JP5345227B2 - Booster for cryogenic fluid - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent heat generated by a piston for second stage compression from being transferred to a piston for first stage compression, and to efficiently raise the pressure of a low temperature fluid in a atmospheric pressure state to desired pressure by the piston for first stage compression. <P>SOLUTION: This booster 2 for the low temperature fluid includes: a piston 51 having piston rings 51a', 51b' and 51c' on an outer peripheral surface; a cylinder block 53 slidably storing the piston 51, and having a first pressurizing chamber S1 for compressing the low temperature fluid by one end surface of the piston 51, and a second pressurizing chamber S2 for further compressing the low temperature fluid compressed in the first pressurizing chamber S1 by the other end surface of the piston 51; and a heat insulating vacuum vessel 54 for storing the piston 51 and the cylinder block 53. A first cooling part 67 is formed at the cylinder block 53. <P>COPYRIGHT: (C)2010,JPO&amp;INPIT

Description

  The present invention relates to a low-temperature fluid booster that compresses and pressurizes a low-temperature fluid.

  2. Description of the Related Art Conventionally, as a low-temperature fluid pressure increasing device that compresses and pressurizes a low-temperature (0 ° C. or lower) fluid (for example, hydrogen), a piston-type device having a piston ring in a piston head is known (for example, non-patent Reference 1).

Endo Takuya et al., “New Energy Vehicle”, Sankai-do, January 1995, p. 221-222

Recently, a pressure booster for a low temperature fluid having a piston for compressing a low temperature fluid from atmospheric pressure to about 1.3 MPa has been proposed.
However, in such a booster for low temperature fluid, the low temperature fluid is compressed to about 1.3 MPa by the piston. Therefore, the high-pressure low-temperature fluid that flows into the inner peripheral surface of the piston ring of the piston acts so as to strongly press the outer peripheral surface of the piston ring against the inner peripheral surface of the cylinder, and the friction between the piston ring and the cylinder wall is intense. Thus, heat generation due to friction is remarkably increased, and this heat is transmitted to the piston, and a part of the low-temperature fluid in the atmospheric pressure state sucked into the piston side is evaporated (boiled off), and a desired pressure (for example, There was a problem that it was not possible to compress to about 1.3 MPa.

  The present invention has been made in view of the above circumstances, can prevent the temperature rise of the cylinder block, can prevent evaporation of the low-temperature fluid sucked into the pressurizing chamber, The main object of the present invention is to provide a cryogenic fluid booster capable of efficiently boosting the cryogenic fluid sucked into the pipe to a desired pressure.

The present invention employs the following means in order to solve the above problems.
The pressurizing device for low-temperature fluid according to claim 1 has a piston having a piston ring on an outer peripheral surface, and a pressurizing chamber in which the piston is slidably received and the low-temperature fluid is compressed by one end surface of the piston. A cylinder liner, a cylinder block that accommodates the cylinder liner so that an inner peripheral surface thereof is in contact with an outer peripheral surface of the cylinder liner, and a heat insulating vacuum container that accommodates the piston and the cylinder block; A pressurizing device for cryogenic fluid in which cryogenic fluid is stored in a space formed between a block and the heat insulating vacuum vessel, wherein the upper end of the cylinder liner has an open end, and A plurality of recesses extending in the up-down direction with the lower end being a closed end are provided along the circumferential direction. A plurality of through-holes are provided along the circumferential direction to guide the low-temperature fluid stored in a space formed between the Linda block and the heat-insulating vacuum vessel into the recess provided in the outer peripheral surface of the cylinder liner. It is characterized by being provided.
According to such a low pressure fluid booster, since the recess is provided between the cylinder block and the cylinder liner and the recess is always filled with the low temperature fluid, the piston ring is connected to the inner wall surface of the cylinder liner. The frictional heat generated by sliding along the cylinder can be efficiently recovered through the cylinder liner sufficiently cooled by the low-temperature fluid, and the temperature rise of the entire apparatus can be prevented.
Thereby, evaporation of the low temperature fluid sucked into the cylinder liner can be prevented, the low temperature fluid can be efficiently compressed to a desired pressure (for example, about 1.3 MPa), and a heat insulating vacuum vessel It is possible to prevent evaporation of the low-temperature fluid stored in the inside.

The pressurizing device for low-temperature fluid according to claim 2 has a piston having a piston ring on an outer peripheral surface, and a pressurizing chamber in which the piston is slidably received and the low-temperature fluid is compressed by one end surface of the piston. A cylinder liner, a fluid inlet that guides the low-temperature fluid in an atmospheric pressure state to the pressurizing chamber, and a cylinder that accommodates the cylinder liner so that an inner peripheral surface thereof is in contact with an outer peripheral surface of the cylinder liner; A cylinder block provided with a fluid outlet through which the low-temperature fluid compressed by one end surface flows out on the bottom surface, and a thick portion of the cylinder liner includes an upper end and A plurality of communication holes extending in the up-down direction with the lower end being an open end are provided along the circumferential direction, and the outer peripheral surface of each of the communication holes is the inside of the communication hole. A pipe in contact with a surface is inserted, and the upstream end of one of the pipes and the fluid outlet are connected via a pipe, the downstream end of the one pipe, and the one of the pipes An upstream end of another pipe disposed adjacent to the pipe is connected via a connecting pipe, and the low-temperature fluid led out of the cylinder block from the fluid outlet exits the pipe. Further, it is configured to pass through sequentially in the circumferential direction.
According to such a low-temperature fluid booster, a plurality of pipes are provided in the thick part of the cylinder liner, and the low-temperature fluid is always passed through these pipes. Frictional heat generated by sliding along the wall surface can be efficiently recovered through the cylinder liner sufficiently cooled by the low-temperature fluid, and temperature rise of the entire apparatus can be prevented.
Thereby, evaporation of the low temperature fluid sucked into the cylinder liner can be prevented, and the low temperature fluid can be efficiently compressed to a desired pressure (for example, about 1.3 MPa).

The fuel supply device according to claim 3 is gasified by any one of the above low-temperature fluid booster, an evaporator that gasifies the low-temperature fluid boosted by the low-temperature fluid booster, and the evaporator. An air reservoir for temporarily storing a low-temperature fluid is provided.
According to such a fuel supply device, the low-temperature fluid boosted by the low-temperature fluid booster is gasified by the evaporator and stored in the temporary air reservoir, and then supplied to a use point (for example, an engine or the like). Will be.

  According to the present invention, the temperature rise of the cylinder block can be prevented, the evaporation of the low-temperature fluid sucked into the pressurizing chamber can be prevented, and the desired low-temperature fluid sucked into the pressurizing chamber can be prevented. There is an effect that the pressure can be efficiently increased to the pressure.

1 is a schematic configuration diagram of a fuel supply apparatus including a first reference embodiment of a booster for a cryogenic fluid according to the present invention. It is a schematic block diagram of the fuel supply apparatus which comprised 2nd Embodiment of the pressure | voltage rise apparatus for low temperature fluid by this invention. It is a schematic block diagram of the fuel supply apparatus which comprised the 3rd embodiment of the pressure | voltage rise apparatus for low temperature fluid by this invention. It is a schematic block diagram of the fuel supply apparatus which comprised the 4th reference embodiment of the pressure | voltage rise apparatus for low temperature fluid by this invention. It is a schematic block diagram of the fuel supply apparatus which comprised 5th Embodiment of the pressure | voltage rise apparatus for low temperature fluid by this invention. It is a schematic block diagram of the fuel supply apparatus which comprised the 6th reference embodiment of the pressure | voltage rise apparatus for low temperature fluid by this invention. It is a schematic block diagram of the fuel supply apparatus provided with 7th reference embodiment of the pressure | voltage rise apparatus for low temperature fluid by this invention. BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows 1st Embodiment of the pressure | voltage rise apparatus for low temperature fluid by this invention, Comprising: (a) is a schematic longitudinal cross-sectional view, (b) The whole cylinder liner perspective view. It is a figure which shows 2nd Embodiment of the pressurization apparatus for low temperature fluid by this invention, Comprising: (a) is a schematic longitudinal cross-sectional view, (b) It is a whole perspective view of a cylinder liner. It is a schematic block diagram of the fuel supply apparatus which comprised 2nd Embodiment of the pressure | voltage rise apparatus for low temperature fluid by this invention. It is a schematic longitudinal cross-sectional view which shows 8th reference embodiment of the pressure | voltage rise apparatus for low temperature fluid by this invention.

Hereinafter, a first reference embodiment of a booster for a cryogenic fluid according to the present invention will be described with reference to the drawings.
As shown in FIG. 1, the pressurizing apparatus 1 for low temperature fluid according to the present embodiment is configured with a first stage compression unit 10 and a second stage compression unit 20 as main elements.
The first stage compression unit 10 includes a piston (first piston) 11, a piston rod 12, a cylinder block (first cylinder block) 13, and an adiabatic vacuum container (first adiabatic vacuum container) 14. It is a thing.
The piston 11 is a member having a substantially cylindrical shape that is accommodated in a cylinder 13a formed inside the cylinder block 13 so as to be able to reciprocate. A low-temperature fluid (for example, a lower end surface in FIG. 1) , Liquid hydrogen, liquid nitrogen, liquefied carbon dioxide gas, liquefied natural gas, liquefied propane gas, etc.) can be compressed.
A ring groove (not shown) is formed on the outer peripheral surface of the piston 11 (that is, the surface facing the inner peripheral surface (cylinder wall) of the cylinder 13a), and the piston ring 11a is disposed in the ring groove. ing.

The piston rod 12 is a substantially rod-shaped member having a circular shape in cross section, and one end thereof is coupled to the center of the other end surface of the piston 11 and the other end is connected to a power transmission unit (not shown). Yes.
The power transmission unit linearly reciprocates the piston rod 12 in a vertical direction with a stroke of 2 mm, for example, by power from a drive source (not shown).

  The cylinder block 13 is a member having a generally hollow cylindrical cylinder 13a therein. The bottom surface of the cylinder 13a (the lower surface in FIG. 1) is provided with a fluid inlet 13b into which a low-temperature fluid in an atmospheric pressure flows, and the inner peripheral surface of the cylinder 13a (the right surface in FIG. 1). ) Is provided with a fluid outlet 13c through which a compressed low-temperature fluid (pressurized to about 1.3 MPa) flows out. Check valves (check valves) 15 and 16 are provided on the pipes 17 located near the upstream side of the fluid inlet 13b and near the downstream side of the fluid outlet 13c, respectively.

  The adiabatic vacuum container 14 is a container in which the inside is evacuated and a radiation shield plate (not shown) such as a copper plate is disposed therein. A low temperature fluid L is stored (or supplied separately) in the adiabatic vacuum container 14, and substantially the entire cylinder block 13 described above is accommodated so as to be immersed in the low temperature fluid L.

  From the above configuration, in the first stage compression unit 10, the piston 11 connected to one end of the piston rod 12 is moved into the cylinder 13a by the piston rod 12 that linearly reciprocates in the vertical direction by the power from the drive source. The low-temperature fluid sucked into the cylinder 13a from the fluid inlet 13b is compressed by one end surface of the piston 11 and pressurized (increased) to a desired pressure (for example, about 1.3 MPa). Then, it is led out of the cylinder block 14 from the fluid outlet 13c.

The second stage compression unit 20 includes a piston (second piston) 21, a piston rod 22, a cylinder block (second cylinder block) 23, and a heat insulating vacuum container (second heat insulating vacuum container) 24. It is a thing.
The piston 21 is a member having a substantially cylindrical shape that is accommodated in a cylinder 23a formed inside the cylinder block 23 so as to be able to reciprocate. The piston 21 is compressed in the first stage by its one end surface (the lower end surface in FIG. 1). The low-temperature fluid compressed in the unit 10 (for example, liquid hydrogen, liquid nitrogen, liquefied carbon dioxide gas, liquefied natural gas, liquefied propane gas, etc.) can be further compressed.
A ring groove (not shown) is formed on the outer peripheral surface of the piston 21 (that is, the surface facing the inner peripheral surface (cylinder wall) of the cylinder 23a), and the piston ring 21a is disposed in the ring groove. ing.

The piston rod 22 is a substantially rod-like member that has a circular shape in cross section, and has one end connected to the center of the other end surface of the piston 21 and the other end connected to a power transmission unit (not shown). Yes.
The power transmission unit linearly reciprocates the piston rod 22 in a vertical direction with a stroke of 2 mm, for example, by power from a drive source (not shown).

  The cylinder block 23 is a member having a generally hollow cylindrical cylinder 23a therein. The bottom surface of the cylinder 23a (the lower surface in FIG. 1) is provided with a fluid inflow port 23b into which the low-temperature fluid compressed by the first stage compression unit 10 flows, and the inner peripheral surface of the cylinder 23a ( The right side surface in FIG. 1 is provided with a fluid outlet 23c through which a compressed low-temperature fluid (pressurized to about 100 MPa) flows out. The above-described check valve (check valve) 16 is arranged in the pipe 17 located upstream of the fluid inlet 23b, and the check valve (check) is arranged in the pipe 17 located near the downstream side of the fluid outlet 23c. Valve) 25 is provided.

  The adiabatic vacuum container 24 is a container in which the inside is evacuated and a radiation shield plate (not shown) such as a copper plate is disposed therein, and the above-described cylinder block 23 is accommodated in the container. ing.

  With the above configuration, in the second stage compression unit 20, the piston 21 connected to one end of the piston rod 22 is moved into the cylinder 23a by the piston rod 22 that linearly reciprocates in the vertical direction by the power from the drive source. The low-temperature fluid sucked into the cylinder 23a from the fluid inflow port 23b is compressed by one end surface of the piston 21 and pressurized (pressure-increasing) to a desired pressure (for example, about 100 MPa), It is led out of the heat insulating vacuum vessel 24 from the fluid outlet 23c.

  The pipe 17 positioned downstream of the check valve 25 includes an evaporator (heat exchanger) 30 that heats and gasifies the low-temperature fluid compressed by the second-stage compression unit 20, and the evaporator An air accumulator (accumulator) 40 that temporarily stores (stores) the low-temperature fluid gasified by 30 is provided. The gasified cryogenic fluid in the gas accumulator 40 is supplied to a use point (for example, an engine or the like) via the pipe 17 and consumed. And the fuel supply apparatus is comprised by making these evaporator 30, the gas accumulator 40, and the pressurizer 1 for low temperature fluids into the main elements.

According to the pressurizing device 1 for low-temperature fluid according to the present embodiment, the first-stage compression unit 10 and the second-stage compression unit 20 are provided separately (configured), so that the first heat generation amount is large. The heat of the two-stage compression unit 20 can be prevented from being transmitted to the first-stage compression unit 10, and the temperature rise of the first-stage compression unit 10 can be prevented.
Thereby, evaporation of the low temperature fluid sucked into the cylinder 13a can be prevented, the low temperature fluid can be efficiently compressed to a desired pressure (for example, about 1.3 MPa), and a heat insulating vacuum vessel Evaporation of the low temperature fluid stored in 14 can be prevented.

A second reference embodiment of the pressure booster for cryogenic fluid according to the present invention will be described with reference to FIG.
In the pressurizing device 1a for low-temperature fluid in the present embodiment, the pipe 17a that connects the fluid outlet 13c of the first stage compression unit 10 and the fluid inlet 23b of the second stage compression unit 20 has a low thermal conductivity material (for example, SUS304, SUS316, titanium alloy, etc.), which differs from that of the first reference embodiment described above. Since other components are the same as those in the above-described embodiment, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 1st reference embodiment mentioned above.

According to the cryogenic fluid booster 1a according to the present embodiment, the first-stage compression unit 10 and the second-stage compression unit 20 are connected by the pipe 17a made of a material having a low thermal conductivity, so that a large amount of heat is generated. The heat of the second stage compression unit 20 can be further prevented from being transmitted to the first stage compression unit 10, and the temperature rise of the first stage compression unit 10 can be further prevented.
Thereby, evaporation of the low temperature fluid sucked into the cylinder 13a can be prevented, the low temperature fluid can be more efficiently compressed to a desired pressure (for example, about 1.3 MPa), and an adiabatic vacuum can be obtained. It is possible to further prevent evaporation of the low temperature fluid stored in the container 14.
In addition, when the calorific value in the second stage compression unit 20 is several hundred W, the material, pipe length, and pipe thickness of the pipe 17a are set so that the amount of heat transmitted to the first stage compression unit 10 is 10 W or less. If is selected, it is more preferable.
Thereby, the evaporation amount of the low temperature fluid in the 1st stage compression part 10 can be made into substantially zero (zero).

A third reference embodiment of the cryogenic fluid booster according to the present invention will be described with reference to FIG.
The low-temperature fluid booster 1b according to this embodiment includes a first cooling unit 27 for cooling the cylinder block 23 and a second cooling unit 28 for cooling the radiation shield plate 26. It differs from that of the first reference embodiment described above. Since other components are the same as those in the above-described embodiment, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 1st reference embodiment mentioned above.

The first cooling unit 27 includes a pipe 17 disposed so as to be in contact with the outer peripheral surface of the cylinder block 23, and heat generated in the cylinder 23 a is taken away (taken away) by the low-temperature fluid passing through the pipe 17. At the same time, the temperature of the second stage compression unit 20a can be lowered.
The second cooling unit 28 includes a pipe 17 disposed so as to be in contact with the outer peripheral surface (or inner peripheral surface) of the radiation shield plate 26, and the entire radiation shield plate 26 is cooled by the low-temperature fluid passing through the pipe 17. Thus, the temperature of the second stage compression unit 20a can be further reduced.

According to the pressurizing device 1b for a low-temperature fluid according to the present embodiment, the first stage compression unit 10 and the second stage compression unit 20a are provided separately (configured), so the first heat generation amount is large. The heat of the two-stage compression unit 20a can be prevented from being transmitted to the first-stage compression unit 10, and the temperature rise of the first-stage compression unit 10 can be prevented.
Thereby, evaporation of the low temperature fluid sucked into the cylinder 13a can be prevented, the low temperature fluid can be efficiently compressed to a desired pressure (for example, about 1.3 MPa), and a heat insulating vacuum vessel Evaporation of the low temperature fluid stored in 14 can be prevented.
Further, since the heat generated in the second stage compression unit 20a is taken away by the low temperature fluid passing through the first cooling unit 27 and the second cooling unit 28, the temperature rise of the second stage compression unit 20 is prevented. This can be further prevented, and the temperature rise of the first stage compression unit 10 can be further prevented.

In addition, although this embodiment demonstrated what comprised both the 1st cooling part 27 and the 2nd cooling part 28, this invention is not limited to this, It comprises only any one cooling part. It is also possible to make it.
Moreover, it is also possible to combine both or any one of these cooling parts, and the piping 17a demonstrated in 2nd reference embodiment, and can anticipate the further effect by this.

A fourth reference embodiment of the cryogenic fluid booster according to the present invention will be described with reference to FIG.
As shown in FIG. 4, the pressurizing device 2 for low temperature fluid according to the present embodiment is configured with a piston 51, a piston rod 52, a cylinder block 53, and a heat insulating vacuum vessel 54 as main elements.
The piston 51 is a substantially cylindrical member having a substantially cross shape in cross-sectional view and accommodated in a cylinder 53a formed inside the cylinder block 53 so as to be reciprocally movable. One end surface of the large-diameter portion 51a (FIG. 1). The low-temperature fluid (for example, liquid hydrogen, liquid nitrogen, liquefied carbon dioxide, liquefied natural gas, liquefied propane gas, etc.) is compressed by one end face (the lower face in FIG. 1) of the small diameter portion 51b. To get.
In addition, ring grooves are formed on the outer peripheral surfaces of the large-diameter portion 51a and the small-diameter portion 51b of the piston 51 (that is, the surfaces facing the inner peripheral surface (cylinder wall) of the cylinder 53a). Piston rings 51 a ′ and 51 b ′ are respectively arranged in the inside.

On the opposite side of the large-diameter portion 51a from the small-diameter portion 51b, an intermediate-diameter portion 51c that penetrates the central portion of the cylinder head 55 is provided. A ring groove is formed on the outer peripheral surface of the medium diameter portion 51c (that is, the surface facing the inner peripheral surface of the cylinder head 55), and a piston ring 51c ′ is disposed in the ring groove.
Inside the piston 51, a communication passage 51d is formed which communicates a flow path inlet 51d 'opening toward one end face of the large diameter part 51a and a flow path outlet 51 "opening at one end face of the small diameter part 51b. Further, a first discharge port 51e is provided in the vicinity of the downstream side of the flow path outlet 51 ″.

The piston rod 52 is a substantially rod-like member having a circular shape in cross section, and one end thereof is connected to the center of one end surface of the medium diameter portion 51c, and the other end is connected to a power transmission unit (not shown). Has been.
The power transmission unit linearly reciprocates the piston rod 52 in a vertical direction with a stroke of 2 mm, for example, by power from a drive source (not shown).

The cylinder block 53 is a member having a substantially hollow cylindrical cylinder 53a therein. The cylinder 53a includes a first cylinder 53a ′ that slidably accommodates the large-diameter portion 51a of the piston 51, and a second cylinder 53a ″ that slidably accommodates the small-diameter portion 51b of the piston 51. Outside the second cylinder 53a ″, there is provided a first cooling part 67 comprising a pipe 57 arranged so as to be in contact with the outer peripheral surface of the cylinder block 53. The heat generated in the second cylinder 53a ″ is taken away (taken away) by the passing low-temperature fluid.
A second discharge port 53b is provided at the bottom (lower end in FIG. 4) of the cylinder block 53, and a cylinder head 55 is provided at the top (upper end in FIG. 4) of the cylinder block 53. Yes.
The cylinder head 55 covers one end surface (the upper end surface in FIG. 4) of the cylinder block 53 and closes the opening end of the first cylinder 53 a ′ formed inside the cylinder block 53.
A suction port 55a is provided on one end face of the cylinder head 55 (the lower end face in FIG. 4), that is, the face facing the one end face of the large-diameter portion 51a. Each of the suction port 55a and the first discharge port 51e and the second discharge port 53b described above is provided with a ball type check valve 56 (a spring is not shown for simplification). Inhalation and discharge are controlled.
A pipe 57 is connected to each of the suction port 55a and the second discharge port 53b.

  The adiabatic vacuum vessel 54 is a vessel in which the inside is evacuated and a radiation shield plate 66 such as a copper plate is disposed therein, and the above-described cylinder block 53 is accommodated therein. A second cooling unit 68 including a pipe 57 disposed so as to be in contact with the outer peripheral surface is provided on the outer peripheral surface of the radiation shield plate 66, and the radiation shield plate 66 is formed by a low-temperature fluid passing through the pipe 57. The whole is cooled.

  From the above configuration, when the piston rod 52 is linearly reciprocated in the vertical direction by the power from the drive source, the piston 51 coupled to the piston rod 52 is linearly reciprocated in the vertical direction, and the pipe 57 Through the suction port 55a and into the first pressurizing chamber (that is, the space surrounded by one end surface of the large diameter portion 51a, one end surface of the cylinder head 55, and the inner peripheral surface of the first cylinder 53a ') S1. Cold fluid is inhaled. The low-temperature fluid sucked into the first pressurizing chamber S1 is compressed by one end surface of the large-diameter portion 51a and pressurized (pressurized) to a desired pressure (for example, about 1.3 MPa), and then communicated. 51d and the first discharge port 51e are surrounded by the second pressurizing chamber (that is, one end surface of the small diameter portion 51b, the bottom surface of the second cylinder 53a ″, and the inner peripheral surface of the second cylinder 53a ″). Space) is led into S2. The low-temperature fluid introduced into the second pressurizing chamber S2 is compressed by one end surface of the small diameter portion 51b and pressurized (pressurized) to a desired pressure (for example, about 100 MPa), and then the second discharge port. The heat insulating vacuum vessel 54 is led out of the heat insulating vacuum vessel 54 through the pipe 57 from 53b.

  The pipe 57 located on the downstream side of the heat insulating vacuum vessel 54 is provided with an evaporator (heat exchanger) 30 that heats and gasifies the low-temperature fluid discharged from the second discharge port 53b, and the evaporator 30. An air accumulator (accumulator) 40 is provided for temporarily (temporarily) accumulating (temporarily) storing the low-temperature fluid gasified by the above. The gasified low-temperature fluid in the air reservoir 40 is supplied to a use point (for example, an engine or the like) via the pipe 57 and consumed. And the fuel supply apparatus is comprised by making these evaporator 30, the gas accumulator 40, and the pressurizer 1 for low temperature fluids into the main elements.

According to the cryogenic fluid booster 2 according to this embodiment, the first cooling unit 67 cools the cylinder block 53 on the second pressurizing chamber S2 side, and the second cooling unit 68 cools the entire radiation shield plate 66. As a result, it is possible to prevent the heat of the second pressurizing chamber S2 that generates a large amount of heat from being transmitted to the first pressurizing chamber S1, and to increase the temperature of the first pressurizing chamber S1. Can be prevented.
Thereby, evaporation of the low temperature fluid sucked into the first pressurizing chamber S1 can be prevented, and the low temperature fluid can be efficiently compressed to a desired pressure (for example, about 1.3 MPa).

  In addition, although this embodiment demonstrated what comprised both the 1st cooling part 67 and the 2nd cooling part 68, this invention is not limited to this, It comprises only any one cooling part. It is also possible to make it.

A fifth reference embodiment of the cryogenic fluid booster according to the present invention will be described with reference to FIG.
In the pressurizing device 2a for low-temperature fluid in the present embodiment, the flange portion F of the cylinder block 153 positioned at least between the first cylinder 53a ′ and the second cylinder 53a ″ is made of a material having a low thermal conductivity (for example, SUS304). SUS316, titanium alloy, etc.) in that the first cooling unit 67 and the second cooling unit 68 described in the fourth reference embodiment are different from those of the fourth reference embodiment described above. Instead, it differs from that of the fourth reference embodiment described above in that a cylinder block 153 having a flange portion F made of a material having a low thermal conductivity is provided. Therefore, the description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 4th reference embodiment mentioned above.

According to the cryogenic fluid booster 2a according to the present embodiment, the heat of the second pressurizing chamber S2 having a large calorific value is transmitted to the first pressurizing chamber S1 by the flange portion F made of a material having low thermal conductivity. It is possible to prevent the temperature of the first pressurizing chamber S1 from rising.
Thereby, evaporation of the low temperature fluid sucked into the first pressurizing chamber S1 can be prevented, and the low temperature fluid can be efficiently compressed to a desired pressure (for example, about 1.3 MPa).
Note that the material and thickness of the flange portion F are selected so that the amount of heat transmitted to the first pressurizing chamber S1 is 10 W or less when the heat generation amount in the second pressurizing chamber S2 is several hundred W. If so, it is more preferable.
Thereby, the evaporation amount of the low temperature fluid in the first pressurizing chamber S1 can be made substantially zero (zero).

A sixth reference embodiment of the cryogenic fluid booster according to the present invention will be described with reference to FIG.
The cryogenic fluid booster 2b in the present embodiment is provided with a tank T inside the heat insulating vacuum vessel 154 instead of the first cooling unit 67 and the second cooling unit 68 described in the fourth reference embodiment. This is different from that of the fourth reference embodiment described above. Since other components are the same as those in the above-described embodiment, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 4th reference embodiment mentioned above.

  The tank T is disposed on the upper part of the heat insulating vacuum vessel 154, and the low temperature fluid L is stored (or supplied separately) therein. Further, as shown in FIG. 6, only the upper portion of the cylinder block 53 (that is, the portion where the first pressurizing chamber S1 exists) is immersed in the low temperature fluid L.

According to the pressurizing device 2b for low temperature fluid according to the present embodiment, the cylinder block 53 on the first pressurizing chamber S1 side is always cooled by the low temperature fluid L stored (or supplied separately) in the tank T. The heat of the second pressurizing chamber S2, which generates a large amount of heat, can be prevented from being transmitted to the first pressurizing chamber S1, and the temperature rise of the first pressurizing chamber S1 can be prevented.
Thereby, evaporation of the low temperature fluid sucked into the first pressurizing chamber S1 can be prevented, and the low temperature fluid can be efficiently compressed to a desired pressure (for example, about 1.3 MPa).

A seventh reference embodiment of the pressurizing device for low-temperature fluid according to the present invention will be described with reference to FIG.
In the pressurizing device 3 for cryogenic fluid according to the present embodiment, the first-stage compression unit 10 shown in FIG. 3 is omitted, and the space between the adiabatic vacuum vessel 24 and the cylinder block 23 constituting the second-stage compression unit 20a is omitted. The third embodiment is different from the third embodiment described above in that the low-temperature fluid L is stored (or supplied separately). Since other components are the same as those in the above-described embodiment, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 3rd reference embodiment mentioned above.
Reference numeral 35 denotes a check valve (check valve) provided in the pipe 17 located in the vicinity of the upstream side of the fluid inflow port 23b.

According to the low-temperature fluid booster 3 according to the present embodiment, the low-temperature fluid L stored (or supplied separately) between the adiabatic vacuum vessel 24 and the cylinder block 23, the first cooling unit 27, and the second cooling unit 28. Since the heat generated inside the cylinder block 23 is taken away by the low-temperature fluid passing through the inside, the temperature rise of the cylinder block 23 can be prevented.
Thereby, evaporation of the low temperature fluid sucked into the cylinder 23a can be prevented, and the low temperature fluid can be efficiently compressed to a desired pressure (for example, about 100 MPa). In addition, the configuration of the apparatus can be simplified.

A first embodiment of a cryogenic fluid booster according to the present invention will be described with reference to FIG.
As shown in FIG. 8A, the cryogenic fluid booster 70 is configured mainly with a drive unit (not shown) and a pump unit 71 driven by the drive unit.
The pump unit 71 includes a piston 72, a piston rod 73, a cylinder block 74, and a heat insulating vacuum container 75.
The piston 72 is a member having a substantially cylindrical shape that is accommodated in a cylinder liner 76 provided in contact with (into) the cylinder block 74 so as to be reciprocally movable, and has one end surface (FIG. 8A). In this case, a low-temperature fluid (for example, liquid hydrogen, liquid nitrogen, liquefied carbon dioxide gas, liquefied natural gas, liquefied propane gas, or the like) can be compressed by the lower end face.
A plurality of (three in this embodiment) ring grooves 77 are provided along the circumferential direction on the outer peripheral surface of the piston 72 (that is, the surface facing the inner peripheral surface (cylinder wall) 76a of the cylinder liner 76). In addition to being formed, piston rings (not shown) are arranged in the ring grooves 77, respectively.

The piston rod 73 is a substantially rod-like member having a circular shape in cross section. One end of the piston rod 73 is connected to the center of the other end surface of the piston 72, and the other end is connected to a power transmission unit of a drive unit (not shown). It is connected.
The power transmission unit linearly reciprocates the piston rod 73 in a vertical direction with a stroke of, for example, 2 mm by power from a drive source.

The cylinder block 74 has a generally hollow cylindrical cylinder liner 76 disposed therein, and is made of, for example, austenitic stainless steel (for example, SUS316 or SUS304). Further, on the side surface of the cylinder block 74 (for example, the left and right surfaces in FIG. 8A), the low-temperature fluid L stored in the heat insulating vacuum vessel 75 is formed on the outer peripheral surface of the cylinder liner 76. A plurality of (six in this embodiment) through-holes 74a to be led into the location 76a are provided at equal intervals (60-degree intervals in this embodiment) along the circumferential direction. The bottom surface of the cylinder block 74 (the lower surface in FIG. 8A) is compressed by a fluid inlet 78 that guides a low-temperature fluid under atmospheric pressure to the inside of the cylinder liner 76 and one end surface of the piston 72 ( There is provided a fluid outlet 79 through which a low-temperature fluid (pressurized to about 1.3 MPa) flows out. A pipe 80 is connected to each of the fluid inlet 78 and the fluid outlet 79, and a check valve (not shown) is connected to each of the pipes 80 located near the upstream side of the fluid inlet 78 and near the downstream side of the fluid outlet 79. Check valves) 81 and 82 are provided.
In addition, a through hole 83 through which the piston rod 73 passes is provided on the upper surface of the cylinder block 74 (the upper surface in FIG. 8A), and a low temperature is provided between the piston rod 73 and the through hole 83. A seal 84 is provided.

  The adiabatic vacuum container 75 is a container in which the inside is evacuated and a radiation shield plate (not shown) such as a copper plate is disposed therein. In this heat insulating vacuum vessel 75, the low temperature fluid L is stored (or supplied separately), and the above-described cylinder block 74 is accommodated so as to be immersed in the low temperature fluid L.

  With the above configuration, in the cryogenic fluid booster 70, the piston 72 connected to one end of the piston rod 73 is connected to the cylinder liner 76 by the piston rod 73 that linearly reciprocates in the vertical direction by the power from the drive source. The low-temperature fluid that reciprocates inside and is sucked into the cylinder liner 76 from the fluid inlet 78 is compressed by one end surface of the piston 72 and pressurized (pressure-increasing) to a desired pressure (for example, about 1.3 MPa). Then, it is led out of the cylinder block 74 from the fluid outlet 79.

Next, the cylinder liner 76 will be described in more detail with reference to FIG.
The piston liner 76 is made of a metal material that is not easily worn (for example, stellite, martensitic stainless steel (for example, SUS440C)), and a plurality of piston liners 76 are arranged along the height direction (vertical direction in FIG. 8) on the outer peripheral surface. This (six in this embodiment) recess 76b is provided. One end (upper end in FIG. 8) of the recess 76b is an open end (open state), and the lower end (lower end in FIG. 8) is a closed end (closed state).
Then, the low temperature fluid L stored in the heat insulating vacuum vessel 75 flows into the respective recesses 76b through the through holes 74a provided corresponding to the respective recesses 76b. The entire cylinder liner 76 is efficiently cooled. Further, the low temperature fluid L evaporated by receiving heat from the cylinder liner 76 flows out from the open end of the recess 76b.

According to the cryogenic fluid booster 70 according to the present embodiment, the recess 76b is provided between the cylinder block 74 and the cylinder liner 76, and the recess 76b is always filled with the cryogenic fluid L. Frictional heat generated when the piston ring slides along the inner wall surface 76a of the cylinder liner 76 can be efficiently recovered via the cylinder liner 76 sufficiently cooled by the low-temperature fluid L. Temperature rise can be prevented.
Thereby, evaporation of the low temperature fluid sucked into the cylinder liner 76 can be prevented, the low temperature fluid can be efficiently compressed to a desired pressure (for example, about 1.3 MPa), and an adiabatic vacuum can be obtained. Evaporation of the low temperature fluid stored in the container 75 can be prevented.

A second embodiment of the low temperature fluid booster according to the present invention will be described with reference to FIGS.
As shown in FIG. 9 (a), the cryogenic fluid booster 90 includes a driving unit (not shown) and a pump unit 91 driven by the driving unit as main elements.
The pump unit 91 includes a piston 92, a piston rod 93, and a cylinder block 94.
The piston 92 is a member having a substantially cylindrical shape which is accommodated in a cylinder liner 96 provided in contact with (into) the cylinder block 94 so as to be reciprocally movable, and has one end surface (FIG. 9A). In this case, a low-temperature fluid (for example, liquid hydrogen, liquid nitrogen, liquefied carbon dioxide gas, liquefied natural gas, liquefied propane gas, or the like) can be compressed by the lower end face.
In addition, a plurality of (three in the present embodiment) ring grooves 97 along the circumferential direction are formed on the outer peripheral surface of the piston 92 (that is, the surface facing the inner peripheral surface (cylinder wall) 96a of the cylinder liner 96). In addition, piston rings (not shown) are arranged in the ring grooves 97, respectively.

The piston rod 93 is a substantially rod-like member having a circular shape in cross section, and one end portion thereof is connected to the center portion of the other end surface of the piston 92, and the other end portion is connected to a power transmission portion of a driving portion (not shown). It is connected.
The power transmission unit linearly reciprocates the piston rod 93 in a vertical direction with a stroke of, for example, 2 mm by power from a drive source.

The cylinder block 94 has a generally hollow cylindrical cylinder liner 96 disposed therein, and is made of, for example, austenitic stainless steel (for example, SUS316 or SUS304). Further, the cylinder block 94 is compressed on the bottom surface (the lower surface in FIG. 9A) by a fluid inlet 98 that guides a low-temperature fluid under atmospheric pressure to the inside of the cylinder liner 96 and one end surface of the piston 92. In addition, a fluid outlet 99 through which a low-temperature fluid (pressurized to about 1.3 MPa) flows out is provided. Pipes 100 are connected to the fluid inlet 98 and the fluid outlet 99, respectively, and check valves (not shown) are respectively connected to the pipes 100 located near the upstream side of the fluid inlet 98 and the downstream side of the fluid outlet 99. Check valves) 101 and 102 are provided.
Further, a through hole 103 through which the piston rod 93 passes is provided on the upper surface (the upper surface in FIG. 9A) of the cylinder block 94, and the temperature between the piston rod 93 and the through hole 103 is low. A seal 104 is provided.

  With the above configuration, in the cryogenic fluid booster 90, the piston 92 connected to one end of the piston rod 93 is connected to the cylinder liner 96 by the piston rod 93 that linearly reciprocates in the vertical direction by the power from the drive source. The low-temperature fluid that reciprocates inside and is sucked into the cylinder liner 96 from the fluid inflow port 98 is compressed by one end surface of the piston 92, and is pressurized (increased) to a desired pressure (for example, about 1.3 MPa). Then, the fluid is led out from the fluid outlet 99 to the outside of the cylinder block 94.

Next, the cylinder liner 96 will be described in more detail with reference to FIG.
The piston liner 96 is made of a metal material that is not easily worn (for example, stellite, martensitic stainless steel (for example, SUS440C), etc.), and has a thick portion along the height direction (vertical direction in FIG. 9). A plurality (six in this embodiment) of communication holes are provided in which both ends (the upper end and the lower end in FIG. 9) are open ends (open state). In addition, a pipe 96b made of, for example, copper or stainless steel is inserted into each of the communication holes by cold fitting so as to contact the inside of the communication hole. One pipe 96b and another pipe 96b disposed adjacent to the one pipe 96b are connected by, for example, a plurality of (in this embodiment, five) connecting pipes 106 made of copper or stainless steel. Has been. Further, the pipe 100 provided on the downstream side of the fluid outlet 99 is connected to one pipe 96 b, and the low-temperature fluid led out of the cylinder block 94 from the fluid outlet 99 becomes the meat of the cylinder liner 96. The pipe 96b provided in the thick part is sequentially passed along the circumferential direction (see FIG. 9B or FIG. 10).

  A pipe 100 is connected to the outlet end of the pipe 96b located on the most downstream side, and the pipe 100 is vaporized by heating and gasifying the low-temperature fluid compressed by the low-temperature fluid booster 90. A heat exchanger (heat exchanger) 30 and an air accumulator (pressure accumulator) 40 that temporarily (temporarily) stores (stores) the low-temperature fluid gasified by the evaporator 30 are provided. The gasified cryogenic fluid in the gas accumulator 40 is supplied to a use point (for example, an engine or the like) via the pipe 100 and consumed. And the fuel supply apparatus is comprised by making these evaporator 30, the air accumulator 40, and the pressure | voltage rise apparatus 90 for low temperature fluids into the main elements. In addition, the code | symbols 107 and 108 in FIG. 10 have each shown the valve | bulb (open / close valve).

According to the pressurizing device 90 for a low temperature fluid according to the present embodiment, a plurality of pipes 96b are provided in the thick part of the cylinder liner 76, and the low temperature fluid is always passed through the pipes 96b. The frictional heat generated by sliding along the inner wall surface 96a of the cylinder liner 96 can be efficiently recovered via the cylinder liner 96 sufficiently cooled by the low-temperature fluid, and the temperature rise of the entire apparatus can be achieved. Can be prevented.
Thereby, evaporation of the low temperature fluid sucked into the cylinder liner 96 can be prevented, and the low temperature fluid can be efficiently compressed to a desired pressure (for example, about 1.3 MPa).

An eighth reference embodiment of the cryogenic fluid booster according to the present invention will be described with reference to FIG.
As shown in FIG. 11, the cryogenic fluid booster 110 includes a drive unit (not shown) and a pump unit 111 driven by the drive unit as main elements.
The pump unit 111 includes a piston 112, a piston rod 113, a cylinder block 114, and a heat insulating vacuum container 115.
The piston 112 is a substantially cylindrical member having an I-shaped cross-sectional view having a recess 112a formed along the circumferential direction at an intermediate portion in the height direction, and a cylinder formed inside the cylinder block 114. 114b is housed in a reciprocable manner so that a low-temperature fluid (for example, liquid hydrogen, liquid nitrogen, liquefied carbon dioxide gas, liquefied natural gas, liquefied propane gas, etc.) is contained at one end face (lower end face in FIG. 11). It can be compressed.
The outer peripheral surface (namely, the diameter-expanded portion located on the lower side of the recess 112a in FIG. 11) and the other end portion (the diameter-expanded portion located on the upper side of the recess 112a in FIG. 11) of the piston 112 (that is, A ring groove 117 is formed along the circumferential direction on the inner peripheral surface (cylinder wall) of the cylinder 114b, and a piston ring (not shown) is formed in each ring groove 117. Are arranged.
Further, a plurality of communication holes 112b penetrating in the plate thickness direction (vertical direction in FIG. 11) are provided in the circumferential end portion of the other end portion of the piston 112 along the circumferential direction (for example, six at intervals of 60 degrees). Is provided.

The piston rod 113 is a substantially rod-like member having a circular shape in cross section, and one end thereof is connected to the central portion of the other end surface of the piston 112, and the other end is connected to a power transmission portion of a drive unit (not shown). It is connected.
The power transmission unit linearly reciprocates the piston rod 113 in a vertical direction with a stroke of, for example, 2 mm by power from a drive source.

The cylinder block 114 is a member having an approximately hollow cylindrical cylinder 114b therein, and the low-temperature fluid L stored in the heat insulating vacuum vessel 115 is disposed on the side surfaces (for example, the left and right surfaces in FIG. 11). A plurality of (for example, six) through holes 114a for guiding the gas into the cylinder 114b are provided at equal intervals (for example, at intervals of 60 degrees) along the circumferential direction. The bottom surface of the cylinder block 114 (the lower surface in FIG. 11) is compressed by a fluid inlet 118 that guides a low-temperature fluid under atmospheric pressure to the inside of the cylinder 114b and one end surface of the piston 112 (about 1.3 MPa). And a fluid outlet 119 through which a low-temperature fluid is discharged. Pipes 180 are connected to the fluid inlet 118 and the fluid outlet 119, respectively, and check valves (not shown) are respectively connected to the pipes 180 located near the upstream side of the fluid inlet 118 and the downstream side of the fluid outlet 119. Check valves) 181 and 182 are provided.
A through hole 183 through which the piston rod 113 passes is provided on the upper surface (the upper surface in FIG. 11) of the cylinder block 114, and a low temperature seal 84 is provided between the piston rod 113 and the through hole 83. Is provided.

  The adiabatic vacuum container 115 is a container in which the inside is evacuated and a radiation shield plate (not shown) such as a copper plate is disposed therein. In this heat insulating vacuum vessel 115, the low temperature fluid L is stored (or supplied separately), and the entire cylinder block 114 described above is accommodated in the low temperature fluid L.

With the above configuration, in the cryogenic fluid booster 110, the piston 112 connected to one end of the piston rod 113 is moved into the cylinder 114b by the piston rod 113 that linearly reciprocates in the vertical direction by the power from the drive source. , The low-temperature fluid sucked into the cylinder 114b from the fluid inlet 118 is compressed by one end face of the piston 112 and pressurized (increased) to a desired pressure (for example, about 1.3 MPa). Thereafter, the fluid is led out from the fluid outlet 119 to the outside of the cylinder block 114.
Further, when the piston 112 moves from the bottom dead center to the top dead center, the through hole 114a formed in the side surface of the cylinder block 114 and the communication formed in the other end of the piston 112 in the recess 112a of the piston 112. The low-temperature fluid L stored in the heat insulating vacuum vessel 115 flows through the hole 112b, so that the entire piston 112 is efficiently cooled. On the other hand, when the piston 112 moves from the top dead center to the bottom dead center, the low-temperature fluid L evaporated and evaporated by receiving heat from the piston 112 (or the cylinder 114) passes through the communication hole 112b and the through hole 114a to form an adiabatic vacuum. The container 115 is returned to the inside.

According to the booster 110 for low-temperature fluid according to the present embodiment, the low-temperature fluid L is guided into the recess 112a of the piston 112 and the entire piston 112 is cooled, so that the piston ring is attached to the inner wall surface of the cylinder 114b. Frictional heat generated by sliding along can be efficiently recovered through the piston 112 (or cylinder 114) sufficiently cooled by the low-temperature fluid L, and temperature rise of the entire apparatus can be prevented. it can.
Thereby, evaporation of the low temperature fluid sucked into the cylinder 114b can be prevented, and the low temperature fluid can be efficiently compressed to a desired pressure (for example, about 1.3 MPa).

In addition, although this embodiment demonstrated what comprised both the 1st cooling part 27 and the 2nd cooling part 28, this invention is not limited to this, It comprises only any one cooling part. It is also possible to make it.
The first cooling unit 27 and the second cooling unit 28 described in the third reference embodiment can also be applied to the cylinder block 13 and the heat insulating vacuum container 14 of the first stage compression unit 10.

Furthermore, the second cooling units 28 and 68 described in the third reference embodiment, the fourth reference embodiment, and the seventh reference embodiment have the pipes 17 and 57 constituting the second cooling units 28 and 68, It is more preferable that the radiating shield plates 26 and 66 are wound along the outer peripheral surface (or inner peripheral surface) from the upper side to the lower side (or from the lower side to the upper side).
Thereby, the radiation shield plates 26 and 66 can be cooled most effectively.

  Furthermore, instead of the first cooling unit 27 described in the third reference embodiment and the seventh reference embodiment, the configuration described in the first embodiment and the second embodiment (that is, the cylinder liners 76 and 96 are cooled at a low temperature). It is also possible to adopt a configuration in which the fluid is cooled.

  Furthermore, the configuration described in the first embodiment and the second embodiment (that is, the configuration in which the cylinder liners 76 and 96 are cooled with a low-temperature fluid) has been described in the first reference embodiment to the third reference embodiment. The cylinder block 13, the cylinder block 23 described in the first reference embodiment and the second reference embodiment, and the cylinder blocks 53 and 153 described in the fourth to sixth reference embodiments are also appropriately required. Can be applied.

  Furthermore, the check valves 16 and 25 described in the first to third reference embodiments and the seventh reference embodiment are more preferably disposed inside the heat insulating vacuum containers 14 and 24. is there. By doing in this way, dead space can be reduced and the freedom degree when arrange | positioning an apparatus will increase.

  Furthermore, the cylinder liner 96 described in the second embodiment may be directly immersed in the low-temperature fluid L stored (or supplied separately) in the heat-insulated vacuum container 75 as in the first embodiment. it can. Thereby, the pipe 96b and the connecting pipe 106 can be omitted, and the manufacturing cost can be reduced.

  Furthermore, the pipe 96b and the connecting pipe 106 described in the second embodiment can be configured as a single pipe. By doing so, the joint that connects the pipe 96b and the connecting pipe 106 can be eliminated, so that the manufacturing cost can be reduced, and leakage from the joint can be eliminated. Can be improved.

DESCRIPTION OF SYMBOLS 30 Evaporator 40 Air accumulator 70 Cryogenic pressure booster 72 Piston 74 Cylinder block 74a Through hole 75 Heat insulation vacuum vessel 76 Cylinder liner 76b Recess 77 Piston ring 90 Cryogenic fluid pressure booster 92 Piston 94 Cylinder block 96 Cylinder liner 96b Pipe 97 Piston ring 98 Fluid inlet 99 Fluid outlet 100 Pipe 106 Connecting pipe L Low temperature fluid

Claims (3)

A piston having a piston ring on the outer peripheral surface;
A cylinder liner that slidably accommodates the piston and has a pressurizing chamber in which a low-temperature fluid is compressed by one end surface of the piston;
A cylinder block that houses the cylinder liner such that its inner peripheral surface is in contact with the outer peripheral surface of the cylinder liner;
A heat insulating vacuum container that houses the piston and the cylinder block, and
A pressurizing device for cryogenic fluid in which cryogenic fluid is stored in a space formed between the cylinder block and the heat insulating vacuum vessel,
On the outer peripheral surface of the cylinder liner, a plurality of recesses extending in the vertical direction are provided along the circumferential direction, with the upper end being an open end and the lower end being a closed end.
A side surface of the cylinder block penetrates the low-temperature fluid stored in a space formed between the cylinder block and the heat insulating vacuum vessel into the recess provided on the outer peripheral surface of the cylinder liner. A pressurizing device for cryogenic fluid, wherein a plurality of holes are provided along the circumferential direction. A piston having a piston ring on the outer peripheral surface;
A cylinder liner that slidably accommodates the piston and has a pressurizing chamber in which a low-temperature fluid is compressed by one end surface of the piston;
The cylinder liner is accommodated such that its inner peripheral surface is in contact with the outer peripheral surface of the cylinder liner, and compressed by a fluid inlet for introducing the low-temperature fluid at atmospheric pressure to the pressurizing chamber and one end surface of the piston. A cylinder block provided on the bottom surface with a fluid outlet through which the cryogenic fluid flows out, and a pressurizing device for cryogenic fluid,
The thick portion of the cylinder liner is provided with a plurality of communication holes extending in the up-down direction with the upper and lower ends being open ends, along the circumferential direction,
In each of the communication holes, a pipe whose outer peripheral surface is in contact with the inner peripheral surface of the communication hole is fitted,
Among the pipes, an upstream end of one pipe and the fluid outlet are connected via a pipe, and another pipe disposed adjacent to the downstream end of the one pipe and the one pipe. The low-temperature fluid led from the fluid outlet to the outside of the cylinder block sequentially passes through the pipe along the circumferential direction. A pressurizing device for low-temperature fluid, which is configured as described above. A booster for a cryogenic fluid according to claim 1 or 2,
An evaporator for gasifying the low-temperature fluid boosted by the low-temperature fluid booster;
And a gas storage device for temporarily storing a low-temperature fluid gasified by the evaporator.

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