JP6324169B2 - Gas filling device - Google Patents

Description

  The present invention relates to a gas filling device.

  In a gas filling device that fills a tank to be filled with compressed fuel gas such as hydrogen gas or CNG (compressed natural gas), a heat exchanger is provided in the fuel supply path in order to suppress an increase in the temperature of the compressed gas. Gas filling is performed while cooling the gas flowing through the gas filling path (see, for example, Patent Document 1).

  In the gas filling device, the supply temperature of the compressed fuel gas filled in the tank to be filled is defined in advance to a predetermined temperature (for example, about −40 ° C. in the case of hydrogen gas). On the other hand, in the heat exchanger, it is set in advance to what temperature the supplied compressed fuel gas is cooled depending on conditions such as the refrigerant temperature and the heat exchange efficiency. For example, even when the temperature of the compressed fuel gas supplied at a high temperature in summer (or daytime) (for example, an air temperature of 25 ° C. to 30 ° C.) is high, the heat exchanger has a cooling capacity so that it can be cooled to a predetermined temperature. Designed.

  The heat exchanger that cools the compressed fuel gas includes, for example, a first layer in which a large number of fine channels to be cooled to which the compressed fuel gas is supplied are formed in parallel, and a large number of fine particles for cooling the compressed fuel gas. Adoption of an integrated laminated structure heat exchanger in which a plurality of second layers formed in parallel with the refrigerant flow paths are alternately laminated and each of the plurality of layers is integrated by diffusion bonding has been studied.

  Here, when the temperature of the compressed fuel gas is cooled to a predetermined temperature or lower using the above-described integrated laminated structure heat exchanger, in order to be able to cool the gas temperature to a predetermined temperature or lower regardless of the temperature level, As the integrated laminated structure heat exchanger, one having a performance capable of cooling the compressed fuel gas having the highest temperature possible to a predetermined temperature or lower is employed.

JP 2006-220275 A

  When the compressed fuel gas is cooled by using the integrated laminated structure heat exchanger as described above, since the compressed fuel gas is configured to pass through a large number of fine cooling channels, the pressure in the fine cooling channels is The loss (flow path resistance) is large, and the pressure loss increases as the cooling performance of the integrated laminated structure heat exchanger increases.

  On the other hand, the shorter the filling time of the compressed fuel gas into the filling tank (for example, the time required for the pressure in the filling tank to rise to a predetermined pressure after the filling of the filling tank is started) is preferable. As described above, a unit having a performance capable of cooling the compressed fuel gas having the highest temperature to a predetermined temperature or less is adopted as the integrated laminated structure heat exchanger. For this reason, for example, the temperature of the compressed fuel gas to be supplied is lower than the above-mentioned temperature that can be assumed, and the heat exchanger having a lower performance than the above-described integrated laminated heat exchanger having a high cooling performance (that is, Even when the temperature of the compressed fuel gas can be cooled to a predetermined temperature or lower by a heat exchanger having a pressure loss smaller than that of the heat exchanger, the heat exchanger having the above high pressure loss is passed. Therefore, even if the temperature of the compressed fuel gas to be supplied is low, the flow rate of the compressed fuel gas supplied to the tank to be filled is restricted by the pressure loss, so that the tank to be filled is filled with the compressed fuel gas. There was a problem that it took time.

  Therefore, in view of the above circumstances, an object of the present invention is to provide a gas filling device that solves the above problems.

  In order to solve the above problems, the present invention has the following means.

The present invention includes a nozzle for filling a tank to be filled with compressed fuel gas, a heat exchanger for cooling the compressed fuel gas filled by the nozzle, and each device provided in a gas supply system including the heat exchanger. Control means for controlling gas filling into the tank to be filled with control, wherein the heat exchanger has a large number of fine cooling channels to which compressed fuel gas is supplied. a first layer formed in parallel, and the second layer are stacked alternately a large number of fine coolant channel for cooling the compressed fuel gas is formed in parallel, a plurality of the layers are an integral structure A plurality of integral laminated structure heat exchangers, and among the plurality of integral laminated structure heat exchangers, one of the integrated laminated structure heat exchangers and the other integrated type The channel resistance of the cooled channel of the laminated heat exchanger is formed differently. Rutotomoni, wherein provided in the gas supply system, a temperature detector for detecting the temperature of the compressed fuel gas, when the temperature of the compressed fuel gas detected by the temperature detector is lower than the first temperature set in advance The one integrated laminated structure heat exchanger having a small flow path resistance among the plurality of integrated laminated structure heat exchangers is used, and the temperature of the compressed fuel gas detected by the temperature detector is the first When the temperature is higher than the temperature, the plurality of integrated laminated structure heat exchangers are used such that the other integrated laminated structure heat exchanger having a large flow path resistance among the plurality of integrated laminated structure heat exchangers is used. and switching means for switching an integral laminate structure heat exchanger using compressed fuel gas of the vessel to cool, to have a characterized.

  According to the present invention, a plurality of integral laminated structure heat exchangers having different flow path resistances of the channels to be cooled are provided, and the compressed fuel gas according to the temperature of the compressed fuel gas among the plurality of integral laminated structure heat exchangers Switch the monolithic laminated heat exchanger used to cool the. For example, when the temperature of the compressed fuel gas to be supplied is low in the first place and the temperature of the compressed fuel gas can be cooled to a predetermined temperature or less by an integrated laminated structure heat exchanger having a cooled channel with a small channel resistance, the channel The compressed fuel gas is cooled by an integral laminated structure heat exchanger having a cooled channel with low resistance. As a result, the flow rate of the cooled compressed fuel gas supplied to the tank to be filled can be increased as compared with the case where the compressed fuel gas is cooled using an integrated laminated structure heat exchanger having a large flow path resistance. Accordingly, it is possible to shorten the time for filling the tank to be filled with the compressed fuel gas.

It is a figure which shows one Embodiment of the gas filling apparatus which concerns on this invention. It is a figure which shows the structural example of an integrated laminated structure heat exchanger. It is a figure which shows the 2nd heat exchanger 30B as an integral laminated structure heat exchanger. It is a figure which shows the 3rd heat exchanger 30C as a modification of the heat exchanger which can be employ | adopted as the 2nd heat exchanger 30B as an integral laminated structure heat exchanger. It is a flowchart for demonstrating the control processing which the control part of the gas filling apparatus which concerns on this invention performs.

  Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings.

[Configuration of gas filling device]
FIG. 1 is a diagram showing a schematic configuration of an embodiment of a gas filling apparatus according to the present invention. As shown in FIG. 1, the gas filling device 10 includes a dispenser unit 20, a cooling device 30, a gas storage device 40, and a compressor 50.

  The dispenser unit 20 is configured to fill a compressed fuel gas such as hydrogen gas, for example, and is connected to a gas supply system 60 communicated with the gas accumulator 40 and a filling tank 72 mounted on the vehicle 70. Nozzle 80 to be used. In the gas supply system 60, each device is arranged in a gas supply pipe 61 having one end communicating with the gas accumulator 40 and the other end connected to the hose 82 of the nozzle 80. Then, after the nozzle 80 is connected to the filling tank 72 of the vehicle 70, each valve of the gas supply line 61 is controlled to open and close, whereby the compressed fuel gas accumulated in the gas accumulator 40 by the compressor 50 is predetermined. It is cooled to a temperature (for example, −30 ° C. to −40 ° C.) and filled in the tank 72 to be filled.

  A temperature sensor (temperature detector) TT, an inlet-side on-off valve V5, a flow meter 63, a control valve 64, and a pressure sensor PT are arranged on the gas supply line 61 from the upstream side. In addition, a pair of branch pipes 67 and 68 provided downstream of the pressure sensor PT in the gas supply pipe 61 includes heat exchangers 30A and 30B (or 30C) of the cooling device 30 and heat exchangers 30A and 30B ( Alternatively, on-off valves V1 to V4 that are opened when 30C) are operated are provided. The downstream side of the pair of branch pipes 67 and 68 joins and is connected to the hose 82.

  The cooling device 30 has a plurality of heat exchangers formed by an integral laminated structure heat exchanger, and in the present embodiment, the first heat exchanger 30A and the second heat exchanger 30B (or 30C) are provided. Connected in parallel. The first heat exchanger 30 </ b> A and the second heat exchanger 30 </ b> B (or 30 </ b> C) are each a heat exchanger called an integral laminated structure heat exchanger, and a large number of refrigerants connected in parallel to the branch pipes 67 and 68. It has a flow path and a gas flow path (cooled flow path). In addition, the detail of the structure of many refrigerant | coolant flow paths and gas flow paths in each heat exchanger 30A-30C is mentioned later.

  The cooling device 30 includes a refrigerant pump 32, a refrigerant cooler 34, and a refrigerant conduit 36. Of each device constituting the cooling device 30, the first heat exchanger 30 </ b> A, the second heat exchanger 30 </ b> B, and the on-off valves V <b> 1 to V <b> 4 (switching means) are built in the dispenser unit 20 and supply the refrigerant. The pump 32 and the refrigerant cooler 34 are provided outside the dispenser unit 20.

  The on-off valves V1 to V5 and the control valve 64 are electromagnetic valves, respectively, and are switched to a valve open state or a valve closed state by a control signal from the control unit 90. The temperature sensor TT is provided downstream of the gas accumulator 40, measures the gas temperature supplied from the gas accumulator 40, and outputs a temperature measurement signal indicating the measured value of the gas measurement temperature to the control unit 90. The gas accumulator 40 and the compressor 50 are installed on the ground or underground. When installed on the ground, the supplied compressed fuel gas is easily affected by the temperature.

  The flow meter 63 includes, for example, a Coriolis type mass flow meter, measures the flow rate of the compressed fuel gas flowing through the gas supply pipe 61, and outputs the flow rate measurement signal to the control unit 90. Further, the pressure sensor PT detects the pressure of the compressed fuel gas flowing through the gas supply pipe 61 and outputs a pressure detection signal at that time to the control unit 90.

  The adjustment valve 64 is configured to adjust the pressure and flow rate of the compressed fuel gas flowing through the gas supply pipe 61, and the valve opening degree is controlled according to a control signal from the control unit 90. Further, in the control unit 90, when the filling start switch 94 is turned on after the nozzle 80 is connected to the filling tank 72 of the vehicle 70, the on-off valve V5 is opened and the adjustment valve 64 is opened. Is gradually opened to start filling the tank 72 with the compressed fuel gas accumulated in the gas accumulator 40. In the gas filling control, the outlet side on-off valve 66 is closed, the on-off valve V5 and the control valve 64 are opened, and the compressed fuel gas is at the temperature of the gas detected by the temperature sensor TT. Based on the switching control (opening or closing control) of the first to fourth on-off valves V1 to V4 based on the first heat exchanger 30A and / or the second heat exchanger 30B (or 30C), the hose 82, supplied to the nozzle 80.

  When the pressure of the tank 72 to be filled reaches a preset target pressure or when the filling stop switch 96 is turned on, the control unit 90 closes all the valves and supplies gas to the tank 72 to be filled. Stop filling. Further, the controller 90 fills the tank to be filled 72 with the gas via the nozzle 80, based on the gas temperature detected by the temperature sensor TT, the first and second heat exchangers 30A, 30B (or 30C). 2), or only one of the first heat exchanger 30A or the second heat exchanger 30B (or 30C), and the flow resistance switching means 92 for executing a control program for efficiently cooling the compressed fuel gas. Have. Further, when the pressure measured by the pressure sensor PT reaches a preset target pressure, or when the filling stop switch 96 is turned on, the control unit 90 ends the gas filling control process.

  In the memory (storage means) 98 of the control unit 90, a control program for calculating the remaining amount of the tank to be filled 72 based on the tank initial pressure, the filling pressure to the tank to be filled 72 or the filling flow rate at a certain ratio ( The first and second heat exchangers 30A and 30B (or 30B) of the cooling device 30 based on the gas temperature detected by the control program and the temperature sensor TT that controls the valve opening degree of the control valve 64 so as to increase at an increase rate). 30C) various programs such as a control program for switching the channel resistance are stored.

[Configuration of heat exchangers 30A and 30B]
FIG. 2 is a diagram showing a configuration example of a heat exchanger 30A as an integral laminated structure heat exchanger. As shown in FIGS. 2A and 2B, the heat exchanger 30A is an integral laminated structure heat exchanger.

  The first heat exchanger 30A includes a large number of gas flow paths (cooled flow paths) 101 extending in the Y direction and a large number of refrigerant flow paths 103 extending in the X direction. The multiple gas flow paths 101 are open at the front and rear surfaces of the first heat exchanger 30A at both ends, and the multiple refrigerant flow paths 103 are open at the left and right side surfaces of the first heat exchanger 30A. . In addition, the flow paths 101 and 103 are formed with fine hole dimensions L1 and L2 (for example, about L1 = L2 = 1.0 mm). The first heat exchanger 30A has dimensions L1 and L2 of the gas flow passage 101 that are relatively larger than those of the second heat exchanger 30B (see FIG. 3) described later, and therefore the second heat exchange described later. The pressure loss due to the flow path resistance when the compressed fuel gas passes through the gas flow path 101 is smaller than that of the vessel 30B. Further, since the depth dimension L4 in the Y direction of the gas flow path 101 is formed relatively short compared to a third heat exchanger 30C (see FIG. 4) described later, compressed fuel is used compared to the third heat exchanger 30C described later. Pressure loss due to channel resistance when gas passes through the gas channel 101 is small.

  In addition, the first heat exchanger 30A includes a first layer 102 in which a large number of gas flow channels 101 serving as fine channels to be cooled are formed in parallel and a large number of fine refrigerant channels 103 formed in parallel. The second layers 104 are alternately stacked, and each of the plurality of layers has a single structure.

  For this reason, in the first heat exchanger 30A, the compressed fuel gas is supplied to and passed through the first layer 102 in which the gas flow paths 101 are formed in parallel, and the refrigerant flow paths 103 arranged in the vertical direction thereof are parallel. The compressed fuel gas is efficiently cooled by supplying and passing the refrigerant through the formed second layer 104.

  Further, in the first heat exchanger 30A, for example, the width dimension L3 in the X direction and the depth dimension L4 in the Y direction are set to specified dimensions, respectively.

  FIG. 3 is a view showing a second heat exchanger 30B as an integral laminated structure heat exchanger. As shown in FIGS. 3A and 3B, the second heat exchanger 30B is an integrated stacked structure heat exchanger similar to the first heat exchanger 30A described above. In the second heat exchanger 30B, the vertical and horizontal hole dimensions L5 and L6 (for example, about L5 = L6 = 0.5 mm) of each gas flow path 101 are formed smaller than those of the first heat exchanger 30A. Therefore, the flow resistance of the gas flow path 101 becomes larger than that of the first heat exchanger 30A, and the pressure loss due to this is high. Moreover, since the flow rate of compressed fuel gas is suppressed because the hole size of each gas flow path 101 is small, the cooling capacity of compressed fuel gas is improving rather than 30 A of 1st heat exchangers.

  That is, the second heat exchanger 30B can efficiently cool the gas temperature to a predetermined temperature even when the temperature of the supplied gas is high as in summer. In addition, the hole dimensions L5 and L6 of the respective flow paths 101 and 103 can be set to arbitrary dimensions, and are set to optimum dimensions from the relationship between the flow path resistance and the flow rate flowing through the respective flow paths 101 and 103. Is done. In this embodiment, the hole size (opening area) and the number of holes of the refrigerant flow path 103 of the first heat exchanger 30A and the second heat exchanger 30B are the same, but The dimensions (opening area) and the number of holes are not necessarily the same, and may be appropriately changed based on how much the compressed fuel gas is cooled.

[Modification of heat exchanger]
FIG. 4 is a view showing a third heat exchanger 30C as a modified example of the heat exchanger that can be employed in the second heat exchanger 30B as an integrated laminated structure heat exchanger. As shown in FIGS. 4A and 4B, the third heat exchanger 30C is an integrated laminated structure heat exchanger similar to the first and second heat exchangers 30A and 30B described above. As compared with the first heat exchanger 30A, the cooling capacity is enhanced as in the second heat exchanger 30B.

  In the third heat exchanger 30C, the hole dimensions L1 and L2 (for example, L1 = L2 = about 1.0 mm) of the flow paths 101 and 103 are formed in the same manner as the first heat exchanger 30A. Since L7 is formed twice as large as L4, the length of the gas flow path (cooled flow path) 101 is also doubled, and the flow resistance is increased as compared with the first heat exchanger 30A. Pressure loss due to resistance is high. Further, since the total length of each gas flow path 101 is twice that of the first heat exchanger 30A, the flow rate of the refrigerant is suppressed by increasing the flow path resistance, so that the cooling capacity by heat exchange with the compressed fuel gas is improved. ing.

  That is, the third heat exchanger 30C can efficiently cool the gas temperature to a predetermined temperature even when the temperature of the supplied gas is high as in the summer, like the second heat exchanger 30B described above. Become. The length dimension L7 can be set to an arbitrary dimension, and is set to an optimal dimension from the relationship between the pressure loss due to the channel resistance and the flow rate flowing through each gas channel 101.

  Moreover, although the flow path length of each gas flow path 101 of the 3rd heat exchanger 30C was made into 2 times the flow path length of each flow path 101 of the 1st heat exchanger 30A, it is not restricted to this, The flow path length of the path 101 may be twice or more that of the first heat exchanger 30A.

  In the present embodiment, as described above, the first layer 102 in which a large number of fine gas flow paths (cooled flow paths) 101 are formed in parallel and the first layer 102 in which a large number of fine refrigerant flow paths 103 are formed in parallel. Two heat exchangers 30A, 30B (or 30A, 30C) in which the two layers 104 are alternately stacked and each of the plurality of layers has an integrated structure are parallel to the refrigerant pipe 36 and the branch pipes 67, 68. Since the compressed fuel gas is cooled by using both the heat exchangers 30A and 30B (or 30A and 30C) at the same time, the pressure loss in the entire cooling device 30 can be reduced. In addition, by selecting heat exchangers with different pressure losses, it is possible to shorten the filling time by increasing the gas supply volume while increasing the cooling efficiency even when the gas temperature supplied is different, such as in summer or winter. Is possible .

[Control processing executed by control unit 90]
FIG. 5 is a flowchart for explaining the control process executed by the control unit of the gas filling apparatus according to the present invention. As shown in FIG. 5, after the nozzle 80 is connected to the connection port of the tank to be filled 72, when the filling start switch 94 is turned on in S11, the control unit 90 proceeds to S12, and the cooling device 30 A valve opening signal is output to the on-off valves V1 and V2 to open the on-off valves V1 and V2. As a result, the gas supply line 61 communicates with the filling tank 72 via the nozzle 80 and the hose 82, so that the pressure of the filling tank 72 before filling can be measured by the pressure sensor PT.

  In the next S13, the temperature detection value signal output from the temperature sensor TT for measuring the gas temperature is read, and the pressure detection value (the tank to be filled) output from the pressure sensor PT for measuring the pressure in the gas supply line 61 is read. 72 pressure) signal.

  Then, it progresses to S14 and the initial pressure (pressure before filling) of the to-be-filled tank 72 is estimated based on the pressure detection signal output from the pressure sensor PT.

  In the next S15, a predetermined control program for controlling the gas flow rate is read based on the temperature detected by the temperature sensor TT and the pressure value detected by the pressure sensor PT, and the inlet side on-off valve V5 and The control valve 64 is opened. Thus, the compressed fuel gas compressed from the gas accumulator 40 is supplied to the gas supply pipe 61, and the filling control based on the valve opening degree of the control valve 64 is started.

  Subsequently, in S16, it is checked whether or not the gas temperature t measured by the temperature sensor TT is lower than a predetermined temperature T1 (for example, T1 = −30 ° C.). In t16, when t <T1 (in the case of YES), the temperature of the supplied compressed fuel gas is lowered. Therefore, the process proceeds to step S17, and the on / off valves V1 and V2 are opened and the on / off valves V3 and V4 are closed. While continuing the valve state, the refrigerant cooler 34 and the refrigerant pump 32 are operated. Thereby, after the compressed fuel gas supplied to the gas supply line 61 is cooled to a predetermined temperature (for example, −40 ° C.) in the process of passing through the first heat exchanger 30A, the compressed fuel gas is passed through the hose 82 and the nozzle 80. The filling tank 72 is filled. In this case, since the compressed fuel gas is supplied only to the first heat exchanger 30A having a relatively small pressure loss, the flow rate can be increased, and the filling time to the filling tank 72 is shortened accordingly. Is possible.

  In S18, the valve opening of the control valve 64 is controlled to perform constant pressure increase filling control (constant pressure increase rate). Thereby, the filling pressure of the filling tank 72 is controlled to a predetermined pressure increase rate, and gas filling is performed.

  In the next S19, the pressure detection signal output from the pressure sensor PT is read, and it is checked whether or not the filling pressure filled in the tank 72 to be filled has reached a target pressure (for example, 70 MPa) set in the memory 98. To do. In S19, when the pressure detected by the pressure sensor PT does not reach the target pressure (in the case of NO), the process returns to the process of S17, and the process of S17 to S19 is repeated to control the gas filling to the tank 72 to be filled. Continue.

  In S19, when the pressure detected by the pressure sensor PT reaches the target pressure (in the case of YES), the process proceeds to S20, where the refrigerant pump 32 and the refrigerant cooler 34 of the cooling device 30 are stopped, and all of them are performed in S21. The valve (the control valve 64 and the on-off valves V1 to V5) is closed, and the gas filling to the filling tank 72 is finished.

  In S16, if t> T1 (in the case of NO), the temperature of the supplied compressed fuel gas has risen to the predetermined temperature T1 or higher, so the process proceeds to S22 and the gas temperature measured by the temperature sensor TT is reached. It is checked whether t is equal to or higher than a predetermined temperature T1 (for example, T1 = −30 ° C.) that is set in advance and lower than a predetermined temperature T2 (for example, T2 = −20 ° C.) (T1 <T2).

  In S22, when the gas temperature t measured by the temperature sensor TT is T1 ≦ t ≦ T2 (in the case of YES), the process proceeds to S23, the on-off valves V1, V2 are closed, and the on-off valves V3, V4 are opened. A signal is output to open the on-off valves V3 and V4, and the refrigerant cooler 34 and the refrigerant pump 32 are operated. Thereby, the compressed fuel gas supplied to the gas supply pipe 61 is supplied only to the second heat exchanger 30B (or 30C).

  Therefore, the compressed fuel gas is cooled to a predetermined temperature (for example, −40 ° C.) in the process of passing through the second heat exchanger 30 </ b> B, and is filled into the filling tank 72 through the hose 82 and the nozzle 80. In this case, the compressed fuel gas is cooled to a predetermined temperature or higher (for example, −40 ° C.) by the second heat exchanger 30B having a relatively large pressure loss due to flow path resistance. The compressed fuel gas cooled in the two heat exchangers 30A and 30B (or 30C) joins and is filled into the filling tank 72 via the hose 82 and the nozzle 80, and thus the filling tank 72 is filled. The compressed fuel gas is kept at a predetermined temperature (for example, −40 ° C.). In addition, since the cooling capacity in the second heat exchanger 30B (or 30C) is improved, the flow rate of the cooled gas can be increased and the filling time can be shortened.

  Thereafter, in S24, as in S18 described above, the valve opening of the control valve 64 is controlled to perform constant pressure increase filling control (a constant pressure increase rate). In S25, the pressure sensor PT detects the same as in S19. When the pressure reaches the target pressure, the process proceeds to S20, the refrigerant pump 32 and the refrigerant cooler 34 of the cooling device 30 are stopped, and all the valves (the control valve 64 and the on-off valves V1 to V5) are closed in S21. The gas filling to the tank to be filled 72 is finished by valve.

  In S22, if the gas temperature t measured by the temperature sensor TT is not T1 ≦ t ≦ T2 (NO), the process proceeds to S26, where the gas temperature t measured by the temperature sensor TT is t> T2. Is determined.

  In next S27, a valve opening signal is output to the on-off valves V1 to V4 to open the on-off valves V1 to V4, and the refrigerant cooler 34 and the refrigerant pump 32 are operated. Thereby, the compressed fuel gas supplied to the gas supply pipe 61 is supplied to the first heat exchanger 30A and the second heat exchanger 30B (or 30C).

  For this reason, the compressed fuel gas cooled to a predetermined temperature (for example, −40 ° C.) in the process of passing through the heat exchangers 30 </ b> A and 30 </ b> B is filled into the filling tank 72 via the hose 82 and the nozzle 80. In this case, the compressed fuel gas is cooled to a predetermined temperature or lower (for example, −35 ° C.) by the first heat exchanger 30A having a relatively small pressure loss, and the second heat exchange having a relatively large pressure loss due to the flow path resistance. Cooled to a predetermined temperature or higher (for example, −45 ° C.) by the vessel 30B. The compressed fuel gas cooled in the two heat exchangers 30A and 30B (or 30C) joins and is filled into the filling tank 72 via the hose 82 and the nozzle 80, and thus the filling tank 72 is filled. The compressed fuel gas is kept at a predetermined temperature (for example, −40 ° C.). Moreover, since the total of the flow path areas of the two heat exchangers 30A, 30B (or 30C) is larger than that of one, the cooled gas flow rate can be increased and the filling time can be shortened.

  In S28 after this, similarly to S18 described above, the valve opening of the control valve 64 is controlled to perform constant pressure increase filling control (a constant pressure increase rate), and then in S29, the pressure sensor PT is used as in S19. When the detected pressure reaches the target pressure, the process proceeds to S20, the refrigerant pump 32 and the refrigerant cooler 34 of the cooling device 30 are stopped, and all the valves (the control valve 64 and the on-off valves V1 to V5) in S21. To close the gas filling to the tank 72 to be filled.

  Although the said embodiment demonstrated the structural example which connected two heat exchangers in parallel, you may arrange | position not only this but 2 or more heat exchangers in parallel, for example.

  In the above embodiment, the temperature sensor TT for measuring the temperature of the compressed fuel gas is cooled on the upstream side of the heat exchangers 30A, 30B (or 30C), that is, the heat exchangers 30A, 30B (or 30C). The temperature of the previous compressed fuel gas is measured. The temperature measured by the temperature sensor TT is downstream of the heat exchangers 30A and 30B (or 30C), that is, the heat exchangers 30A and 30B (or 30C). The temperature of the compressed fuel gas after being cooled may be measured. In this case, when the temperature measured by the temperature sensor TT is equal to or higher than a predetermined temperature, the heat exchanger 30B (or 30C) is used. The flow path of the compressed fuel gas is switched so as to cool the compressed fuel gas. When the temperature measured by the temperature sensor TT is lower than the predetermined temperature, the compressed fuel gas is cooled by the heat exchanger 30A. It may be as switching the flow path of the compressed fuel gas to. Further, the temperature sensor TT directly measures the temperature of the compressed fuel gas. However, the temperature sensor TT is not limited to this. For example, the temperature of the compressed fuel gas is indirectly measured by measuring the ambient temperature. It may be.

  Moreover, in the said embodiment, although the heat exchanger from which cooling performance (flow path resistance of a to-be-cooled flow path) differs between heat exchanger 30A and heat exchanger 30B is used, it replaces with this and heat exchanger The compressed fuel gas may be cooled by using the heat exchanger 30B and the heat exchanger 30C without using 30A. In this case, the hole of the channel 101 to be cooled of the heat exchanger 30 may be cooled. The cooling capacity of the heat exchanger itself may be varied by appropriately adjusting the area and the channel length.

  Moreover, in the said embodiment, based on the temperature detected by the temperature sensor TT, heat exchanger 30A, 30B (or 30C) used automatically by controlling opening / closing of the on-off valves V1-V4 is determined. Although it is configured, the operator may select and use the heat exchangers 30A and 30B (or 30C) to be used by manually operating the on-off valves V1 to V4 according to the situation on the spot. Good.

DESCRIPTION OF SYMBOLS 10 Gas filling apparatus 20 Dispenser unit 30 Cooling apparatus 30A 1st heat exchanger 30B 2nd heat exchanger 30C 3rd heat exchanger 32 Refrigerant pump 34 Refrigerant cooler 36 Refrigerant pipe line 40 Accumulator 50 Compressor 60 Gas supply system 61 Gas supply pipe 63 Flow meter 64 Control valve 67, 68 Branch pipe 72 Filled tank 80 Nozzle 90 Control unit (control means)
94 Filling start switch 96 Filling stop switch 101 Gas flow path (cooled flow path)
102 First layer 103 Refrigerant flow path 104 Second layer PT Pressure sensor TT Temperature sensor (temperature detector)
V1 to V4 open / close valve (switching means)
V5 open / close valve

Claims (3)

A nozzle that fills a tank to be filled with compressed fuel gas;
A heat exchanger for cooling the compressed fuel gas filled by the nozzle;
Control means for controlling the gas filling into the tank to be filled by controlling each device provided in the gas supply system including the heat exchanger;
A gas filling device comprising:
The heat exchanger includes a first layer large number of fine cooled flow passages compressed fuel gas is supplied is formed in parallel, a number of fine coolant channel for cooling the compressed fuel gas is concurrently A plurality of integral laminated structure heat exchangers in which the second layers formed in the above are alternately laminated, and each of the plurality of layers has an integral structure,
Of the plurality of integrated laminated heat exchangers, the flow resistance of the cooled channel of one integrated laminated heat exchanger and the flow channel of the cooled channel of another integrated laminated heat exchanger The resistors are formed differently,
A temperature detector provided in the gas supply system for detecting the temperature of the compressed fuel gas ;
When the temperature of the compressed fuel gas detected by the temperature detector is lower than a preset first temperature, the one integrated type having a small flow path resistance among the plurality of integrated laminated structure heat exchangers When a laminated structure heat exchanger is used and the temperature of the compressed fuel gas detected by the temperature detector is higher than the first temperature, the flow resistance of the plurality of integrated laminated structure heat exchangers is Switching to switch the integral laminate heat exchanger used to cool the compressed fuel gas of the plurality of integral laminate heat exchangers so as to use the other integral laminate heat exchanger that is larger gas filling apparatus comprising: the means. When the temperature of the compressed fuel gas detected by the temperature detector is higher than a second temperature set higher than the first temperature, the switching means is configured to switch the plurality of integral laminated structure heat exchangers. The gas filling device according to claim 1, wherein the gas filling device is switched to use two or more of the integrated laminated structure heat exchangers . A detecting means for detecting whether or not filling of the compressed fuel gas into the filling tank is started;
3. The gas filling device according to claim 1 , wherein the temperature detector detects the temperature of the compressed fuel gas when the start of the filling is detected by the detection unit. 4.

Images