US20050223734A1 - Screw compressor-expander machine - Google Patents

Screw compressor-expander machine Download PDF

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Publication number
US20050223734A1
US20050223734A1 US10/513,289 US51328905A US2005223734A1 US 20050223734 A1 US20050223734 A1 US 20050223734A1 US 51328905 A US51328905 A US 51328905A US 2005223734 A1 US2005223734 A1 US 2005223734A1
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United States
Prior art keywords
rotors
compressor
expander
partition
machine
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.)
Abandoned
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US10/513,289
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English (en)
Inventor
Ian Smith
Nikola Stosic
Ahmed Kovacevic
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City University of London
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City University of London
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Publication date
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Assigned to CITY UNIVERSITY reassignment CITY UNIVERSITY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KOVACEVIC, AHMED, SMITH, IAN KENNETH, STOSIC, NIKOLA RUDI
Publication of US20050223734A1 publication Critical patent/US20050223734A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/003—Systems for the equilibration of forces acting on the elements of the machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/16—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • F01C11/004—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle and of complementary function, e.g. internal combustion engine with supercharger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/084—Toothed wheels
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure

Definitions

  • This invention relates to plural-screw compressor-expander machines. These are positive displacement rotary machines which consist, essentially, of a pair of meshing helically lobed rotors, contained in a casing.
  • Plural-screw machines are widely used as compressors.
  • An important feature of such machines is that if the direction of gas flow is reversed, so that high-pressure gas is delivered to flow into the machine through the high pressure port and out through the low pressure port, it will act as an expander with the direction of rotation reversed.
  • the machine will also work as an expander when rotating in the same direction as a compressor provided that the suction and discharge ports are positioned on the opposite sides of the casing to those for a compressor since this is effectively the same as reversing the direction of rotation relative to the ports.
  • mechanical power When operating as a compressor, mechanical power must be supplied to a main rotor to rotate the machine. When acting as an expander, the rotor will rotate automatically and generate power.
  • a major problem with the plural screw machines is that the pressure difference between entry and exit creates very large radial and axial forces on the rotors whose magnitude and direction is independent of the direction of rotation. It is normal practice to have bearings on each end of the rotors and these have to withstand both the radial and axial loads induced by the pressure difference. As a result, some of the power transmitted through the rotors is lost in bearing friction. More importantly, in these machines, the pressure difference by which it is possible to compress gases within one pair of rotors is limited to approximately 60 bar in normal designs.
  • a plural-screw expander-compressor machine comprising intermeshing first and second helically-profiled rotors mounted for rotation in opposite directions in a housing by means of bearings at the opposite ends of the rotors, the interior of the housing being divided by a transverse, partition into a compressor portion and an expander portion, the rotors extending through the partition and having circularly profiled portions where they extend through the partition, the two housing portions each having a higher pressure port and a lower pressure port, the higher pressure ports being adjacent the partition and on opposite sides of the rotors.
  • an expander-compressor in accordance with the invention mitigates the problem of high bearing loads associated with twin screw machines, and at the same time enables some power to be recovered from the expansion of the fluid between the cooler and evaporator for example in a CO 2 vapour compression cycle system.
  • FIG. 1 is a schematic circuit diagram of a refrigeration system with carbon dioxide as refrigerant and incorporating a machine embodying the invention
  • FIG. 2 is a longitudinal sectional view of the machine on the axes of the two rotors
  • FIG. 3 is a longitudinal sectional view through the axis of the main rotor at right angles to FIG. 2 ,
  • FIG. 4 shows the forces acting on the compressor-forming portions of the rotors
  • FIG. 5 shows the forces acting on the expander-forming portions of the rotors
  • FIG. 6 shows the net forces acting on the rotors
  • FIG. 7 is an enthalpy entropy diagram of the system shown in FIG. 1 .
  • FIG. 8 is a schematic diagram of a fuel cell system incorporating a machine embodying the invention.
  • FIGS. 9 and 10 are views similar to FIGS. 2 and 3 of an alternative machine suitable for use in the system of FIG. 8 .
  • FIG. 1 shows the layout of a CO 2 refrigeration system, operating between an evaporating temperature of 0° C. and a cooler exit temperature of 40° C.
  • CO 2 at approximately 35 bar has its pressure raised to 100 bar in a compressor 1 driven by a motor 2 . It then passes through a cooler 3 where it is cooled in the supercritical state at approximately constant pressure until it reaches a temperature of 40° C.
  • the cooled dense fluid would then pass in conventional practice through a throttle valve in which the pressure is reduced back to 35 bar. As a result of the pressure drop, it liquefies and part flashes into vapour, causing the liquid-vapour mixture to fall in temperature to 0° C.
  • the cooled liquid CO 2 together with the vapour formed during flashing, then passes through an evaporator 4 , where it receives heat from the cold surroundings at approximately 35 bar and 0° C. until all the refrigerant is evaporated.
  • the dry, or slightly superheated vapour then enters the compressor 1 to complete the cycle.
  • the required pressure rise across the compressor is 65.2 bar, which is beyond the limit of what is readily achievable in a single stage twin screw compressor; due to excessive loads on the rotor bearings. Further, the energy losses due to the throttle valve would be substantial.
  • FIGS. 2 and 3 The resulting machine is shown schematically in FIGS. 2 and 3 and includes a housing 10 defining a chamber containing a helically lobed main rotor 11 and a helically grooved gate rotor 12 which meshes with the main rotor 11 .
  • Each rotor has a cylindrical extension at each end by means of which it is rotatably supported in bearings (not shown) in the end walls of the housing 10 , the extension at one end of the main rotor 11 being prolonged at 13 for a driving connection to the motor 2 .
  • the interior of the chamber in the housing is divided by a transverse partition 14 into a longer compressor portion and a shorter expander portion.
  • the partition 14 is divided along a plane through the axes of the rotors and extends into an annular groove in each rotor 11 , 12 .
  • the two halves of the partition are engaged in the rotors and the assembly thus formed is introduced into the chamber through one end thereof.
  • the compressor portion of the housing has a large diameter (and thus large area) inlet port 15 at one end of the housing (its position relative to the rotors being indicated in FIG. 2 ) and a smaller diameter (and thus small area) outlet port 16 adjacent the partition 14 , on the opposite side of the rotors.
  • the compressor inlet port 15 is connected by a line 21 ( FIG. 1 ) to the outlets of the evaporator and the compressor outlet port 16 is connected to the inlet of the cooler 3 by a line 22 .
  • the expander portion of the housing has a larger diameter (and thus large area) outlet port 17 , at the opposite end of the housing 10 to the compressor inlet port 15 , and a smaller area inlet port 18 adjacent the partition 14 on the opposite side of the rotors 11 and 12 to the outlet port 17 .
  • the expander outlet port 17 is connected by a line 24 to the inlet of the evaporator 4 and the expander inlet port 18 is connected by a line 23 to the outlet of the cooler 3 .
  • the ports 16 and 18 are the high pressure ports of the compressor and expander. They are on opposite sides of the rotors ( FIG. 3 ) but axially close to each other, adjacent the partition 14 .
  • high pressure dense fluid enters the expander port 18 at the top of the casing 10 , near the centre, and leaves through the low pressure port 17 at the bottom of the casing at one end, as a mixture of liquid and vapour.
  • the expansion process causes the temperature to drop, as in passing through a throttle valve. However, here the fall in pressure is used to recover power and causes or assists the rotors to turn.
  • Vapour from the evaporator 4 enters the low pressure compressor inlet port 15 , at the top of the opposite end of the casing, is compressed within it and expelled from the high pressure discharge port 16 at the bottom of the casing, near the centre, to be delivered to the cooler 3 .
  • the high pressure ports are in the centre of the unit and arranged so that they are on opposite sides of the casing, the high pressure forces due to compression and expansion are opposed to each other and, more significantly, only displaced axially from each other by a relatively short distance. The radial forces on the bearings are thereby significantly reduced. In addition, since both ends of the rotors are at more or less equal pressure, the axial forces virtually balance out.
  • the following example indicates the extent of the advantages, which are possible from this arrangement.
  • FIG. 4 shows the compressor rotors portions 11 C, 12 C and the bearing loads which must be resisted if the refrigeration system is designed with a conventional screw compressor drive.
  • FIG. 5 the expander rotor portions 11 E, 12 E and their corresponding bearing forces are similarly shown.
  • the axial bearing load on the main rotor is 92 kN while the corresponding radial loads are 86 kN at the high pressure end and 34 kN at the low pressure end.
  • FIG. 6 shows the bearing forces as a result of use of the invention if the compressor and expander rotors are machined on the same shafts with the high pressure ports in the middle and the low pressure ports at each end of the housing.
  • thermodynamic performance an enthalpy entropy diagram of the idealised cycle with reversible compression and expansion of the CO 2 is shown in FIG. 7 .
  • the curve 31 is the saturation line for CO 2 and the curve 32 is the saturation line for CO 2 vapour.
  • point 21 corresponds to vapour being admitted to the compressor through the line 21 of FIG. 1 , point 22 to discharge from the compressor 1 at 22 and entry to the cooler 3 and point 23 to exit from the cooler 3 .
  • the fluid then passes through a throttle-valve, isenthalpic expansion will lead to it entering the evaporator at point 24 t .
  • the expansion process will be adiabatic and the fluid will enter the evaporator at point 24 e .
  • work extraction reduces the specific enthalpy of the fluid entering the evaporator by 14.9 kJ/kg. This causes the same mass of fluid to enter the evaporator with less vapour and hence has the effect of increasing the refrigerating capacity of the plant by 12.4%.
  • a further preferred feature is the use of rotors which seal on both contacting surfaces so that the same profile may be used both for the expander and the compressor sections.
  • the compressor and expander profiles could be different. However, this would make manufacture extremely difficult, due to the very small clearance space, which could be less than 10 mm, between the, two rotor portions.
  • the compressor and expander rotors can be machined or ground in a single cutting operation and then separated by machining a parting groove in them for the partition on completion of the lobe formation.
  • the expansion section can contain a capacity control such as a slide or lifting valve to alter the volume passing through it at part load, in a manner identical to capacity controls normally used in screw compressors. This would be in addition to any capacity or volume ratio control used for the compression section. This would then replace the throttle valve control system normally required in conventional vapour compression systems.
  • a capacity control such as a slide or lifting valve to alter the volume passing through it at part load, in a manner identical to capacity controls normally used in screw compressors. This would be in addition to any capacity or volume ratio control used for the compression section. This would then replace the throttle valve control system normally required in conventional vapour compression systems.
  • the invention is especially suitable for operation on high pressure CO 2 systems, it may equally be used with more conventional refrigerants, or indeed, wherever there is a need for combined expansion and compression processes or even if a combined expansion-compression process is established only to reduce the rotor loads.
  • the balanced rotor concept is also applicable for the “expressor” system of a motorless self-driven expander-compressor machine described in the paper ‘Expressor’ mentioned above.
  • FIG. 8 is a block diagram of a fuel cell system using hydrogen as fuel and incorporating a machine as shown in FIGS. 2 and 3 .
  • Hydrogen is supplied from a source 41 , such as a hydrogen generator or a pressurised tank, through a pressure regulator 42 to a fuel cell stack 43 . Unused hydrogen from the stack is recirculated at 44 .
  • air is drawn in from an intake 45 and intake filter 46 via the compressor portion 1 of the machine shown in FIGS. 2 and 3 .
  • Combustion products from the fuel cell stack 43 under pressure are delivered to the inlet port 18 of the expander portion 5 and leave the latter through its outlet port 17 , such exhaust consisting of water, and nitrogen.
  • a cooling system including a radiator 47 and a coolant circulating pump 48 driven by electricity generated within the fuel cell stack.
  • the main electrical power output from the fuel cell stack is delivered to a power distribution unit 49 which distributes power to the driving motor 50 for the compressor expander machine, a DC converter 51 for charging a storage battery 52 and a traction motor assembly 53 for driving a vehicle axis 54 in the case of a vehicle.
  • FIGS. 9 and 10 correspond to FIGS. 2 and 3 and show an alternative form of machine which may in some cases be used. in the fuel cell system shown in FIG. 8 .
  • parts corresponding to those of FIGS. 2 and 3 have the corresponding reference numerals increased by 100. It will be noted that the large area low pressure ports 115 and 117 are adjacent the partition 114 and the small area high pressure ports 116 and 118 are at opposite ends of the machine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US10/513,289 2002-05-01 2003-04-30 Screw compressor-expander machine Abandoned US20050223734A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GB0210018A GB0210018D0 (en) 2002-05-01 2002-05-01 Plural-screw machines
GB0210018.8 2002-05-01
PCT/GB2003/001864 WO2003093649A1 (fr) 2002-05-01 2003-04-30 Compresseur-extenseur a vis

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EP (1) EP1502007A1 (fr)
AU (1) AU2003229965A1 (fr)
GB (1) GB0210018D0 (fr)
WO (1) WO2003093649A1 (fr)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060194091A1 (en) * 2005-02-28 2006-08-31 Willi Strohl Fuel cell system with a recirculating operating material
US20070137173A1 (en) * 2005-12-16 2007-06-21 Murrow Kurt D Axial flow positive displacement gas generator with combustion extending into an expansion section
US20070175202A1 (en) * 2006-02-02 2007-08-02 Murrow Kurt D Axial flow positive displacement worm compressor
US20070237642A1 (en) * 2006-04-10 2007-10-11 Murrow Kurt D Axial flow positive displacement worm pump
US20080310983A1 (en) * 2004-08-06 2008-12-18 Katsumi Sakitani Expander
US20100071458A1 (en) * 2007-06-12 2010-03-25 General Electric Company Positive displacement flow measurement device
US20100086402A1 (en) * 2008-10-07 2010-04-08 Eaton Corporation High efficiency supercharger outlet
CN102003214A (zh) * 2010-12-14 2011-04-06 范年宝 一种新型螺杆膨胀动力机
US20120090349A1 (en) * 2010-10-13 2012-04-19 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Refrigerator
CZ304109B6 (cs) * 2005-12-19 2013-10-30 Bríza@Zdenek Spalovací motor
WO2015167619A1 (fr) * 2014-04-30 2015-11-05 Edward Charles Mendler Moyen de refroidissement de compresseur de suralimentation
WO2017008037A1 (fr) * 2015-07-08 2017-01-12 Freeman Bret Moteur à turbine à cylindrée fixe

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GB0511864D0 (en) * 2005-06-10 2005-07-20 Univ City Expander lubrication in vapour power systems
CN101975094B (zh) * 2010-11-08 2012-10-17 上海维尔泰克螺杆机械有限公司 螺杆膨胀机液体泵
US8857170B2 (en) 2010-12-30 2014-10-14 Electratherm, Inc. Gas pressure reduction generator
CN102587993B (zh) * 2011-01-07 2014-02-12 江西华电电力有限责任公司 螺杆膨胀动力机转速控制方法及控制系统
JP6100652B2 (ja) * 2013-08-30 2017-03-22 株式会社神戸製鋼所 スクリュ圧縮機
GB201619656D0 (en) * 2016-11-21 2017-01-04 Rotor Design Solutions Ltd Screw rotor device

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US6616424B2 (en) * 2000-08-25 2003-09-09 General Motors Corporation Drive system and method for the operation of a fuel cell system

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US3209990A (en) * 1962-01-18 1965-10-05 Atlas Copco Ab Two stage screw rotor machines
US4291547A (en) * 1978-04-10 1981-09-29 Hughes Aircraft Company Screw compressor-expander cryogenic system
US4311021A (en) * 1978-04-10 1982-01-19 Hughes Aircraft Company Screw compressor-expander cryogenic system with mist lubrication
US4328684A (en) * 1978-04-10 1982-05-11 Hughes Aircraft Company Screw compressor-expander cryogenic system with magnetic coupling
US4609329A (en) * 1985-04-05 1986-09-02 Frick Company Micro-processor control of a movable slide stop and a movable slide valve in a helical screw rotary compressor with an enconomizer inlet port
US4791787A (en) * 1985-12-05 1988-12-20 Paul Marius A Regenerative thermal engine
US4828036A (en) * 1987-01-05 1989-05-09 Shell Oil Company Apparatus and method for pumping well fluids
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US6296461B1 (en) * 1996-05-16 2001-10-02 City University Plural screw positive displacement machines
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US6616424B2 (en) * 2000-08-25 2003-09-09 General Motors Corporation Drive system and method for the operation of a fuel cell system

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7784303B2 (en) * 2004-08-06 2010-08-31 Daikin Industries, Ltd. Expander
US20080310983A1 (en) * 2004-08-06 2008-12-18 Katsumi Sakitani Expander
US20060194091A1 (en) * 2005-02-28 2006-08-31 Willi Strohl Fuel cell system with a recirculating operating material
US20070137173A1 (en) * 2005-12-16 2007-06-21 Murrow Kurt D Axial flow positive displacement gas generator with combustion extending into an expansion section
US7530217B2 (en) 2005-12-16 2009-05-12 General Electric Company Axial flow positive displacement gas generator with combustion extending into an expansion section
CZ304109B6 (cs) * 2005-12-19 2013-10-30 Bríza@Zdenek Spalovací motor
US7726115B2 (en) 2006-02-02 2010-06-01 General Electric Company Axial flow positive displacement worm compressor
US20070175202A1 (en) * 2006-02-02 2007-08-02 Murrow Kurt D Axial flow positive displacement worm compressor
US20070237642A1 (en) * 2006-04-10 2007-10-11 Murrow Kurt D Axial flow positive displacement worm pump
US20100071458A1 (en) * 2007-06-12 2010-03-25 General Electric Company Positive displacement flow measurement device
US20100086402A1 (en) * 2008-10-07 2010-04-08 Eaton Corporation High efficiency supercharger outlet
US8096288B2 (en) 2008-10-07 2012-01-17 Eaton Corporation High efficiency supercharger outlet
US20120090349A1 (en) * 2010-10-13 2012-04-19 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Refrigerator
US8904818B2 (en) * 2010-10-13 2014-12-09 Kobe Steel, Ltd. Refrigerator
CN102003214A (zh) * 2010-12-14 2011-04-06 范年宝 一种新型螺杆膨胀动力机
WO2015167619A1 (fr) * 2014-04-30 2015-11-05 Edward Charles Mendler Moyen de refroidissement de compresseur de suralimentation
WO2017008037A1 (fr) * 2015-07-08 2017-01-12 Freeman Bret Moteur à turbine à cylindrée fixe
US10138731B2 (en) 2015-07-08 2018-11-27 Bret Freeman Fixed displacement turbine engine

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AU2003229965A1 (en) 2003-11-17
GB0210018D0 (en) 2002-06-12
WO2003093649A1 (fr) 2003-11-13
EP1502007A1 (fr) 2005-02-02

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