WO2024100445A1 - Unité de compresseur pour comprimer un gaz utilitaire par un liquide de travail et procédé associé - Google Patents

Unité de compresseur pour comprimer un gaz utilitaire par un liquide de travail et procédé associé Download PDF

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Publication number
WO2024100445A1
WO2024100445A1 PCT/IB2022/062862 IB2022062862W WO2024100445A1 WO 2024100445 A1 WO2024100445 A1 WO 2024100445A1 IB 2022062862 W IB2022062862 W IB 2022062862W WO 2024100445 A1 WO2024100445 A1 WO 2024100445A1
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WO
WIPO (PCT)
Prior art keywords
vessel
utility
working liquid
gas
utility gas
Prior art date
Application number
PCT/IB2022/062862
Other languages
English (en)
Inventor
Anil Kumar Sharma
Original Assignee
Anil Kumar Sharma
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Anil Kumar Sharma filed Critical Anil Kumar Sharma
Publication of WO2024100445A1 publication Critical patent/WO2024100445A1/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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/008—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being a fluid transmission link
    • 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
    • F04B41/00—Pumping installations or systems specially adapted for elastic fluids
    • F04B41/06—Combinations of two or more pumps
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/18—Centrifugal pumps characterised by use of centrifugal force of liquids entrained in pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F1/00—Pumps using positively or negatively pressurised fluid medium acting directly on the liquid to be pumped
    • F04F1/06—Pumps using positively or negatively pressurised fluid medium acting directly on the liquid to be pumped the fluid medium acting on the surface of the liquid to be pumped

Definitions

  • Embodiments of the present disclosure relate to the field of refrigeration and more particularly to a compressor unit for compressing a utility gas by a working liquid and a method thereof.
  • compressed gas uses as in, Air in motor transport for inflating tires, Oxygen in medical treatment, Carbon-di-oxide in fire extinguishing, Hydrogen with Oxygen in rocket engine power sciences, Refrigerant in common living comfort arrangements, etc. and the list goes on and it does, go umpteen.
  • Refrigeration involves removing unwanted heat from at least one of an object by a refrigerant.
  • the refrigerant in daily life include chlorofluorocarbons, hydro chlorofluorocarbons, ammonia, fluorocarbons, hydrocarbons, R12, R32 and the like.
  • a refrigeration process starts with a compressor converting the low pressure gaseous Refrigerant into a high-pressure gaseous form.
  • the temperature of the refrigerant elevates on par with the extent of compression.
  • the refrigerant in the high-pressure gaseous form turns into a high-pressure liquid form by exchanging heat energy with the surroundings.
  • the high-pressure liquid refrigerant is capable of absorbing heat energy from the object and the space being cooled thereby cooling the object.
  • reciprocating pistons - cylinder type of compressors are used in refrigeration applications for compressing the refrigerant in refrigeration applications or utility gases in cryogenic applications, as these gases are capable of attaining temperatures in cryogenic range.
  • the reciprocating pistons require multiple cyclic strokes to compress the utility gas to the required pressure and throughput quantum, thereby making the compression process time consuming and inefficient.
  • a compressor unit for compressing a utility gas by a working liquid.
  • the compressor unit includes a middle segment including a vessel A adapted to store the working liquid.
  • the working liquid includes at least one of a transformer oil, and a synthetic mineral oil.
  • the middle segment also includes a vessel B adapted to store the utility gas.
  • the vessel A and the vessel B are fabricated by partitioning the middle segment by a vertical plate.
  • the compressor unit includes a bottom segment positioned beneath the middle segment.
  • the bottom segment includes a centrifugal pump adapted to compress the utility gas stored in the vessel B to obtain a compressed utility gas by forcing the working liquid stored in the vessel A to the vessel B by the centrifugal pump via a plurality of direction control valve block.
  • the compressor unit includes a top segment located in proximity to the bottom segment and positioned above the middle segment.
  • the top segment includes a first non-returning valve adapted to guide the compressed utility gas obtained from the vessel B to a utility tank.
  • the top segment also includes a second non-returning valve adapted to guide the utility gas supplied by a gas storage tank to the vessel A to occupy a vacuum created in the vessel A upon forcing the working liquid from the vessel A to the vessel B by a force exerted by the centrifugal pump.
  • the plurality of direction control valve block of the bottom segment is adapted to direct the working liquid from the vessel B to the vessel A to obtain the compressed utility gas by compressing the utility gas received by the vessel A at the occurrence of the pressure corresponding to the working liquid in the vessel B exceeds a predefined threshold.
  • the top segment includes a third non-returning valve adapted to guide the compressed utility gas obtained from the vessel A to the utility tank.
  • the top segment also includes a fourth non-returning valve adapted to guide the utility gas supplied by the gas storage tank into the vessel B to occupy the vacuum created in the vessel B upon displacing the working liquid from the vessel B to the vessel A by a force applied by the centrifugal pump.
  • a method of operation of a compressor unit for compressing a utility gas by a working liquid includes storing, by a vessel A, a working liquid.
  • the working liquid includes at least one of a transformer oil and a synthetic mineral oil.
  • the method also includes storing, by a vessel B a utility gas.
  • the vessel A and the vessel B are fabricated by partitioning the middle segment by a vertical plate.
  • the method further includes compressing, by a centrifugal pump, the utility gas stored in the vessel B to obtain a compressed utility gas by forcing the working liquid stored in the vessel A to the vessel B via a plurality of direction control valve block.
  • the method also includes guiding, by a first non-returning valve, the compressed utility gas obtained from the vessel B to a utility tank.
  • the method further includes guiding, by a second nonreturning valve, the utility gas supplied by a gas storage tank to the vessel A to occupy a vacuum created in the vessel A upon forcing the working liquid out from the vessel A to the vessel B by the pump.
  • the method also includes directing, by the plurality of direction control valve blocks the working liquid from the vessel B to the vessel A to obtain the compressed utility gas by compressing the utility gas received by the vessel A at the occurrence of the pressure corresponding to the working liquid in the vessel B exceeds a predefined threshold.
  • the method further includes guiding, by a third nonreturning valve, the compressed utility gas obtained from the vessel A to the utility tank.
  • the method also includes guiding, by a fourth non-returning valve, the utility gas supplied by the gas storage tank into the vessel B to occupy the vacuum created in the vessel B upon displacing the working liquid from the vessel B to the vessel A by a force applied by the pump.
  • FIG. la is a schematic representation of a compressor unit for compressing a utility gas by a working liquid in accordance with an embodiment of the present disclosure
  • FIG. lb is a schematic representation of one embodiment of the compressor unit of FIG. la, depicting a cylindrical container in accordance with an embodiment of the present disclosure
  • FIG. 2a is a flow chart representing the steps involved in a method of operation of a compressor unit for compressing a utility gas by a working liquid in accordance with an embodiment of the present disclosure
  • FIG. 2b is a flow chart representing the continued steps involved in a method of FIG. 2a, in accordance with an embodiment of the present disclosure.
  • references will be made to “vessel A”, and “vessel B” with reference to an entity (chamber) that is used to hold a utility gas and a working liquid interchangeably during the operation of the compressor unit.
  • references will be made to “first non-returning valve”, “second non-returning valve”, third non-returning valve”, and “fourth non-returning valve” with reference to the entity (non-returning valve NRV) that is used to direct the flow of the utility gas and the working liquid through a predetermined path.
  • Embodiments of the present disclosure relate to a compressor unit for compressing a utility gas by a working liquid and a method thereof.
  • the compressor unit includes a middle segment including a vessel A adapted to store the working liquid.
  • the working liquid includes at least one of a transformer oil, and a synthetic mineral oil.
  • the middle segment also includes a vessel B adapted to store the utility gas.
  • the vessel A and the vessel B are fabricated by partitioning the middle segment by a vertical plate.
  • the compressor unit includes a bottom segment positioned beneath the middle segment.
  • the bottom segment includes a centrifugal pump adapted to compress the utility gas stored in the vessel B to obtain a compressed utility gas by forcing the working liquid stored in the vessel A to the vessel B by the centrifugal pump via a plurality of direction control valve block.
  • the compressor unit includes a top segment located in proximity to the bottom segment and positioned above the middle segment.
  • the top segment includes a first non-returning valve adapted to guide the compressed utility gas obtained from the vessel B to a utility tank.
  • the top segment also includes a second non-returning valve adapted to guide the utility gas supplied by a gas storage tank to the vessel A to occupy a vacuum created in the vessel A upon forcing the working liquid from the vessel A to the vessel B by a force exerted by the centrifugal pump.
  • the plurality of direction control valve block of the bottom segment is adapted to direct the working liquid from the vessel B to the vessel A to obtain the compressed utility gas by compressing the utility gas received by the vessel A at the occurrence of the pressure corresponding to the working liquid in the vessel B exceeds a predefined threshold.
  • the top segment includes a third non-returning valve adapted to guide the compressed utility gas obtained from the vessel A to the utility tank.
  • the top segment also includes a fourth non-returning valve adapted to guide the utility gas supplied by the gas storage tank into the vessel B to occupy the vacuum created in the vessel B upon displacing the working liquid from the vessel B to the vessel A by a force applied by the centrifugal pump.
  • FIG. la is a schematic representation of a compressor unit (10) for compressing a utility gas by a working liquid in accordance with an embodiment of the present disclosure.
  • the compressor unit (10) includes a middle segment (20).
  • the middle segment (20) includes a vessel A (30) adapted to store the working liquid.
  • the compressor unit (10) is a liquid layer compressor having an open architecture (OaLLC).
  • the working liquid includes at least one of a transformer oil and a synthetic mineral oil. Usage of water or any water based liquid solution may be avoided as the working liquid.
  • the water may freeze in coolest section of refrigeration piping circuitry, chocking and blocking refrigerant flow path, thereby making the refrigeration process discontinuous.
  • Choice of the working liquid shall be made judiciously by checking compatibility of the working liquid with the utility gas being compressed.
  • the middle segment (20) also includes a vessel B (40) adapted to store a utility gas.
  • the utility gas may include, but not limited to, at least one of tetrafluoroethene, freon R32, freon R12, air, oxygen, hydrogen, nitrogen, argon, helium, carbon-di-oxide.
  • the vessel A and the vessel B may be any conveniently shaped pressure vessels.
  • the vessel A (30) and the vessel B (40) may be fabricated by partitioning the middle segment (20) by a vertical plate (not shown in FIG. la).
  • the compressor unit (10) also includes a bottom segment (50) positioned beneath the middle segment (20).
  • the bottom segment (50) includes a centrifugal pump (60) and an associated electric motor to run the centrifugal pump (60).
  • the centrifugal pump (60) is adapted to compress the utility gas stored in the vessel B (40) to obtain a compressed utility gas by forcing the working liquid stored in the vessel A (30) to the vessel B (40) via a plurality of direction control valve block (70).
  • the plurality of direction control valve block may include at least one of a hybrid port slider shifter (HPSS) and a multi-port slider shifter (MPSS).
  • the plurality of direction control valve block (70) may be activated by at least one of a one or more corresponding pneumatic actuators, solenoid coils, and a pair of hydraulic piston cylinder utilizing hydraulic potential of the centrifugal pump (60).
  • the MPSS exhibits six combined working liquid flow path ports.
  • the MPSS has one common handle slider to operate on all of these ports simultaneously as logically and sequentially arranged. Operation of the slider shifting opens or closes all MPSS ports simultaneously changing flow direction of the working liquid between the vessel A (30) and the vessel B (40). Functionally of the MPSS is equivalent to a pair of three way valve since the MPSS includes six ports.
  • Operation of the HPSS is similar to the MPSS except, the HPSS includes additional ports for forced suction enabler.
  • the compressor unit (10) also includes a top segment (80) located in proximity to the bottom segment (50) and positioned above the middle segment (20).
  • the top segment (80) includes a first non-returning valve (90) adapted to guide the compressed utility gas obtained from the vessel B (40) to a utility Tank (100).
  • the utility tank (100) may be capable of storing high pressure gases.
  • the top segment (80) also includes a second non-returning valve (110) adapted to guide the utility gas supplied by a gas storage tank (120) to the vessel A (30) to occupy a vacuum created in the vessel A (30) upon forcing the working liquid from the vessel A (30) to the vessel B (40) by the pump (60).
  • the gas storage tank (120) may be a low pressure tank.
  • the vessel A (30) and the vessel B (40) may include one or more corresponding liquid non-forwarding valves (LNFV) (150) located above the vessel A (30) and the vessel B (40).
  • the one or more LNFV (150) may be adapted to prevent entry of the working liquid into pipe leading to the utility tank (100) via the first non-returning valve (90) and the third non-returning valve (130).
  • the gas storage tank (120) and the utility tank (100) may be associated with corresponding one or more isolation valves (160) adapted to isolate the gas storage tank (120) and the utility tank (100).
  • the plurality of direction control valve block (70) of the bottom segment (50) is adapted to direct the working liquid from the vessel B (40) to the vessel A (30) to obtain the compressed utility gas by compressing the utility gas received by the vessel A (30) at the occurrence of the pressure corresponding to the working liquid in the vessel B (40) exceeds a predefined threshold.
  • the top segment (80) includes a third non-returning valve (130) adapted to guide the compressed utility gas obtained from the vessel A (30) to the utility tank (100).
  • the vessel A (30) and the vessel B (40) may include one or more corresponding pressure switches (not shown in FIG. la) adapted to sense the pressure corresponding to the working liquid in each of the vessel A (30) and the vessel B (30).
  • one or more corresponding pressure switches may relay a signal to an electromagnetic coil associated with the HPSS to change position of the HPSS to reverse direction of flow of the working liquid.
  • the top segment (80) also includes a fourth non-returning valve (140) adapted to guide the utility gas supplied by the gas Storage tank (120) into the vessel B (40) to occupy the vacuum created in the vessel B (40) upon displacing the working liquid from the vessel B (40) to the vessel A (30) by a force applied by the pump (60).
  • the first non-returning valve (90) and second non-returning valve (110) may be adapted to prevent intermixing of the utility gas supplied by the gas Storage tank (120) and the compressed utility gas being guided by the third nonreturning valve (130) to the utility tank (100) from the vessel A (30).
  • the third non-returning valve (130) and the fourth nonreturning valve (140) may be adapted to prevent intermixing of the utility gas supplied by the gas storage tank (120) and the compressed utility gas being guided by the first non-returning valve (90) to the utility tank (100) from the vessel B (40) to the utility tank (100).
  • the top segment (80), the middle segment (20), and the bottom segment (50) may be hermetically sealed in a cylindrical container (180) as shown in FIG. lb.
  • Fig. lb is another schematic representation of one embodiment of the compressor unit as shown in FIG. la, depicting a cylindrical container (180) in accordance with an embodiment of the present disclosure.
  • the cylindrical container (180) may hermetically isolate the the top segment (80), the middle segment (20), and the bottom segment (50) from an external environment to provide a hermetically sealed architecture (HsaLLC) of the compressor unit (10).
  • HsaLLC hermetically sealed architecture
  • the heat exchanger (170) may be avoided to scale down the compressor unit (10) depicted in FIG. la.
  • the utility gas may cool the working liquid present in the bottom segment (50) via the heat exchanger (170) through the surfaces of piping circuitry and body of the HPSS.
  • the heat exchanger may expel the heat to the atmosphere via outer cylindrical surface of the middle segment (20).
  • Another function of the heat exchanger (170) is to provide flow resistance at an outlet of the centrifugal pump (60) to obviate pump run out condition.
  • the pump run out condition may occur due to sudden pressure drop at a discharge port of the centrifugal pump (60) due to sudden operation of the HPSS.
  • the multi bend structure and varying cross sectional area of the heat exchanger (170) provides flow resistance to the working liquid during the operation of the HPSS.
  • the HPSS may combine two three way valves as a single entity enables the heat removal in a loop and along with dissipating heat energy from the working liquid thereby ensuring uninterrupted and continuous operation of the compressor unit.
  • the HPSS has same ten ports as in the MPSS. But, driving force required for moving the slider in the HPSS is required to be much stronger potent, versatile, multipurpose and, powerful.
  • This is an advance embodiment of the MPSS to culminate into twelve port working of the HPSS where two additional ports 11 th & 12 th on the HPSS are provided to hydraulically power the slider of the HPSS. The two additional ports are positioned at either ends of the HPSS. Hydraulic multipurpose functionality in the HPSS entails slider push, hold and retrieve which otherwise would require six solenoid elements. With hydraulic piston cylinder arrangement provided at port 11 and 12 for hydraulic implementation necessitate an additional layer of slider shifter named control port slider shifter (CPSS).
  • CPSS control port slider shifter
  • the CPSS may control and operate complete scope of the HPSS and essential functionality of liquid layer compressor (LLC) as an integral unit.
  • the CPSS has six ports for slider Shifter function along with two additional ports for hydraulically operating on slider of the CPSS integrating full scope of push pull and retrieve function in two special pass-through hydraulic solenoid valve.
  • CPSS is a sort of hydraulic potential amplifier and six logical gates between HPSS and operating point push button for operation. Making it to work with a grand total of twenty ports and only two push button operating point or port 19 and 20.for entire Liquid Layer Compressor (LLC).
  • the independent layer of Slider Shifter to form CPSS dictates unmatchable simultaneous functioning on all ten critical output functioning ports of HPSS.
  • the entire schema of HPSS, CPSS and one special pass -through hydraulic solenoid valve provides full unperturbed calm and tranquil automation to operate on Liquid Layer Compressor, with highest reliability and economy in conjunction with the LZC.
  • Four additional ports, over and above six ports of the MPSS or the basic configuration of the HPSS incorporate forced suction enabler (FSE) wherein the utility gas route from the gas storage tank (120) or from the bottom segment (50) to top of the vessel A (30) and the vessel B (40) by bypassing the second non-returning valves (110) and the fourth non-returning valve (140) to occupy the vacuum created in the vessel A (30) and the vessel B (40) upon shifting the working liquid between the vessel A (30) and the vessel B (40).
  • FSE forced suction enabler
  • CPSS control port slider shifter
  • valves 110,140, 130, 90 3x70, 3x70 that counts to ten plus two more ports to power sliding of the working liquid valves to drive the HPSS slider nicely count up ten, all accommodated in a fully automatic implement working on one electronic switch on/off per side, only way to stop LLC is to stop pump PMP.
  • the weakest flow link in the entire flow circuitry of LLC implement is the suction function at the vessel A (30), the vessel B (40) via the second non -returning valve (110), and the fourth non-returning valve (140), is provided with dedicated bypass shortcut path (not shown in FIG. la) from its origin gas storage tank just bypassing the second non -returning valve (110), and the fourth non-returning valve (140) to destination point via HPSS to top of the vessel A (30) and the vessel B(40) for utility gas supply to the vessel A (30), and the vessel B (40). Meaning thereby that it opens or closes along with other requisite ports in HPSS.
  • mLLC uses (Ten port micro Liquid Layer Compressor) MPSS
  • the other second embodiment of OaLLC uses (Twenty port HPSS+CPSS) in HPSS.
  • Both MPSS and HPSS+CPSS have same common minimum piping connection circuitry of working liquid adapted to compress the utility gas stored in the vessel B to obtain a compressed HP utility gas by forcing the working liquid stored in the vessel A into the vessel B via a direction control valve block (70) using MPSS or HPSS+CPSS.
  • the compressor unit also includes a top segment (80) located in proximity to the bottom segment (50) and positioned above the middle segment (20).
  • FIG. 2a and FIG. 2b are flow charts representing the steps involved in a method (200) of operation of the compressor unit for compressing a utility gas by a working liquid in accordance with an embodiment of the present disclosure.
  • the method (200) includes storing a working liquid in step 210.
  • storing a working liquid includes storing a working liquid by a vessel A.
  • the working liquid includes at least one of a transformer oil and a synthetic mineral oil. but never water or any water based liquid solution especially in refrigeration application, as even water moisture gets frozen and will chock and clog utility gas path in cool region and make refrigeration process discontinue.
  • the method (200) also includes storing a utility gas in step 220.
  • storing a utility gas includes storing a utility gas by a vessel B.
  • the vessel A and the vessel B may be any convenient shape pressure vessels.
  • the vessel A and the vessel B may be fabricated by partitioning the middle segment by a vertical plate.
  • the Utility gas may include, but not limited to, at least one of tetrafluoroethene, freon, R12, or R32.
  • the method (200) also includes compressing the utility gas stored in the vessel B to obtain a compressed utility gas by forcing the working liquid stored in the vessel A to the vessel B by forcing the working liquid stored in the vessel A to the vessel B via a plurality of direction control valve block in step 230.
  • compressing the utility gas stored in the vessel B to obtain a compressed utility gas by forcing the working liquid stored in the vessel A to the vessel B via a plurality of direction control valve block includes compressing the utility gas stored in the vessel B to obtain a compressed utility gas by forcing the working liquid stored in the vessel A to the vessel B via a plurality of direction control valve block by a centrifugal pump.
  • the plurality of direction control valve block be associated with a solenoid coil for switching the position of the plurality of direction control valve block.
  • the method (200) further includes guiding the compressed utility gas obtained from the vessel B to a utility tank in step 240.
  • guiding the compressed utility gas obtained from the vessel B to a utility tank includes guiding the compressed utility gas obtained from the vessel B to a utility tank by a first non-returning valve.
  • the method (200) also includes guiding the utility gas supplied by a gas storage tank to the vessel A to occupy a vacuum created in the vessel A upon forcing the working liquid from the vessel A to the vessel B by the pump in step 250.
  • guiding the utility gas supplied by a gas storage tank to the vessel A to occupy a vacuum created in the vessel A upon forcing the working liquid from the vessel A to the vessel B by the pump includes guiding the utility gas supplied by a gas storage tank to the vessel A to occupy a vacuum created in the vessel A upon forcing the working liquid from the vessel A to the vessel B by the pump by a second non-retuning valve.
  • the vessel A and the vessel B may include one or more corresponding LNFV located above the vessel A and the vessel B.
  • the one or more LNFV may be adapted to prevent entry of the working liquid into the utility tank via the first non-returning valve and the third non-returning valve.
  • the storage tank and the utility tank may be associated with corresponding one or more isolation valves adapted to isolate the gas storage tank and the utility tank from each of the vessel A and the vessel B.
  • the method (200) also includes directing the working liquid from the vessel B to the vessel A to obtain the compressed utility gas by compressing the utility gas received by the vessel A at the occurrence of the pressure corresponding to the working liquid in the vessel B exceeds a predefined threshold in step 260.
  • the method (200) also includes guiding the compressed utility gas obtained from the vessel A to the utility tank (100) in step 270.
  • guiding the compressed utility gas obtained from the vessel A to the utility tank includes guiding the compressed utility gas obtained from the vessel A to the utility tank (100) by a third non-returning valve (130).
  • the method (200) further includes guiding the utility gas supplied by the gas storage tank into the vessel B to occupy the vacuum created in the vessel B upon displacing the working liquid from the vessel B to the vessel A by a force applied by the pump in step 280.
  • guiding the utility gas supplied by the gas storage tank into the vessel B to occupy the vacuum created in the vessel B upon displacing the working liquid from the vessel B to the vessel A by a force applied by the pump includes guiding the utility gas supplied by the gas storage tank into the vessel B to occupy the vacuum created in the vessel B upon displacing the working liquid from the vessel B to the vessel A by a force applied by the pump by a fourth non-returning valve (140).
  • the first non-returning valve and second nonreturning valves may be adapted to prevent intermixing of the utility gas supplied by the gas storage tank and the compressed utility gas being guided by the third nonreturning valve to the utility tank from the vessel A.
  • the third non-returning valve and the fourth non-returning valves may be adapted to prevent intermixing of the utility gas supplied by the gas storage tank and the compressed utility gas being guided by the first non-returning valve to the utility tank from the vessel B.
  • the compressed utility gas supplied to the utility tank may be recollected into the gas storage tank.
  • the pump may include a centrifugal pump adapted to displace the working liquid from the vessel A to the vessel B and vice versa based on one or more settings of the plurality of direction control valve block.
  • the pump may be hydraulically coupled to a heat exchanger.
  • the heat exchanger may be adopted to cool down Working liquid flowing through the pump by exchanging heat energy of the Working liquid with an external environment.
  • the heat exchanger may be also adapted to neutralize one or more pressure variations occurring in a discharge line associated with the pump during actuation of the plurality of direction control valve block.
  • the top segment, the middle segment, and the bottom segment may be hermetically sealed in a cylindrical container leaving only utility gas input nozzles and compressed utility gas output nozzles along with electrical connections to the centrifugal pump and HPSS.
  • the electrical connections from the pressure switches that are housed in the bottom Segment may be left penetrating through the hermetically sealed cylindrical container.
  • the vessel A and the vessel B may include one or more corresponding pressure switches adapted to sense the condition that the vessel A or vessel B has become full of liquid up to brim and any further continued forcing of working liquid actuates corresponding pressure switch. These pressure switches generate signal alternately for the plurality of direction control valve block to flip direction of working fluid from vessel A and vessel B and from vessel B to vessel A respectively.
  • the compressor unit for compressing a utility gas by a working liquid and a method thereof described above enables various advantages.
  • the compressor unit is capable of compressing the utility gas twice in a single cycle of its operation.
  • the pressurization cycle from start to finish of the stroke is a linear graphical stretch without any start, stop, acceleration deceleration, break and restart, thereby providing superior mechanical and also thermodynamic efficiency compared to any other type of compressors having the reciprocating pistons, cylinders, a liquid ring compressor (LRC) and the like.
  • LRC liquid ring compressor
  • the compressor unit is simple mechanism and easy to operate. Provision of the heat exchanger is capable of dissipating heat energy from the working liquid thereby ensuring continuous operation of the compressor unit.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)

Abstract

L'invention concerne une unité de compresseur (10) pour comprimer un gaz utilitaire par un liquide de travail. L'unité de compresseur comprend un segment intermédiaire (20) comprenant un récipient A (30) pour stocker un liquide de travail. Le segment intermédiaire comprend également un récipient B (40) pour stocker le gaz utilitaire. L'unité de compresseur comprend un segment inférieur (50) comprenant une pompe (60) pour comprimer le gaz utilitaire. L'unité de compresseur comprend un segment supérieur (80) comprenant une première soupape de non-retour (90) pour guider le gaz utilitaire comprimé vers un réservoir utilitaire (100). Le segment supérieur comprend une seconde soupape de non-retour (110) pour guider le gaz utilitaire fourni par un réservoir de stockage de gaz (120) au récipient A. La pluralité de blocs de soupape de commande de direction (70) du segment inférieur dirigeant le liquide de travail du récipient B vers le récipient A pour comprimer le gaz utilitaire stocké dans le récipient A.
PCT/IB2022/062862 2022-11-11 2022-12-29 Unité de compresseur pour comprimer un gaz utilitaire par un liquide de travail et procédé associé WO2024100445A1 (fr)

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Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2932106A1 (fr) * 2012-12-16 2015-10-21 Isocurrent Energy Incorporated Système de stockage d'énergie utilisant l'air comprimé

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2932106A1 (fr) * 2012-12-16 2015-10-21 Isocurrent Energy Incorporated Système de stockage d'énergie utilisant l'air comprimé

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