EP2071190B1 - Pompe booster et moyens d'amené pour fluides à température basse comprenant une telle pompe - Google Patents

Pompe booster et moyens d'amené pour fluides à température basse comprenant une telle pompe Download PDF

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Publication number
EP2071190B1
EP2071190B1 EP09157231A EP09157231A EP2071190B1 EP 2071190 B1 EP2071190 B1 EP 2071190B1 EP 09157231 A EP09157231 A EP 09157231A EP 09157231 A EP09157231 A EP 09157231A EP 2071190 B1 EP2071190 B1 EP 2071190B1
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EP
European Patent Office
Prior art keywords
low
temperature
fluid
piston
piston rod
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
EP09157231A
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German (de)
English (en)
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EP2071190A1 (fr
Inventor
Shuichi Kawasaki
Kenji Nakamichi
Yasuharu Chuman
Atsushi Yuge
Ichirou Takeno
Takashi Maemura
Takanobu Kamiya
Ryo Nakamura
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Publication of EP2071190A1 publication Critical patent/EP2071190A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/06—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure
    • F04B15/08—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure the liquids having low boiling points
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/06—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/02—Pumping installations or systems having reservoirs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B45/00—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids
    • F04B45/02—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having bellows
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/02—Packing the free space between cylinders and pistons

Definitions

  • the present invention relates to a booster pump for compressing low-temperature fluids to increase the pressure and to a low-temperature-fluid feeder having the same.
  • Non-Patent Document 1 Some known low-temperature-fluid booster pumps for compressing low-temperature (e.g., -273°C to 0°C) fluids (e.g., hydrogen, nitrogen, LNG) to increase the pressure have piston rings on piston heads thereof.
  • low-temperature fluids e.g., hydrogen, nitrogen, LNG
  • such a known low-temperature-fluid booster pump has a problem in that a sliding motion occurs while the outer circumferential surfaces of the piston rings are being pressed onto the inner circumferential surface of a cylinder in order to maintain hermeticity, and consequently, friction between these piston rings and the cylinder generates heat, which warms up the fluid.
  • Another problem is that, particularly when high pressure is to be achieved, a high-pressure fluid flowing towards the inner circumferential surfaces of the piston rings even more forcibly presses the outer circumferential surfaces of the piston rings onto the inner circumferential surface of the cylinder, which produces still more considerable friction between these piston rings and the cylinder and consequently generates a larger amount of heat.
  • such a known (low-temperature-fluid) booster pump requires a piston rod disposed between a piston head and a drive mechanism to have a large diameter in order to prevent this piston rod from buckling due to compressive force when a low-temperature fluid is to be compressed. For this reason, heat originating from the drive mechanism is transmitted to low-temperature fluid via the piston rod and the piston head, thereby warming up the low-temperature fluid so considerably as to cause boil-off.
  • JP53-107306U discloses a 2-way diaphragm pump which comprises a piston head that is connected to a piston rod and is reciprocably accomodated in a compression chamber.
  • the piston head is connected to an outer peripheral wall of the compression chamber by means of a diaphragm so as to separate two pump spaces from each other.
  • a drive unit is provided on one side of the piston head and a bellows is provided so as to surround the piston rod in one of the pump spaces and seal it from the compression volume of that pump space.
  • the pump effects alternating compression in the two pump spaces during the reciprocating movement of the piston head.
  • GB 535977 discloses a bellows pump which comprises a pump cylinder, a bellows within the cylinder to provide a space between the cylinder and the bellows for the fluid to be pumped.
  • the bellows has one end sealed to a head of a reciprocating piston member and another end sealed to a base wall of the cylinder which also constitutes a guide for the reciprocating piston member.
  • the head of the piston member is circumferentially spaced from the inner peripheral wall of the cylinder.
  • US-A-3456595 which shows a pump having the technical features as defined in the preamble of patent claim 1, discloses a cryogenic metering pump with a reciprocating pump assembly installed within an insulated enclosure.
  • the pump assembly comprises a piston carried on a rod and sliding within a cylinder.
  • the rod is reciproacting by a motor arranged on a side of the piston where the compression is effected.
  • the piston is sealed with respect to the cylinder wall by means of one or more seal rings and the rod is sealed from the pump space by means of bushings.
  • the present invention has been conceived in light of the above-described circumstances, and an object of the present invention is to provide a booster pump for increasing the pressure of a fluid efficiently without heating the fluid and to provide a low-temperature-fluid storage tank having such a booster pump.
  • the present invention provides a low-temperature-fluid boosting pump as defined in claim 1 and a low-temperature-fluid feeder as defined in claim 13.
  • Preferred embodiments are defined in the dependent claims.
  • the present invention provides a boosting pump which includes a piston having a piston head and a piston rod and a cylinder having a compression chamber that accommodates the piston head so that a fluid is compressed by one end surface of the piston head, wherein there is provided a bellows (flexible partition) for separating a space adjacent to the piston rod from a space adjacent to the cylinder in the compression chamber.
  • a bellows flexible partition
  • the bellows separates a space adjacent to the piston rod from a space adjacent to the cylinder in the compression chamber, and there is no component (e.g., piston ring in the known art) that moves in contact with the inner circumferential surface of the compression chamber. This prevents heat from being generated in the compression chamber and therefore prevents the fluid from being heated.
  • the bellows completely separates a space adjacent to the piston rod from a space adjacent to the cylinder in the compression chamber, the fluid is prevented from leaking from the cylinder side of the compression chamber to the piston rod side of the compression chamber. This improves the pump efficiency.
  • the present invention provides a low-temperature-fluid boosting pump which includes the piston rod driven by a drive unit connected to a driving source; the piston head that is connected to the piston rod and reciprocates with the piston rod; and the cylinder having the compression chamber that accommodates the piston head so that a low-temperature fluid is compressed by one end surface of the piston head, wherein the drive unit is disposed adjacent to the one end surface of the piston head, and a shank of the piston rod is subjected to a tensile force in a direction substantially equal to a direction in which the shank extends when the low-temperature fluid is to be compressed.
  • the low-temperature fluid is compressed by one end surface of the piston head. In other words, when the low-temperature fluid is to be compressed, no compressive force is applied to the piston rod.
  • the diameter of the piston rod can be reduced compared with a piston rod in the known art, which is subjected to a compressive force. Therefore, not only can the amount of heat entering from a driving source be reduced, but also the weight of the piston rod can be reduced. Consequently, the weight of the entire pump can also be reduced.
  • the diameter of the piston head can be increased.
  • the diameter of the piston head is limited to, for example, 40 mm to prevent the piston rod from buckling.
  • the known pump required, for example, five cylinders to achieve a sufficient flow volume of low-temperature fluid.
  • the diameter of the piston head can be, for example, 100 mm, and therefore, a sufficient flow volume can be achieved with a single cylinder.
  • the pump according to the present invention not only can the structure of the pump be simplified, but also the entire pump can be made lightweight and compact.
  • the piston head be divided into at least two concentric subsections to achieve a multistage compression structure where the low-temperature fluid is gradually increased to a desired pressure by sequentially passing through the one end surface of the divided piston head.
  • the piston head is divided into, for example, two subsections, one subsection disposed towards the outside in the radial direction and the other disposed towards the inside in the radial direction, so that the first compression (first-stage compression) is carried out with the subsection disposed towards the outside in the radial direction and the second compression (second-stage compression) is carried out with the subsection disposed towards the inside in the radial direction.
  • first-stage compression is carried out with the subsection disposed towards the outside in the radial direction
  • second compression is carried out with the subsection disposed towards the inside in the radial direction.
  • the stroke of the piston head can be made small, and therefore, the size of the entire pump in the longitudinal direction can be reduced. This contributes to compact design of the pump.
  • the flexible partition for separating a space adjacent to the piston rod from a space adjacent to the cylinder in the compression chamber be provided adjacent to the one end surface and adjacent to the other end surface of the piston head.
  • the partition separates the space adjacent to the piston rod from the space adjacent to the cylinder in the compression chamber, and there is no component (e.g., piston ring in the known art) that moves in contact with the inner circumferential surface of the compression chamber. This prevents heat from being generated in the compression chamber and therefore prevents the flow-temperature fluid from being heated.
  • the partition completely separates a space adjacent to the piston rod from a space adjacent to the cylinder in the compression chamber, the low-temperature fluid is prevented from leaking from the cylinder side of the compression chamber to the piston rod side of the compression chamber. This improves the compression efficiency.
  • the flexible partition for separating a space adjacent to the piston rod from a space adjacent to the cylinder in the compression chamber be provided adjacent to the other end surface of the piston head.
  • the one end surface (compressive surface) of the piston head can be utilized to the full extent for compression of the low-temperature fluid, a larger amount of low-temperature fluid can be compressed at a time. In short, the efficiency (performance) of the pump can be improved.
  • a precooling layer be formed in the cylinder.
  • the entire pump can be cooled sufficiently before the pump is started. This decreases vaporization (boil-off) of the low-temperature fluid supplied to the pump.
  • this precooling layer also serves as a heat-insulating layer while the pump is being operated, vaporization (boil-off) of the low-temperature fluid can be reduced also while the pump is being operated.
  • the drive unit be linked to the piston rod via a heat-insulating connection section.
  • the drive unit is linked to the piston rod via, for example, rolling elements (e.g., balls and rollers) in point or line contact, heat can be significantly prevented from being transmitted (entering) from the drive unit (i.e., driving source) to the piston rod (i.e., piston head).
  • rolling elements e.g., balls and rollers
  • the piston head be linked to the piston rod via a heat insulator.
  • a guiding member for guiding the shank of the piston rod be provided between the cylinder and the piston rod.
  • the guiding member is provided to prevent the piston rod, the piston head, etc., which are housed in the cylinder and reciprocate in the cylinder, from interfering with the inner wall surface (cylinder wall) of the cylinder.
  • reciprocating members such as the piston rod and the piston head perform reciprocal movement in the cylinder without wobbling or vibrating. This can prevent such reciprocating members from interfering with the inner wall surface of the cylinder, and furthermore, allows the reciprocating members to be driven smoothly with minimum driving force.
  • a space between the cylinder and the shank of the piston rod be a vacuum.
  • the cylinder be immersed in low-temperature fluid stored in a low-temperature-fluid storage tank and be attachable to and detachable from the low-temperature-fluid storage tank.
  • the exterior of a portion that accommodates portions for compressing the low-temperature fluid therein, such as the cylinder and the piston head, is immersed in the low-temperature fluid and is always maintained in a low-temperature state.
  • the cylinder is mounted on a lower portion (bottom portion) of the low-temperature-fluid storage tank such that it is easily replaceable.
  • the drive unit and the cylinder be immersed in low-temperature fluid stored in a low-temperature-fluid storage tank and be attachable to and detachable from the low-temperature-fluid storage tank.
  • the exterior of the entire pump including a portion that accommodates portions for compressing the low-temperature fluid therein, such as the cylinder and the piston head, is immersed in the low-temperature fluid and is always maintained in a low-temperature state.
  • the low-temperature-fluid boosting pump is mounted on a lower portion (bottom portion) of the low-temperature-fluid storage tank such that it is easily replaceable.
  • the present invention provides a low-temperature-fluid feeder which includes the above-described low-temperature-fluid boosting pump; a chamber for reserving a low-temperature fluid whose pressure has been increased by the above-described low-temperature-fluid boosting pump; and a fuel injector supplied with the low-temperature fluid from the chamber.
  • the low-temperature fluid whose pressure has been increased to a desired pressure by the low-temperature-fluid boosting pump is temporarily reserved in the chamber disposed downstream of the low-temperature-fluid boosting pump and then passes through a fuel injector into, for example, a combustion chamber, such as an engine.
  • a booster-fluid feeding unit for liquefying or vaporizing the low-temperature fluid in the chamber and supplying the low-temperature fluid into the cylinder disposed adjacent to the other end surface of the piston head of the low-temperature-fluid boosting pump be provided.
  • the low-temperature fluid in the chamber (or the fluid generated by liquefying or vaporizing the low-temperature fluid in the chamber and decreasing the pressure of the liquefied or vaporized fluid using, for example, a pressure regulator) is supplied into the cylinder disposed adjacent to the other end surface of the piston head. This decreases the difference between the pressure on the one end surface (compressive surface) side and the pressure on the other end surface side of the piston head, thus allowing a bellows with low pressure resistance to be employed.
  • a booster-fluid feeding unit for vaporizing the low-temperature fluid in the above-described chamber in a path to the fuel injector and for supplying the low-temperature fluid to the cylinder disposed adjacent to the other end surface of the piston head of the low-temperature-fluid boosting pump be provided.
  • the low-temperature fluid in the chamber (or the fluid generated by or vaporizing the low-temperature fluid in the chamber and decreasing the pressure of the vaporized fluid using, for example, a pressure regulator) is supplied into the cylinder disposed adjacent to the other end surface of the piston head. This decreases the difference between the pressure on the one end surface (compressive surface) side and the pressure on the other end surface side of the piston head, thus allowing a bellows with low pressure resistance to be employed.
  • the chamber be provided with a relief valve.
  • the relief valve operates to prevent the chamber from being damaged.
  • the low-temperature fluid discharged from the relief valve returns through, for example, a return pipe to the suction side of the pump (or a separate fuel battery, if any fuel battery is provided).
  • a pressure-boosted fluid reside on an inner side of the partition.
  • a vaporized low-temperature fluid having a predetermined pressure is provided at (supplied to) an inner side of the partition, and the pressure difference between the inner side and the outer side of the partition becomes small (becomes closer).
  • a low-temperature fluid that has been vaporized as a result of being heated by the heat exchanger and subjected to pressure adjustment by the pressure regulator to a predetermined pressure exists on the inner side (towards the inside in the radial direction) of the partition. Because of this, deformation of the partition can be prevented when the low-temperature fluid drawn into the compression chamber is to be compressed, and therefore, the service life of the partition can be extended. This improves the reliability of the low-temperature-fluid boosting pump.
  • an inner side of the partition be vacuumed.
  • a guiding member for guiding the piston head be provided between the cylinder block and the piston head.
  • the guiding member is provided to prevent the piston rod, the piston head, etc., which are housed in the cylinder and reciprocate in the cylinder, from interfering with the inner wall surface (cylinder wall) of the cylinder.
  • the present invention affords an advantage in that the pressure of fluid can be increased efficiently without heating the fluid.
  • Figs. 1 to 10 , 13 and 26 respectively show embodiments disclosing certain aspects of the invention.
  • a booster pump 1 is a so-called swash-plate (or swash) booster pump.
  • the booster pump 1 includes major components such as a plurality of (e.g., seven) pistons 11; a cylinder block 12; a cylinder head 13; a drive shaft 14; and a swash plate (also called a "yoke") 15.
  • Each piston 11 is a substantially rod-like member which has a circular cross-section.
  • Each piston 11 has a piston head 11a on one end portion thereof and a piston shoe 11b on the other end portion thereof.
  • Each of the pistons 11 is reciprocably housed in a cylinder 12a, which will be described later.
  • the piston head 11a is a so-called large-diameter portion that has an outer diameter larger than the outer diameter of a piston rod 11c that links this piston head 11a and the piston shoe 11b.
  • a low-temperature fluid e.g., liquid hydrogen, liquid nitrogen, liquefied carbon dioxide, liquefied natural gas, or liquefied propane gas
  • the piston shoe 11b is also a so-called large-diameter portion that has an outer diameter larger than the outer diameter of the piston rod 11c.
  • the piston shoe 11b is partially interposed, on an end-surface side thereof, between a shoe plate 15a and a retainer ring 15b of the swash plate 15, which will be described later. Furthermore, the end surface of the piston shoe 11b slides along a tilt angle of the swash plate 15 (a sliding surface P of a thrust roller bearing 16 disposed between the shoe plate 15a and the retainer ring 15b).
  • the cylinder block 12 has therein the same number of cylinders 12a as that of the pistons 11 and the cylinders 12a are formed in a ring, extending along a longitudinal direction (vertical direction in Fig. 1 ). Each cylinder 12a accommodates one piston 11.
  • a compression chamber 12b having an inner diameter larger than the outer diameter of the piston head 11a is provided on one end of each cylinder 12a (upper side in Fig. 1 ) so that this compression chamber 12b accommodates the piston head 11a.
  • a bellows 17 is provided in the compression chamber 12b.
  • This bellows 17 partitions (separates) an inner circumferential side (piston 11 side) from an outer circumferential side (cylinder block 12 side) of the compression chamber 12b, which is disposed closer to the piston shoe 11b (lower side in Fig. 1 ) than the piston head 11a.
  • One end surface of the bellows 17 is affixed to a surface opposite (other end surface) one end surface of the piston head 11a, and the other end of the bellows 17 is affixed to an inner wall surface of the cylinder block 12.
  • this bellows 17 is made of, for example, stainless steel or Inconel, which exhibits elasticity at (super) low temperatures.
  • the cylinder head 13 covers one end surface (upper end surface in Fig. 1 ) of the cylinder block 12 to close the open ends of the cylinders 12a formed in the cylinder block 12 (i.e., open ends of the compression chambers 12b).
  • each suction port 13a and a discharge port 13b are provided for each compression chamber 12b.
  • Each of the suction port 13a and the discharge port 13b is provided with a ball check valve 18 (a spring is not shown in the figure for the sake of simplicity) to control suction and discharge of low-temperature fluid.
  • each suction port 13a communicates with a fluid-suction channel 19 formed in the cylinder head 13
  • each discharge port 13b communicates with a fluid-discharge channel 20 formed in the cylinder head 13 and the cylinder block 12.
  • the drive shaft 14 transmits a driving force from a driving source (e.g., an electric motor or an engine), not shown in the figure, to the swash plate 15.
  • a driving source e.g., an electric motor or an engine
  • the drive shaft 14 is rotatably supported at the other end portion of the cylinder block 12 by bearings 21.
  • the swash plate 15 includes the shoe plate 15a and the retainer ring 15b.
  • the sliding surface P of the thrust roller bearing 16 disposed between the shoe plate 15a and the retainer ring 15b is defined at an angle of, for example, 1.43 degree relative to an axis perpendicular to the longitudinal axis of the cylinder block 12. Furthermore, the above-described piston shoe 11b is partially interposed between the retainer ring 15b and the thrust roller bearing 16.
  • a thrust roller bearing 22 is disposed also between the shoe plate 15 and the cylinder block 12. This thrust roller bearing 22 provides a thrust (load) in the axial direction (longitudinal direction of the cylinder block 12).
  • the shoe plate 15a, retainer ring 15b, and thrust roller bearings 16 and 22 rotate integrally with the drive shaft 14.
  • the piston shoes 11b slide along the sliding surface P, and thereby the pistons 11 reciprocate in the cylinder 12a, thus causing low-temperature fluid flowing in the compression chambers 12b to be compressed successively.
  • the stroke of each piston 11 is set to 2 mm.
  • Reference numeral 23 in Fig. 1 denotes continuous holes that allow the respective compression chambers 12b to communicate with the outside of the booster pump 1.
  • a pipe 24 is connected to each of these continuous holes 23, and an on-off valve 25 is disposed at an intermediate point in this pipe 24.
  • each compression chamber 12b When low-temperature fluid is drawn into each compression chamber 12b, the continuous hole 23, the pipe 24, and the on-off valve 25 are used to cause low-temperature fluid residing adjacent to the other end surface of the piston head 11a to flow out of the compression chamber 12b to reduce the drive resistance of the piston 11 or to cause low-temperature fluid built up in the compression chamber 12b disposed adjacent to the other end surface of the piston head 11a to flow out of the compression chamber 12b.
  • the on-off valves 25 are closed (off) during a compression stroke or if it is not necessary to expel low-temperature fluids out of the compression chambers 12b.
  • the booster pump 1 does not include a component (e.g., piston ring in the known art) that moves in contact with the inner circumferential surfaces of the compression chambers 12b. This prevents heat from being generated in the compression chambers 12b and therefore prevents the low-temperature fluid from being heated.
  • a component e.g., piston ring in the known art
  • the bellows 17 completely separates the inner circumferential side from the outer circumferential side of each compression chamber 12b disposed closer to the piston shoe 11b than the piston head 11a. This can prevent the low-temperature fluid from leaking from the outer circumferential side of the compression chamber 12b into the inner circumferential side of the compression chamber 12b. In other words, the low-temperature fluid can be prevented from flowing out from the compression chamber 12b side towards the piston shoe 11b side along the piston rods 11c. As a result, the compression efficiency of the booster pump 1 can be improved.
  • a booster pump 2 in this embodiment differs from the booster pump according to the above-described first embodiment in that (thin) wires (fillers) 31 made of a material that can be used at (super) low temperatures, such as Teflon ® , is wound around the outer circumferential surface of the bellows 17.
  • the other components are the same as those described in the above-described embodiment, and hence a description thereof will be omitted.
  • the wires 31 are wound around the outer surface of the bellows 17 so as to minimize the gap between the outer surface of the bellows 17 and the inner circumferential surface of the compression chamber 12b.
  • the gap between the outer surface of the bellows 17 and the inner circumferential surface of the compression chamber 12b is minimized to reduce a dead volume of the compression chamber 12b. This increases the compression efficiency.
  • a third embodiment of a (low-temperature-fluid) booster pump according to the present invention will now be described with reference to Fig. 4 .
  • a booster pump 3 in this embodiment differs from the booster pump according to the above-described second embodiment in that spacers (fillers) 41 made of a material that can be used at (super) low temperatures, such as Teflon ® , are provided on the outer circumferential surface of the bellows 17.
  • spacers (fillers) 41 made of a material that can be used at (super) low temperatures, such as Teflon ® , are provided on the outer circumferential surface of the bellows 17.
  • the other components are the same as those described in the above-described embodiment, and hence a description thereof will be omitted.
  • one spacer 41 which is substantially ring-shaped in plan view, is disposed in each valley (portion recessed towards the piston rod 11c, that is, portion further away from the inner circumferential surface of the compression chamber 12b) of the bellows 17 so as to minimize the gap between the outer surface of the bellows 17 and the inner circumferential surface of the compression chamber 12b.
  • This spacer 41 in each valley has a cross section whose shape is substantially equal to the shape of the cross section of each valley of the bellows 17 so as not to prevent the bellows 17 from extending and contracting.
  • the gap between the outer surface of the bellows 17 and the inner circumferential surface of the compression chamber 12b is minimized to reduce a dead volume of the compression chamber 12b. This increases the compression efficiency.
  • a fourth embodiment of a (low-temperature-fluid) booster pump according to the present invention will now be described with reference to Fig. 5 .
  • a booster pump 4 in this embodiment differs from the booster pumps according to the above-described second and third embodiments in that particulate filler 51 made of a material that can be used at (super) low temperatures, such as Teflon ® , is disposed on or near the outer circumferential surface of the bellows 17.
  • particulate filler 51 made of a material that can be used at (super) low temperatures, such as Teflon ® , is disposed on or near the outer circumferential surface of the bellows 17.
  • the other components are the same as those described in the above-described embodiments, and hence a description thereof will be omitted.
  • the particulate filler 51 is disposed between the outer surface of the bellows 17 and the inner circumferential surface of the compression chamber 12b so as to minimize the gap between the outer surface of the bellows 17 and the inner circumferential surface of the compression chamber 12b.
  • an anti-flow ring 52 is provided at one end portion of the bellows 17 to prevent the filler 51 from flowing towards one end surface of the piston head 11a.
  • This ring 52 is formed so as to have an outer diameter that is smaller than the inner diameter of the compression chamber 12b. This prevents the outer circumferential surface of the ring 52 from sliding along the inner circumferential surface of the compression chamber 12b.
  • Particles constituting the filler 51 are each formed so as to have an outer diameter larger than the size of the gap between the outer circumferential surface of the ring 52 and the inner circumferential surface of the compression chamber 12b. Furthermore, as much filler 51 as necessary is supplied so long as it does not prevent the bellows 17 from extending and contracting.
  • the gap between the outer surface of the bellows 17 and the inner circumferential surface of the compression chamber 12b is minimized to reduce a dead volume of the compression chamber 12b. This increases the compression efficiency.
  • a fifth embodiment of a (low-temperature-fluid) booster pump according to the present invention will now be described with reference to Fig. 6 .
  • a booster pump 5 in this embodiment differs from the booster pump according to the above-described embodiment in that a sealing member 61 made of a material that can be used at (super) low temperatures, such as Teflon ® , is affixed at one end portion on the outer circumferential surface of the bellows 17.
  • the other components are the same as those described in the above-described embodiment, and hence a description thereof will be omitted.
  • the sealing member 61 for reducing the pressure applied by the low-temperature fluid to the outer circumferential surface of the bellows 17 is disposed at one end portion of the bellows 17.
  • This sealing member 61 is formed so as to have an outer diameter that is substantially equal to the inner diameter of the compression chamber 12b so that the outer circumferential surface of the ring 52 moves along in slight contact with the inner circumferential surface of the compression chamber 12b.
  • This sealing member 61 neither has tension, as has been problematic, for example, with a piston ring in the known art, nor generates heat, as with a known piston ring, because the bellows 17 considerably restricts the stroke of the piston 11 (the stroke is small).
  • low-temperature fluid built up in the compression chamber 12b disposed adjacent to the other end surface of the piston head 11a are stored temporarily in a buffer (chamber), not shown in the figure, through the above-described continuous hole 23, pipe 24, and on-off valve 25 and are then vaporized for use.
  • this low-temperature fluid returns through a pipe, not shown in the figure, to the fluid-suction channel 19 of the booster pump 5 for the purpose of recompression.
  • the sealing member 61 can reduce leakage of the low-temperature fluid from one end surface towards the other end surface of the piston head 11a, which would reduce the pressure applied to the outer circumferential surface of the bellows 17. This allows a low-pressure bellows which does not need to meet strict robust design requirements to be employed and therefore allows the piston 11 to have a large stroke. Consequently, the compression efficiency (pump efficiency) can be improved.
  • the outer circumferential surface of the sealing member 61 is designed to move along in slight contact with the inner circumferential surface of the compression chamber 12b, heat generation in the compression chamber 12b can be reduced significantly. Consequently, heating of the low-temperature fluid can also be moderated.
  • a (low-temperature-fluid) booster 6 including one of the above-described (low-temperature-fluid) booster pumps as a low-pressure pump 6L and one of the above-described (low-temperature-fluid) booster pumps as a high-pressure pump 6H will be described below with reference to Figs. 7 and 8 .
  • the low-pressure pump 6L compresses low-pressure (low bulk modulus) low-temperature fluid to an intermediate pressure.
  • the low-pressure pump 6L includes a low-pressure bellows 17a which does not need to meet strict robust design requirements so long as it can withstand intermediate pressure.
  • the high-pressure pump 6H compresses to high pressure the intermediate-pressure (high bulk modulus) low-temperature fluid compressed by the low-pressure pump 6L.
  • the high-pressure pump 6H includes a high-pressure bellows 17b which meets strict robust design requirements so as to withstand high pressure.
  • the piston 11 can have a large stroke to easily increase the pressure of the low-temperature fluid to an intermediate pressure. Furthermore, since the high-pressure pump 6H employs the high-pressure bellows 17b, the intermediate pressure of the low-temperature fluid can easily be increased to a high pressure, even though the piston 11 cannot have a large stroke in the high-pressure pump 6H.
  • the high-pressure bellows 17b needs to be employed, which does not allow a large stroke. This makes it difficult to increase the low-temperature fluid to the desired pressure (high pressure).
  • the low-temperature fluid can be increased to the desired pressure more easily by carrying out dual-stage compression of the low-temperature fluid using two pumps.
  • a low-temperature-fluid storage tank including a (low-temperature-fluid) booster pump or a (low-temperature-fluid) booster will now be described with reference to Fig. 9 .
  • a low-temperature-fluid storage tank 7 in this embodiment includes major components such as a (low-temperature-fluid) booster pump 71 or a (low-temperature-fluid) booster 72; a low-temperature container 73 having therein a heat-insulated vacuum chamber 73a; a low-temperature-fluid reservoir 74; and a heat exchanger 75.
  • the booster pump 71 or the booster 72 increases low-temperature fluid to a desired pressure.
  • the booster pump 71 can be realized by, for example, one of the above-described (low-temperature-fluid) booster pumps 1, 2, 3, 4, and 5.
  • the booster 72 can be realized by, for example, the above-described (low-temperature-fluid) booster 6.
  • the low-temperature container 73 has a vacuum inside and has a radiation shield plate 76, such as a copper plate, affixed to the inner surface thereof.
  • the above-described booster pump 71 or the booster 72, the low-temperature-fluid reservoir 74, to be described later, and the heat exchanger 75 are housed in the heat-insulated vacuum chamber 73a of the low-temperature container 73.
  • the low-temperature-fluid reservoir 74 stores therein a low-temperature (e.g., -253°C) fluid (e.g., liquid hydrogen).
  • a low-temperature fluid e.g., liquid hydrogen.
  • This stored low-temperature fluid is guided to the low-temperature-fluid boosting pump 71 or the low-temperature-fluid booster 72 through a pipe 77.
  • the heat exchanger 75 exchanges heat with the low-temperature container 73 to vaporize a low-temperature fluid that has been subjected to a pressure increase by the booster pump 71 or the booster 72 and guided through a pipe 78.
  • the low-temperature fluid (gas) vaporized by the heat exchanger 75 is supplied to, for example, an engine through a pipe 79.
  • cool air collected by the heat exchanger 75 is used to cool the above-described radiation shield plate 76 or is stored in a regenerating agent, not shown in the figure, provided in the heat-insulated vacuum chamber 73.
  • the booster pump 71 or the booster 72 is disposed in the heat-insulated vacuum chamber 73a and outside the low-temperature-fluid reservoir 74 (i.e., disposed separated from the low-temperature-fluid reservoir 74 in the heat-insulated vacuum chamber 73a). Therefore, the booster pump 71 or the booster 72 is forcibly cooled and is not easily heated up, and furthermore, heat generated from the driving source can be prevented from being transmitted to the low-temperature fluid reserved in the low-temperature-fluid reservoir 74. Consequently, an increase in temperature of the low-temperature fluid can also be prevented.
  • the booster pump 71 or the booster 72 be cooled sufficiently before being operated.
  • a low-temperature-fluid storage tank provided with a (low-temperature-fluid) booster pump or a (low-temperature-fluid) booster will be described below with reference to Fig. 10 .
  • a low-temperature-fluid storage tank 8 in this embodiment includes major components such as a (low-temperature-fluid) booster pump 81 or a (low-temperature-fluid) booster 82; a low-temperature container 83 having therein a heat-insulated vacuum chamber 83a; a low-temperature-fluid reservoir 84; and a heater 85.
  • the booster pump 81 or the booster 82 increases low-temperature fluid to a desired pressure.
  • the booster pump 81 can be realized by, for example, one of the above-described (low-temperature-fluid) booster pumps 1, 2, 3, 4, and 5.
  • the (low-temperature-fluid) booster 82 can be realized by, for example, the above-described (low-temperature-fluid) booster 6.
  • the low-temperature container 83 has a vacuum inside and has a radiation shield plate 86, such as a copper plate, affixed to the inner surface thereof.
  • the above-described booster pump 81 or the booster 82 and the low-temperature-fluid reservoir 84, to be described later, are housed in the heat-insulated vacuum chamber 83a of the low-temperature container 83.
  • the low-temperature-fluid reservoir 84 stores therein a low-temperature (e.g., -260°C) slushy fluid (e.g., slush hydrogen: mixture of solid hydrogen and liquid hydrogen in a liquid/ice state, with higher density and a higher coldness capacity than liquid hydrogen).
  • a low-temperature (e.g., -260°C) slushy fluid e.g., slush hydrogen: mixture of solid hydrogen and liquid hydrogen in a liquid/ice state, with higher density and a higher coldness capacity than liquid hydrogen.
  • This stored low-temperature fluid is guided to the low-temperature-fluid boosting pump 81 or the low-temperature-fluid booster 82 through a pipe 87.
  • the slush hydrogen is stored in the low-temperature-fluid reservoir 84, the slush hydrogen is produced by a slush hydrogen producing apparatus, not shown in the figure, provided in this low-temperature-fluid reservoir 84 or by a slush hydrogen producing facility 88 separately provided outside the low-temperature container 83.
  • a mesh (screen) 89 is provided in the pipe 87.
  • This mesh 89 is formed so as to pass only liquid low-temperature fluid (e.g., liquid hydrogen) (i.e., so as to block solid hydrogen).
  • liquid low-temperature fluid e.g., liquid hydrogen
  • the booster pump 81 or the booster 82 downstream is supplied with only liquid low-temperature fluid to prevent clogging from occurring in the booster pump 81 or the booster 82.
  • the heater 85 changes (melts) solid low-temperature fluid (e.g., solid hydrogen) into liquid low-temperature fluid (e.g., liquid hydrogen).
  • solid low-temperature fluid e.g., solid hydrogen
  • liquid low-temperature fluid e.g., liquid hydrogen
  • the above-described heat exchanger 75 be disposed downstream of the booster pump 81 or the booster 82 inside (or outside) the low-temperature container 83.
  • the low-temperature-fluid reservoir 84 contains a slushy low-temperature fluid and experiences vaporization less easily than tanks containing only liquid low-temperature fluids. This improves the suction performance of the booster pump 81 or the booster 82 and therefore increases the amount of low-temperature fluid supplied.
  • multi-stage compression does not always require a plurality of pumps. Instead, multi-stage compression may be achieved with a single pump.
  • the booster pump according to the present invention can be used to increase the pressure of not only low-temperature fluids but also fluids having various temperatures ranging from normal to high temperatures.
  • the piston rods of the booster pump preferably have a heat-insulating vacuum structure that is hollow and vacuumed.
  • the weight of the piston rods can be reduced so that the pistons can be pushed up under a small load.
  • the piston rods can block heat to reduce the amount of heat propagating from the piston rods into the fluids.
  • a low-temperature-fluid boosting pump 101 includes major components such as a drive unit 111 and a pump unit 112 driven by this drive unit 111.
  • the drive unit 111 includes a rod 115 and a power transmission unit 116 for transmitting a driving force from a driving source (e.g., an electric motor or an engine), not shown in the figure, to the rod 115.
  • a driving source e.g., an electric motor or an engine
  • the rod 115 is a substantially rod-like member having a circular cross section, extending downwards from the lower end surface of the power transmission unit 116.
  • the rod 115 has a heat-insulating connection section 128 at a lower end portion thereof.
  • the power transmission unit 116 causes the rod 115 to reciprocate linearly in the vertical direction (in the direction indicated by the arrow in Fig. 11 ) with a stroke of, for example, 2 mm by using a driving force from the driving source, not shown in the figure.
  • the pump unit 112 includes a piston 121, a piston rod 122, and a cylinder block 123.
  • the piston 121 includes one piston main body 124 and one or more (four in this embodiment) piston heads 125, and is reciprocably housed in a cylinder 126 formed in the cylinder block 123.
  • the piston main body 124 is a substantially disc-shaped member. One end portion of the piston rod 122 is linked to a center portion of the piston main body 124. In addition, four rods 127 for linking the lower end surfaces of the respective piston heads 125 to the upper end surface of the piston main body 124 are provided on the outer circumference of the piston main body 124.
  • the four piston heads 125 are arranged at regular intervals (90°) as shown in Fig. 12 .
  • Each of the piston heads 125 is a substantially disc-shaped member and is constructed so as to compress low-temperature fluids (e.g., liquid hydrogen, liquid nitrogen, liquefied carbon dioxide, liquefied natural gas), liquefied propane gases, etc. by means of one end surface thereof (upper end surface in Fig. 11 ).
  • low-temperature fluids e.g., liquid hydrogen, liquid nitrogen, liquefied carbon dioxide, liquefied natural gas
  • propane gases etc.
  • the piston rod 122 is a circular-cross-section, substantially rod-like member and has one end portion thereof linked to the upper end surface of the piston main body 124, as described above, and the other end portion thereof connected to an end portion (lower end portion in Fig. 11 ) of the rod 115 via the heat-insulating connection section 128.
  • the heat-insulating connection section 128 includes an end portion 128a of the rod 115 having a structure similar to the inner race of a roller bearing; the other end portion 128b of the piston rod 122 having a structure similar to the outer race of a roller bearing; and a plurality of (four in this embodiment) rolling elements (e.g., balls and rollers) 128c disposed between the end portion 128a of the rod 115 and the other end portion 128b of the piston rod 122.
  • rolling elements e.g., balls and rollers
  • piston rod 122 is designed to have the maximum possible length, even if heat is transmitted (enters) from the rod 115 to the piston rod 122, the amount of heat transmitted (entering) from the piston rod 122 to the piston main body 124 is minimized.
  • a through-hole 123a through which the rod 115 passes is formed in the top center of the cylinder block 123.
  • An inner space 129 communicating with the through-hole 123a is formed inside the top portion of the cylinder block 123.
  • the heat-insulating connection section 128 is accommodated in this inner space 129.
  • the cylinder 126 communicating with the inner space 129 via a through-hole 123b through which the piston rod 122 passes is formed in the longitudinal direction (vertical direction in Fig. 11 ).
  • One end (upper side in Fig. 11 ) of the cylinder 126 constitutes compression chambers 126a each having an inner diameter larger than the outer diameter of the piston head 125.
  • the piston heads 125 are accommodated in these compression chambers 126a, respectively.
  • the interiors of the side wall, the bottom surface, and the top surface of the cylinder block 123 are hollow and vacuumed to achieve a heat-insulating vacuum structure.
  • a suction port 123d and a discharge port 123e communicating with a compression chamber 126a are provided at a position which faces the center of one end surface of the corresponding piston head 125 in the cylinder block 123, disposed between the compression chamber 126a and the inner space 129.
  • the suction port 123d and the discharge port 123e are each provided with a ball check valve 130 to control suction and discharge of low-temperature fluids.
  • Each suction port 123d is provided so as to communicate with a fluid-suction channel 131 formed in the cylinder block 123, whereas each discharge port 123e is provided so as to communicate with a fluid-discharge channel 132 formed in the cylinder block 123. Therefore, a low-temperature fluid guided from the fluid-suction channel 131 via each suction port 123d into the compression chamber 126a is compressed by one end surface of the piston head 125 so that the pressure is increased to, for example, 30 MPa. Thereafter, the low-temperature fluid is guided out of the cylinder block 123 from the discharge port 123e via the fluid-discharge channel 132.
  • the low-temperature fluid that has been guided out of the cylinder block 123 via the fluid-discharge channel 132 is temporarily stored (reserved) in a chamber 134 via a pipe 133.
  • the low-temperature fluid reserved in the chamber 134 is guided into a heat exchanger 136 through a pipe 135 and then vaporized.
  • Low-temperature fluid whose pressure has been increased to, for example, 30 MPa is reserved in the chamber 134.
  • vaporized low-temperature fluid whose pressure has been decreased to, for example, 15 MPa by the pressure regulator 139 is supplied into the cylinder 126.
  • Each compression chamber 126a has a bellows (partition) 140 therein.
  • This bellows 140 partitions (separates) an inner circumferential side (inward position in the radial direction) from an outer circumferential side (outward position in the radial direction) of the corresponding compression chamber 126a, which is disposed above the piston head 125 (on the opposite side to the piston main body 124).
  • One end of the bellows 140 is affixed to an outer circumferential end portion on one end surface of the piston head 125, and the other end of the bellows 140 is affixed to the inner wall surface of the cylinder block 123 located at an outward position in the radial direction of the suction port 123d and the discharge port 123e.
  • a bellows (partition) 141 is also provided at an outward position in the radial direction at one end portion of the piston rod 122.
  • This bellows 141 partitions (separates) an inner circumferential side (adjacent to the piston rod 122) from an outer circumferential side (adjacent to the cylinder block 123) of the piston rod 122 at one end portion thereof.
  • One end of the bellows 141 is affixed to the upper end surface of the piston main body 124, and the other end of the bellows 141 is affixed to the inner wall surface of the cylinder block 123.
  • bellows 140 and 141 are made of, for example, stainless steel or Inconel, which exhibits elasticity at (super) low temperatures.
  • Reference numerals 142, 143, and 144 in Fig. 11 each denote a (heat-insulating) sealing member which is ring-shaped in plan view.
  • Fig. 12 is a cross-sectional view taken along line XII-XII of Fig. 11 .
  • the low-temperature-fluid boosting pump 101 does not include a component (e.g., piston ring in the known art) that moves in contact with the inner circumferential surfaces of the compression chambers 126a. This prevents heat from being generated in the compression chambers 126a and therefore prevents the low-temperature fluid from being heated.
  • a component e.g., piston ring in the known art
  • each bellows 140 completely partitions an inner circumferential side (inward position in the radial direction) from an outer circumferential side (outward position in the radial direction) of the corresponding compression chamber 126a. Therefore, low-temperature fluid can be prevented from leaking from the inner circumferential side of the compression chamber 126a to the outer circumferential side of the compression chamber 126a (or from the outer circumferential side of the compression chamber 126a to the inner circumferential side of the compression chamber 126a). This improves the compression efficiency of the low-temperature-fluid boosting pump 101.
  • each bellows 140 since low-temperature fluid is compressed in the inner space of each bellows 140 (the space defined by the inner circumferential surface of the bellows 140, one end surface of the piston head 125, and the top surface of the compression chamber 126a), the length of each rod 127 linking the piston head 125 to the piston main body 124 can be reduced. Consequently, not only can the length of the pump unit 112 in the longitudinal direction (axial direction) be reduced, but also the length of the entire pump in the longitudinal direction (axial direction) can be reduced. This contributes to compact and lightweight design of the pump.
  • the diameter of the piston rod 122 can be reduced compared with a piston rod in the known art, which is subjected to a compressive force. Therefore, not only can the amount of heat entering from a driving source be reduced, but also the weight of the piston rod 122 can be reduced. Consequently, the weight of the entire pump can also be reduced.
  • the heat-insulating connection section 128 reduces the amount of heat entering from the rod 115 to the piston rod 122, thereby further reducing the amount of heat entering from the driving source.
  • piston main body 124 is provided between the piston rod 122 and the piston heads 125, heat from the piston rod 122 reaches the piston heads 125 through the piston main body 124. This can further reduce the input amount of heat.
  • the rod 115 connecting to the power transmission unit 116 extends to the side where the suction ports 123d and the discharge ports 123e are disposed (upper side in Fig. 11 ), not only can the length of the pump unit 112 in the longitudinal direction (axial direction) be reduced, but also the length of the entire pump in the longitudinal direction (axial direction) can be reduced. This contributes to compact and lightweight design of the pump.
  • a seventh embodiment of a low-temperature-fluid boosting pump according to the present invention will now be described with reference to Fig. 13 .
  • a low-temperature-fluid boosting pump 202 is a so-called swash plate (or swash) pump.
  • the low-temperature-fluid boosting pump 202 includes major components such as a drive unit 261 and a pump unit 262 that is driven by this drive unit 261.
  • the drive unit 261 includes a rod 265 and a power transmission unit 266 that transmits a driving force from a driving source (e.g., an electric motor or an engine), not shown in the figure, to the rod 265.
  • a driving source e.g., an electric motor or an engine
  • the rod 265 is a substantially rod-like member having a circular cross section, extending downwards from the lower end surface of the power transmission unit 266.
  • the power transmission unit 266 rotates the rod 265 in one direction (direction indicated by the arrow in Fig. 13 ) using a driving force from a driving source, not shown in the figure.
  • the pump unit 262 includes one or more (four in this embodiment) pistons 271, a swash plate (also called a "yoke”) 272, and a cylinder block 273.
  • Each piston 271 is a circular-cross-section, substantially rod-like member having a piston head 271a at one end portion thereof and a piston shoe 271b at the other end portion thereof.
  • Each piston 271 is reciprocably housed in a cylinder 276.
  • the piston head 271a is a so-called large-diameter portion that has an outer diameter larger than the outer diameter of a piston rod 271c that links this piston head 271a and the piston shoe 271b.
  • Low-temperature fluid e.g., liquid hydrogen, liquid nitrogen, liquefied carbon dioxide, liquefied natural gas
  • liquefied propane gas, etc. are compressed by one flat end surface (upper end surface in Fig. 13 ) of this piston head 271a.
  • the piston shoe 271b is also a so-called large-diameter portion that has an outer diameter larger than the outer diameter of the piston rod 271c.
  • One end surface (lower surface in Fig. 13 ) of the piston shoe 271b slides along a sliding surface P of the swash plate 272 having a tilt angle.
  • the cylinder block 273 has therein the same number of compression chambers 126a as that of the pistons 271 and the compression chambers 126a are formed along a longitudinal direction (vertical direction in Fig. 13 ). Each compression chamber 126a accommodates one piston head 271a.
  • the piston shoes 271b and the swash plate 272 are housed adjacent to the other end side (lower side in Fig. 13 ) of the cylinder 276.
  • a through-hole 123a through which the rod 265 passes is formed in the center of the cylinder block 273. Furthermore, the interiors of the side wall, the bottom surface, and the top surface of the cylinder block 273 constitute a heat-insulating vacuum structure that is hollow and vacuumed, as shown by reference symbol 123c.
  • a suction port 123d and a discharge port 123e communicating with a compression chamber 126a are provided at a position which faces the center of one end surface of the corresponding piston head 271a, i.e., at a top portion in the cylinder block 273.
  • the suction port 123d and the discharge port 123e are each provided with a ball check valve 130 to control suction and discharge of low-temperature fluid.
  • Each suction port 123d is provided so as to communicate with a fluid-suction channel 131 formed in the cylinder block 123, whereas each discharge port 123e is provided so as to communicate with a fluid-discharge channel 132 formed in the cylinder block 123. Therefore, low-temperature fluid guided from the fluid-suction channel 131 via each suction port 123d into the compression chamber 126a is compressed by one end surface of the piston head 271a so that the pressure is increased to, for example, 30 MPa. Thereafter, the low-temperature fluid is guided out of the cylinder block 273 from the discharge port 123e via the fluid-discharge channel 132.
  • the low-temperature fluid that has been guided out of the cylinder block 273 via the fluid-discharge channel 132 is temporarily stored (reserved) in a chamber 134 via a pipe 133.
  • the low-temperature fluid reserved in the chamber 134 is guided into a heat exchanger 136 through a pipe 135 and then vaporized.
  • Most of the low-temperature fluid is supplied to a fuel injector, not shown in the figure, through a pipe 137, whereas part of the low-temperature fluid is guided through a pipe 138 and a pressure regulator (decompressor) 139 into the compression chamber 126a (i.e., a space adjacent to the other end surface of each piston head 271a, located opposite to a bellows 140).
  • Low-temperature fluid whose pressure has been increased to, for example, 30 MPa is reserved in the chamber 134.
  • vaporized low-temperature fluid whose pressure has been decreased to, for example, 15 MPa by the pressure regulator 139 is supplied into the compression chamber 126a.
  • Each compression chamber 126a has the bellows (partition) 140 therein.
  • This bellows 140 partitions (separates) an inner circumferential side (inward position in the radial direction) from an outer circumferential side (outward position in the radial direction) of the corresponding compression chamber 126a, which is disposed above the piston head 271a (on the opposite side to the piston rod 271c).
  • One end of the bellows 140 is affixed to an outer circumferential end portion on one end surface of the piston head 271a, and the other end of the bellows 140 is affixed to the inner wall surface of the cylinder block 273 located at an outward position in the radial direction of the suction port 123d and the discharge port 123e.
  • a bellows (partition) 280 is also provided at an outward position in the radial direction at one end portion of the piston rod 271c.
  • This bellows 280 partitions (separates) an inner circumferential side (adjacent to the piston rod 271c) from an outer circumferential side (adjacent to the cylinder block 273) of the piston rod 271c at one end portion thereof.
  • One end of the bellows 280 is affixed to an outer circumferential end portion on the other end surface (upper surface in Fig. 13 ) of the piston shoe 271b, and the other end of the bellows 280 is affixed to the inner wall surface of the cylinder block 273.
  • bellows 140 and 280 are made of, for example, stainless steel or Inconel, which exhibits elasticity at (super) low temperatures.
  • Reference numerals 142, 143, and 144 in Fig. 13 each denote a (heat-insulating) sealing member which is ring-shaped in plan view.
  • Reference numerals 281 and 282 each denote a thrust roller bearing.
  • the piston shoes 271b slide along the sliding surface P by means of the thrust bearings 281, and furthermore, the pistons 271 are caused to reciprocate in the cylinder 276, thereby successively compressing low-temperature fluid flowing into the compression chambers 126a.
  • the strokes of the pistons 271 are set to, for example, 2 mm.
  • the low-temperature-fluid boosting pump 202 does not include a component (e.g., piston ring in the known art) that moves in contact with the inner circumferential surfaces of the compression chambers 126a. This prevents heat from being generated in the compression chambers 126a and therefore prevents the low-temperature fluid from being heated.
  • a component e.g., piston ring in the known art
  • each bellows 140 completely partitions (separates) an inner circumferential side (inward position in the radial direction) from an outer circumferential side (outward position in the radial direction) of the corresponding compression chamber 126a. Therefore, low-temperature fluid can be prevented from leaking from the inner circumferential side of the compression chamber 126a to the outer circumferential side of the compression chamber 126a (or from the outer circumferential side of the compression chamber 126a to the inner circumferential side of the compression chamber 126a). This improves the compression efficiency of the low-temperature-fluid boosting pump 202.
  • each piston rod 271c linking the piston head 271a to the piston shoe 271b can be reduced. Consequently, not only can the length of the pump unit 262 in the longitudinal direction (axial direction) be reduced, but also the length of the entire pump in the longitudinal direction (axial direction) can be reduced. This contributes to compact and lightweight design of the pump.
  • the diameter of the rod 265 can be reduced compared with the type of piston rod used in the known art, which is subjected to a compressive force. Therefore, not only can the amount of heat entering from a driving source be reduced, but also the weight of the rod 265 can be reduced. Consequently, the weight of the entire pump can also be reduced.
  • the rod 265 connecting to the power transmission unit 266 extends to the side where the suction ports 123d and the discharge ports 123e are disposed (upper side in Fig. 13 ), not only can the length of the pump unit 262 in the longitudinal direction (axial direction) be reduced, but also the length of the entire pump in the longitudinal direction (axial direction) can be reduced. This contributes to compact and lightweight design of the pump.
  • the present invention is not limited to this structure.
  • a single-cylinder, two-cylinder, three-cylinder, or five-or-more-cylinder structure is also acceptable.
  • the thrust roller bearing 282 described in the seventh embodiment is not limited to the type of bearing that supports the swash plate 272 at a single point in the center on the bottom surface of the swash plate 272, as shown in Fig. 13 . Instead, the entire bottom surface of the swash plate 272 can be supported with two or more thrust roller bearings disposed in the circumferential direction.
  • this swash plate 272 be variable using, for example, an actuator.
  • a variable-capacity structure is preferable. By doing so, the amount of discharge by the pump can be changed simply by changing the angle of the swash plate 272, i.e., without changing the number of revolutions for driving the pump.
  • each of the suction port 123d and the discharge port 123e is provided with the ball check valve 130 in the above-described embodiment
  • the present invention is not limited to this structure. Instead, a forcible drive system as seen with, for example, a DOHC of an internal-combustion engine is also acceptable. Furthermore, a structure with a reed valve, a poppet valve, etc. can also be used.
  • low-temperature fluid vaporized by the heat exchanger 136 is supplied to the outside of the bellows 140 and 280 in the above-described sixth embodiment or the seventh embodiment, the present invention is not limited to this structure. Instead, the space receiving vaporized low-temperature fluid can be vacuumed.
  • the spaces between the bellows 140 and 280 and the cylinder blocks 123 and 273 are vacuumed to prevent heat in the bellows 140 and 280 (i.e., heat of low-temperature fluid compressed at the inner sides of the bellows 140 and 280) from being transmitted to the cylinder blocks 123 and 273.
  • heat in the bellows 140 and 280 i.e., heat of low-temperature fluid compressed at the inner sides of the bellows 140 and 280
  • a guiding member be provided, for example, between the piston rod 122 and the cylinder block 123 or between the piston main body 124 and the cylinder 126 so that the piston main body, the piston heads, etc. that are housed in the cylinder to reciprocate in the cylinder do not interfere with the inner wall surface of the cylinder (cylinder wall).
  • Examples of such a guiding member include a linear bearing disposed between the piston rod 122 and the cylinder block 123 or between the outer circumferential surface of the piston main body 124 and the inner wall surface of the cylinder 126, a member that guides a cylindrical protrusion protruding downwards from the lower end surface of the piston main body 124 into a cylindrical indentation (dent) formed in the center of the bottom surface of cylinder 126, and so forth.
  • reciprocating members such as the piston main body and the piston heads perform reciprocal movement in the cylinder without wobbling or vibrating. This can prevent such reciprocating members from interfering with the inner wall surface of the cylinder, and furthermore, allows the reciprocating members to be driven smoothly with minimum driving force.
  • an vacuumed space be formed between the piston rod 122 and the cylinder block 123.
  • a bellows (same as the bellows 141) for separating a space adjacent to the inner circumferential side from a space adjacent to the outer circumferential side of the piston rod 122 is provided between the lower surface of the other end portion 128b of the piston rod 122 and the upper surface of the bottom of the inner space 129 shown in Fig. 11 .
  • the space between the cylinder block 123 and the piston rod 122 is vacuumed to prevent heat from the piston rod 122 (i.e., heat moving from the drive unit 111 side to the piston rod 122 side) from being transmitted to the cylinder block 123.
  • a low-temperature-fluid boosting pump 301 includes major components such as a drive unit 311 and a pump unit 312 driven by this drive unit 311.
  • the drive unit 311 includes a cam 313; a reciprocating section 314; a linear bearing 315; an urging member 316; and a casing 317 for accommodating these elements.
  • the cam 313 is a circular arc cam (convex cam) having a maximum lift of, for example, 2 mm and is fixed on a drive shaft 318 of a driving source (e.g., an electric motor or an engine), not shown in the figure.
  • the cam 313 rotates in one direction along with the drive shaft 318, which rotates as a result of the driving source being driven.
  • the reciprocating section 314 is a substantially cylindrical member having an inner space formed therein.
  • the reciprocating section 314 has a roller bearing 319 in the inner space thereof, and furthermore, a substantially bar-like rod 320 having a circular cross section extends downwards from the lower end surface of the reciprocating section 314.
  • the roller bearing 319 includes an inner race (inner ring) 319a; an outer race (outer ring) 319b; and a plurality of rolling elements (e.g., balls and rollers) 319c disposed between the inner race 319a and the outer race 319b.
  • the inner race 319a is affixed to a shaft 314a protruding in the inner space of the reciprocating section 314, whereas the outer race 319b rotates together with the cam 313 as a result of the outer surface thereof being in line contact with the outer surface of the rotating cam 313.
  • the linear bearing 315 guides the outer circumferential surface, at a radially outward position, of the reciprocating section 314 such that the reciprocating section 314 reciprocates linearly in the vertical direction.
  • the linear bearing 315 is affixed to an inner surface of a side wall of the casing 317 at a radially outward position of the reciprocating section 314.
  • a plurality of rolling elements (e.g., balls and rollers) 315a is disposed in the linear bearing 315. By doing so, the reciprocating section 314 can perform smooth linear reciprocation in the vertical direction.
  • the linear bearing 315 can be made of, for example, resin, titanium, or ceramic.
  • the urging member 316 is affixed to an inner wall surface at the upper portion of the casing 317.
  • the urging member 316 is, for example, a compression spring that is disposed above the reciprocating section 314 to urge the reciprocating section 314 downwards, that is, to urge the outer surface of the outer race 319b of the roller bearing 319 onto the outer surface of the cam 313.
  • the casing 317 is a substantially cylindrical member having an inner space therein for accommodating the cam 313, the reciprocating section 314, the linear bearing 315, and the urging member 316.
  • the casing 317 is disposed above the pump unit 312.
  • the roller bearing 319 whose outer surface is pressed against the outer surface of the cam 313, reciprocates linearly in the vertical direction together with the reciprocating section 314. Accordingly, the rod 320 also reciprocates in the vertical direction.
  • the pump unit 312 includes a piston 321, a piston rod 322, and a cylinder block 323.
  • the piston 321 includes a piston main body 324 and a piston head 325 and is reciprocably housed in a cylinder 326 formed in the cylinder block 323.
  • the piston main body 324 is a substantially cup-shaped hollow member with a bottom.
  • the piston main body 324 has the piston head 325 formed at one end portion (upper end portion in Fig. 14 ) thereof and has, in the center of the other end portion (bottom) thereof, a through-hole 324a through which one end portion of the piston rod 322 passes and one end portion of the piston rod 322 which is mounted via a heat insulator 327.
  • the interior of the side wall of the piston main body 324 has a heat-insulating vacuum structure that is hollow and vacuumed.
  • the piston head 325 is a member which is ring-shaped in plan view (doughnut) and has in the center thereof a through-hole 325a through which the piston rod 322 and a bulkhead 334, to be described later, pass.
  • a low-temperature fluid e.g., liquid hydrogen, liquid nitrogen, liquefied carbon dioxide, liquefied natural gas, or liquefied propane gas
  • the piston rod 322 is a circular-cross-section, substantially rod-like member and has one end portion thereof affixed to the center at the other end portion of the piston main body 324 via the heat insulator 327, as described above, and the other end portion thereof connected to an end portion (lower end portion in Fig. 14 ) of the rod 320 via a heat-insulating connection section 328.
  • the heat-insulating connection section 328 includes an end portion 328a of the rod 320 having a structure similar to the inner race of a roller bearing; the other end portion 328b of the piston rod 322 having a structure similar to the outer race of a roller bearing; and a plurality of (four in this embodiment) rolling elements (e.g., balls and rollers) 328c disposed between the end portion 328a of the rod 320 and the other end portion 328b of the piston rod 322.
  • rolling elements e.g., balls and rollers
  • a through-hole 323a through which the rod 320 passes is formed in the top center of the cylinder block 323.
  • An inner space 329 communicating with the through-hole 323a is formed inside the top portion of the cylinder block 323.
  • the heat-insulating connection section 328 is accommodated in this inner space 329.
  • the cylinder 326 communicating with the inner space 329 via a through-hole 323b through which the piston rod 322 passes is formed in the longitudinal direction (vertical direction in Fig. 14 ).
  • One end (upper side in Fig. 14 ) of the cylinder 326 constitutes a compression chamber 126a having an inner diameter larger than the outer diameter of the piston head 325.
  • the piston head 325 is accommodated in this compression chamber 326a.
  • the interiors of the side wall, the bottom surface, and the top surface of the cylinder block 323 are hollow and vacuumed to achieve a heat-insulating vacuum structure.
  • a suction port 323d and a discharge port 323e communicating with the compression chamber 326a are provided at a position which faces a circumferential portion on one end surface of the piston head 325 between the compression chamber 326a and the inner space 329 in the cylinder block 323.
  • the suction port 323d and the discharge port 323e are each provided with a poppet check valve (or a ball check valve, a reed valve, a forcibly driven valve) 330 having a valve body 330a and a spring 330b to control suction and discharge of low-temperature fluid.
  • the suction port 323d is provided so as to communicate with a fluid-suction channel 331 formed in the cylinder block 323, whereas the discharge port 323e is provided so as to communicate with a fluid-discharge channel 332 formed in the cylinder block 323. Therefore, low-temperature fluid guided from the fluid-suction channel 331 via the suction port 323d into the compression chamber 326a is compressed by one end surface of the piston head 325 so that the pressure is increased to, for example, 30 MPa. Thereafter, the low-temperature fluid is guided out of the cylinder block 323 from the discharge port 323e via the fluid-discharge channel 332.
  • the low-temperature fluid that has been guided out of the cylinder block 323 via the fluid-discharge channel 332 is temporarily stored (reserved) in a chamber C via a pipe 333. Thereafter, the low-temperature fluid is supplied to a fuel injector, not shown in the figure, via a pipe 335.
  • Low-temperature fluid whose pressure has been increased to, for example, 30 MPa is reserved in the chamber C.
  • the bulkhead 334 enclosing the shank outer surface of the piston rod 322 is disposed between the piston rod 322 and the piston 321. As indicated by reference symbol 334a, this bulkhead 334 has a heat-insulating vacuum structure that is hollow and vacuumed. Because of this, radiant heat from the piston rod 322 is prevented from being transmitted to the piston 321.
  • the compression chamber 326a has a bellows (partition) 336 therein.
  • This bellows 336 separates (partitions) an inner circumferential side (piston 321 side) from an outer circumferential side (cylinder block 323 side) of the compression chamber 326a, which is disposed closer to the piston main body 324 (lower side in Fig. 14 ) than the piston head 325.
  • One end of the bellows 336 is affixed to a surface opposite (the other end surface) one end surface of the piston head 325, and the other end of the bellows 336 is affixed to the inner wall surface of the cylinder block 323.
  • a bellows (partition) 337 is also provided at a radially outward position of the bulkhead 334 and above one end surface of the piston head 325.
  • This bellows 337 separates (partitions) an inner circumferential side (piston rod 322 side) from an outer circumferential side (cylinder block 323 side) in the upper section of the cylinder 326.
  • One end of the bellows 337 is affixed to one end surface of the piston head 325, whereas the other end of the bellows 337 is affixed to the inner wall surface of the cylinder block 323.
  • bellows 336 and 337 are each made of, for example, stainless steel or Inconel, which exhibits elasticity at (super) low temperatures.
  • Fig. 15 is a cross-sectional view taken along line XV-XV of Fig. 14 .
  • the imaginary line in Fig. 15 (two-dot chain line) denotes the bellows 337.
  • reference numerals 338, 339, 340, and 341 in Fig. 14 each denote a (heat-insulating) sealing member which is ring-shaped in plan view.
  • the piston rod 322 As a result of the piston rod 322 being pulled towards the drive unit 311 (upwards in Fig. 14 ), low-temperature fluid is compressed by one end surface of the piston head 325. In short, when low-temperature fluid is to be compressed, the piston rod 322 is not subjected to a compressive force.
  • the diameter of the piston rod 322 can be reduced compared with a piston rod in the known art, which is subjected to a compressive force (if the piston rod 322 is made of, for example, Inconel, the diameter of the piston rod 322 can be, for example, 8 mm). Therefore, not only can the amount of heat entering from the driving source be reduced, but also the weight of the piston rod 322 can be reduced. Consequently, the weight of the entire pump can also be reduced.
  • the diameter of the piston head 325 can be increased (e.g., diameter of 100 mm).
  • the diameter of the piston head is limited to, for example, 40 mm to prevent the piston rod from buckling.
  • the known pump required, for example, five cylinders to achieve a sufficient flow volume of low-temperature fluid.
  • the diameter of the piston head 325 can be, for example, 100 mm, and therefore, a sufficient flow volume can be achieved with a single cylinder.
  • the pump according to the present invention not only can the structure of the pump be simplified, but also the entire pump can be made lightweight and compact.
  • the heat-insulating connection section 328 reduces the amount of heat entering from the rod 320 into the piston rod 322, the amount of heat entering from the driving source can be further reduced.
  • the piston main body 324 is provided between the piston rod 322 and the piston head 325 so that heat from the piston rod 322 reaches the piston head 325 via the piston main body 324, the amount of heat input can be further reduced.
  • the piston main body 324 has a heat-insulating vacuum structure that is hollow and vacuumed, the amount of heat input can be further reduced.
  • the amount of heat input to the piston head 325 can be reduced, and therefore, low-temperature fluid compressed by one end surface of the piston head 325 can be prevented from being vaporized (boiled off).
  • the low-temperature-fluid boosting pump 301 does not include a component (e.g., piston ring in the known art) that moves in contact with the inner circumferential surface of the compression chamber 326a. This prevents heat from being generated in the compression chamber 326a and therefore prevents the low-temperature fluid from being heated.
  • a component e.g., piston ring in the known art
  • a ninth embodiment of a low-temperature-fluid boosting pump according to the present invention will now be described with reference to Fig. 16 .
  • a low-temperature-fluid boosting pump 402 according to this embodiment differs from the pump in the above-described eighth embodiment in that the piston head 325 is provided directly at one end portion of the piston rod 322.
  • the other components are the same as those described in the above-described embodiment, and hence a description thereof will be omitted.
  • the length of the piston rod 322 is about one-fourth of that in the eighth embodiment, and one end portion of the piston rod 322 is affixed directly to a through-hole 325b formed in the center of the piston head 325 via the heat insulator 327.
  • the piston main body 324, the bulkhead 334, and the cylinder 326 that is provided below the bellows 336 in the eighth embodiment are omitted. Therefore, in this embodiment, the length of the entire pump in the longitudinal direction (vertical direction in the figure) is reduced by the length of the omitted components.
  • This embodiment affords an advantage in that the longitudinal length of a pump unit 412 can be reduced considerably, which allows the longitudinal length of the entire pump to be reduced and therefore the pump to be made compact.
  • a tenth embodiment of a low-temperature-fluid boosting pump according to the present invention will be described with reference to Fig. 17 .
  • a low-temperature-fluid boosting pump 503 according to this embodiment differs from the pump in the above-described eighth embodiment in that a first compression (first-stage compression) is performed with the outer circumferential side of a piston head 525 and a second compression (second-stage compression) is performed with the inner circumferential side of the piston head 525.
  • first-stage compression is performed with the outer circumferential side of a piston head 525
  • second-stage compression is performed with the inner circumferential side of the piston head 525.
  • the other components are the same as those described in the above-described embodiment, and hence a description thereof will be omitted.
  • a first compression is performed with the outer circumferential side of the piston head 525
  • a second compression is performed with the inner circumferential side of the piston head 525
  • a drive unit 311 and a low-pressure chamber 534 are provided in a cylinder block 523.
  • a piston 521 in this embodiment includes a piston main body 524 and the piston head 525, and is reciprocably housed in a cylinder 326 formed in the cylinder block 523.
  • the piston head 525 is a member which is ring-shaped in plan view (doughnut), and has a first compressive surface 525a on one end surface (upper end surface in Fig. 17 ) adjacent to the outer circumferential side thereof and a second compressive surface 525b on one end surface adjacent to the inner circumferential side thereof.
  • a low-temperature fluid e.g., liquid hydrogen, liquid nitrogen, liquefied carbon dioxide, liquefied natural gas, or liquefied propane gas
  • a low-temperature fluid e.g., liquid hydrogen, liquid nitrogen, liquefied carbon dioxide, liquefied natural gas, or liquefied propane gas
  • low-temperature fluid guided from a fluid-suction channel 331 through a suction port P1 on the low-pressure side into a compression chamber 326a is compressed by the first compressive surface 525a of the piston head 525 for pressure increase to, for example, 5 MPa. Thereafter, the low-temperature fluid flows from a discharge port P2 on the low-pressure side through a first communication channel (a flow channel for connecting between the discharge port P2 on the low-pressure side and the low-pressure chamber 534) R1 and is then temporarily reserved in the low-pressure chamber 534.
  • the low-temperature fluid reserved in the low-pressure chamber 534 is guided from the low-pressure chamber 534 through a second communication channel (flow channel that connects between the low-pressure chamber 534 and a suction port P3 on the high-pressure side) into the suction port P3 on the high-pressure side, and is then drawn into the compression chamber 326a.
  • the low-temperature fluid drawn into the compression chamber 326a is compressed by the second compressive surface 525b of the piston head 525 to increase the pressure to, for example, 30 MPa.
  • the low-temperature fluid is expelled out of the cylinder block 523 from a discharge port P4 on the high-pressure side via a fluid-discharge channel 332.
  • the low-temperature fluid that has been expelled out of the cylinder block 523 passes through a pipe 333, is temporarily reserved in a chamber C, and is supplied to a fuel injector, not shown in the figure, through a pipe 335.
  • low-temperature fluid is subjected to a pressure increase to, for example, 5 MPa with the first compressive surface 525a of the piston head 525 and is then subjected to another pressure increase with the second compressive surface 525b of the piston head 525, up to a desired pressure (e.g., 30 MPa).
  • a desired pressure e.g. 30 MPa
  • this embodiment employs a dual-stage compression technique where low-temperature fluid is temporarily increased to an intermediate pressure and is then further increased to a desired pressure (high pressure), instead of increasing the low-temperature fluid from a low pressure to a high pressure in one stroke.
  • the expansion ratio of the bellows 336 and 337 can be decreased (i.e., the bellows 336 and 337 can be expanded or contracted within a smaller range). Therefore, the service life of these bellows 336 and 337 can be extended, and accordingly, the reliability of the pump can be improved.
  • a low-temperature-fluid boosting pump 604 according to this embodiment differs from the pump in the above-described eighth embodiment in that a precooling layer 630 is provided on an inner side of a heat-insulating vacuum structure 323c of a cylinder block 623 which constitutes a pump unit 612.
  • the other components are the same as those described in the above-described embodiment, and hence a description thereof will be omitted.
  • the low-temperature-fluid boosting pump 604 is provided with the precooling layer 630 in the side wall, the bottom surface, and the top surface of the cylinder block 623.
  • a coolant inlet pipe 631 and a coolant outlet pipe 632 are connected to this precooling layer 630 so that a coolant (low-temperature fluid such as liquid hydrogen, liquid nitrogen, liquefied carbon dioxide, liquefied natural gas, or liquefied propane gas) supplied into the precooling layer 630 from the coolant inlet pipe 631 is guided to the outside of the cylinder block 623 via the coolant outlet pipe 632.
  • a coolant low-temperature fluid such as liquid hydrogen, liquid nitrogen, liquefied carbon dioxide, liquefied natural gas, or liquefied propane gas
  • the entire pump can be cooled sufficiently before the pump is started. This decreases vaporization (boil-off) of low-temperature fluid supplied to the low-temperature-fluid boosting pump 604.
  • this precooling layer 630 also serves as a heat-insulating layer while the pump is being operated, vaporization (boil-off) of the low-temperature fluid can be reduced also while the pump is being operated.
  • a low-temperature-fluid boosting pump 705 according to this embodiment differs from the pump in the above-described eleventh embodiment in that a bellows 737 is provided in place of the bellows 337.
  • the other components are the same as those described in the above-described embodiment, and hence a description thereof will be omitted.
  • the bellows (partition) 737 of the low-temperature-fluid boosting pump 705 is provided at a radially inward position of a bellows 336 and in a compression chamber 326a, which is disposed closer to a piston main body 324 (lower side in Fig. 19 ) than a piston head 325.
  • One end of the bellows 737 is affixed to a surface opposite (the other end surface) the one end surface of the piston head 325, and the other end of the bellows 737 is affixed to the top surface of a tongue portion of a bulkhead 334.
  • the bellows 737 is made of, for example, stainless steel or Inconel, which exhibits elasticity at (super) low temperatures.
  • the bellows 737 on the same side as the bellows 336, that is, the side opposite to the one end surface (compressive surface) of the piston head 325, the length of the pump in the height direction (vertical direction in the figure) can be reduced, and therefore, the entire pump can be made compact.
  • the compressive surface of the piston head 325 can have a larger area than that in the eleventh embodiment, a larger amount of low-temperature fluid can be compressed at a time. In short, the efficiency (performance) of the pump can be improved.
  • Reference numeral 712 in the figure denotes a pump unit.
  • a thirteenth embodiment of a low-temperature-fluid boosting pump according to the present invention will be described with reference to Fig. 20 .
  • a low-temperature-fluid boosting pump 806 according to this embodiment differs from the pump in the above-described twelfth embodiment in that a bellows 837 is additionally provided.
  • the other components are the same as those described in the above-described embodiment, and hence a description thereof will be omitted.
  • the low-temperature-fluid boosting pump 806 is provided with another bellows (partition) 837 adjacent to the other end side (lower side in the figure) of the bellows 737.
  • This bellows 837 has one end thereof affixed to a lower surface of a tongue portion of a bulkhead 334 and has the other end thereof affixed to an upper surface of the inner wall at the other end portion of a piston main body 324.
  • This bellows 837 separates (partitions) an inner circumferential side (piston rod 322 side) from an outer circumferential side (cylinder block 323 side) in the space between the lower surface of the tongue portion of the bulkhead 334 and the upper surface of the inner wall at the other end portion of the piston main body 324.
  • the bellows 837 is made of, for example, stainless steel or Inconel, which exhibits elasticity at (super) low temperatures.
  • the pressure in the space defined by the bellows 837 and the above-described sealing member 341 adjacent to the piston rod 322 is maintained substantially at atmospheric pressure. Therefore, the difference (pressure difference) between the pressure on the inner circumferential side and the pressure on the outer circumferential side of the bellows 336, 737, and 837 can be reduced. This allows the service life of these bellows 336, 737, and 837 to be extended. Consequently, the reliability of the pump can be improved.
  • Reference numeral 812 in the figure denotes a pump unit.
  • a fourteenth embodiment of a low-temperature-fluid boosting pump according to the present invention will be described with reference to Fig. 21 .
  • a low-temperature-fluid boosting pump 907 according to this embodiment differs from the pump in the above-described eighth embodiment in that a booster-fluid feeding unit 930 is provided.
  • the other components are the same as those described in the above-described embodiment, and hence a description thereof will be omitted.
  • the low-temperature-fluid boosting pump 907 is provided with the booster-fluid feeding unit 930.
  • This booster-fluid feeding unit 930 includes a communicating tube 931 that connects the interior of a chamber C to the interior of a cylinder 326 (a space between the lower surface at the other end portion of a piston main body 324, disposed adjacent to the other end side, i.e., the side opposite to a compression chamber 326a, of the cylinder 326, and the bottom surface of the cylinder 326) and a pressure regulator (decompressor) 932 disposed at an intermediate point in this communicating tube 931.
  • a communicating tube 931 that connects the interior of a chamber C to the interior of a cylinder 326 (a space between the lower surface at the other end portion of a piston main body 324, disposed adjacent to the other end side, i.e., the side opposite to a compression chamber 326a, of the cylinder 326, and the bottom surface of the cylinder 326) and a
  • Reference numeral 912 in the figure denotes a pump unit.
  • the bellows 336, 337, 737, and 837 can be realized by bellows having cross sections as indicated by solid lines or two-dot chain lines in Fig. 22 .
  • convex bellows having one projection towards the outside in the radial direction, as indicated by the solid lines in Fig. 22 , or concave bellows having one indentation towards the inside in the radial direction, as indicated by the two-dot chain lines in Fig. 22 , can be employed.
  • heat-insulating connection sections 128 and 328 are not limited to those described above.
  • a heat-insulating connection section as shown in, for example, Fig. 23 can also be employed.
  • a heat insulator 428c is interposed between an end portion 428a of a cross-sectionally T-shaped rod 320 and the other end portion 428b of a cross-sectionally T-shaped piston rod 322, and furthermore, these elements are linked to each other with fasteners J, such as bolts or nuts.
  • a dual-stage compression technique for compression using the outer circumferential side and the inner circumferential side of the piston head 525 has been employed in the embodiment described with reference to Fig. 17
  • the present invention is not limited to this technique. Instead, one end surface of the piston head may be further divided in a concentric manner to achieve a three-or-more-stage compression technique.
  • the above-described chamber C and the low-pressure chamber 534 include a relief valve so that low-temperature fluid discharged from this relief valve returns through a return pipe to the suction side of the pump (or a separate fuel battery, if any fuel battery is provided).
  • a fifteenth embodiment of a low-temperature-fluid boosting pump according to the present invention will be described with reference to Fig. 24 .
  • a low-temperature-fluid boosting pump 1008 includes major components such as a drive unit 1111 and a pump unit 1112 driven by this drive unit 1111.
  • the drive unit 1111 includes a rod 1115 and a power transmission unit 1116 for transmitting a driving force from a driving source (e.g., an electric motor or an engine), not shown in the figure, to the rod 1115.
  • a driving source e.g., an electric motor or an engine
  • the rod 1115 is a circular-cross-section, substantially rod-like member extending downwards from a lower end surface of the power transmission unit 1116 and has a heat-insulating connection section 328 at a lower end portion thereof.
  • the power transmission unit 1116 causes the rod 1115 to reciprocate linearly in the vertical direction (as indicated by the arrow in Fig. 24 ) with a stroke of, for example, 2 mm by using a driving force from the driving source, not shown in the figure.
  • the pump unit 1112 includes a piston 1121, a piston rod 1122, and a cylinder block 1123.
  • the piston 1121 includes one linkage member 1124 and one or more (four in this embodiment) piston heads 1125, and is reciprocably housed in a cylinder 1126 formed in the cylinder block 1123.
  • the linkage member 1124 is a substantially disc-shaped member. One end portion of the piston rod 1122 is linked to a center portion of the linkage member 1124. In addition, four rods 1127 for linking the lower end surfaces of the respective piston heads 1125 to the upper end surface of the linkage member 1124 are provided on the outer circumference of the linkage member 1124. These four rods 1127 are arranged at regular intervals (90°) as shown in Fig. 25 .
  • Each of the piston heads 1125 is a substantially disc-shaped member and is constructed so as to compress a low-temperature fluid (e.g., liquid hydrogen, liquid nitrogen, liquefied carbon dioxide, liquefied natural gas), liquefied propane gases, etc. by means of one end surface thereof (upper end surface in Fig. 24 ).
  • a low-temperature fluid e.g., liquid hydrogen, liquid nitrogen, liquefied carbon dioxide, liquefied natural gas
  • propane gases etc.
  • the piston rod 1122 is a circular-cross-section, substantially rod-like member and has one end portion thereof linked to the upper end surface of the linkage member 1124, as described above, and the other end portion thereof connected to an end portion (lower end portion in Fig. 24 ) of the rod 1115 via the heat-insulating connection section 328.
  • the heat-insulating connection section 328 includes an end portion 328a of the rod 1115 having a structure similar to the inner race of a roller bearing; the other end portion 328b of the piston rod 1122 having a structure similar to the outer race of a roller bearing; and a plurality of (four in this embodiment) rolling elements (e.g., balls and rollers) 328c disposed between the end portion 328a of the rod 1115 and the other end portion 328bof the piston rod 1122.
  • rolling elements e.g., balls and rollers
  • piston rod 1122 is designed to have a maximum possible length, even if heat is transmitted (enters) from the rod 1115 to the piston rod 1122, the amount of heat being transmitted (entering) from the piston rod 1122 to the linkage member 1124 is minimized.
  • a through-hole 323a through which the rod 1115 passes is formed in the top center of the cylinder block 1123.
  • An inner space 329 communicating with the through-hole 323a is formed inside the top portion of the cylinder block 1123.
  • the heat-insulating connection section 328 is accommodated in this inner space 329.
  • the cylinder 1126 communicating with the inner space 329 via a through-hole 1123b through which the piston rod 1122 passes is formed in the longitudinal direction (vertical direction in Fig. 24 ).
  • One end (upper side in Fig. 24 ) of the cylinder 1126 constitutes compression chambers 1126a each having an inner diameter larger than the outer diameter of the piston head 1125.
  • the piston heads 1125 are accommodated in these compression chambers 1126a, respectively.
  • the interiors of the side wall, the bottom surface, and the top surface of the cylinder block 1123 are hollow and vacuumed to achieve a heat-insulating vacuum structure.
  • a suction port 1123d and a discharge port 1123e communicating with a compression chamber 1126a are provided at a position that faces the center of one end surface of the corresponding piston head 1125 in the cylinder block 1123, disposed between the compression chamber 1126a and the inner space 329.
  • the suction port 1123d and the discharge port 1123e are each provided with a ball check valve 1130 to control suction and discharge of low-temperature fluid.
  • Each suction port 1123d is provided so as to communicate with a fluid-suction channel 1131 formed in the cylinder block 1123, whereas each discharge port 1123e is provided so as to communicate with a fluid-discharge channel 1132 formed in the cylinder block 1123. Therefore, low-temperature fluid guided from the fluid-suction channel 1131 via each suction port 1123d into the compression chamber 1126a is compressed by one end surface of the piston head 1125 so that the pressure is increased to, for example, 30 MPa. Thereafter, the low-temperature fluid is guided out of the cylinder block 1123 from the discharge port 1123e via the fluid-discharge channel 1132.
  • the low-temperature fluid that has been guided out of the cylinder block 1123 via the fluid-discharge channel 1132 is temporarily stored (reserved) in a chamber 1134 via a pipe 1133.
  • the low-temperature fluid reserved in the chamber 1134 is guided into a heat exchanger 1136 through a pipe 1135 and then vaporized.
  • Low-temperature fluid whose pressure has been increased to, for example, 30 MPa is reserved in the chamber 1134.
  • vaporized low-temperature fluid whose pressure has been decreased to, for example, 15 MPa by the pressure regulator 1139 is supplied into the cylinder 1126.
  • Each compression chamber 1126a has a bellows (partition) 1140 therein.
  • This bellows 1140 partitions (separates) an inner circumferential side (rod 1127 side) from an outer circumferential side (cylinder block 1123 side) of the corresponding compression chamber 1126a, which is disposed closer to the linkage member 1124 (lower side in Fig. 24 ) than the piston head 1125.
  • One end of the bellows 1140 is affixed to a surface opposite (the other end surface) one end surface of the piston head 1125, and the other end of the bellows 1140 is affixed to the inner wall surface of the cylinder block 1123.
  • a bellows (partition) 1141 is also provided at an outward position in the radial direction at one end portion of the piston rod 1122.
  • This bellows 1141 partitions (separates) an inner circumferential side (adjacent to the piston rod 1122) from an outer circumferential side (adjacent to the cylinder block 1123) of the piston rod 1122 at one end portion thereof.
  • One end of the bellows 1141 is affixed to the upper end surface of the linkage member 1124, and the other end of the bellows 1141 is affixed to the inner wall surface of the cylinder block 1123.
  • bellows 1140 and 1141 are made of, for example, stainless steel or Inconel, which exhibits elasticity at (super) low temperatures.
  • Reference numerals 1142, 1143, and 1144 in Fig. 24 each denote a (heat-insulating) sealing member which is ring-shaped in plan view.
  • Fig. 25 is a cross-sectional view taken along line XXV-XXV of Fig. 24 .
  • low-temperature-fluid boosting pump 1008 of this embodiment as a result of the piston rod 1122 being pulled towards the drive unit 1111 (upward in Fig. 24 ), low-temperature fluid is compressed by one end surface of each piston head 1125. In other words, when low-temperature fluid is to be compressed, no compressive force is applied to the piston rod 1122.
  • the diameter of the piston rod 1122 can be reduced compared with a piston rod in the known art, which is subjected to a compressive force. Therefore, not only can the amount of heat entering from a driving source be reduced, but also the weight of the piston rod 1122 can be reduced. Consequently, the weight of the entire pump can also be reduced.
  • each bellows 1140 completely partitions (separates) an inner circumferential side (inward position in the radial direction) from an outer circumferential side (outward position in the radial direction) of the corresponding compression chamber 1126a. Therefore, low-temperature fluid can be prevented from leaking from the inner circumferential side of the compression chamber 1126a to the outer circumferential side of the compression chamber 1126a (or from the outer circumferential side of the compression chamber 1126a to the inner circumferential side of the compression chamber 1126a). This improves the compression efficiency of the low-temperature-fluid boosting pump 1008.
  • the heat-insulating connection section 328 reduces the amount of heat entering from the rod 1115 to the piston rod 1122, thereby further reducing the amount of heat entering from the driving source.
  • linkage member 1124 is provided between the piston rod 1122 and the piston heads 1125, heat from the piston rod 1122 reaches the piston heads 1125 through the linkage member 1124. This can further reduce the amount of input heat.
  • the rod 1115 connecting to the power transmission unit 1116 extends to the side where the suction ports 1123d and the discharge ports 1123e are disposed (upper side in Fig. 24 ), not only can the length of the pump unit 1112 in the longitudinal direction (axial direction) be reduced, but also the length of the entire pump in the longitudinal direction (axial direction) can be reduced. This contributes to compact and lightweight design of the pump.
  • a sixteenth embodiment of a low-temperature-fluid boosting pump according to the present invention will be described with reference to Fig. 26 .
  • a low-temperature-fluid boosting pump 2009 is a so-called swash plate (or swash) pump.
  • the low-temperature-fluid boosting pump 2009 includes major components such as a drive unit 2161 and a pump unit 2162 that is driven by this drive unit 2161.
  • the drive unit 2161 includes a rod 2165 and a power transmission unit 2166 that transmits a driving force from a driving source (e.g., an electric motor or an engine), not shown in the figure, to the rod 2165.
  • a driving source e.g., an electric motor or an engine
  • the rod 2165 is a substantially rod-like member having a circular cross section, extending downwards from the lower end surface of the power transmission unit 2166.
  • the power transmission unit 2166 rotates the rod 2165 in one direction (direction indicated by the arrow in Fig. 26 ) using a driving force from a driving source, not shown in the figure.
  • the pump unit 2162 includes one or more (four in this embodiment) pistons 2171, a swash plate (also called a "yoke") 2172, and a cylinder block 2173.
  • Each piston 2171 is a circular-cross-section, substantially rod-like member having a piston head 2171a at one end portion thereof and a piston shoe 2171b at the other end portion thereof.
  • Each piston 2171 is reciprocably housed in the cylinder 2176.
  • the piston head 2171a is a so-called large-diameter portion that has an outer diameter larger than the outer diameter of a piston rod 2171c that links this piston head 2171a and the piston shoe 2171b, and (for example, liquid hydrogen, liquid nitrogen, liquefied carbon dioxide, liquefied natural gas), liquefied propane gas, etc. is compressed by one flat end surface (upper end surface in Fig. 26 ) of this piston head 2171a.
  • the piston shoe 2171b is also a so-called large-diameter portion that has an outer diameter larger than the outer diameter of the piston rod 2171c.
  • One end surface (lower surface in Fig. 26 ) of the piston shoe 2171b slides along a sliding surface P of the swash plate 2172 having a tilt angle.
  • the cylinder block 2173 contains the same number of compression chambers 1126a as that of the pistons 2171, and the compression chambers 1126a are formed along a longitudinal direction (vertical direction in Fig. 26 ). Each compression chamber 1126a accommodates one piston head 2171a.
  • the piston shoes 2171b and the swash plate 2172 are housed adjacent to the other end side (lower side in Fig. 26 ) of the cylinder 2176.
  • a through-hole 1123a through which the rod 2165 passes is formed in the center of the cylinder block 2173.
  • the interiors of the side wall, the bottom surface, and the top surface of the cylinder block 2173 constitute a heat-insulating vacuum structure that is hollow and vacuumed, as shown by reference symbol 1123c.
  • a suction port 1123d and a discharge port 1123e communicating with a compression chamber 1126a are provided at a position that faces the center of one end surface of the corresponding piston head 2171a, i.e., at a top portion in the cylinder block 2173.
  • the suction port 1123d and the discharge port 1123e are each provided with a ball check valve 1130 to control suction and discharge of low-temperature fluid.
  • Each suction port 1123d is provided so as to communicate with a fluid-suction channel 1131 formed in the cylinder block 2173, whereas each discharge port 1123e is provided so as to communicate with a fluid-discharge channel 1132 formed in the cylinder block 2173. Therefore, a low-temperature fluid guided from the fluid-suction channel 1131 via each suction port 1123d into the compression chamber 1126a is compressed by one end surface of the piston head 2171a so that the pressure is increased to, for example, 30 MPa. Thereafter, the low-temperature fluid is guided out of the cylinder block 2173 from the discharge port 1123e via the fluid-discharge channel 1132.
  • the low-temperature fluid that has been guided out of the cylinder block 2173 via the fluid-discharge channel 1132 is temporarily stored (reserved) in a chamber 1134 via a pipe 1133.
  • the low-temperature fluid reserved in the chamber 1134 is guided into a heat exchanger 1136 through a pipe 1135 and then vaporized.
  • Most of the low-temperature fluid is supplied to a fuel injector, not shown in the figure, through a pipe 1137, whereas part of the low-temperature fluid is guided through a pipe 1138 and a pressure regulator (decompressor) 1139 into the compression chambers 1126a (i.e., a space adjacent to the other end surface of each piston head 2171a, located opposite to a bellows 1140).
  • Low-temperature fluid whose pressure has been increased to, for example, 30 MPa is reserved in the chamber 1134.
  • vaporized low-temperature fluid whose pressure has been decreased to, for example, 15 MPa by the pressure regulator 1139 is supplied into the compression chambers 1126a.
  • Each compression chamber 1126a has the bellows (partition) 1140 therein.
  • This bellows 1140 partitions (separates) an inner circumferential side (piston rod 2171c side) from an outer circumferential side (cylinder block 2173 side) of the corresponding compression chamber 1126a, which is disposed closer to the piston shoe 2171b (lower side in Fig. 26 ) than the piston head 2171a.
  • One end of the bellows 1140 is affixed to a surface opposite (the other end surface) one end surface of the piston head 2171a, and the other end of the bellows 1140 is affixed to the inner wall surface of the cylinder block 2173.
  • a bellows (partition) 2180 is also provided at an outward position in the radial direction at one end portion of each piston rod 2171c.
  • This bellows 2180 partitions (separates) an inner circumferential side (adjacent to the piston rod 2171c) from an outer circumferential side (adjacent to the cylinder block 2173) of the corresponding piston rod 2171c at one end portion thereof.
  • One end of the bellows 2180 is affixed to an outer circumferential end portion on the other end surface (upper surface in Fig. 26 ) of the piston shoe 2171b, and the other end of the bellows 2180 is affixed to the inner wall surface of the cylinder block 2173.
  • bellows 1140 and 2180 are made of, for example, stainless steel or Inconel, which exhibits elasticity at (super) low temperatures.
  • Reference numerals 1142, 1143, and 1144 in Fig. 26 each denote a (heat-insulating) sealing member which is ring-shaped in plan view.
  • Reference numerals 2181 and 2182 each denote a thrust roller bearing.
  • the piston shoes 2171b slide along the sliding surface P by means of the thrust bearings 2181, and furthermore, the pistons 2171 are caused to reciprocate in the cylinder 2176, thereby successively compressing low-temperature fluid flowing into the compression chambers 1126a.
  • the strokes of the pistons 2171 are set to, for example, 2 mm.
  • low-temperature-fluid boosting pump 2009 of this embodiment as a result of the rod 2165 being rotated in one direction (as indicated by the arrow in Fig. 26 ), low-temperature fluid is compressed by one end surface of each piston head 2171a. In other words, when low-temperature fluid is to be compressed, no compressive force is applied to the rod 2165.
  • the diameter of the rod 2165 can be reduced compared with the type of piston rod used in the known art, which is subjected to a compressive force. Therefore, not only can the amount of heat entering from a driving source be reduced, but also the weight of the rod 2165 can be reduced. Consequently, the weight of the entire pump can also be reduced.
  • each bellows 1140 completely partitions (separates) an inner circumferential side (inward position in the radial direction) from an outer circumferential side (outward position in the radial direction) of the corresponding compression chamber 1126a. Therefore, low-temperature fluid can be prevented from leaking from the inner circumferential side of the compression chamber 1126a to the outer circumferential side of the compression chamber 1126a (or from the outer circumferential side of the compression chamber 1126a to the inner circumferential side of the compression chamber 1126a). This improves the compression efficiency of the low-temperature-fluid boosting pump 2009.
  • the rod 2165 connecting to the power transmission unit 2166 extends to the side where the suction ports 1123d and the discharge ports 1123e are disposed (upper side in Fig. 26 ), not only can the length of the pump unit 2162 in the longitudinal direction (axial direction) be reduced, but also the length of the entire pump in the longitudinal direction (axial direction) can be reduced. This contributes to compact and lightweight design of the pump.
  • the present invention is not limited to this structure.
  • a single-cylinder, two-cylinder, three-cylinder, or five-or-more-cylinder structure is also acceptable.
  • the thrust roller bearing 2182 described in the sixteenth embodiment is not limited to the type of bearing that supports the swash plate 2172 at a single point in the center on the bottom surface of the swash plate 2172, as shown in Fig. 26 . Instead, the entire bottom surface of the swash plate 2172 can be supported with two or more thrust roller bearings disposed in the circumferential direction.
  • this swash plate 2172 be variable using, for example, an actuator.
  • a variable-capacity structure is preferable. By doing so, the amount of discharge of the pump can be changed simply by changing the angle of the swash plate 2172, i.e., without changing the number of revolutions for driving the pump.
  • each of the suction port 1123d and the discharge port 1123e is provided with the ball check valve 1130 in the above-described embodiment
  • the present invention is not limited to this structure. Instead, a forcible drive system as seen with, for example, a DOHC of an internal-combustion engine is also acceptable. Furthermore, a structure with a reed valve, a poppet valve, etc. can also be used.
  • the present invention is not limited to the above-described embodiments.
  • the bellows 1140, 1141, and 2180 can be realized by bellows having cross sections as indicated by solid lines or two-dot chain lines in Fig. 22 .
  • convex bellows having one projection towards the outside in the radial direction, as indicated by the solid lines in Fig. 22 , or concave bellows having one indentation towards the inside in the radial direction, as indicated by the two-dot chain lines in Fig. 22 , can be employed.
  • heat-insulating connection section 328 shown in Fig. 24 is not limited to that described above.
  • a heat-insulating connection section as shown in, for example, Fig. 23 can also be employed.
  • the above-described chamber 1134 include a relief valve so that low-temperature fluid discharged from this relief valve returns through a return pipe to the suction side of the pump (or a separate fuel battery, if any fuel battery is provided).
  • the drive unit 311 according to the eighth to fourteenth embodiments is not limited to a cam-driven drive unit as shown in the figures.
  • the drive unit 311 can be realized by, for example, a crank-driven drive unit where the rod 320 is forcibly driven.
  • the piston rod 1122 be linked (connected) to the linkage member 1124 and the rod 2165 be linked (connected) to the swash plate 2172 through the heat insulator 327 described in the eighth to fourteenth embodiments.
  • a guiding member be provided, for example, between the piston rods 322 and 1122 and the cylinder blocks 323 and 1123, between the piston main bodies 324 and 524 and the cylinder 326, or between the linkage member 1124 and the cylinder 1126, so that the piston main bodies, the piston heads, etc. that are housed in the cylinders and reciprocate in the cylinders do not interfere with the inner wall surfaces of the cylinders (cylinder walls).
  • Examples of such a guiding member include a linear bearing disposed between the piston rods 322 and 1122 and cylinder blocks 323 and 1123, between the outer circumferential surfaces of the piston main bodies 324 and 524 and the inner wall surface of the cylinder 326, or between the outer circumferential surface of the linkage member 1124 and the inner wall surface of the cylinder 1126, a member that guides a cylindrical protrusion protruding downwards from the lower end surfaces of the piston main bodies 324 and 524 into a cylindrical indentation (dent) formed in the centers of the bottom surfaces of the cylinders 326 and 1126, and so forth.
  • a linear bearing disposed between the piston rods 322 and 1122 and cylinder blocks 323 and 1123, between the outer circumferential surfaces of the piston main bodies 324 and 524 and the inner wall surface of the cylinder 326, or between the outer circumferential surface of the linkage member 1124 and the inner wall surface of the cylinder 1126, a member that guides a cylindrical protrusion protru
  • reciprocating members such as the piston main bodies and the piston heads perform reciprocal movement in the cylinders without wobbling or vibrating. This can prevent such reciprocating members from interfering with the inner wall surfaces of the cylinders, and furthermore, allows the reciprocating members to be driven smoothly with minimum driving force.
  • an vacuumed space be formed between the piston rods 322 and 1122 and the cylinder blocks 323 and 1123.
  • a bellows (same as the bellows 1141) for separating a space adjacent to the inner circumferential side from a space adjacent to the outer circumferential side of the piston rod 1122 is provided between the lower surface of the other end portion 328b of the piston rod 1122 and the upper surface of the bottom of the inner space 329.
  • the space between the cylinder block 1123 and the piston rod 1122 is vacuumed to prevent heat from the piston rod 1122 (i.e., heat moving from the driving source 1111 side to the piston rod 1122 side) from being transmitted to the cylinder block 1123.
  • low temperature designates temperatures of about -273°C to 0°C
  • high pressure designates pressures of about 0.2 MPa to 200 MPa.
  • fluid used in the current description includes “liquid,” “gas,” and “colloid.”

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Compressor (AREA)
  • Details Of Reciprocating Pumps (AREA)

Claims (16)

  1. Pompe de surpression pour un fluide basse température (101 ; 301 ; 402 ; 503 ; 604 ; 705 ; 806 ; 907 ; 1008) pour un fluide basse température d'une température ≤ 0 °C, comprenant :
    un bloc-cylindres (123 ; 323 ; 523 ; 623 ; 1123) dans lequel un cylindre (126 ; 326 ; 1126) est formé ;
    une tige de piston (122 ; 322 ; 1122) agencée pour être entraînée par une unité d'entraînement (111 ; 311 ; 1111) qui peut être connectée à une source d'entraînement ; et
    une tête de piston (125 ; 325 ; 525 ; 1125) qui est connectée à la tige de piston (122 ; 322 ; 1122) et est accueillie en va-et-vient dans une chambre de compression (126a ; 126a ; 326a ; 1126a) du cylindre (126 ; 326 ; 1126), en étant de ce fait capable de compresser en fonctionnement le fluide basse température par une surface d'extrémité de la tête de piston (125 ; 325 ; 525 ; 1125) ; caractérisée en ce que
    la tête de piston (125 ; 325 ; 525 ; 1125) est mobile en va-et-vient dans la chambre de compression (126a ; 126a ; 326a ; 1126a) sans contact avec une surface circonférentielle intérieure de la chambre de compression (126a ; 126a ; 326a ; 1126a) ;
    dans laquelle une cloison flexible (140, 141 ; 336, 337 ; 737, 837 ; 1140, 1141) est prévue pour séparer un espace dans la chambre de compression (126a ; 126a ; 326a ; 1126a) adjacent à la tige de piston (122 ; 322 ; 1122) d'un espace dans la chambre de compression (126a ; 126a ; 326a ; 1126a) adjacent au bloc-cylindres (123 ; 323 ; 523 ; 623 ; 1123) ; et
    dans laquelle l'unité d'entraînement (111 ; 311 ; 1111) est disposée sur le côté de la surface d'extrémité de la tête de piston (125 ; 325 ; 525 ; 1125) de sorte qu'une pointe de la tige de piston (122 ; 322 ; 1122) soit soumise à une force de traction dans une direction dans laquelle la pointe s'étend lorsque la tige de piston (122 ; 322 ; 1122) est entraînée pour compresser le fluide basse température.
  2. Pompe de surpression pour un fluide basse température (503) selon la revendication 1, dans laquelle la surface d'extrémité de la tête de piston (525) est divisée en au moins deux sous-sections concentriques (525a, 525b) pour obtenir une structure de compression à plusieurs étages où la pression du fluide basse température peut être graduellement accrue à une pression souhaitée en étant séquentiellement compressée par les sous-sections (525a, 525b).
  3. Pompe de surpression pour un fluide basse température (301 ; 402 ; 503 ; 604) selon la revendication 1 ou 2, dans laquelle la cloison flexible (336, 337) est prévue adjacente à la surface d'extrémité de la tête de piston (325 ; 525) et adjacente à une autre surface d'extrémité de la tête de piston (325 ; 525) qui est opposée à la surface d'extrémité de celle-ci, pour séparer l'espace dans la chambre de compression (326a) adjacent à la tige de piston (322) de l'espace dans la chambre de compression (326a) adjacent au bloc-cylindres (323 ; 523 ; 623).
  4. Pompe de surpression pour un fluide basse température (301 ; 402 ; 503 ; 604 ; 705 ; 806 ; 907 ; 1008) selon la revendication 1 ou 2, dans laquelle la cloison flexible (336) est prévue adjacente à une autre surface d'extrémité de la tête de piston (325 ; 525) qui est opposée à la surface d'extrémité de celle-ci, pour séparer l'espace dans la chambre de compression (326a) adjacent à la tige de piston (322) de l'espace dans la chambre de compression (326a) adjacent au bloc-cylindres (323 ; 523 ; 623).
  5. Pompe de surpression pour un fluide basse température (604 ; 705 ; 806 ; 907) selon l'une quelconque des revendications 1 à 4, dans laquelle une couche de pré-refroidissement (630) est formée dans le bloc-cylindres (623).
  6. Pompe de surpression pour un fluide basse température (101 ; 301 ; 402 ; 503 ; 604 ; 705 ; 806 ; 907 ; 1008) selon l'une quelconque des revendications 1 à 5, dans laquelle l'unité d'entraînement (111 ; 311) est reliée à la tige de piston (122 ; 322) par l'intermédiaire d'une section de connexion d'isolation thermique (128 ; 328).
  7. Pompe de surpression pour un fluide basse température (101 ; 301 ; 402 ; 503 ; 604 ; 705 ; 806 ; 907) selon l'une quelconque des revendications 1 à 6, dans laquelle la tête de piston (325) est reliée à la tige de piston (322) par l'intermédiaire d'un isolant thermique (327).
  8. Pompe de surpression pour un fluide basse température selon l'une quelconque des revendications 1 à 7, dans laquelle un élément de guidage pour guider la pointe de la tige de piston (322) est prévu entre le bloc-cylindres (326) et la tige de piston (322).
  9. Pompe de surpression pour un fluide basse température (301 ; 503 ; 604 ; 705 ; 806 ; 907) selon l'une quelconque des revendications 1 à 8, dans laquelle un espace (334a) entre le bloc-cylindres (323 ; 623) et la pointe de la tige de piston (322) est ou peut être évacué.
  10. Pompe de surpression pour un fluide basse température (101 ; 907 ; 1008) selon l'une quelconque des revendications 1 à 9, dans laquelle il est prévu un moyen pour fournir sélectivement un fluide basse température d'une température ≤ 0 °C stocké dans un réservoir de stockage de fluide basse température (134 ; C) dans le cylindre (126 ; 326 ; 1126).
  11. Pompe de surpression pour un fluide basse température (101 ; 907 ; 1008) selon l'une quelconque des revendications 1 à 9, dans laquelle il est prévu un moyen pour fournir sélectivement un fluide basse température d'une température ≤ 0 °C stocké dans un réservoir de stockage de fluide basse température (134 ; C) dans l'unité d'entraînement et le cylindre (126 ; 326 ; 1126).
  12. Pompe de surpression pour un fluide basse température selon l'une quelconque des revendications 1 à 11, dans laquelle il est prévu un élément de guidage pour guider la tête de piston entre le bloc-cylindres et la tête de piston.
  13. Dispositif d'alimentation de fluide basse température pour un fluide basse température d'une température ≤ 0 °C, comprenant :
    une pompe de surpression pour un fluide basse température (101 ; 301 ; 402 ; 503 ; 604 ; 705 ; 806 ; 907 ; 1008) selon l'une quelconque des revendications 1 à 12 ;
    une chambre (134 ; C) pour contenir un fluide basse température d'une température ≤ 0 °C dont la pression a été accrue par la pompe de surpression pour un fluide basse température ; et
    un injecteur de combustible auquel du fluide basse température est fourni de la chambre (134 ; C).
  14. Dispositif d'alimentation de fluide basse température selon la revendication 13, comprenant :
    une unité d'alimentation de fluide de surpression pour liquéfier ou vaporiser le fluide basse température dans la chambre (134) et pour fournir le fluide basse température dans un espace du cylindre disposé adjacent à l'autre surface d'extrémité de la tête de piston de la pompe de surpression pour un fluide basse température.
  15. Dispositif d'alimentation de fluide basse température selon la revendication 13, comprenant :
    un échangeur thermique (136) pour vaporiser de l'hydrogène liquide prévu entre la chambre (134) et l'injecteur de combustible ; et
    une unité d'alimentation de fluide de surpression pour ajuster la pression de l'hydrogène vaporisé et fournir l'hydrogène dans un espace du cylindre disposé adjacent à l'autre surface d'extrémité de la tête de piston de la pompe de suralimentation pour un fluide basse température.
  16. Dispositif d'alimentation de fluide basse température selon l'une quelconque des revendications 13 à 15, dans laquelle la chambre est pourvue d'un clapet de détente.
EP09157231A 2004-06-30 2005-06-28 Pompe booster et moyens d'amené pour fluides à température basse comprenant une telle pompe Expired - Fee Related EP2071190B1 (fr)

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JP2004194641 2004-06-30
JP2004302048 2004-10-15
JP2004377938 2004-12-27
JP2005003993 2005-01-11
EP05755797A EP1767783B1 (fr) 2004-06-30 2005-06-28 Pompe de surpression et réservoir pour liquide basse température muni de cette pompe

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WO (1) WO2006003871A1 (fr)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007040089A1 (de) * 2007-08-24 2009-02-26 Linde Ag Pumpe, insbesondere für kryogene Medien
AT507941B1 (de) 2009-03-02 2011-06-15 Spantec Gmbh Verfahren zur detektion einer aussergewöhnlichen situation
ES2527505T3 (es) * 2011-11-29 2015-01-26 Cryostar Sas Bombas criogénicas
US20160123313A1 (en) * 2014-11-05 2016-05-05 Simmons Development, Llc Pneumatically-operated fluid pump with amplified fluid pressure, and related methods
US10006449B2 (en) 2015-01-14 2018-06-26 Caterpillar Inc. Bearing arrangement for cryogenic pump
US9828987B2 (en) * 2015-01-30 2017-11-28 Caterpillar Inc. System and method for priming a pump
EP3297699B1 (fr) * 2015-05-18 2020-04-29 Smith & Nephew PLC Systèmes de pompe thermo-assistés pour utilisation dans le traitement des plaies par pression négative
DE102016210737A1 (de) * 2016-06-16 2017-12-21 Robert Bosch Gmbh Förderpumpe für kryogene Kraftstoffe
US10240722B2 (en) 2016-10-24 2019-03-26 Progress Rail Locomotive Inc. Cryogenic fluid system and method of operating same
US10240562B2 (en) 2016-10-24 2019-03-26 Progress Rail Locomotive Inc. Machine system having submersible pumping system, and method
CN110192060A (zh) * 2017-02-03 2019-08-30 伊格尔工业股份有限公司 隔热结构以及液体供给系统
EP3578812A1 (fr) * 2017-02-03 2019-12-11 Eagle Industry Co., Ltd. Système de distribution de liquide
DE102018217644A1 (de) * 2018-10-15 2020-04-16 Hyundai Motor Company Hochdruckpumpe und verfahren zum verdichten eines fluids
JP6781795B2 (ja) * 2019-04-09 2020-11-04 株式会社Ｉｈｉ回転機械エンジニアリング 往復動圧縮機
US11268487B1 (en) * 2020-12-10 2022-03-08 EP Transfer Systems LLC Energy balanced system for generating electric power

Family Cites Families (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB535977A (en) * 1939-10-25 1941-04-29 Harry Da Costa Improvements in bellows pumps
GB702746A (en) * 1950-10-05 1954-01-20 Self Priming Pump & Eng Co Ltd A new or improved fluid proportioner applicable, for example, to aircraft fuel systems
US3456595A (en) * 1966-09-20 1969-07-22 Union Carbide Corp Cryogenic liquid metering pump
US3530770A (en) * 1968-12-30 1970-09-29 Mcmurry Oil Tools Inc Bellows assembly and method
GB1279418A (en) * 1969-04-21 1972-06-28 Gen Eng Radcliffe Bellows type vacuum pump
JPS539925Y2 (fr) * 1973-10-20 1978-03-16
JPS5222906U (fr) * 1975-08-06 1977-02-18
US4156584A (en) * 1976-07-19 1979-05-29 Carpenter Technology Corporation Liquid cryogen pump
JPS53107306U (fr) * 1977-02-04 1978-08-29
JPS5489503U (fr) * 1977-12-07 1979-06-25
AU545577B2 (en) * 1980-07-31 1985-07-18 Anton Braun Hermetic seal for compressors or the like
JPS58158173U (ja) * 1982-04-17 1983-10-21 日本フイ−ダ−工業株式会社 往復動ポンプ
US4769992A (en) * 1986-12-30 1988-09-13 Matsushita Electric Industrial Co., Ltd. Reciprocation apparatus with sealing mechanism
JPS6247782U (fr) 1985-09-11 1987-03-24
IT208731Z2 (it) * 1986-08-05 1988-05-28 Grillini Marco Dispositivo a tenura per la separazione di duie fluidi interessanti zone attigue di organi in movimento relativo
JP2818410B2 (ja) * 1987-05-30 1998-10-30 日機装株式会社 無漏洩往復動ポンプ
JP2962729B2 (ja) * 1988-08-26 1999-10-12 東京エレクトロン株式会社 レジスト塗布装置
GB8902763D0 (en) * 1989-02-08 1989-03-30 Smiths Industries Plc Seals
JP2575756Y2 (ja) * 1993-10-12 1998-07-02 有限会社エム・アイテクノ 高温液体移送用ベローズポンプ
US5511955A (en) * 1995-02-07 1996-04-30 Cryogenic Group, Inc. Cryogenic pump
JPH09152214A (ja) * 1995-11-30 1997-06-10 Sanyo Electric Co Ltd 外燃機関のピストン
JPH10159976A (ja) * 1996-11-26 1998-06-16 Nhk Spring Co Ltd ベローズ構造体およびポンプ装置
US5884488A (en) * 1997-11-07 1999-03-23 Westport Research Inc. High pressure fuel supply system for natural gas vehicles
US6729860B1 (en) * 2000-01-24 2004-05-04 Daniel A. Holt Pneumatically driven liquified gas booster pump
JP2002147362A (ja) * 2000-11-10 2002-05-22 Denso Corp ベローズおよびベローズ式ポンプ装置
JP2003184734A (ja) * 2001-10-10 2003-07-03 Yamagiwa Kanagata:Kk ポンプとその駆動方式。
JP2003148326A (ja) 2001-11-07 2003-05-21 Takako:Kk シリンダ装置およびアキシャルピストンポンプ
JP2003286961A (ja) * 2002-03-27 2003-10-10 Sanyo Electric Co Ltd 冷熱搬送装置
JP2003287310A (ja) * 2002-03-28 2003-10-10 Sanyo Electric Co Ltd スターリング冷凍機

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Publication number Publication date
EP1767783A4 (fr) 2008-07-30
US20090165640A1 (en) 2009-07-02
JPWO2006003871A1 (ja) 2008-04-17
EP2071190A1 (fr) 2009-06-17
EP1767783A1 (fr) 2007-03-28
DE602005020794D1 (de) 2010-06-02
WO2006003871A1 (fr) 2006-01-12
EP1767783B1 (fr) 2010-04-21

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