WO2012124363A1 - 液体供給システム - Google Patents
液体供給システム Download PDFInfo
- Publication number
- WO2012124363A1 WO2012124363A1 PCT/JP2012/050738 JP2012050738W WO2012124363A1 WO 2012124363 A1 WO2012124363 A1 WO 2012124363A1 JP 2012050738 W JP2012050738 W JP 2012050738W WO 2012124363 A1 WO2012124363 A1 WO 2012124363A1
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- WO
- WIPO (PCT)
- Prior art keywords
- liquid
- bellows
- pump chamber
- container
- sealed space
- Prior art date
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- 239000007788 liquid Substances 0.000 title claims abstract description 158
- 239000000872 buffer Substances 0.000 claims description 13
- 230000003139 buffering effect Effects 0.000 claims description 6
- 239000012530 fluid Substances 0.000 claims description 5
- 238000001816 cooling Methods 0.000 abstract description 10
- 239000007789 gas Substances 0.000 description 43
- 230000010349 pulsation Effects 0.000 description 27
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 12
- 238000010586 diagram Methods 0.000 description 10
- 230000000694 effects Effects 0.000 description 7
- 230000008602 contraction Effects 0.000 description 5
- 229910052757 nitrogen Inorganic materials 0.000 description 5
- 230000007423 decrease Effects 0.000 description 4
- 239000011347 resin Substances 0.000 description 4
- 229920005989 resin Polymers 0.000 description 4
- 229910001873 dinitrogen Inorganic materials 0.000 description 2
- 239000001307 helium Substances 0.000 description 2
- 229910052734 helium Inorganic materials 0.000 description 2
- SWQJXJOGLNCZEY-UHFFFAOYSA-N helium atom Chemical compound [He] SWQJXJOGLNCZEY-UHFFFAOYSA-N 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000008016 vaporization Effects 0.000 description 2
- 238000009834 vaporization Methods 0.000 description 2
- 239000006096 absorbing agent Substances 0.000 description 1
- 239000000853 adhesive Substances 0.000 description 1
- 230000001070 adhesive effect Effects 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 230000009172 bursting Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000001747 exhibiting effect Effects 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 230000001629 suppression Effects 0.000 description 1
Images
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B67—OPENING, CLOSING OR CLEANING BOTTLES, JARS OR SIMILAR CONTAINERS; LIQUID HANDLING
- B67D—DISPENSING, DELIVERING OR TRANSFERRING LIQUIDS, NOT OTHERWISE PROVIDED FOR
- B67D7/00—Apparatus or devices for transferring liquids from bulk storage containers or reservoirs into vehicles or into portable containers, e.g. for retail sale purposes
- B67D7/06—Details or accessories
- B67D7/80—Arrangements of heating or cooling devices for liquids to be transferred
- B67D7/82—Heating only
-
- 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
- F04B43/00—Machines, pumps, or pumping installations having flexible working members
- F04B43/08—Machines, pumps, or pumping installations having flexible working members having tubular flexible members
- F04B43/084—Machines, pumps, or pumping installations having flexible working members having tubular flexible members the tubular member being deformed by stretching or distortion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
- F25D17/02—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating liquids, e.g. brine
-
- 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
- F04B2015/081—Liquefied gases
- F04B2015/082—Helium
-
- 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
- F04B2015/081—Liquefied gases
- F04B2015/0824—Nitrogen
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
Definitions
- the present invention relates to a liquid supply system for supplying an ultra-low temperature liquid such as liquid nitrogen or liquid helium.
- FIG. 7 is a schematic configuration diagram showing a usage state of a liquid supply system according to a conventional example.
- the container 310 In the liquid supply system 500 according to this conventional example, in order to maintain the superconducting coil 320 in a superconducting state with respect to the cooled apparatus 300 provided with the superconducting coil 320 inside the resin container 310, the container 310 An ultra-low temperature liquid L is always supplied into the inside.
- the liquid supply system 500 enters the inside of the first container 510 in which the ultra-low temperature liquid L is stored, the second container 520 disposed in the liquid L stored in the first container 510, and the second container 520. And a bellows 530 disposed on the surface.
- a pump chamber P is configured by a region outside the bellows 530 in the second container 520.
- the second container 520 has an inlet 521 for sucking the liquid L into the pump chamber P and an outlet 522 for sending the sucked liquid L from the pump chamber P to the supply passage K1 leading to the outside of the system. Is provided.
- One-way valves 521a and 522a are provided at the suction port 521 and the delivery port 522, respectively.
- a shaft 550 configured to reciprocate by the drive source 540 enters the inside of the bellows 530 from the outside of the first container 510, and the tip thereof is fixed to the tip of the bellows 530. Thereby, the bellows 530 expands and contracts when the shaft 550 reciprocates.
- the bellows 530 contracts to increase the volume of the pump chamber P, and the liquid L in the first container 510 is sucked into the pump chamber P through the suction port 521.
- the bellows 530 extends to reduce the volume of the pump chamber P, and the liquid in the pump chamber P is sent into the supply passage K1 through the delivery port 522.
- the liquid L is supplied to the to-be-cooled apparatus 300 through the supply passage K1 by repeating the expansion and contraction operation of the bellows 530.
- a return passage K2 that connects the liquid supply system 500 and the apparatus to be cooled 300 is also provided so that the liquid L returns to the first container 510 of the liquid supply system 500 by the amount supplied to the apparatus to be cooled 300.
- a cooler 200 that cools the liquid L to an ultra-low temperature state is provided in the middle of the supply passage K1. With such a configuration, the liquid L cooled to an ultra-low temperature by the cooler 200 circulates between the liquid supply system 500 and the cooled apparatus 300.
- the liquid L is intermittently supplied to the cooled apparatus 300 through the supply passage K1 by the expansion and contraction of the bellows 530. That is, since the hydraulic pressure in the supply passage K1 alternately repeats a high pressure state and a low pressure state, so-called pulsation occurs. Therefore, when the resin container 310 is configured by bonding two resin molded products with an adhesive or the like, there is a possibility that low-temperature brittle fracture may occur due to pressure load due to pulsation. As a countermeasure against this, conventionally, the damper 600 is provided in the supply passage K1 to suppress the pressure fluctuation.
- An object of the present invention is to provide a liquid supply system capable of saving space and improving cooling efficiency.
- the present invention employs the following means in order to solve the above problems.
- the liquid supply system of the present invention is A first container that contains a cryogenic liquid; A second container disposed in the liquid contained in the first container and configured to inhale the liquid and deliver the inhaled liquid to a supply passage leading to the exterior of the system; A bellows arranged to enter the interior of the second container; A shaft configured to reciprocate by a drive source and extend and contract the bellows; A liquid supply system comprising: The outside of the bellows in the second container is a first pump chamber.
- the first pump chamber has a first suction port for sucking the liquid in the first container into the first pump chamber, and the first pump chamber.
- a first delivery port for delivering the liquid from the first pump chamber to the supply passage is provided;
- the inside of the bellows is a second pump chamber constituted by a sealed space.
- the second pump chamber has a second suction port for sucking the liquid in the first container into the second pump chamber, and the sucked liquid. Is provided in the second pump chamber to the supply passage.
- the liquid when the bellows contracts, the liquid is sent from the second pump chamber to the supply passage, and the liquid is sucked into the first pump chamber.
- the liquid When the bellows extends, the liquid is sucked into the second pump chamber.
- the liquid is sent from the first pump chamber to the supply passage. Therefore, the liquid supply amount by the expansion and contraction operation of the bellows can be doubled as compared with the case where the pump function is exhibited only in the first pump chamber.
- the liquid when the pump function is exhibited only in the first pump chamber, the liquid is intermittently supplied, whereas in the case of the present invention, the liquid is supplied both when the bellows contracts and when it expands. The Therefore, since the liquid is continuously supplied, the pulsation itself can be suppressed. Therefore, it is not necessary to provide a damper outside the system, so that space can be saved and cooling efficiency can be increased as compared with the case where a damper is provided outside the system.
- the shaft extending from the outside of the first container to reach the bellows is inserted and a sealed space filled with gas is formed.
- a sealed space in which the shaft extending from the outside of the first container to reach the bellows is inserted and the inside of the shaft is in a vacuum state is formed.
- the heat insulating effect is exhibited by the sealed space in a vacuum state, it is possible to prevent the liquid from being vaporized by being heated in the first pump chamber or the second pump chamber. Accordingly, it is possible to suppress a decrease in pump function.
- the vacuum state has a more heat insulating effect.
- a sealed space is formed through which the shaft extending from the outside of the first container to reach the bellows is inserted, and the liquid layer and the gas layer are formed in the sealed space and branched from the supply passage. It is preferable that a buffer structure for buffering fluctuations in pressure of the liquid supplied through the supply passage is provided by connecting the branched passage to the sealed space.
- the buffer structure for buffering the fluctuation (pulsation) of the pressure of the liquid supplied through the supply passage is provided in the system, the space is saved and the cooling efficiency is improved as described above. In combination with suppressing the pulsation itself, the pulsation can be suppressed synergistically.
- a buffering function function as a gas damper in the above-described sealed space Since the gas layer for exhibiting the above is only thickened and the vaporization in the pump chamber is suppressed, the pump function is not lowered.
- the buffer structure may be provided with a safety valve for releasing the internal pressure to the outside when the pressure in the sealed space through which the shaft is inserted exceeds a predetermined value.
- a heater for adjusting the temperature may be provided in the vicinity of the small bellows that separates the sealed space from the external space.
- the thickness of the liquid and gas layer can be adjusted. Thereby, according to the pulsation which may arise when there is no damper, the thickness of each layer can be adjusted and it becomes possible to control the fluctuation (pulsation) of pressure effectively.
- a shaft member and a bearing for the shaft member are provided below the bellows.
- the bottom side of the second container and the bellows are It is good to connect with the inside of the 1st container, and it is connected by the small bellows whose outside diameter is smaller than the bellows which expands and contracts with the reciprocating movement of the axis.
- the pump amount by the first pump chamber can be reduced, and the difference from the pump amount by the second pump chamber can be reduced. Therefore, pulsation can be further suppressed.
- FIG. 1 is a schematic configuration diagram illustrating a usage state of a liquid supply system according to Embodiment 1 of the present invention.
- FIG. 2 is a schematic configuration diagram illustrating a usage state of the liquid supply system according to the second embodiment of the present invention.
- FIG. 3 is a schematic configuration diagram illustrating a usage state of the liquid supply system according to the third embodiment of the present invention.
- FIG. 4 is a schematic configuration diagram illustrating a usage state of the liquid supply system according to the fourth embodiment of the present invention.
- FIG. 5 is a schematic cross-sectional view of a liquid supply system according to Embodiment 4 of the present invention.
- FIG. 6 is a graph showing pressure fluctuation.
- FIG. 7 is a schematic configuration diagram showing a usage state of a liquid supply system according to a conventional example.
- Example 1 With reference to FIG. 1, the liquid supply system which concerns on Example 1 of this invention is demonstrated.
- ⁇ Liquid supply system> With reference to FIG. 1, an overall configuration and usage method of a liquid supply system 100 according to Embodiment 1 of the present invention will be described. Also in the liquid supply system 100 according to the present embodiment, as in the conventional example, the case where the ultra-low temperature liquid L is supplied to the cooled apparatus 300 in which the superconducting coil 320 is provided inside the resin container 310 is taken as an example. explain. Specific examples of the ultra-low temperature liquid L include liquid nitrogen and liquid helium.
- the liquid supply system 100 enters the inside of the first container 110 in which the ultra-low temperature liquid L is stored, the second container 120 disposed in the liquid L stored in the first container 110, and the second container 120. And a bellows 130 disposed on the surface.
- the first pump chamber P ⁇ b> 1 is configured by a region outside the bellows 130 in the second container 120. Further, the inside of the bellows 130 is also a sealed space, and this sealed space is the second pump chamber P2.
- the second container 120 includes a first suction port 121 that sucks the liquid L in the first container 110 into the first pump chamber P1, and the sucked liquid L from the first pump chamber P1 to the outside of the system.
- first outlet 122 for feeding to a supply passage (supply pipe) K1 that communicates.
- second container 120 has a second suction port 123 for sucking the liquid L in the first container 110 into the second pump chamber P2, and the sucked liquid L from the second pump chamber P2 to the supply passage K1.
- a second delivery outlet 124 for delivery is also provided.
- the first suction port 121 and the second suction port 123 are respectively provided with one-way valves 121a and 123a, and the first and second delivery ports 122 and 124 are also provided with one-way valves 122a and 124a, respectively. Is provided.
- a shaft 150 configured to reciprocate by a linear actuator 140 as a drive source enters the inside of the bellows 130 from the outside of the first container 110, and the tip thereof is fixed to the tip of the bellows 130. Thereby, the bellows 130 expands and contracts when the shaft 150 reciprocates.
- a sealed space R1 filled with gas is formed around the shaft 150.
- the sealed space R1 includes a tubular (preferably cylindrical) tube 161 through which a shaft 150 extending from the outside of the first container 110 to the bellows 130 is inserted, and a lower end and an upper end of the tube 161. Are formed by small bellows 162 and 163, respectively.
- the tips of the small bellows 162 that separates the sealed space R1 and the second pump chamber P2 and the small bellows 163 that separates the sealed space R1 and the external space are fixed to the shaft 150, respectively.
- the shaft 150 is configured to expand and contract as the shaft 150 reciprocates. Further, the small bellows 162 and 163 are configured such that the outer diameter thereof is smaller than the outer diameter of the bellows 130.
- the small bellows 162 is provided on the upper end side of the bellows 130 as described above, so that the inside of the bellows 130 becomes a sealed space, and the sealed space is as described above. It is the second pump chamber P2.
- the liquid L is sent from the second pump chamber P2 to the supply passage K1 through the second delivery port 124, and the liquid L is first supplied through the first suction port 121. It is sucked into the pump chamber P1.
- the liquid L is sucked into the second pump chamber P2 through the second suction port 123, and the liquid L is supplied from the first pump chamber P1 through the first delivery port 122. Sent to K1.
- the liquid L is delivered to the supply passage K1 when the bellows 130 is contracted and expanded.
- the liquid L is supplied to the cooled apparatus 300 through the supply passage K ⁇ b> 1 by repeating the expansion and contraction of the bellows 130.
- a return passage (return pipe) K2 that connects the liquid supply system 100 and the apparatus to be cooled 300 is also provided, and the liquid L is returned to the liquid supply system 100 by the amount supplied to the apparatus to be cooled 300.
- a cooler 200 that cools the liquid L to an ultra-low temperature state is provided in the middle of the supply passage K1. With such a configuration, the liquid L cooled to an ultra-low temperature by the cooler 200 circulates between the liquid supply system 100 and the apparatus to be cooled 300.
- the second pump chamber P2 is formed with the inside of the bellows 130 as a sealed space.
- the liquid L is sent to the supply passage K1 both when the bellows 130 is contracted and when the bellows 130 is extended, and the liquid supply amount due to the expansion / contraction operation of the bellows 130 is exhibited only by the first pump chamber P1. It can be doubled compared to the case. Therefore, compared with the case where the pump function is exhibited only in the first pump chamber P1 with respect to the desired supply amount, the supply amount for one time can be halved, and the maximum pressure of the liquid in the supply passage K1. Can be halved. Therefore, adverse effects due to pressure fluctuations (pulsations) of the supplied liquid can be suppressed.
- the liquid L is intermittently supplied, whereas in the case of the present embodiment, both the bellows 130 contracts and extends. Liquid L is supplied. Therefore, since the liquid L is continuously supplied, the pulsation itself can be suppressed. Therefore, space saving can be achieved as compared with the case where a shock absorber (damper) is provided outside the system, and the number of parts where heat exchange occurs can be reduced, so that the cooling efficiency can be increased.
- a shock absorber damper
- the sealed space R a structure is adopted in which the inside of the cylindrical tube portion 161 through which the shaft 150 is inserted is used as the sealed space R1, and the inside is filled with gas. Therefore, since the sealed space R ⁇ b> 1 filled with gas exhibits a function of hindering heat transfer, heat generated from the linear actuator 140 and atmospheric heat can be prevented from being transmitted to the liquid L. Further, even if heat is transmitted to the liquid L and vaporizes, the new liquid L is always supplied and has a cooling effect, so that it is possible to suppress the temperature rising to the temperature at which the liquid L vaporizes in the pump chamber. Therefore, the pump function is not lowered.
- the liquid L in the bellows 130 is vaporized and gas is generated due to heat transfer from the shaft 150 or the like, even if the pump function of the second pump chamber P2 is reduced, the first pump chamber P1.
- the pump function can be stably exhibited.
- each of the inner side and the outer side of the bellows 130 (which is an incompressible fluid). Since the liquid L exists, the swirling and buckling of the bellows 130 can be suppressed when the bellows 130 expands and contracts.
- the sealed space R1 is formed by the pipe portion 161 and the pair of small bellows 162 and 163 is employed.
- the small bellows 162, 163 each has a tip fixed to the shaft 150, and is configured to expand and contract as the shaft 150 reciprocates. Therefore, since the sealed space R1 is formed without forming the sliding portion, heat is not generated with the frictional resistance due to the sliding.
- the sealed space R1 is filled with gas.
- a configuration in which the inside of the sealed space R1 is in a vacuum state may be employed. By making the inside of the sealed space R1 into a vacuum state, the heat insulating effect can be further enhanced.
- FIG. 2 shows a second embodiment of the present invention.
- a configuration when a small bellows is provided below the bellows will be described. Since other configurations and operations are the same as those in the first embodiment, the same components are denoted by the same reference numerals and description thereof is omitted.
- the bottom side of the second container 120 and the bellows 130 communicate with the inside of the first container 110 and expand and contract as the shaft 150 reciprocates, and the outer diameter is smaller than that of the bellows 130.
- the structure connected with the bellows 125 is employ
- the pump amount (discharge amount) by the first pump chamber P1 is larger than the pump amount by the second pump chamber P2.
- the difference between these pump amounts is small.
- the pressure receiving area due to the effective diameter of the bellows 130 is S1
- the pressure receiving area due to the effective diameter of the small bellows 162 is S2
- the pressure receiving area due to the effective diameter of the small bellows 125 is S3, the movement distance of the shaft is L.
- the effective diameter of the bellows 130 is D1
- the effective diameter of the small bellows 162 is D2
- the effective diameter of the small bellows 125 is D3
- S1 ⁇ ⁇ (D1) 2 ⁇ 4
- S2 ⁇ ⁇ (D2) 2 ⁇ .
- S3 ⁇ ⁇ (D3) 2 ⁇ 4.
- the pump amount of the first pump chamber P1 is S1 ⁇ L
- the pump amount of the second pump chamber P2 is (S1-S2) ⁇ L.
- Example 2 the pump amount of the first pump chamber P1 is (S1-S3) ⁇ L, and the pump amount of the second pump chamber P2 is (S1-S2) ⁇ L.
- the difference between the pump amount of the first pump chamber P1 and the pump amount of the second pump chamber P2 can be reduced.
- S2 and S3 equal, theoretically, the pump amount of the first pump chamber P1 and the pump amount of the second pump chamber P2 can be made equal, and pulsation can be more effectively suppressed. It becomes.
- FIG. 3 shows a third embodiment of the present invention.
- a configuration in the case where a structure for suppressing shaft shake is provided below the bellows will be described. Since other configurations and operations are the same as those in the first embodiment, the same components are denoted by the same reference numerals and description thereof is omitted.
- a configuration in which a shaft member 181 is provided at the lower end portion of the bellows 130 and a bearing 182 of the shaft member 181 is provided at the bottom of the second container 120 is employed.
- the bearing 182 is composed of an annular member, and a bearing member 182a is provided on the inner peripheral portion at the tip. Since the other configuration is the same as that of the first embodiment, the description thereof is omitted.
- the bearing 182 be provided with a through-hole on its side surface so that the liquid L can freely travel between the inside and the outside of the bearing 182. Thereby, it can suppress that the reciprocation of the axis
- a part of the shaft 150 can also function as the shaft member 181 by projecting the shaft 150 so as to penetrate below the bottom of the bellows 130.
- the shaft member 181a is made of a permanent magnet
- the bearing member 182a provided at the tip of the bearing 182 is made of a permanent magnet. It is also possible to configure the member 182a to repel by magnetic force. Thereby, the contact between the shaft member 181a and the bearing member 182a can be suppressed, and the shaft blur can be further suppressed.
- the shaft member is provided on the bellows 130 side and the bearing is provided on the bottom of the second container 120.
- the shaft member is provided on the bottom of the second container 120 and the bellows 130 side is provided. It is also possible to adopt a configuration in which a bearing is provided on the front.
- the arrangement and number of shaft members and bearings can be set as appropriate.
- the configuration shown in the present embodiment can be adopted in the configuration shown in the second embodiment. In this case, the shaft member and the bearing are arranged at the center of the bellows 130 as shown in FIG. It is necessary to arrange at a position shifted from the center, not near.
- Example 4 With reference to FIG.4 and FIG.5, the liquid supply system which concerns on Example 4 of this invention is demonstrated.
- the first embodiment the case where the sealed space through which the shaft is inserted is filled with gas or in a vacuum state is shown.
- a liquid layer and a gas layer are included in the sealed space.
- the case where it functions as a gas damper by forming is shown. Since other configurations and operations are the same as those in the first embodiment, the same components are denoted by the same reference numerals and description thereof is omitted.
- a buffer structure 160 is provided around the shaft 150 to buffer fluctuations (pulsations) in the pressure of the liquid L supplied through the supply passage K1.
- the buffer structure 160 includes a cylindrical (preferably cylindrical) tube portion 161 through which a shaft 150 extending from the outside of the first container 110 to the bellows 130 is inserted, and a lower end portion and an upper end portion of the tube portion 161. Are provided with small bellows 162 and 163, respectively.
- the inside of the pipe portion 161 and the pair of small bellows 162, 163 is a sealed space R2.
- each of the small bellows 162 that separates the sealed space R2 and the second pump chamber P2 and the small bellows 163 that separates the sealed space R2 and the external space are fixed to the shaft 150,
- the shaft 150 is configured to expand and contract as the shaft 150 reciprocates.
- the small bellows 162 and 163 are configured such that the outer diameter thereof is smaller than the outer diameter of the bellows 130.
- the sealed space R2 a layer of the liquid L and a layer of the gas G in which the liquid L is vaporized are formed.
- FIG. 4 the state of the temperature gradient inside the sealed space R2 is shown by a graph (X in the figure). As shown in this graph, the temperature is stable at the temperature T1 (about 70K in the case of liquid nitrogen) in the lower part of the sealed space R2, and the temperature increases toward the upper side exposed to the outside air. A boundary surface between the liquid L layer and the gas G layer is formed in the vicinity of the saturation temperature T0 (about 78K in the case of liquid nitrogen).
- a branch passage K3 branched from the supply passage K1 is provided so as to be connected to the sealed space R2.
- the buffer structure 160 is provided with a safety valve 164 near the small bellows 163 for releasing the internal pressure to the outside when the pressure in the sealed space R2 exceeds a predetermined value.
- a safety valve 164 near the small bellows 163 for releasing the internal pressure to the outside when the pressure in the sealed space R2 exceeds a predetermined value.
- FIG. 5 is a schematic cross-sectional view taken along the axis of the shaft 150 in the liquid supply system 100 according to the embodiment of the present invention.
- the return passage (return pipe) K2 is omitted.
- the shaft 150 is hollow.
- the weight of the shaft 150 can be reduced, and the cross-sectional area can be reduced, so that heat on the atmosphere side can be prevented from being transmitted to the inside by the shaft 150.
- the shaft 150 is provided with an escape hole 151 that allows communication between the hollow portion inside and the outside of the shaft 150. For this reason, it is possible to prevent the shaft 150 from bursting due to a sudden increase in internal pressure due to vaporization of the liquid that has entered the hollow interior due to cracks or the like.
- heaters 171 and 172 are provided in the vicinity of the small bellows 163 (specifically, the hollow interior of the shaft 150 and the outer peripheral side of the shaft 150 near the end on the atmosphere side). Yes. Thereby, the temperature in sealed space R2 can be adjusted, and it can suppress (prevent) that frost and an ice block adhere to the small bellows 163 during a driving
- the buffer structure 160 that buffers the fluctuation (pulsation) of the pressure of the liquid L supplied through the supply passage (supply pipe) K1 is provided in the system. It has been. Therefore, pulsation can be further suppressed as compared with the case of each of the above embodiments.
- the buffer structure 160 employs a structure in which a cylindrical tube portion 161 through which the shaft 150 is inserted is used as a sealed space R2, and a liquid L layer and a gas G layer are formed therein. is doing. Therefore, since the layer of the gas G exhibits a function of hindering heat transfer, it is possible to suppress the heat generated from the linear actuator 140 and the atmospheric heat from being transmitted to the liquid L. Even if heat is transmitted to the liquid L and vaporizes, the new liquid L is always supplied and has a cooling effect. Therefore, the gas G layer that exhibits a buffering function (function as a gas damper) in the sealed space R2 Only thickens.
- heaters 171 and 172 capable of adjusting the temperature in the sealed space R2 inside the pipe portion 161 are provided. Therefore, the thicknesses of the liquid L layer and the gas G layer can be adjusted according to the pulsation that can occur when there is no damper, and the pressure fluctuation (pulsation) can be effectively suppressed.
- the pulsation itself can be further suppressed by adopting a configuration in which the small bellows 125 is provided below the bellows 130.
- the third embodiment by providing a structure that suppresses shaft shake, shaft shake can be suppressed and a damper function can be stably exhibited.
- V1 ⁇ q ⁇ K ⁇ (Pm ⁇ P1) 1 / n ⁇ ⁇ ⁇ 1 ⁇ (Pm ⁇ P2) 1 / n ⁇ [l] It becomes.
- q is the discharge amount [l] per reciprocating pump
- K is a constant according to the pump type, which is 0.25 in a series of double-acting reciprocating pumps as in this embodiment.
- Pm is the discharge average pressure [MPa]
- P1 which is the sealed gas pressure is (0.6 to 0.8) ⁇ Pm [MPa] when there is no temperature change.
- P1 0.7 ⁇ Pm [PMa].
- N is a polytropic index, which is 1.41 when the gas is nitrogen gas.
- P2 is the target maximum pipe internal pressure
- P2 ⁇ 1+ (pulsation rate ⁇ 100) ⁇ ⁇ Pm [Mpa] It becomes.
- the “pipe” corresponds to the supply passage K1 and the return passage K2 in the present embodiment.
- V2 Va ⁇ (Pa ⁇ P1) It becomes.
- Pa is the pressure (ordinary pressure) in the piping (supply passage K1 and return passage K2) when no impact pressure is generated.
- P1 is (0.8 to 0.9) ⁇ Pa [MPa].
- P1 0.9 ⁇ Pa [MPa].
- Va which is the amount of gas when the pressure is Pa
- Va ⁇ W ⁇ v2 ⁇ (n ⁇ 1) ⁇ ⁇ ⁇ 200 ⁇ Pa ⁇ ((Pb / Pa) (n ⁇ 1) / n ⁇ 1 ⁇ .
- d is the pipe diameter (inner diameter) [mm]
- L is the pipe length [m]
- ⁇ is the fluid density [kg / m3].
- v is a flow velocity
- v 21.23 ⁇ Q / d2 [m / s].
- the flow velocity v is an average flow velocity in the supply passage K1 and the return passage K2.
- Q is the flow rate [l / min].
- N is a polytropic index, which is 1.41 when the gas is nitrogen gas.
- FIG. 6A shows a case where the pressure fluctuation is a SIN wave in the conventional example (when the pump function is exhibited only in the first pump chamber), and the left figure shows a case where no damper is provided. This figure shows a case where a damper is provided.
- FIG. 6B shows a case where the pressure fluctuation is a SIN wave in the present embodiment (when the pump function is exhibited in the first pump chamber and the second pump chamber), and the left diagram is not provided with a damper. Cases (Examples 1 to 3) are shown, and the diagram on the right shows a case where a damper is provided (Example 4).
- the amount of gas is set to an amount that satisfies the above expression of V1
- the difference between Pmax and Pmin is 30% or less (pulsation rate 30) compared to the case where no damper is provided. % Or less).
- FIG. 6C shows a case where the pressure fluctuation is a rectangular wave in the conventional example (when the pump function is exhibited only in the first pump chamber), and the left figure shows a case where no damper is provided, This figure shows a case where a damper is provided.
- FIG. 6D shows a case where the pressure fluctuation is a rectangular wave in the present embodiment (when the pump function is exhibited in the first pump chamber and the second pump chamber), and the left diagram is not provided with a damper. Cases (Examples 1 to 3) are shown, and the diagram on the right shows a case where a damper is provided (Example 4).
- the difference between Pmax and Pmin is 30% or less (pulsation rate 30) compared to the case where no damper is provided. % Or less).
- Japanese Patent Application No. 2011-56426 the graph is simplified, but more specifically, when a damper is provided as shown in FIG. It becomes a behavior that increases for a moment and then decreases after reaching Pmax.
- the pressure fluctuation (pulsation) itself can be suppressed by exerting the pump function in the first pump chamber and the second pump chamber.
- pressure fluctuation can be effectively suppressed in the case of a rectangular wave.
- the pressure fluctuation can be effectively suppressed in combination with the suppression of the pressure fluctuation itself.
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Abstract
Description
超低温の液体が収容される第1容器と、
第1容器に収容された液体中に配置され、該液体を吸入し、かつ吸入した液体をシステムの外部に通じる供給通路に送出するように構成される第2容器と、
第2容器の内部に入り込むように配置されるベローズと、
駆動源によって往復移動するように構成され、前記ベローズを伸縮させる軸と、
を備える液体供給システムにおいて、
第2容器内のうち前記ベローズの外側は第1ポンプ室となっており、当該第1ポンプ室には、第1容器内の液体を第1ポンプ室内に吸入する第1吸入口、及び吸入した液体を第1ポンプ室内から前記供給通路に送出する第1送出口が設けられ、
前記ベローズ内は密閉空間により構成された第2ポンプ室となっており、当該第2ポンプ室には、第1容器内の液体を第2ポンプ室内に吸入する第2吸入口、及び吸入した液体を第2ポンプ室内から前記供給通路に送出する第2送出口が設けられていることを特徴とする。
第1容器内部と連通し、かつ、前記軸の往復移動に伴って伸縮する、外径が前記ベローズよりも小さな小ベローズによって連結されているとよい。
図1を参照して、本発明の実施例1に係る液体供給システムについて説明する。
図1を参照し、本発明の実施例1に係る液体供給システム100の全体構成、及び使用方法について説明する。本実施例に係る液体供給システム100においても、従来例と同様に、樹脂製の容器310の内部に超電導コイル320が備えられた被冷却装置300に超低温の液体Lを供給する場合を例にして説明する。なお、超低温の液体Lの具体例としては、液体窒素や液体ヘリウムを挙げることができる。
以上説明したように、本実施例に係る液体供給システム100によれば、ベローズ130内を密閉空間として第2ポンプ室P2を形成している。これにより、ベローズ130が縮む際、及び伸びる際のいずれにおいても液体Lが供給通路K1に送出され、ベローズ130の伸縮動作による液体供給量を、第1ポンプ室P1のみでポンプ機能を発揮させた場合に比べて2倍にすることができる。そのため、所望の供給量に対して、第1ポンプ室P1のみでポンプ機能を発揮させた場合に比べて、一回分の供給量を半分にすることができ、供給通路K1内における液体の最大圧力を半分程度にすることができる。従って、供給される液体の圧力変動(脈動)による悪影響を抑制することができる。
図2には、本発明の実施例2が示されている。本実施例においては、ベローズの下方に小ベローズを設けた場合の構成について説明する。その他の構成および作用については実施例1と同一なので、同一の構成部分については同一の符号を付して、その説明は省略する。
図3には、本発明の実施例3が示されている。本実施例においては、ベローズの下方に軸ブレを抑制するための構造を設けた場合の構成について説明する。その他の構成および作用については実施例1と同一なので、同一の構成部分については同一の符号を付して、その説明は省略する。
図4及び図5を参照して、本発明の実施例4に係る液体供給システムについて説明する。上記実施例1においては、軸が挿通される密閉空間内をガスで満たしたり真空状態としたりする場合を示したが、本実施例においては、当該密閉空間内に液体の層と気体の層とを形成することによって、ガスダンパーとして機能させる場合について示す。その他の構成および作用については実施例1と同一なので、同一の構成部分については同一の符号を付して、その説明は省略する。
ここで、本実施例において、密閉空間R2の内部をガスダンパーとして有効に機能させるために必要なガスの量について簡単に説明する。
圧力変動がSIN波の場合において、密閉空間R2の内部をガスダンパーとして有効に機能させるために必要なガスの量V1は、
V1={q×K×(Pm÷P1)1/n}÷{1-(Pm÷P2)1/n}[l]
となる。
P2={1+(脈動率÷100)}×Pm[Mpa]
となる。なお、「配管」は、本実施例においては、供給通路K1及び戻り通路K2に相当する。また、「脈動率」は目標最大配管内圧力と吐出平均圧力との差圧を吐出平均圧量で割った割合である。つまり、「脈動率」={(P2-Pm)÷Pm}×100となる。
圧力変動が矩形波の場合において、密閉空間R2の内部をガスダンパーとして有効に機能させるために必要なガスの量V2は、
V2=Va×(Pa÷P1)
となる。
Va={W×v2×(n-1)}÷{200×Pa×((Pb/Pa)(n-1)/n-1}となる。
図6を参照して、従来例と上記各実施例における圧力変動(脈動)についての比較結果を説明する。図6においては、経過時間(横軸)に対する圧力(縦軸)の変動をグラフにて示している。
110 第1容器
120 第2容器
121 第1吸入口
122 第1送出口
123 第2吸入口
124 第2送出口
121a,122a,123a,124a 1方向弁
130 ベローズ
140 リニアアクチュエータ
150 軸
151 逃がし孔
160 緩衝構造
161 管部
162,163 小ベローズ
164 安全弁
171,172 ヒータ
181,181a 軸部材
182 軸受
182a,182b 軸受部材
200 冷却機
300 被冷却装置
310 容器
320 超電導コイル
K1 供給通路
K2 戻り通路
K3 分岐通路
L 液体
P1 第1ポンプ室
P2 第2ポンプ室
R1,R2 密閉空間
Claims (9)
- 超低温の液体が収容される第1容器と、
第1容器に収容された液体中に配置され、該液体を吸入し、かつ吸入した液体をシステムの外部に通じる供給通路に送出するように構成される第2容器と、
第2容器の内部に入り込むように配置されるベローズと、
駆動源によって往復移動するように構成され、前記ベローズを伸縮させる軸と、
を備える液体供給システムにおいて、
第2容器内のうち前記ベローズの外側は第1ポンプ室となっており、当該第1ポンプ室には、第1容器内の液体を第1ポンプ室内に吸入する第1吸入口、及び吸入した液体を第1ポンプ室内から前記供給通路に送出する第1送出口が設けられ、
前記ベローズ内は密閉空間により構成された第2ポンプ室となっており、当該第2ポンプ室には、第1容器内の液体を第2ポンプ室内に吸入する第2吸入口、及び吸入した液体を第2ポンプ室内から前記供給通路に送出する第2送出口が設けられていることを特徴とする液体供給システム。 - 第1容器外部から前記ベローズに至るように伸びる前記軸が挿通され、かつその内部が気体によって満たされた密閉空間が形成されていることを特徴とする請求項1に記載の液体供給システム。
- 第1容器外部から前記ベローズに至るように伸びる前記軸が挿通され、かつその内部が真空状態となっている密閉空間が形成されていることを特徴とする請求項1に記載の液体供給システム。
- 第1容器外部から前記ベローズに至るように伸びる前記軸が挿通される密閉空間を形成し、かつ当該密閉空間内は前記液体の層と気体の層が形成されており、前記供給通路から分岐された分岐通路が当該密閉空間に繋がれることによって、前記供給通路を通じて供給される液体の圧力の変動を緩衝する緩衝構造が設けられていることを特徴とする請求項1に記載の液体供給システム。
- 前記緩衝構造には、前記軸が挿通される密閉空間内の圧力が所定以上になった場合に、内部の圧力を外部に逃がす安全弁が設けられていることを特徴とする請求項4に記載の液体供給システム。
- 前記軸が挿通される密閉空間と第2ポンプ室との間、及び当該密閉空間と外部空間との間は、いずれも前記軸の往復移動に伴って伸縮する、外径が前記ベローズよりも小さな小ベローズによって隔てられていることを特徴とする請求項1~5のいずれか一つに記載の液体供給システム。
- 前記密閉空間と外部空間との間を隔てる前記小ベローズの付近に温度を調整するヒータが設けられることを特徴とする請求項6に記載の液体供給システム。
- 前記ベローズの下方に、軸部材及び該軸部材の軸受が設けられていることを特徴とする請求項1~7のいずれか一つに記載の液体供給システム。
- 第2容器の底側と前記ベローズとは、
第1容器内部と連通し、かつ、前記軸の往復移動に伴って伸縮する、外径が前記ベローズよりも小さな小ベローズによって連結されていることを特徴とする請求項1~8のいずれか一つに記載の液体供給システム。
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EP12758269.0A EP2687793B1 (en) | 2011-03-15 | 2012-01-16 | Liquid supply system |
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US10233913B2 (en) | 2014-07-10 | 2019-03-19 | Eagle Industry Co., Ltd. | Liquid supply system |
CN106662372B (zh) * | 2014-07-10 | 2019-07-12 | 伊格尔工业股份有限公司 | 液体供给系统 |
JPWO2016047620A1 (ja) * | 2014-09-22 | 2017-07-06 | イーグル工業株式会社 | 液体供給システム |
WO2016047620A1 (ja) * | 2014-09-22 | 2016-03-31 | イーグル工業株式会社 | 液体供給システム |
US10584692B2 (en) | 2014-09-22 | 2020-03-10 | Eagle Industry Co., Ltd. | Liquid supply system |
WO2018038005A1 (ja) * | 2016-08-23 | 2018-03-01 | イーグル工業株式会社 | 液体供給システム |
KR20190026900A (ko) | 2016-08-23 | 2019-03-13 | 이글 고오교 가부시키가이샤 | 액체 공급 시스템 |
Also Published As
Publication number | Publication date |
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US8991658B2 (en) | 2015-03-31 |
JP5844348B2 (ja) | 2016-01-13 |
CN103261817B (zh) | 2015-04-01 |
CN103261817A (zh) | 2013-08-21 |
EP2687793B1 (en) | 2017-05-24 |
EP2687793A1 (en) | 2014-01-22 |
US20140054318A1 (en) | 2014-02-27 |
EP2687793A4 (en) | 2015-06-10 |
JPWO2012124363A1 (ja) | 2014-07-17 |
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