winding part 51i of the inner heat transfer coil 50id and the inner heat transfer coil so that the one-dot chain lines L1 and L2 along the radial direction of the maximum diameter part in the tube winding part 51i of the heat coil 50ia coincide with each other. 50 ia tube winding portions 51 i are arranged side by side in the tube length direction of the container body 40.

  Thereby, in the heat exchanger 30 for cooling hydrogen gas of this example, the tube winding part 51i in the inner heat transfer coil 50id and the tube winding part 51i in the inner heat transfer coil 50ia are in the cylinder length direction. In FIG. 2, no “non-overlapping portion” is formed.

  Next, the hydrogen gas cooling process by the hydrogen gas cooling device 1 will be described.

  In the hydrogen gas cooling device 1, when the hydrogen gas cooling process for cooling the hydrogen gas is not performed in the hydrogen gas cooling heat exchanger 30, between the brine tank 12 and the hydrogen gas cooling heat exchanger 30. A configuration in which a small amount of brine is circulated is employed. Specifically, the control unit 16 controls the liquid feed pump 14b when the hydrogen gas cooling process is not performed, so that a small amount is transferred from the brine tank 12 to the hydrogen gas cooling heat exchanger 30 at a predetermined time interval. Of brine is intermittently fed. Thereby, the low-temperature brine cooled by the brine cooling process described later is supplied from the brine tank 12 to the hydrogen gas cooling heat exchanger 30 via the brine pipe 13c, and the brine in the hydrogen gas cooling heat exchanger 30 is supplied. As a result of returning to the brine tank 12 through the brine pipe 13d, the brine whose temperature has been increased due to geothermal heat or the like has remained in the brine pipe 13c or the hydrogen gas cooling heat exchanger 30, that is, hydrogen at the start of the hydrogen gas cooling process. It is possible to preferably avoid a state in which a long time is required until the gas can be suitably cooled.

  In addition, the control unit 16 performs brine cooling in which the brine in the brine tank 12 is cooled by the refrigeration circuit 11 in parallel with the above-described process of circulating the brine between the brine tank 12 and the hydrogen gas cooling heat exchanger 30. By executing the processing, the temperature of the brine in the brine tank 12 is maintained at a temperature within a temperature range suitable for cooling the hydrogen gas. Specifically, by executing the brine circulation process as described above, the temperature of the brine supplied from the brine tank 12 to the heat exchanger 30 for cooling the hydrogen gas, that is, the temperature of the brine in the brine tank 12 is increased. It is detected by the temperature sensor 15. Therefore, the control unit 16 repeatedly executes a process of determining whether or not the brine temperature specified based on the sensor signal S15 from the temperature sensor 15 is within the specified temperature range (brine temperature monitoring process). .

  When the controller 16 determines that the specified brine temperature is higher than the upper limit value of the specified temperature range, the controller 16 starts the brine cooling process by the refrigeration circuit 11 and controls the liquid feed pump 14a. Then, the brine is circulated between the brine tank 12 and the refrigeration circuit 11 (evaporator 24). At this time, in the hydrogen gas cooling device 1 of this example, the controller 16 suitably cools the brine in the evaporator 24 by changing the rotation speed of the compressor 21 according to the specified brine temperature, for example. Compress the amount of chlorofluorocarbon needed to do it.

  Thereby, the flon discharged from the compressor 21 and condensed in the condenser 22 is supplied to the evaporator 24 through the expansion valve 23, and the brine is cooled by heat exchange with the vaporized flon. In the hydrogen gas cooling device 1 of this example, a known process for changing the valve opening rate of the expansion valve 23 in parallel with the change of the operating state of the compressor 21 (the amount of chlorofluorocarbon supplied to the evaporator 24 is changed). In order to facilitate understanding of the operation of the hydrogen gas cooling device 1, description of the process of changing the valve opening rate of the expansion valve 23 is omitted. By continuing such processing until the temperature of the brine specified based on the sensor signal S15 reaches a temperature within the specified temperature range, the temperature of the brine in the brine tank 12 is a target suitable for cooling hydrogen gas. It is maintained at a temperature within the temperature range.

  On the other hand, in filling (supplying) hydrogen gas to the supply target X, as an example, supply of air from the main control device (not shown) of the hydrogen gas supply system 100 to the control unit 16 of the hydrogen gas cooling device 1 is performed. A start signal is output, and the controller 16 controls the liquid feed pump 14b to increase the amount of brine supplied from the brine tank 12 to the hydrogen gas cooling heat exchanger 30. As a result, an amount of brine required for cooling the hydrogen gas is supplied from the brine tank 12 to the hydrogen gas cooling heat exchanger 30 via the brine pipe 13c. As a result, the hydrogen gas that is moved from the gas tank 2 through the dispenser 3 toward the supply target X is cooled by heat exchange with the brine when passing through the heat exchanger 30 for cooling the hydrogen gas, and the temperature is sufficiently lowered. The hydrogen gas (for example, hydrogen gas having a temperature in the temperature range of −33 ° C. to −40 ° C.) is filled in the fuel tank (gas tank) of the supply target X. Thereby, the filling efficiency of the hydrogen gas to the air supply target X can be sufficiently improved.

  In this case, in the hydrogen gas cooling device 1 (hydrogen gas cooling heat exchanger 30) of this example, the brine in the brine tank 12 is cooled by the liquid feed pump 14b via the brine pipe 13c when the hydrogen gas is cooled as described above. When the brine fed to the hydrogen gas cooling heat exchanger 30 is ejected from the ejection nozzle 43a of the brine introduction part 43 into the heat exchange treatment space S, the direction of the arrow A shown in FIG. The container body 40 is moved in the upward direction from the bottom of the container body 40.

  Specifically, in the hydrogen gas cooling heat exchanger 30 of the present example, as shown in FIG. 12, the brine pumped to the hydrogen gas cooling heat exchanger 30 via the brine pipe 13c by the liquid feed pump 14b is stored. When the spray nozzle 43a of the brine introduction part 43 is ejected upward in the heat exchange processing space S as indicated by the arrow C1, the brine near the ejection nozzle 43a is ejected from the fluid suction port of the ejection nozzle 43a. It is sucked into the heat exchange space S together with the brine pumped by the liquid feed pump 14b as shown by the arrow C2, and is again ejected upward in the heat exchange processing space S. In the figure, the arrows C1, C2, and C2 are distinguished in order to facilitate understanding of the flow of brine pumped by the liquid feed pump 14b and the flow of brine sucked from the fluid suction port due to the ejector effect. Although illustrated, actually, the brine is ejected from the ejection nozzle 43a in a state where the above two flows are mixed in the ejection nozzle 43a. Thereby, a turbulent flow is generated in the brine ejected from the ejection nozzle 43a.

  On the other hand, the brine ejected from the ejection nozzle 43a is firstly wound in the tubular body winding portion 51o of the outer heat transfer coil 50ob and the tubular body winding of the inner heat transfer coil 50ic arranged at the lowermost part of the heat exchange processing space S. It contacts the turning portion 51i. Thereby, hydrogen gas in the outer heat transfer coil 50ob (hydrogen gas introduced from the hydrogen gas introduction portion 46 and flowing through the hydrogen gas flow path L50b), and hydrogen gas in the inner heat transfer coil 50ic (hydrogen gas introduction portion) The hydrogen gas is cooled by heat exchange with the hydrogen gas introduced from the gas flow path 46 and flowing through the hydrogen gas flow path L50c.

  In this case, in the hydrogen gas cooling heat exchanger 30 in which the ejection nozzle 43a is disposed in the brine introduction part 43, the brine immediately after being introduced into the bottom of the container body 40 is ejected from the ejection nozzle 43a. Due to the influence of the turbulent flow generated at the time when the heat is applied, the heat reaches the outer heat transfer coil 50ob and the inner heat transfer coil 50ic while diffusing in the radial direction of the cylindrical portion 41. Therefore, in the hydrogen gas cooling heat exchanger 30 of this example, the brine goes straight upward around the tube winding portion 51o of the outer heat transfer coil 50ob and the tube winding portion 51i of the inner heat transfer coil 50ic. A situation of passing through the tube winding portions 51o and 51i, that is, a situation where the heat exchange efficiency between the brine and the hydrogen gas in the outer heat transfer coil 50ob and the inner heat transfer coil 50ic is preferably avoided.

  Thereby, the brine introduced into the heat exchange processing space S is not only lower than the lowermost tube in the tube winding portion 51o of the outer heat transfer coil 50ob but also above the lowermost portion of the tube winding portion 51o. And a tube above the lowermost portion of the tubular body winding portion 51i as well as the lowermost tubular body in the tubular body winding portion 51i of the inner heat transfer coil 50ic. The body also preferably comes into contact.

  Further, the brine in which the hydrogen gas is cooled in the tube winding part 51o of the outer heat transfer coil 50ob and the tube winding part 51i of the inner heat transfer coil 50ic is newly introduced into the heat exchange processing space S. The container body 40 is further moved in the direction of arrow A so as to be pushed up by the brine, and reaches the outer heat transfer coil 50oa and the inner heat transfer coil 50id. Thereby, hydrogen gas in the outer heat transfer coil 50oa (hydrogen gas introduced from the hydrogen gas introduction part 46 and flowing through the hydrogen gas flow path L50a) and hydrogen gas in the inner heat transfer coil 50id (hydrogen gas introduction part) The hydrogen gas is cooled by heat exchange with the hydrogen gas introduced through the gas flow path 46 and flowing through the hydrogen gas flow path L50d.

  In this case, when the brine reaches the outer heat transfer coil 50oa and the inner heat transfer coil 50id disposed above the outer heat transfer coil 50ob and the inner heat transfer coil 50ic, the effect of the ejection nozzle 43a (the brine is changed). (Force to move in the direction of diffusion) is weakened. However, in the heat exchanger 30 for cooling the hydrogen gas of this example, as described above, the tube winding portion 51o of the outer heat transfer coil 50ob and the outer heat transfer coil disposed above the outer heat transfer coil 50ob. The tube winding portion 51o of 50 oa is disposed so as to generate a “non-overlapping portion”, and is disposed above the tube winding portion 51i of the inner heat transfer coil 50ic and the inner heat transfer coil 50ic. It arrange | positions so that it may be in the state which the pipe body winding part 51i of the arrange | positioned inner heat-transfer coil 50id produces a "non-overlapping part."

  For this reason, in the heat exchanger 30 for cooling hydrogen gas of this example, the “non-overlapping portion” of the lowermost tube in the tube winding portion 51o of the outer heat transfer coil 50oa and the tube of the inner heat transfer coil 50id The brine that rises in the heat exchange processing space S is preferably brought into contact with the lowermost “non-overlapping portion” of the winding portion 51i. Further, the brine moves in contact with the lowermost “non-overlapping portion” of the tube winding portions 51o and 51i, so that the movement direction of the brine is changed (warped from the direction of going straight upward) and turbulent flow is generated. As a result, the brine goes straight upward around the tube winding portion 51o of the outer heat transfer coil 50oa and the tube winding portion 51i of the inner heat transfer coil 50id and passes through the tube winding portions 51o and 51i. That is, a situation in which the heat exchange efficiency between the brine and the hydrogen gas in the outer heat transfer coil 50oa and the inner heat transfer coil 50id is suitably avoided.

  Thereby, the brine rising the heat exchange processing space S is suitable not only for the lowermost tube body in the tube winding portion 51o of the outer heat transfer coil 50oa but also for the tube body above the lowermost portion. As a result of abutting and suitably abutting not only on the lowermost tube in the tube winding portion 51i of the inner heat transfer coil 50id but also on the tube above the lowermost portion, the hydrogen gas is suitably cooled. Is done.

  Further, the brine in which the hydrogen gas is cooled in the tube winding part 51o of the outer heat transfer coil 50oa and the tube winding part 51i of the inner heat transfer coil 50id is indicated by an arrow from the outer heat transfer coil 50ob and the inner heat transfer coil 50ic. The inside of the container body 40 is further moved in the direction of the arrow A so as to be pushed up by the brine moving in the direction A, and reaches the outer heat transfer coil 50od and the inner heat transfer coil 50ia. Thereby, hydrogen gas in the outer heat transfer coil 50od (hydrogen gas introduced from the hydrogen gas introduction portion 46 and flowing through the hydrogen gas flow path L50d) and hydrogen gas in the inner heat transfer coil 50ia (hydrogen gas introduction portion) These hydrogen gases are cooled by heat exchange with the hydrogen gas introduced through the hydrogen gas flow path L50a.

  In this case, as described above, in the heat exchanger 30 for cooling the hydrogen gas of this example, “non-overlapping portions” are generated in the tube winding portions 51o and 51o of the outer heat transfer coils 50ob and 50oa, and the inner heat transfer is performed. The tube winding portions 51i and 51i of the coils 50ic and 50id are configured to have “non-overlapping portions”, and heat exchange is performed in the tube winding portions 51o and 51o and the tube winding portions 51i and 51i. The brine passage resistance is slightly increased by the amount that the brine rising in the processing space S comes into contact with the “non-overlapping portion”. For this reason, the flow rate of the brine that has passed through the tube winding part 51o of the outer heat transfer coil 50oa and the tube winding part 51i of the inner heat transfer coil 50id is slightly reduced due to the above-described passage resistance. In the state where the flow rate of the brine is reduced, the amount of brine exchanged with the hydrogen gas in the tube winding portions 51o and 51i per unit time is reduced, and the heat exchange efficiency is slightly reduced. It will be.

  Therefore, in the heat exchanger 30 for cooling hydrogen gas of this example, the heat exchanger 30 is arranged on the upstream side of the tube winding parts 51o, 51o of the outer heat transfer coils 50ob, 50oa arranged so as to generate “non-overlapping parts”. The tube winding portion 51o of the outer heat transfer coil 50od is overlapped with the tube winding portion 51o of the outer heat transfer coil 50oa in the tube length direction of the container body 40 so that a “non-overlapping portion” does not occur. The tube winding of the inner heat transfer coil 50ia arranged upstream of the tube winding portions 51i, 51i of the inner heat transfer coils 50ic, 50id arranged so as to generate “non-overlapping portions”. By arranging the portion 51i so as not to produce a “non-overlapping portion” by overlapping the tubular body winding portion 51i of the inner heat transfer coil 50id in the tube length direction of the container body 40, the “non-overlapping portion” Increased passage drop due to existence And, configured to increase the flow rate of the brine is employed.

  Thereby, in the hydrogen gas cooling heat exchanger 30 of this example, the brine generated when passing through the tube winding part 51o of the outer heat transfer coil 50oa and the tube winding part 51i of the inner heat transfer coil 50id. However, it reaches the tube winding portion 51o of the outer heat transfer coil 50od and the tube winding portion 51i of the inner heat transfer coil 50ia without greatly reducing the flow velocity. Therefore, it is preferable to avoid a situation in which the amount of brine that is heat exchanged with hydrogen gas per unit time in the tube winding part 51o of the outer heat transfer coil 50od and the tube winding part 51i of the inner heat transfer coil 50ia is reduced. Is done.

  In addition, the brine in a state where turbulent flow is generated due to the existence of the “non-overlapping portion” on the upstream side reaches the outer heat transfer coil 50od and the inner heat transfer coil 50ia by reaching the flow rate without greatly reducing the flow velocity. Since the state of turbulent flow is maintained, the brine moves straight around the tube winding portion 51o of the outer heat transfer coil 50od and the tube winding portion 51i of the inner heat transfer coil 50ia, so that the tube winding is performed. The situation of passing through the sections 51o and 51i, that is, the situation where the heat exchange efficiency between the brine and hydrogen gas in the outer heat transfer coil 50od and the inner heat transfer coil 50ia is preferably avoided.

  Accordingly, the brine preferably comes into contact with all the pipes in the pipe winding part 51o of the outer heat transfer coil 50od, and also for all the pipes in the pipe winding part 51i of the inner heat transfer coil 50ia. Even so, as a result of the favorable contact of the brine, the hydrogen gas is suitably cooled.

  Moreover, the brine which cooled the hydrogen gas in the tube winding part 51o of the outer heat transfer coil 50od and the tube winding part 51i of the inner heat transfer coil 50ia is the tube winding part 51o of the outer heat transfer coil 50od, And the inside of the container body 40 is further moved in the direction of arrow A so as to be pushed up by a new brine flowing into the tube winding part 51i of the inner heat transfer coil 50ia, and the outer heat transfer coil 50oc and the inner heat transfer coil Reach 50ib. Thereby, hydrogen gas in the outer heat transfer coil 50oc (hydrogen gas introduced from the hydrogen gas introduction portion 46 and flowing through the hydrogen gas flow path L50c) and hydrogen gas in the inner heat transfer coil 50ib (hydrogen gas introduction portion) These hydrogen gases are cooled by heat exchange with the hydrogen gas introduced from 46 and flowing through the hydrogen gas flow path L50b.

  In this case, in the heat exchanger 30 for cooling the hydrogen gas of this example, as described above, the outer heat transfer coil 50od of the outer heat transfer coil 50od and the outer heat transfer arranged above the outer heat transfer coil 50od. The tube winding part 51o of the coil 50oc is arranged so that a "non-overlapping part" is generated, and the tube winding part 51i of the inner heat transfer coil 50ia and the upper side of the inner heat transfer coil 50ia are arranged. And the tube winding part 51i of the inner heat transfer coil 50ib arranged in such a manner that a “non-overlapping part” is generated.

  For this reason, in the heat exchanger 30 for cooling the hydrogen gas of this example, the “non-overlapping portion” of the lowermost tube in the tube winding portion 51o of the outer heat transfer coil 50oc and the tube of the inner heat transfer coil 50ib. The brine that rises in the heat exchange processing space S is preferably brought into contact with the lowermost “non-overlapping portion” of the winding portion 51i. Further, the brine moves in contact with the lowermost “non-overlapping portion” of the tube winding portions 51o and 51i, so that the movement direction of the brine is changed (warped from the direction of going straight upward). The situation where the brine goes straight upward around the tube winding part 51o of the heat coil 50oc and the tube winding part 51i of the inner heat transfer coil 50ib and passes through the tube winding parts 51o and 51i, that is, the outer transmission. A situation in which the heat exchange efficiency between the brine and the hydrogen gas in the heat coil 50oc and the inner heat transfer coil 50ib is suitably avoided.

  Thereby, the brine rising in the heat exchange processing space S is suitable not only for the lowermost tube body in the tube winding portion 51o of the outer heat transfer coil 50oc but also for the tube body above the lowermost portion. As a result of abutting and suitably abutting not only on the lowermost tube in the tube winding portion 51i of the inner heat transfer coil 50ib but also on the tube above the lowermost portion, the hydrogen gas is suitably cooled. Is done. Further, as described above, since the flow velocity of the brine is increased on the upstream side of the outer heat transfer coil 50oc and the inner heat transfer coil 50ib, the tube winding portion 51o and the inner heat transfer of the outer heat transfer coil 50oc are increased. A situation in which the amount of brine that is heat-exchanged with hydrogen gas per unit time in the tube winding part 51i of the coil 50ib is also suitably avoided.

  Furthermore, in the heat exchanger 30 for cooling hydrogen gas of the present example, the tube winding part 51o of each outer heat transfer coil 50o and the tube winding part 51i of each inner heat transfer coil 50i are passed through the container. A speed increasing shaft 45 is disposed along the tube length direction at the center of the body 40. Therefore, in the hydrogen gas cooling heat exchanger 30 of this example, the brine introduced into the heat exchange processing space S and moved upward in the cylinder length direction of the container body 40 (in the direction of arrow A shown in FIG. 2). When the speed increasing shaft 45 is reached, the brine flow path is reduced by the cross-sectional area of the speed increasing shaft 45, so that the moving speed is increased. Thereby, in the heat exchanger 30 for cooling hydrogen gas of the present example, the tube winding part 51o of each outer heat transfer coil 50o and the tube winding part 51i of each inner heat transfer coil 50i per unit time. The amount of brine that can be heat exchanged with the hydrogen gas can be sufficiently increased, which makes it possible to cool the hydrogen gas more suitably.

  On the other hand, the hydrogen gas cooled by heat exchange with the brine (hydrogen gas that has passed through the hydrogen gas flow paths L50a to L50d and reached the hydrogen gas discharge unit 47) passes through the hydrogen gas pipe 4c as described above. The brine that has been supplied to the air supply target X and has risen in temperature by cooling the hydrogen gas in the hydrogen gas cooling heat exchanger 30 is collected in the brine tank 12 via the brine pipe 13d. Thereafter, when the supply of hydrogen gas is completed, a supply end signal is output from the main control device of the hydrogen gas supply system 100 to the control unit 16 of the hydrogen gas cooling device 1. Along with this, the control unit 16 ends the hydrogen gas cooling process and starts the above-described brine circulation process by controlling the liquid feed pump 14b (the brine from the brine tank 12 to the hydrogen gas cooling heat exchanger 30). And the above-described processing for maintaining the brine in the brine tank 12 within the specified temperature range is continued.

  Thus, in this heat exchanger 30 for cooling a hydrogen gas, each outer heat transfer coil 50o is in the cylinder length direction so that the winding axis direction of the tube winding portion 51o is along the cylinder length direction of the container body 40, respectively. And the inner heat transfer coils 50i are arranged in the cylinder length direction so that the winding axis direction of the tube winding part 51i is along the cylinder length direction of the container body 40, respectively. Along with being accommodated in the container body 40, a part of the tube winding part 51o in the outer heat transfer coil 50ob is overlapped in the tube length direction with respect to the tube winding part 51o in the outer heat transfer coil 50oa. "Non-overlapping part" that does not overlap, a part of the tube winding part 51o in the outer heat transfer coil 50od does not overlap in the tube length direction with respect to the tube winding part 51o in the outer heat transfer coil 50oc, Inner heat transfer coil 50 “Non-overlapping portion” in which a part of the tubular body winding portion 51i in c does not overlap with the tubular body winding portion 51i in the inner heat transfer coil 50id in the tube length direction, and the tubular body winding in the inner heat transfer coil 50ia The outer heat transfer coils 50o and the inner heat transfer coils 50i are formed so that a “non-overlapping portion” in which a part of the portion 51i does not overlap with the tubular body winding portion 51i in the inner heat transfer coil 50ib in the cylinder length direction is generated. Has been placed.

  Therefore, according to the heat exchanger 30 for cooling the hydrogen gas, the brine that is going to go straight along the cylinder length direction of the container body 40 abuts on the “non-overlapping portion”, so that the “non-overlapping portion” Not only can the heat exchange with the hydrogen gas be suitably performed, but also the contact of the “non-overlapping portion” causes the movement direction of the brine to be deflected from the tube length direction of the container body 40, resulting in turbulent flow. The brine can be suitably brought into contact with not only the most upstream tube in the turning portions 51o and 51i but also each tube downstream of the most upstream tube. Since heat exchange with the hydrogen gas in 51o, 51i can be carried out suitably, heat exchange with the hydrogen gas in the tube winding parts 51o, 51i can be carried out more suitably. As a result, it is possible to sufficiently improve the heat exchange efficiency between hydrogen gas and brine without providing a propeller or the like that causes a rise in parts cost or assembly cost or requires a large `` container body ''. The manufacturing cost can be sufficiently reduced and the size can be sufficiently reduced. Further, since a motor or the like for rotating the propeller becomes unnecessary, the running cost can be sufficiently reduced.

  Moreover, in this heat exchanger 30 for cooling a hydrogen gas, the winding shape of the tube winding part 51o is the same non-circular shape (in this example, a substantially rounded square), and in the tube winding part 51o. Each tube winding part 51o is configured such that the winding diameters of the maximum diameter part are equal to each other, and an imaginary line along the radial direction of the maximum diameter part of the tube winding part 51o in the outer heat transfer coil 50ob ( The alternate long and short dash lines L1 and L2) in FIG. 9 and the imaginary lines along the radial direction of the maximum diameter portion of the tube winding portion 51o in the outer heat transfer coil 50oa (the alternate long and short dash lines L3 and L4 in FIG. 9) intersect. The outer heat transfer coils 50ob, 50oa are disposed on the outer heat transfer coil 50a, a "non-overlapping portion" is provided, and an imaginary line along the radial direction of the maximum diameter portion of the tubular body winding portion 51o in the outer heat transfer coil 50od (FIG. 10). Dash-dot line L3, L4) in The outer heat transfer coils 50od and 50oc are arranged so that the virtual lines (alternate long and short dashed lines L1 and L2 in FIG. 10) along the radial direction of the maximum diameter portion of the tube winding portion 51o in the outer heat transfer coil 50oc intersect. Thus, a “non-overlapping portion” is provided.

  Further, in this heat exchanger 30 for cooling a hydrogen gas, the tube winding part 51i has an equal non-circular shape (in this example, a rounded substantially square shape), and the tube winding part 51i has the same winding shape. Each tube winding portion 51i is configured such that the winding diameters of the maximum diameter portions are equal to each other, and an imaginary line along the radial direction of the maximum diameter portion of the tube winding portion 51i in the inner heat transfer coil 50ic ( The alternate long and short dash lines L3 and L4) in FIG. 9 and the virtual lines along the radial direction of the maximum diameter portion of the tubular body winding portion 51i in the inner heat transfer coil 50id (the alternate long and short dash lines L1 and L2 in FIG. 9) intersect. The inner heat transfer coils 50ic and 50id are arranged on the inner heat transfer coils 50ic and 50id to provide a "non-overlapping portion", and an imaginary line along the radial direction of the maximum diameter portion of the tubular body winding portion 51i in the inner heat transfer coil 50ia (FIG. 10). Dash-dot line L1, L2) in FIG. The inner heat transfer coils 50ia and 50ib are arranged so that the virtual lines (alternate long and short dashed lines L3 and L4 in FIG. 10) along the radial direction of the maximum diameter portion of the tube winding portion 51i in the side heat transfer coil 50ib intersect. Thus, a “non-overlapping portion” is provided.

  Therefore, according to the heat exchanger 30 for cooling the hydrogen gas, the outer winding coils 50o and 50o having the same winding shape and winding diameter of the tube winding portion 51o and the winding shape and winding of the tube winding portion 51i are used. Since the inner heat transfer coils 50i, 50i having the same diameter are used, and the “non-overlapping portion” can be generated only by changing the arrangement angle thereof, the winding shape and the winding diameter of the “tubular winding portion” The manufacturing cost can be further reduced as compared with a configuration in which a plurality of types of “heat transfer coils” having different values are manufactured to generate “non-overlapping portions”.

  Further, in the heat exchanger 30 for cooling hydrogen gas, the tube winding part 51o of the outer heat transfer coil 50oa on the downstream side of the outer heat transfer coils 50ob, 50oa provided with the “non-overlapping part”, and the outer side The outer heat transfer coils 50o of the outer heat transfer coil 50od arranged side by side further downstream of the heat transfer coil 50oa overlap each other in the tube length direction of the container body 40 so that a “non-overlapping portion” does not occur. Among the inner heat transfer coils 50 ic and 50 id provided with the “non-overlapping part”, the tube winding part 51 i of the downstream inner heat transfer coil 50 id and the inner heat transfer coil 50 id are arranged. The inner heat transfer coils 50 i of the inner heat transfer coils 50 ia arranged side by side on the further downstream side of the inner heat transfer coils 50 i overlap in the tube length direction of the container body 40 so that a “non-overlapping portion” does not occur. Coil 50i is disposed.

  Therefore, according to the heat exchanger 30 for cooling the hydrogen gas, the flow velocity of the brine that has decreased in the “non-overlapping portion” provided on the upstream side can be sufficiently increased. Since the amount of brine to be heat exchanged with the gas can be sufficiently increased, hydrogen gas, brine, and the like in the tube winding part 51o of the outer heat transfer coil 50od and the tube winding part 51i of the inner heat transfer coil 50ia The situation where the heat exchange efficiency of this falls can be avoided suitably.

  Further, in the heat exchanger 30 for cooling the hydrogen gas, the tubular body winding portion 51o of the upstream outer heat transfer coil 50od of the outer heat transfer coils 50od, 50oc provided with the “non-overlapping portion”, and the outer side The outer heat transfer coils 50oa of the outer heat transfer coils 50oa arranged side by side on the further upstream side of the heat transfer coil 50od overlap each other in the tube length direction of the container body 40 so that a “non-overlapping portion” does not occur. Among the inner heat transfer coils 50ia and 50ib provided with the “non-overlapping portion”, the tube winding portion 51i of the inner heat transfer coil 50ia on the upstream side and the inner heat transfer coil 50ia are arranged. The inner heat transfer coils 50i of the inner heat transfer coils 50id arranged side by side on the upstream side overlap each other in the tube length direction of the container body 40 so that a “non-overlapping portion” does not occur. Coil 50i is disposed.

  Therefore, according to the heat exchanger 30 for cooling the hydrogen gas, the tube winding portion 51o of the outer heat transfer coil 50oc and the tube of the inner heat transfer coil 50ib whose flow velocity decreases due to the presence of the “non-overlapping portion”. Since brine can flow into the body winding part 51i at a sufficient flow rate, hydrogen gas and hydrogen gas can be detected in the tube winding part 51o of the outer heat transfer coil 50oc and the tube winding part 51i of the inner heat transfer coil 50ib. A situation in which the efficiency of heat exchange with brine decreases can be suitably avoided.

  In addition, according to the heat exchanger 30 for cooling the hydrogen gas, the tube winding part 51o and the tube winding part 51i as “heat transfer coils” are arranged for every N = 4 hydrogen gas flow paths L50a to L50d. Each tube winding portion 51o is arranged so that there is at least one “non-overlapping portion”, and each tube winding portion 51i is arranged so that at least one “non-overlapping portion” exists. As a result of the arrangement, the flow of hydrogen gas in the heat exchange treatment space S is compared with a configuration in which only one of the “outer heat transfer coil” and the “inner heat transfer coil” is provided for each “flow path”. Since the path length is sufficiently long, and the heat exchange time between the brine and the hydrogen gas is sufficiently long, the heat exchange between the hydrogen gas and the brine can be more suitably performed.

  Furthermore, according to the heat exchanger 30 for cooling the hydrogen gas, the N = 4 hydrogen gas flow paths L50a to L50d are configured so that the flow path lengths are equal to each other. In configurations with different path lengths, there is a time difference in the time for the hydrogen gas to reach the “fluid merging section”, resulting in a change in the amount of hydrogen gas discharged from the “heat exchanger” per unit time. On the other hand, the time until the hydrogen gas passes through the hydrogen gas flow paths L50a to L50d and reaches the hydrogen gas discharge part 47 by equalizing the flow lengths of the hydrogen gas flow paths L50a to L50d. Therefore, since the hydrogen gas starts to be discharged from the hydrogen gas cooling heat exchanger 30 (hydrogen gas discharge portion 47), the discharge amount can be kept constant until the discharge is completed.

  In addition, according to the heat exchanger 30 for cooling the hydrogen gas, the injection nozzle 43a as an “ejector” is attached to the brine introduction part 43, thereby providing a propeller for stirring and a power source for rotating the propeller. Therefore, since the turbulent flow can be generated simply by ejecting the brine into the heat exchange processing space S, the tube winding portion 51o of the outer heat transfer coil 50ob is not caused without causing an increase in manufacturing cost and running cost. And the situation where the brine goes straight up around the tube winding part 51i of the inner heat transfer coil 50ic and passes through the tube winding parts 51o, 51i can be preferably avoided. In the coil 50ob and the inner heat transfer coil 50ic, it is possible to suitably exchange heat between the brine and the hydrogen gas.

  Further, in the heat exchanger 30 for cooling the hydrogen gas, the hydrogen gas as the “first heat exchange target fluid” and the brine which is an example of the “heat medium liquid” as the “second heat exchange target fluid” are mutually exchanged. It is configured to be capable of heat exchange. Further, the hydrogen gas cooling device 1 includes the hydrogen gas cooling heat exchanger 30 and the refrigeration circuit 11 for cooling the brine, and the brine and hydrogen gas cooled by the refrigeration circuit 11 are used for hydrogen gas cooling. The heat exchanger 30 is configured to be able to cool the hydrogen gas by exchanging heat with each other. Therefore, the hydrogen gas cooling heat exchanger 30 and the hydrogen gas cooling device 1 can sufficiently reduce the hydrogen gas supply cost for the supply target X.

The configurations of the “heat exchanger” and the “hydrogen gas cooling device” are not limited to the configuration examples of the heat exchanger 30 for hydrogen gas cooling and the hydrogen gas cooling device 1 described above. For example, the structure provided with the outer side heat transfer coil 50o provided with the pipe | tube winding part 51o of the substantially square shape in planar view, and the inner side heat transfer coil 50i provided with the pipe | tube winding part 51i of the substantially square shape in plan view is an example. As described above, the winding shape of the “tubular winding portion” is not limited to the above-described substantially square shape, and may be any non-circular shape (for example, a triangle, an arbitrary polygon more than a pentagon, and an ellipse) Shape). Further, the tube winding portions 51o, 51o of the outer heat transfer coils 50o, 50o adjacent in the tube length direction of the container body 40 (tubular portion 41) and the inner heat transfer coils 50i, 51i adjacent in the tube length direction. The configuration in which eight “non-overlapping portions” are generated in each of the tube winding portions 51i and 51i has been described as an example, but both “tube windings” of “heat transfer coils” adjacent in the tube length direction are described. The number of “non-overlapping parts” generated in the “parts” is not limited to this, and can be defined as an arbitrary number.

  In addition, a configuration in which two types of “heat transfer coils”, that is, an outer heat transfer coil 50o and an inner heat transfer coil 50i are disposed in the container body 40 (a configuration in which the “tube winding portion” is disposed in a double ring shape in a plan view. ) As an example, but only one of the “outer heat transfer coil” and “inner heat transfer coil” is arranged, or between the “outer heat transfer coil” and “inner heat transfer coil”. Alternatively, a configuration in which one or more “heat transfer coils” are arranged (a configuration in which the “tubular winding portion” is arranged in an annular shape that is not less than a triple ring in plan view) may be employed. Furthermore, the configuration of the hydrogen gas cooling heat exchanger 30 having N = 4 hydrogen gas flow paths L50a to L50d has been described as an example, but N = 2 or N = 3 “flow paths”. And a configuration having N = 5 or more “flow paths” may be employed.

  In addition, the tube winding portions 51o and 51o of the outermost heat transfer coil 50ob at the most upstream portion in the moving direction of the brine and the outer heat transfer coil 50oa downstream thereof are arranged so as to generate “non-overlapping portions”. As an example, a configuration in which the tube winding portions 51i and 51i of the innermost heat transfer coil 50ic in the most upstream portion in the moving direction of the brine and the inner heat transfer coil 50id downstream thereof are arranged so that "non-overlapping portions" are generated. As explained, both the “tube winding part” of the “heat transfer coil” at the most upstream part and the “heat transfer coil” downstream from it are overlapped in the tube length direction of the “container body” to produce a “non-overlapping part”. It can be arranged so that there is no. By adopting such a configuration, the brine that is in a state in which it is difficult to go straight in the cylinder length direction of the “container” due to the turbulent flow generated immediately after being introduced into the “container”, the uppermost stream portion The situation in which the flow velocity is greatly reduced in can be suitably avoided.

  Further, the brine introduction part 43 is disposed in the lower part of the container body 40 and the brine discharge part 44 is disposed in the upper part of the container body 40 so that the brine flows in the container body 40 from below to above. Although the configuration has been described as an example, instead of such a configuration, a configuration in which the “second heat exchange target fluid (such as brine)” flows from the upper side to the lower side of the “container body” may be employed. Yes (not shown). When such a configuration is adopted, a configuration is adopted in which the “first heat exchange target fluid (hydrogen gas, etc.)” flows through the “tubular winding portion” of the “heat transfer coil” from below to above. By doing so, it is preferable that the “first heat exchange target fluid” and the “second heat exchange target fluid” are caused to flow in opposite directions in the same manner as the hydrogen gas cooling heat exchanger 30 described above. Further, it is also possible to employ a configuration in which the “heat exchanger” is laid down so that the “first heat exchange target fluid” and the “second heat exchange target fluid” move in the horizontal direction (not shown). .

  Furthermore, in the “container body” constituted by the tubular portion 41 and the lid portions 42b and 42t, the tube winding portions 51o of the respective outer heat transfer coils 50o and the tube winding portions 51i of the respective inner heat transfer coils 50i. In addition, the configuration of the container body 40 in which the speed increasing shaft 45 is accommodated has been described as an example, but a “container body” may be configured without accommodating the speed increasing shaft 45.

  In addition, the configuration in which the brine that is an example of the “heating medium liquid” is cooled by the refrigeration circuit 11 that is an example of the “unified refrigeration circuit” has been described as an example, but the evaporation of the first refrigeration circuit (the high temperature side refrigeration circuit). The condenser of the second refrigeration circuit (low temperature side refrigeration circuit) is cooled by the condenser to condense a sufficient amount of the refrigerant in the condenser of the second refrigeration circuit in a short time, and the evaporator of the second refrigeration circuit " It is also possible to adopt a “two-way refrigeration circuit” that can lower the temperature of the “heat transfer fluid” to a sufficiently low temperature suitable for cooling hydrogen gas by cooling the “heat transfer fluid” (not shown) .

  Furthermore, hydrogen gas that cools the hydrogen gas by heat exchange between hydrogen gas, which is an example of “first heat exchange target fluid”, and brine, which is an example of “second heat exchange target fluid”, as “heat medium liquid” The cooling device 1 (hydrogen gas cooling heat exchanger 30) has been described as an example. However, the fluid to be exchanged with each other by the “heat exchanger” is not limited to hydrogen gas or brine, and may be any gas. Or any liquid can exchange heat with each other. Further, the use of the “heat exchanger” is not limited to cooling of an arbitrary fluid, and can be used for the purpose of heating an arbitrary fluid.

DESCRIPTION OF SYMBOLS 100 Hydrogen gas supply system 1 Hydrogen gas cooling device 11 Refrigeration circuit 30 Heat exchanger for hydrogen gas cooling 40 Container body 41 Cylindrical part 42b, 42t Lid part 43 Brine introduction part 43a Blowing nozzle 44 Brine discharge part 45 Speed increasing shaft 46 Hydrogen gas introduction part 47 Hydrogen gas discharge part 50ia-50id Inner heat transfer coil 50oa-50od Outer heat transfer coil 51i, 51o Tube winding part 61ad, 61ba-61bc, 63ad, 63bb, 63cb, 63db Hydrogen gas piping L1 L4 Dash-dot line L50a to L50d Hydrogen gas flow path S Heat exchange space X Air supply target

Claims (8)

A heat transfer coil having a tube winding portion in which a tube capable of passing the first heat exchange target fluid is spirally wound, and a cylindrical shape capable of passing the second heat exchange target fluid are formed. And a heat exchanger configured such that the first heat exchange target fluid and the second heat exchange target fluid can exchange heat with each other in the container. And
A fluid branching section for branching the flow path of the first heat exchange target fluid into N (N is a natural number of 2 or more) flow paths; and a fluid merging section for joining the N flow paths; The heat transfer coil is disposed for each of the N channels,
Each of the heat transfer coils has a non-circular shape in which the winding shapes of the tube winding portions are equal to each other, and the winding diameters of the maximum diameter portions in the tube winding portions are equal to each other. The body winding part is housed in the container side by side along the cylinder length direction so that the winding axis direction of the body winding part is along the cylinder length direction of the container body, and two adjacent in the cylinder length direction. At least one non-overlapping part in which a part of the tube winding part in one of the heat transfer coils does not overlap in the tube length direction with respect to the tube winding part in the other of the two adjacent heat transfer coils. Arranged so as to occur at a location , and when viewed along the tube length direction of the container body, along the radial direction of the maximum diameter portion of the tubular body winding portion in one of the two adjacent heat transfer coils. Imaginary line and the two adjacent heat transfer carp Heat exchange with the virtual line along the radial direction of the maximum diameter of the tubular body winding portion on the other is the by the Ryoden'netsu coil is arranged non-overlapping portion is provided so as to intersect vessel. N = 3 or more of the heat transfer coils are accommodated in the container along the cylinder length direction,
Of the two adjacent heat transfer coils provided with the non-overlapping part, the tube winding part of the heat transfer coil on the downstream side in the moving direction of the second heat exchange target fluid, and the downstream side claim 1 Symbol disposed such that the non-overlapping portion further has said tube winding section of the heat transfer coils arranged side by side to the downstream side overlap in the tube length direction of the heat transfer coil does not occur The listed heat exchanger. N = 3 or more of the heat transfer coils are accommodated in the container along the cylinder length direction,
Of the two adjacent heat transfer coils provided with the non-overlapping portion, the tubular body winding portion of the heat transfer coil on the upstream side in the moving direction of the second heat exchange target fluid, and the upstream side claim 1 or are arranged such that the non-overlapping portion further said tube winding section of the heat transfer coils arranged side by side on the upstream side overlaps in the tube length direction of the heat transfer coil does not occur 2. The heat exchanger according to 2 . An outer heat transfer coil as the heat transfer coil and an inner heat transfer coil as the heat transfer coil arranged inside the outer heat transfer coil are provided for each of the N flow paths, and the non-overlapping portion any but with said respective outer heat transfer coil such that there is at least one position is arranged, the non-overlapping portions of claims 1, said respective inner heat transfer coil such that there is at least one location is arranged 3 The heat exchanger according to crab. The heat exchanger according to any one of claims 1 to 4 , wherein the N channels are configured to have the same channel length. The heat exchanger according to any one of claims 1 to 5 , wherein an ejector is attached to a fluid introduction part that introduces the second heat exchange target fluid into the container body. The heat exchange according to any one of claims 1 to 6 , wherein the hydrogen gas as the first heat exchange target fluid and the heat transfer fluid as the second heat exchange target fluid are configured to be able to exchange heat with each other. vessel. A heat exchanger according to claim 7 , and a refrigeration circuit for cooling the heat transfer fluid,
A hydrogen gas cooling device configured to be capable of cooling the hydrogen gas by mutually exchanging heat in the heat exchanger and the hydrogen gas cooled by the refrigeration circuit.

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