WO2017126580A1 - 冷却水素供給ステーション及び水素冷却装置 - Google Patents
冷却水素供給ステーション及び水素冷却装置 Download PDFInfo
- Publication number
- WO2017126580A1 WO2017126580A1 PCT/JP2017/001658 JP2017001658W WO2017126580A1 WO 2017126580 A1 WO2017126580 A1 WO 2017126580A1 JP 2017001658 W JP2017001658 W JP 2017001658W WO 2017126580 A1 WO2017126580 A1 WO 2017126580A1
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- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- hydrogen
- cooling
- heat exchanger
- path
- Prior art date
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- 239000001257 hydrogen Substances 0.000 title claims abstract description 219
- 229910052739 hydrogen Inorganic materials 0.000 title claims abstract description 219
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 title claims abstract description 207
- 238000001816 cooling Methods 0.000 title claims abstract description 149
- 239000003507 refrigerant Substances 0.000 claims abstract description 251
- 238000001514 detection method Methods 0.000 claims description 28
- 239000007788 liquid Substances 0.000 claims description 14
- 150000002431 hydrogen Chemical class 0.000 claims description 12
- 230000007246 mechanism Effects 0.000 claims description 10
- WFIZEGIEIOHZCP-UHFFFAOYSA-M potassium formate Chemical compound [K+].[O-]C=O WFIZEGIEIOHZCP-UHFFFAOYSA-M 0.000 claims description 7
- KYKAJFCTULSVSH-UHFFFAOYSA-N chloro(fluoro)methane Chemical group F[C]Cl KYKAJFCTULSVSH-UHFFFAOYSA-N 0.000 claims description 6
- 230000003247 decreasing effect Effects 0.000 claims description 6
- 238000007599 discharging Methods 0.000 claims description 6
- 230000000630 rising effect Effects 0.000 claims description 5
- 239000000446 fuel Substances 0.000 description 19
- 230000000694 effects Effects 0.000 description 8
- 239000007789 gas Substances 0.000 description 7
- 239000012267 brine Substances 0.000 description 6
- HPALAKNZSZLMCH-UHFFFAOYSA-M sodium;chloride;hydrate Chemical compound O.[Na+].[Cl-] HPALAKNZSZLMCH-UHFFFAOYSA-M 0.000 description 6
- 238000005265 energy consumption Methods 0.000 description 4
- 239000007864 aqueous solution Substances 0.000 description 3
- 239000002826 coolant Substances 0.000 description 3
- 239000000498 cooling water Substances 0.000 description 3
- 230000007797 corrosion Effects 0.000 description 3
- 238000005260 corrosion Methods 0.000 description 3
- 238000011161 development Methods 0.000 description 3
- 230000018109 developmental process Effects 0.000 description 3
- 238000009434 installation Methods 0.000 description 3
- 238000009833 condensation Methods 0.000 description 2
- 230000005494 condensation Effects 0.000 description 2
- 230000008602 contraction Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 231100001261 hazardous Toxicity 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000008021 deposition Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000009897 systematic effect Effects 0.000 description 1
- 230000008685 targeting Effects 0.000 description 1
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- F17C5/00—Methods or apparatus for filling containers with liquefied, solidified, or compressed gases under pressures
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/70—Energy storage systems for electromobility, e.g. batteries
Definitions
- the present invention relates to a cooling hydrogen supply station for supplying cooling hydrogen to a fuel cell vehicle or the like, and a hydrogen cooling device used in the cooling hydrogen supply station.
- Fuel cell vehicles that use hydrogen as fuel are superior in terms of environment because they do not emit exhaust gas. Accordingly, various developments have been promoted in recent years in order to widely spread such fuel cell vehicles. Development of the vehicle itself is important for the spread of fuel cell vehicles, but the development of a hydrogen supply station for supplying hydrogen to the fuel cell vehicles is also important.
- the present applicant has already obtained a patent (see Japanese Patent No. 5632065).
- the cooling hydrogen supply station of the patent can realize sufficiently efficient cooling with high accuracy.
- a water-cooled refrigerator unit is employed for cooling the first refrigerant.
- the inventor of the present invention has intensively studied to replace this with an air-cooled condenser that obtains a cooling action by driving an air-cooling fan.
- the present inventor has also intensively studied to obtain an energy saving effect by adopting inverter control for drive control of the air cooling fan.
- An object of the present invention is to employ a cooling hydrogen supply station that employs an air-cooled condenser that drives an air-cooling fan by inverter control, and that can realize sufficiently high-efficiency cooling with respect to hydrogen, preferably with high accuracy, and
- the present invention provides a hydrogen cooling device used in the cooling hydrogen supply station.
- the present invention is provided for a first refrigerant path through which a first refrigerant is circulated and a part of the first refrigerant path, and enables cooling of the first refrigerant by driving an air cooling fan.
- a first heat exchanger that enables cooling of the second refrigerant; a pressure detection sensor that detects a pressure of the first refrigerant from the air-cooled condenser to the first heat exchanger; Based on the pressure detected by the pressure detection sensor, an inverter controller for controlling the number of revolutions of the air cooling fan to maintain the pressure within a range of 1.5 MPa to 1.7 MPa, and hydrogen storage Hydrogen storage unit and hydrogen stored in the hydrogen storage unit are transported And a second heat exchanger that enables cooling of the hydrogen by the second refrigerant between the other part of the second refrigerant path and a part of the hydrogen channel.
- the inverter type controller increases or maintains the driving rotational speed of the air cooling fan while the pressure detected by the pressure detection sensor is rising or at a high level, and the pressure detection sensor As long as the pressure detected by the air pressure decreases or is at a low level, the driving speed of the air cooling fan is decreased or maintained at a low level, and the first refrigerant is chlorofluorocarbon.
- the second refrigerant is an aqueous potassium formate solution, and the flow rate of the second refrigerant in the second refrigerant path is 135 L / min to 165 L / min at a flow pressure of 0.3 MPa, and the hydrogen is , In the second heat exchanger Thus, the hydrogen is cooled to within a temperature range of ⁇ 43 ° C.
- the hydrogen passage is provided with a discharge port for discharging hydrogen after being cooled by the second heat exchanger, and the amount of hydrogen discharged from the discharge port is 4.5 kg / 3 min to 5. It is a cooling hydrogen supply station characterized by being 5 kg / 3 min.
- the hydrogen cooling capacity is 13.5 kW to 16.5 kW when cooling hydrogen to ⁇ 40 ° C. (13.5 kW @ ⁇ 40 ° C. to 16.5 kW @ ⁇ 40 ° C.), hydrogen cooling can be realized with high efficiency, that is, extremely energy saving.
- the hydrogen is cooled by the second heat exchanger within an error range of + 2 ° C. to ⁇ 3 ° C. with respect to a set temperature within a temperature range of ⁇ 43 ° C. to ⁇ 20 ° C. . That is, according to the cooling hydrogen supply station developed by the present inventors, the cooling accuracy within the error range of + 2 ° C. to ⁇ 3 ° C. with respect to the set temperature within the temperature range of ⁇ 43 ° C. to ⁇ 20 ° C. As a result, sufficiently efficient cooling of hydrogen can be realized with high accuracy.
- the cooling hydrogen supply station is provided with a discharge port for discharging hydrogen after being cooled by the second heat exchanger in the hydrogen flow path, and the amount of hydrogen discharged from the discharge port is 4.5 kg / 3 min to 5.5 kg / 3 min.
- a hydrogen supply amount it is possible to supply hydrogen to at least one fuel cell vehicle in 3 minutes (the current hydrogen capacity of a normal fuel cell vehicle is 5 kg).
- the first refrigerant is chlorofluorocarbon
- the second refrigerant is a potassium formate aqueous solution, specifically, cold brine manufactured by Showa Co., Ltd., thereby realizing each of the aforementioned performances. The inventor has confirmed that this is possible.
- the pressure detected by the pressure detection sensor is rising or at a high level (during so-called high load, for example, during the temperature drop of the first refrigerant during initial operation or by the second heat exchanger) While cooling with hydrogen), while the driving speed of the air cooling fan is set to 57.5 Hz, while the pressure detected by the pressure detection sensor is decreasing or at a low level (so-called low load, for example, idling), air cooling is performed.
- the fan rotation speed at 32.9 Hz, an effective energy saving effect can be obtained.
- the condensation pressure of the first refrigerant is also stabilized within the range of 1.5 MPa to 1.7 MPa. 1 refrigerant can always be used in a stable state (see FIG. 3).
- the air cooling fan since the air cooling fan needs to be arranged in a state exposed to the outside air, it needs to have an explosion-proof structure against hydrogen.
- explosion-proof structure against hydrogen safety explosion-proofing can be given as an explosion-proof electrical equipment standard that can be used in hazardous areas where hydrogen exists.
- the cooling hydrogen supply station includes a valve for controlling the circulation amount of the first refrigerant passing through the air-cooled condenser, and immediately after passing through the first heat exchanger in the second refrigerant path.
- a temperature sensor that detects the temperature of the second refrigerant
- a temperature feedback control unit that controls the valve based on a detection result of the temperature sensor.
- the second refrigerant can be controlled to a desired temperature with high accuracy by simple temperature feedback control.
- the opening degree of the valve can be operated with an upper limit of 40% or more, for example, 50%, and the temperature of the second refrigerant When the temperature is ⁇ 40 ° C. or lower, the opening of the valve can be operated at a lower limit of 10%, for example, 20-30%.
- the valve is, for example, an electronic expansion valve.
- the output of the compressor is also 60 More preferably, it is reduced to ⁇ 80%.
- the output of the compressor may be reduced to 70%, and the opening of the valve may be reduced to 12.8%.
- a hot gas bypass passage that bypasses the air-cooled condenser in the first refrigerant passage, and a second valve that controls the circulation amount of the first refrigerant in the hot gas bypass passage are further provided,
- the opening degree of the two valves is preferably set to 100%.
- the cooling hydrogen supply station is operated by selecting either the first operation mode or the second operation mode.
- the hydrogen In the first operation mode, the hydrogen is cooled to ⁇ 20 ° C.
- the hydrogen In the second operation mode, the hydrogen is preferably cooled to ⁇ 40 ° C.
- the first operation mode corresponding to the idle operation state is selected, and when the necessity is high, the second operation mode corresponding to the standby state is selected.
- energy consumption related to cooling can be effectively suppressed.
- the selection of the first operation mode or the second operation mode may be automatically performed according to a time zone.
- the first operation mode is selected in the nighttime period when the necessity for hydrogen supply is low (for example, outside business hours), and in the daytime period (for example, during business hours) when the necessity for hydrogen supply is high.
- the second operation mode it is possible to effectively suppress the energy consumption related to cooling in the night time zone where the necessity of hydrogen supply is low.
- the second refrigerant path further includes a tank portion, and the tank portion maintains the liquid level of the second refrigerant in the tank portion within a predetermined range.
- the refrigerant quantity adjusting mechanism may be connected.
- the second refrigerant by maintaining the liquid level of the second refrigerant in the tank within a predetermined range, a highly corrosive liquefied refrigerant is used as the second refrigerant, and the second refrigerant expands as the temperature changes. Even if it shrinks, it is possible to prevent the corrosion of the inner wall of the tank portion and the deposition of deposits due to the rise and fall of the liquid level of the second refrigerant.
- the present invention is also a hydrogen cooling device for cooling hydrogen conveyed in the hydrogen flow path, wherein the first refrigerant path through which the first refrigerant is circulated and a part of the first refrigerant path.
- An air-cooled condenser provided to drive the air-cooling fan to enable the cooling of the first refrigerant, a second refrigerant path through which the second refrigerant flows, and another one of the first refrigerant paths.
- a first heat exchanger that enables cooling of the second refrigerant by the first refrigerant between a portion and a part of the second refrigerant path, and the first heat exchanger from the air-cooled condenser Based on the pressure detection sensor for detecting the pressure of the first refrigerant during the period up to and the pressure detected by the pressure detection sensor, the pressure is maintained in the range of 1.5 MPa to 1.7 MPa.
- An inverter type controller for controlling the rotational speed of the air cooling fan by inverter, and the second A second heat exchanger that enables cooling of the hydrogen by the second refrigerant between the other part of the medium passage and a part of the hydrogen passage, and the first refrigerant comprises:
- the second refrigerant is a potassium formate aqueous solution, and the flow rate of the second refrigerant in the second refrigerant path is 135 L / min to 165 L / min at a flow pressure of 0.3 MPa.
- the hydrogen is cooled to a temperature range of ⁇ 43 ° C. to ⁇ 20 ° C. by the second heat exchanger, and the hydrogen is ⁇ 43 ° C. by the second heat exchanger.
- the temperature is cooled within an error range of + 2 ° C. to ⁇ 3 ° C. with respect to a set temperature within a temperature range of ⁇ 20 ° C., and the hydrogen cooling capacity is 13 when cooling hydrogen to ⁇ 40 ° C. 0.5 kW to 16.5 kW, and the hydrogen flow path includes the second A discharge port for discharging hydrogen after being cooled by the exchanger is provided, and the amount of hydrogen discharged from the discharge port is 4.5 kg / 3 min to 5.5 kg / 3 min. Hydrogen cooling device.
- the hydrogen cooling capacity is 13.5 kW to 16.5 kW when hydrogen is cooled to ⁇ 40 ° C., so that the cooling of hydrogen is highly efficient, that is, extremely energy saving. Can be realized.
- the hydrogen is cooled by the second heat exchanger within an error range of + 2 ° C. to ⁇ 3 ° C. with respect to a set temperature within a temperature range of ⁇ 43 ° C. to ⁇ 20 ° C. . That is, according to the cooling hydrogen supply station developed by the present inventors, the cooling accuracy within the error range of + 2 ° C. to ⁇ 3 ° C. with respect to the set temperature within the temperature range of ⁇ 43 ° C. to ⁇ 20 ° C. As a result, sufficiently efficient cooling of hydrogen can be realized with high accuracy.
- the cooling hydrogen supply station is provided with a discharge port for discharging hydrogen after being cooled by the second heat exchanger in the hydrogen flow path, and the amount of hydrogen discharged from the discharge port is 4.5 kg / 3 min to 5.5 kg / 3 min.
- a hydrogen supply amount it is possible to supply hydrogen to at least one fuel cell vehicle in 3 minutes (the current hydrogen capacity of a normal fuel cell vehicle is 5 kg).
- the first refrigerant is chlorofluorocarbon
- the second refrigerant is an aqueous potassium formate solution, specifically a cold brine manufactured by Showa Co., Ltd. The present inventors have confirmed that this can be realized.
- FIG. 1 is a system diagram of a cooling hydrogen supply station 1 according to an embodiment of the present invention
- FIG. 2 is a schematic perspective view of a hydrogen cooling device 20 in the cooling hydrogen supply station 1.
- the cooling hydrogen supply station 1 includes a hydrogen storage unit 11 in which hydrogen is stored, and a hydrogen flow path 12 through which the hydrogen stored in the hydrogen storage unit 11 is conveyed. .
- the downstream end of the hydrogen flow path 12 serves as a discharge port 13 (generally, a filling nozzle), and hydrogen is supplied from the discharge port 13 to the fuel supply port of the fuel cell vehicle.
- the discharge port 13 and the fuel supply port of the fuel cell vehicle are connected in an airtight manner.
- Compressed hydrogen is stored in the hydrogen storage unit 11 of the present embodiment. Accordingly, hydrogen in a compressed state is supplied into the hydrogen flow path 12.
- the amount of hydrogen discharged from the discharge port 13 is 4.5 kg / 3 min to 5.5 kg / 3 min, particularly 5.0 kg / min. , The compressed state is adopted.
- the cooling hydrogen supply station 1 is provided for a first refrigerant path 21 through which the first refrigerant is circulated and a part of the first refrigerant path 21 and drives an air cooling fan 22f.
- the air-cooled condenser 22 that enables the cooling of the first refrigerant
- the second refrigerant path 23 through which the second refrigerant flows and another part of the first refrigerant path 21 (the air-cooled condenser 22
- a first heat exchanger 24 that allows the second refrigerant to be cooled by the first refrigerant between the second refrigerant passage 23 and a part of the second refrigerant path 23.
- the direction of circulation of the first refrigerant in the first refrigerant path 21 is as shown by the arrow in FIG. That is, it is cooled by the air-cooled condenser 22 and then passes through the first heat exchanger 24 and returns to the air-cooled condenser 22 again.
- a compressor 25 is provided in a portion of the first refrigerant path 21 from the first heat exchanger 24 to the air-cooled condenser 22.
- a pressure detection sensor 26 is provided to detect the pressure (condensation pressure) of the first refrigerant from the air-cooled condenser 22 to the first heat exchanger 24. Then, based on the pressure detected by the pressure detection sensor 26, the rotational speed of the air cooling fan 22f is maintained so that the pressure is maintained in the range of 1.5 MPa to 1.7 MPa (targeting 1.6 MPa).
- An inverter type controller 27 for controlling the inverter is provided. Specifically, as shown in FIGS. 3 and 5, the inverter type controller 27 of the present embodiment operates while the pressure detected by the pressure detection sensor 26 is rising or at a high level (at the time of initial operation).
- the drive rotation speed of the air cooling fan is set to 57.5 Hz, while being detected by the pressure detection sensor 26 While the pressure is decreasing or at a low level (during idling), the driving speed of the air cooling fan is kept at 32.9 Hz.
- an electronic expansion valve 28 is provided between the pressure detection sensor 26 and the first heat exchanger 24 as a valve for controlling the circulation amount of the first refrigerant passing through the air-cooled condenser 22.
- a temperature sensor 29 is provided to detect the temperature of the second refrigerant immediately after passing through the first heat exchanger in the second refrigerant path 23, and the electronic expansion valve is based on the detection result of the temperature sensor 29.
- a temperature feedback control unit 30 for controlling the control unit 28 is provided.
- a hot gas bypass passage 31 that bypasses the air-cooled condenser 22 in the first refrigerant passage 21 and a second valve 32 that controls the circulation amount of the first refrigerant in the hot gas bypass passage 31 are further provided. It has been.
- the second refrigerant cools the hydrogen.
- the 2nd heat exchanger 40 which enables is provided.
- the second heat exchanger 40 cools hydrogen before reaching the discharge port 13 in the hydrogen flow path 12.
- the second refrigerant path 23 includes a part of the second refrigerant path 23 in which heat exchange is performed with the other part of the first refrigerant path 21 by the first heat exchanger 24.
- a second half passage including the other part of the second refrigerant passage 23 in which heat exchange is performed between the first half passage and the second heat exchanger 40 and a part of the hydrogen passage 12;
- a tank portion 23T that connects the flow path to the first half flow path.
- the second refrigerant is stored in the tank portion 23T in a substantially full state, and the pump portion 23p provided in the first-half passage passage causes the first-half passage passage from the tank portion 23T as shown by an arrow in FIG.
- the second refrigerant supplied to the second refrigerant is supplied to the second half flow path after passing through the first heat exchanger 24 and cooled by the first refrigerant, and is supplied to the second half flow path. Is returned to the tank portion 23T after passing through the second heat exchanger 40 and cooling the hydrogen (after the temperature has been raised for the second refrigerant).
- the flow rate of the second refrigerant is 135 L/[email protected] MPa to 165 L/[email protected] MPa (that is, 135 L / min to 165 L / min at a flow pressure of 0.3 MPa),
- the operation of the pump 23p is controlled so as to be 150 L/[email protected] MPa (that is, 150 L / min at a flow pressure of 0.3 MPa).
- the operation of the pump 23p is feedback-controlled based on a flow value (detection result) detected by a flow sensor (not shown) provided as appropriate.
- the temperature of the second refrigerant flowing through the second heat exchanger 40 is adjusted by the control of the electronic expansion valve 28 or the like, so that the hydrogen in the hydrogen flow path 12 is passed through the second heat exchanger 40. Is adjusted to a set temperature set within a temperature range of ⁇ 43 ° C. to ⁇ 20 ° C. Specifically, as shown in FIG. 4, when the temperature of the second refrigerant is higher than ⁇ 40 ° C., the opening of the electronic expansion valve 28 is operated with an upper limit of 40% or more, for example, 50%.
- the temperature of the second refrigerant detected by the temperature sensor 29 is such that the opening degree of the electronic expansion valve 28 is, for example, 20-30% with a lower limit of 10% when the temperature of the refrigerant is -40 ° C. or less. Feedback control is performed based on the value (detected value).
- chlorofluorocarbon is used as one refrigerant that circulates in the first refrigerant passage 21.
- an HFC mixed refrigerant R-404A manufactured by Mitsui DuPont Fluorochemical Co., Ltd. is used. It is used.
- cold brine FP-40 (potassium formate aqueous solution) manufactured by Showa Co., Ltd. is used.
- the second refrigerant, cold brine FP-40 is a liquefied refrigerant and can maintain fluidity in a temperature range of ⁇ 43 ° C. to ⁇ 20 ° C. Further, the cold brine FP-40, which is the second refrigerant, can be expanded and contracted according to the temperature. In the present embodiment, even if such expansion and contraction occur, the second coolant level in the tank unit 23T is set in the tank unit 23T so that the liquid level of the second refrigerant in the tank unit 23T does not rise and fall to cause corrosion.
- a refrigerant amount adjusting mechanism 33 is connected to maintain the liquid level of the refrigerant in a predetermined range (preferably a constant liquid level height).
- the refrigerant amount adjustment mechanism 33 includes an adjustment tank 33A connected to the tank portion 23T and a check valve (not shown).
- the refrigerant amount adjusting mechanism 33 replenishes the tank portion 23T with the second refrigerant from the adjustment tank 33A, so that the liquid level of the second refrigerant is predetermined. The range is to be maintained.
- the refrigerant amount adjusting mechanism 33 discharges the second refrigerant to the outside through the check valve from the tank portion 23T, so that the liquid level of the second refrigerant Is maintained within a predetermined range.
- the hydrogen flow path 12 passing through the hydrogen reservoir 11 and the second heat exchanger 40 constitutes the hydrogen supply dispenser 10 in the cooling hydrogen supply station 1.
- the part excluding the hydrogen storage part 11 and the hydrogen flow path 12 in the cooling hydrogen supply station 1 can be understood as the hydrogen cooling device 20. It can be said that the cooling hydrogen supply station 1 is configured by connecting the hydrogen supply dispenser 10 and the hydrogen cooling device 20 via the second heat exchanger 40.
- the air cooling fan 22f needs to be arranged in a state exposed to the outside air as shown in FIG. For this reason, the air-cooling fan 22f needs to have an explosion-proof structure against hydrogen, and an example of the explosion-proof structure against hydrogen is safety explosion-proof as an explosion-proof electrical equipment standard that can be used in a hazardous area where hydrogen exists. .
- the cooling hydrogen supply station 1 described above employs an air-cooled condenser 22 to cool hydrogen to ⁇ 40 ° C. as a hydrogen cooling capacity by selecting a plurality of refrigerant paths and refrigerant circulating through them.
- 13.5 kW to 16.5 kW (13.5 kW @ ⁇ 40 ° C. to 16.5 kW @ ⁇ 40 ° C.). That is, 13.5 kW to 16.5 kW is realized as a cooling capacity for maintaining hydrogen at ⁇ 40 ° C.
- cooling accuracy of hydrogen cooling is realized within an error range of + 2 ° C. to ⁇ 3 ° C. with respect to a set temperature within a temperature range of ⁇ 43 ° C. to ⁇ 20 ° C.
- the cooling hydrogen supply station 1 is operated by selecting either the first operation mode or the second operation mode.
- hydrogen is ⁇ It is cooled to 20 ° C.
- hydrogen is cooled to ⁇ 40 ° C.
- the selection of the first operation mode or the second operation mode is automatically performed according to the time zone. As an example, in the present embodiment, during the period from 5 pm to 9 am The first operation mode is set, and the time zone other than 5 pm to 9 am is set to be the second operation mode.
- the setting of the time zone in which the first operation mode is selected and the time zone in which the second operation mode is selected can be manually changed.
- a touch panel (not shown) or the like can be provided on the housing 20C of the hydrogen cooling device 20 as shown in FIG. 2 so that an operator can manually operate the touch panel. .
- the selection itself between the first operation mode and the second operation mode may be manually performed.
- the selection of the first operation mode or the second operation mode may be automatically performed according to the outside air temperature.
- the hydrogen supply station 1 is operated by selecting the first operation mode in which hydrogen is cooled to ⁇ 20 ° C. or the second operation mode in which hydrogen is cooled to ⁇ 40 ° C. .
- the operation of the hydrogen supply station 1 in the first operation mode will be described.
- the compressor 25 in the first refrigerant path 21 is driven, and the circulation of the first refrigerant in the first refrigerant path 21 in the direction of the arrow in FIG.
- the pump 23p in the second refrigerant path 23 is driven, and the circulation of the second refrigerant in the direction of the arrow in FIG. 1 is started.
- the first refrigerant circulating in the first refrigerant path 21 passes through the first heat exchanger 24, and the second refrigerant circulating in the second refrigerant path 23 also passes through the first heat exchanger 24.
- the second refrigerant is cooled by the first refrigerant via the first heat exchanger 24. Thereafter, the second refrigerant passes through the second heat exchanger 40 in the second half flow path of the second refrigerant path 23 and returns to the tank portion 23T.
- the temperature of the second refrigerant that has passed through the first heat exchanger 24 is detected by the temperature sensor 29. Then, the temperature feedback control unit 30 controls the electronic expansion valve 28 of the first refrigerant path 21 as necessary according to the difference between the temperature of the second refrigerant detected by the temperature sensor 29 and ⁇ 20 ° C. To do. As described above, the temperature of the second refrigerant is controlled to ⁇ 20 ° C.
- the compressor 25 of the first refrigerant path 21 is driven, and the circulation of the first refrigerant in the first refrigerant path 21 in the direction of the arrow in FIG.
- the pump 23p of the refrigerant path 23 is driven, and the circulation of the second refrigerant in the direction of the arrow in FIG. 1 is started. Accordingly, the first refrigerant circulating in the first refrigerant path 21 passes through the first heat exchanger 24, and the second refrigerant circulating in the second refrigerant path 23 also passes through the first heat exchanger 24.
- the second refrigerant is cooled by the first refrigerant via the first heat exchanger 24. Thereafter, the second refrigerant passes through the second heat exchanger 40 in the second half flow path of the second refrigerant path 23 and returns to the tank portion 23T.
- the temperature of the second refrigerant that has passed through the first heat exchanger 24 is detected by the temperature sensor 29. Then, the temperature feedback control unit 30 controls the electronic expansion valve 28 of the first refrigerant path 21 as necessary according to the difference between the temperature of the second refrigerant detected by the temperature sensor 29 and ⁇ 40 ° C. (See FIG. 4). As described above, the temperature of the second refrigerant is controlled to ⁇ 40 ° C.
- the hydrogen filling operation is started. That is, compressed hydrogen is supplied from the hydrogen storage unit 11 through the hydrogen flow path 12 to the discharge port 13 (to the fuel cell vehicle). At this time, the hydrogen passing through the hydrogen flow path 12 is accurately cooled to ⁇ 40 ° C. by the second refrigerant through the second heat exchanger 40. At this time, the flow rate of the second refrigerant is 135 L/[email protected] MPa to 165 L/[email protected] MPa, particularly 150 L/[email protected] MPa.
- the second refrigerant that has passed through the second heat exchanger 40 is in a heated state and returns to the tank unit 23T.
- the temperature of the second refrigerant is detected by the temperature sensor 29 and the opening degree of the electronic expansion valve 28 is controlled by the temperature feedback control unit 30 based on the temperature (see FIG. 4), the second half flow path
- the temperature of the second refrigerant circulating in the can be stably maintained at ⁇ 40 ° C.
- the temperature of the second refrigerant can be cooled with high accuracy within an error range of + 2 ° C. to ⁇ 3 ° C.
- the hydrogen cooled by the second refrigerant can be cooled with high accuracy within an error range of + 2 ° C. to ⁇ 3 ° C.
- the second operation mode of the present embodiment for example, it takes 120 minutes to cool the second refrigerant to ⁇ 40 ° C. at a stretch from the state of the ambient temperature + 40 ° C. Further, it takes only 30 minutes from the state of being cooled to ⁇ 20 ° C. in the first operation mode until the second refrigerant is cooled to ⁇ 40 ° C.
- the cooled hydrogen supply station 1 is a fuel cell in which the hydrogen cooled with high accuracy as described above is supplied at a flow rate of 4.5 kg / 3 min to 5.5 kg / 3 min, particularly 5.0 kg / min. Can be supplied to cars. Further, according to the cooling hydrogen supply station 1 according to the present embodiment, after supplying hydrogen at 4.5 kg / 3 min to 5.5 kg / 3 min, particularly 5.0 kg / min, to one fuel cell vehicle, If an interval of 7 min is set, hydrogen can be supplied again to the next one fuel cell vehicle at 4.5 kg / 3 min to 5.5 kg / 3 min, particularly 5.0 kg / min.
- the cooling capacity when the second refrigerant cooled to ⁇ 40 ° C. is stably maintained at ⁇ 40 ° C. is 13.5 kW @ ⁇ 40 ° C. to 16.5 kW @ ⁇ 40 ° C. Is 15.0 kW @ ⁇ 40 ° C.
- the compressor 25 in the first refrigerant path 21 and the pump 23P in the second refrigerant path 23 may be driven continuously from the first operation mode.
- the compressor 25 in the first refrigerant path 21 and the pump 23P in the second refrigerant path 23 may be driven continuously from the second operation mode.
- the cold brine FP-40 which is the second refrigerant
- the tank portion 23T has the second refrigerant in the tank portion 23T so that the liquid level of the second refrigerant in the tank portion 23T does not rise and fall to cause corrosion or the like.
- the refrigerant quantity adjusting mechanism 33 functions so as to maintain the liquid level of the second refrigerant in a predetermined range (preferably a constant liquid level height).
- the refrigerant amount adjusting mechanism 33 replenishes the tank portion 23T with the second refrigerant from the adjustment tank 33A, so that the liquid level of the second refrigerant is predetermined. Keep in range.
- the refrigerant amount adjusting mechanism 33 discharges the second refrigerant to the outside through the check valve from the tank portion 23T, so that the liquid level of the second refrigerant Is maintained within a predetermined range.
- the hydrogen cooling capacity can be increased from 13.5 kW @ ⁇ 40 ° C. to 16.5 kW @ ⁇ 40 ° C. It can be realized in efficiency, that is, extremely energy saving.
- the cooling accuracy within the error range of + 2 ° C. to ⁇ 3 ° C. can be realized with respect to the set temperature within the temperature range of ⁇ 43 ° C. to ⁇ 20 ° C. Highly efficient cooling can be realized with high accuracy.
- the use of the air-cooled condenser 22 instead of the water-cooled refrigerator unit eliminates the need for cooling water power equipment. Thereby, the freedom degree of an installation place has improved notably. Further, by adopting inverter control based on the pressure of the first refrigerant from the air-cooled condenser 22 to the first heat exchanger 24 for controlling the air-cooling fan 22f, an energy saving effect and high-precision operation are achieved. Obtainable.
- the opening degree of the electronic expansion valve 28 is operated at an upper limit of 40% or more, for example, 50%.
- the opening degree of the electronic expansion valve 28 is operated at, for example, 20 to 30% with 10% being the lower limit. Also by this, an effective energy saving effect can be obtained.
- the second valve 32 that controls the circulation amount of the first refrigerant in the hot gas bypass path 31 is configured so that the pressure of the pressure detection sensor 41 is maintained at ⁇ 46 kPa or more. Feedback control is performed based on the pressure value (detected value), and the pressure is released. Such an operation state is collectively shown in FIG.
- either the first operation mode or the second operation mode is selected and operated, and in the first operation mode, hydrogen is supplied. Is cooled to ⁇ 20 ° C., and in the second operation mode, hydrogen is cooled to ⁇ 40 ° C.
- the necessity of hydrogen supply when the necessity is low, the first operation mode corresponding to the idle operation state is selected, and when the necessity is high, the second operation mode corresponding to the standby state is selected. By selecting, the energy consumption regarding cooling can be suppressed effectively.
- the selection of the first operation mode or the second operation mode is automatically performed according to the time zone.
- the first operation mode is selected in the nighttime period when the need for hydrogen supply is low (eg, outside business hours), and the second operation is performed during the daytime period (eg, within business hours) when the need for hydrogen supply is high.
- the mode it is possible to effectively suppress the energy consumption related to cooling in the night time period when the necessity of hydrogen supply is low.
- FIG. 6 shows a modification of the operation state shown in FIG.
- the output of the compressor 25 is reduced to 70%
- the opening of the electronic expansion valve is reduced to 12.8%
- the second valve The opening degree of 32 is set to 100%. Even in such an operating state, an effective energy saving effect can be obtained.
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Abstract
Description
10 水素供給装置
11 水素貯留部
12 水素流路
13 排出口
20 水素冷却装置
21 第1冷媒路
22 空冷式凝縮器
22f 空冷ファン
23 第2冷媒路
23T タンク部
24 第1熱交換器
25 コンプレッサ
26 圧力検出センサ
27 インバータ式制御器
28 電子膨張弁
29 温度センサ
30 温度フィードバック制御部
31 ホットガスバイパス路
32 第2バルブ
33 冷媒量調整機構
33A 冷媒量調整タンク
40 第2熱交換器
41 圧力検出センサ
Claims (9)
- 第1の冷媒が循環される第1冷媒路と、
前記第1冷媒路の一部に対して設けられ、空冷ファンを駆動することで前記第1の冷媒の冷却を可能にする空冷式凝縮器と、
第2の冷媒が通流される第2冷媒路と、
前記第1冷媒路の他の一部と前記第2冷媒路の一部との間で前記第1の冷媒によって前記第2の冷媒の冷却を可能にする第1熱交換器と、
前記空冷式凝縮器から前記第1熱交換器に至るまでの間の第1の冷媒の圧力を検出する圧力検出センサと、
前記圧力検出センサにより検出される圧力に基づいて、当該圧力が1.5MPa~1.7MPaの範囲に維持されるよう、前記空冷ファンの駆動回転数をインバータ制御するインバータ式制御器と、
水素が貯蔵された水素貯蔵部と、
前記水素貯蔵部に貯蔵された水素が搬送される水素流路と、
前記第2冷媒路の他の一部と前記水素流路の一部との間で前記第2の冷媒によって前記水素の冷却を可能にする第2熱交換器と、
を備え、
前記インバータ式制御器は、前記圧力検出センサにより検出される圧力が上昇しているか高レベルにある間は、前記空冷ファンの駆動回転数を上昇させるか高レベルに維持し、前記圧力検出センサにより検出される圧力が下降しているか低レベルにある間は、前記空冷ファンの駆動回転数を下降させるか低レベルに維持するようになっており、
前記第1の冷媒は、フロンであり、
前記第2の冷媒は、ギ酸カリウム水溶液であり、
前記第2冷媒路における前記第2の冷媒の通流量は、0.3MPaの通流圧力で135L/min乃至165L/minであり、
前記水素は、前記第2熱交換器によって、-43℃乃至-20℃の温度範囲内にまで冷却されるようになっており、
前記水素は、前記第2熱交換器によって、-43℃乃至-20℃の温度範囲内の設定温度に対して+2℃乃至-3℃の誤差範囲内に冷却されるようになっており、
水素冷却能力は、水素を-40℃に冷却するときに13.5kW乃至16.5kWであり、
前記水素流路には、前記第2熱交換器によって冷却された後の水素を排出する排出口が設けられており、
前記排出口から排出される水素の量は、4.5kg/3min乃至5.5kg/3minである
ことを特徴とする冷却水素供給ステーション。 - 前記空冷ファンは、水素に対する防爆構造からなっている
ことを特徴とする請求項1に記載の冷却水素供給ステーション。 - 前記空冷式凝縮器を通る前記第1の冷媒の循環量を制御するバルブと、
前記第2冷媒路内の前記第1熱交換器通過直後の前記第2の冷媒の温度を検出する温度センサと、
前記温度センサの検出結果に基づいて前記バルブを制御する温度フィードバック制御部と、
を更に備えたことを特徴とする請求項1または2に記載の冷却水素供給ステーション。 - 前記第2の冷媒の温度が-40℃よりも高い時には、前記バルブの開度は40%~50%であり、
前記第2の冷媒の温度が-40℃以下である時には、前記バルブの開度は10%~30%である
ことを特徴とする請求項3に記載の冷却水素供給ステーション。 - 前記第1の冷媒は、コンプレッサによって前記第1冷媒路内を循環するようになっており、
前記第2の冷媒の温度が-40℃以下である時には、前記コンプレッサの出力も60~80%に低減される
ことを特徴とする請求項3または4に記載の冷却水素供給ステーション。 - 第1運転モードと第2運転モードとのいずれかが選択されて運転されるようになっており、
第1運転モードにおいては、前記水素が-20℃に冷却され、
第2運転モードにおいては、前記水素が-40℃に冷却される
ことを特徴とする請求項1乃至5のいずれかに記載の冷却水素供給ステーション。 - 前記第1運転モードまたは前記第2運転モードの選択は、時間帯に応じて自動的に行われるようになっている
ことを特徴とする請求項6に記載の冷却水素供給ステーション。 - 前記第2冷媒路は、タンク部を更に有しており、
前記タンク部には、当該タンク部内における前記第2の冷媒の液面を所定範囲に維持するための冷媒量調整機構が接続されている
ことを特徴とする請求項1乃至7のいずれかに記載の冷却水素供給ステーション。 - 水素流路内を搬送される水素を冷却する水素冷却装置であって、
第1の冷媒が循環される第1冷媒路と、
前記第1冷媒路の一部に対して設けられ、空冷ファンを駆動することで前記第1の冷媒の冷却を可能にする空冷式凝縮器と、
第2の冷媒が通流される第2冷媒路と、
前記第1冷媒路の他の一部と前記第2冷媒路の一部との間で前記第1の冷媒によって前記第2の冷媒の冷却を可能にする第1熱交換器と、
前記空冷式凝縮器から前記第1熱交換器に至るまでの間の第1の冷媒の圧力を検出する圧力検出センサと、
前記圧力検出センサにより検出される圧力に基づいて、当該圧力が1.5MPa~1.7MPaの範囲に維持されるよう、前記空冷ファンの駆動回転数をインバータ制御するインバータ式制御器と、
前記第2冷媒路の他の一部と前記水素流路の一部との間で前記第2の冷媒によって前記水素の冷却を可能にする第2熱交換器と、
を備え、
前記第1の冷媒は、フロンであり、
前記第2の冷媒は、ギ酸カリウム水溶液であり、
前記第2冷媒路における前記第2の冷媒の通流量は、0.3MPaの通流圧力で135L/min乃至165L/minであり、
前記水素は、前記第2熱交換器によって、-43℃乃至-20℃の温度範囲内にまで冷却されるようになっており、
前記水素は、前記第2熱交換器によって、-43℃乃至-20℃の温度範囲内の設定温度に対して+2℃乃至-3℃の誤差範囲内に冷却されるようになっており、
水素冷却能力は、水素を-40℃に冷却するときに13.5kW乃至16.5kWであり、
前記水素流路には、前記第2熱交換器によって冷却された後の水素を排出する排出口が設けられており、
前記排出口から排出される水素の量は、4.5kg/3min乃至5.5kg/3minである
ことを特徴とする水素冷却装置。
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