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WO2013078132A1 - Appareil de detente/compression monovis - Google Patents

Appareil de detente/compression monovis Download PDF

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Publication number
WO2013078132A1
WO2013078132A1 PCT/US2012/065853 US2012065853W WO2013078132A1 WO 2013078132 A1 WO2013078132 A1 WO 2013078132A1 US 2012065853 W US2012065853 W US 2012065853W WO 2013078132 A1 WO2013078132 A1 WO 2013078132A1
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WO
WIPO (PCT)
Prior art keywords
gas
main rotor
high pressure
rotor
housing
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.)
Ceased
Application number
PCT/US2012/065853
Other languages
English (en)
Inventor
Jean-Louis Picouet
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Copeland Industrial LP
Original Assignee
Vilter Manufacturing LLC
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 Vilter Manufacturing LLC filed Critical Vilter Manufacturing LLC
Publication of WO2013078132A1 publication Critical patent/WO2013078132A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F01C3/00—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members
    • F01C3/02—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees
    • F01C3/025—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • 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
    • F01C21/001—Injection of a fluid in the working chamber for sealing, cooling and lubricating

Definitions

  • the present invention relates generally to expanders and compressors, in one aspect, the present invention relates to lubrication of a sealing structure in screw compressors or screw expanders. In another aspect the present invention relates to injected or forced lubrication of or into a high pressure seal or sealing structure so as allow oil to lubricate the seal and decrease the leakage rate of the seal, as well as to lubricate one or more components of the expander or compressor.
  • Compressors are used, for example, in compression systems, such as refrigeration systems, to compress a gas, such as refrigerant gas, for -example "Freon,” ammonia, natural gas, or the like.
  • a gas such as refrigerant gas
  • refrigerant gas for -example "Freon,” ammonia, natural gas, or the like.
  • One type of compressor is a single screw gas compressor. This type of compressor employs a housing in which a motor-driven single main rotor having helical grooves thereon meshes with a pair of gate or star-shaped rotors on opposite sides of the rotor to define gas compression chambers.
  • the housing is provided with two gas suction ports (one near each gate rotor) and with two gas discharge channels (one near each gate rotor).
  • each slide valve assembly comprises a suction (also referred to as a "capacity slide valve”) arid a discharge slide valve (also referred to as a " volume slide valve”) for controlling, an associated intake channel and an associated, discharge channel, respectively.
  • a suction also referred to as a "capacity slide valve”
  • a discharge slide valve also referred to as a " volume slide valve”
  • Farmer a single screw compressor in particular provides several specific benefits over various other compressors. For example, since the dual gate rotors are situated opposite each other with respect to the main rotor, their rotational forces substantially cancel each other, thereby providing a more balanced load at the bearings that support the main, rotor.
  • the single screw compressor typically utilizes a. metallic main rotor and non-metallic gate rotors, thereby reducing the operational wear between these components and therefore reducing the overall lubrication, requirements.
  • compressors In. general, a person, of skill in. the art will recognize that at least some types of compressors, including single screw compressors, can be configured to ran in reverse so that it can operate as an expander. Still, a person of skill in the art will recognize that, in. order to accomplish such reverse operation, certain, modifications are typically be made to a given compressor.
  • a compressor generally uses a drive source to output compressed gas. in. contrast, an expander can use an input of compressed gas to operate as a drive source for another machine.
  • an apparatus that, can be configured to operate as a single screw expander, or a single screw compressor, is disclosed.
  • the apparatus includes a housing having a cylindrical bore; one or more bearing assemblies, wherein the one or more bearing assemblies are mounted, to the housing; a pair of gate rotors mounted for rotation in the housing, each having a plurality of gate rotor teeth; a main rotor rotatably mounted at least partially within the cylindrical bore, the main rotor including a plurality of grooves that meshingly engage at least one of the plurality of gear teeth from each gate rotor; a plurality of gas chambers, each of the gas chambers formed by a respective portion of one of the plurality of gate rotors, a.
  • the high, pressure sealing structure can include a conventional labyrinth seal that has been modified in accordance with embodiments of the present disclosure. Methods of using and operating the apparatus are also disclosed.
  • a method of generating power from a single screw expander comprises: flowing compressed gas .from at least one intake channel into the intake side of at least one gas expansion chamber, the gas expansion, chamber including at least a portion of a grooved main rotor and a plurality of teeth from at least one gate rotor; expanding the gas in the at least one gas expansion chamber as the gas moves from the higher pressure intake side of the gas expansion chamber to a.
  • a single screw expander comprising: a housing including a cylindrical bore; a plurality of bearing assemblies mounted to the housing; a pair of ga te ro tors mounted for rotation in the housing, each having a plurality of gate rotor teeth; a main rotor rotatably mounted at least partially in the cylindrical bore, wherein the main rotor has one or more grooves that .meshmgly engage at least one of the plurality of gate rotor gear teeth from, each of the pair of gate rotors; a pair of gas expansion chambers each at least partially created by a portion of a respective one of the pair of gate rotors, a portion of the main rotor groove, and a portion of the cylindrical bore, wherein each of the respective one of the pair of gas expansion chambers includes an intake side and a discharge side to provide, associated with each gate rotor; and a high, pressure sealing structure situated at least partially between the houstng and the bearing assemblies, and at
  • a method of operating a single screw compressor as a single screw expander comprises: flowing compressed gas into a discharge end of the compressor; expanding a higher pressure compressed gas as it passes through a gas compression chamber to a lower pressure suction end, the expansion of the gas thereby rotating a main rotor situated at least partially in the compression chamber; and injecting oil into a space between a high pressure seal and a running surface of the main, rotor via at least one channel formed or otherwise provided in a high pressure seal; and discharging the gas through the suction end.
  • FIG. I is a top view, partly in cross-section and with portions broken away, of an exemplary apparatus representative of an expander and a compressor employing a single screw rotor, a pair of gate rotors and having dual slide valves (not visible) in accordance with at least some embodiments of the present invention
  • FIG. 2 is an enlarged cross -sectional view taken along line 2-2 of FIG, 1 ;
  • FIG, 3 is a schematic v iew of the apparatus of FIG, I , particularly when the apparatus is configured to operate as an expander, and illustrating i) exemplary intake and discharge flow paths, it) exemplary intake and discharge sides, and iii) exemplary intake and discharge channels, in accordance with at least some embodiments of the present disclosure;
  • FIG. 4 is a Moliier diagram depicting a theoretical expansion process for an expander apparatus in accordance with embodiments of the present disclosure;
  • FIG. 5 shows a schematic view of a portion of the apparatus shown in FIG. 3, when the apparatus is configured to operate as an expander, and further illustrating i) exemplary- intake and discharge flow paths, and ii) exemplary intake and discharge sides, but utilizing a conventional sealing arrangement;
  • FIG. 6A shows an enlarged schematic view of a portion of the apparatus shown in FIG. 3 and similar to FIG. 5, with the apparatus again configured to operate as an expander, and illustrating a sealing arrangement in accordance with alternative embodiments of the present invention
  • FIG. 6B shows an enlarged schematic view of a portion of the apparatus shown in FIG. 3 and similar to FIG. 6a, with the apparatus configured to operate as a compressor, and illustrating the sealing arrangement, again in accordance with alternative embodiments of the present invention
  • FIG. 7 is a partially schematic cross-sectional view with portions broken sway taken along line 7-7 of FIG. 3;
  • FIG. 8 is a partially schematic cross-sectional view of a portion of a .main rotor of a conventional single screw compressor.
  • FIG. 9 is a partially schematic cross-sectional view of a portion of a main rotor of a single screw expander in accordance with alternative embodiments of the present inven tion.
  • Apparatus 10 designates an exemplary embodiment of an apparatus 10. that can be configured for use as a single screw gas compressor, or a single screw gas expander that can be used as a drive source.
  • Apparatus 10 generally comprises an housing 12, a single main rotor 14 mounted for rotation in housing 12, and a pair of gate rotors 16 and IS mounted for rotation in housing 12 and engaged with main rotor 14.
  • housing 12 includes a cylindrical bore .24 in which a main rotor 14 is rotatably mounted.
  • Bore 24 is open at its end 27 and is closed by an end wall 29.
  • the end 27 is a discharge end and. the end wall 29 is an intake end wall when the apparatus is configured to operate as an expander (and as an intake end and discharge end wall respectively, when the apparatus is configured to operate as a compressor).
  • Main rotor 14, which is generally cylindrical and has a plurality of helical grooves 25 formed therein defining gas chambers 35, is provided with a rotor shaft 26 which is rotatably supported at opposite ends on the bearing assemblies 28 mounted on housing 12.
  • the gas chambers 35 are gas expansion chambers when the apparatus is configured to operate as an expander (and are compression chambers when the apparatus is configured to operate as a compressor).
  • the apparatus .10 includes two exemplary slide valve assemblies 2.0 (one of which is shown), each of which are mounted within, or at least substantially within, housing 12, and which are positioned axial!y opposite one another, ami which cooperate with the main rotor 14 to control gas flow into and from the gas chambers 35 of the main rotor.
  • Apparatus housing 12 includes spaces 30 in which the gate rotors 16 and 18 are rotatably mounted and are located on opposite sides of, and 180 degrees apart from one another and about, the main rotor 14.
  • Each of the gate rotors 16 and 18 has a plurality of gear teeth 32 and is provided with, a gate rotor shaft 34 which is rotatably supported at opposite ends on bearing assemblies 34A and 34B (FIG. 2) mounted on housing 12.
  • Each of the gate rotors 16 and 1.8 rotate on an axis that is pei.pendku.1ar to and spaced from the axis of rotation of main rotor 14 and its teeth 32 extend through an opening 36 communicating with bore 24.
  • Each, tooth 32 of each of the gate rotors 16 and 18 successively engages a groove 25 in main rotor 14 and, in cooperation with the wall of bore 24 and specifically its end wall 29, defines one of the gas chambers 35, The aforementioned engagement allows the gate rotors 16 and 18 to drive the main rotor 14, and subsequently the rotor shaft 26.
  • the rotor shaft 26 can be coupled with another machine (not shown) to thereby provide a drive source, and thus can be configured, to operate as an output shaft or rotor output shaft.
  • Apparatus 10 further includes a high pressure seal or sealing structure 1 situated at least partially between the housing 12 and bearing assemblies 28, and at least partially between the housing 12 and the main rotor 14.
  • the high pressure sealing structure 1 can take the form of a conventional labyrinth seal modified in accordance with embodiments of the present disclosure.
  • die apparatus 10 is configured to receive compressed gas at chatutels 40 (configured as intake channels when the apparatus is configured to operate as an expander), from an outside source, such as a condenser (not shown).
  • the compressed gas travels along flow paths 42, namely intake flo w paths, passing die high pressure seal 1 , to the sides 44, of the gas chambers 35.
  • the sides 44 are intake sides and the gas chambers 35 are gas expansion chambers when the apparatus is configured to operate as an expander (and as discharge sides and compression chambers, respectively, when the apparatus is configured to operate as a compressor).
  • the compressed gas meets resistance at die sides 44 of the gas chambers 35 where the gear teeth 32 and the groove 25 are engaged.
  • the pressure at the sides 44 exceeds the pressure at sides 48 of the gas chambers 35.
  • the sides 44 are intake sides when the apparatus 10 is configured to operate as an expander (and the sides are discharge sides when the apparatus is configured to operate as a compressor).
  • the main rotor 14 and the gate rotors 16 and 18 begin to rotate to allow the compressed gas to expand in the gas chambers 35, and then released at sides 48 of the gas chambers 35.
  • the now expanded gas is relieved through channels 50 and exits the housing 12, as shown along paths 52.
  • the channels 50 are discharge channels and the paths 52 are discharge paths when the apparatus 10 is configured to operate as an expander (and as intake channels and intake paths when the apparatus is configured to opemte as an compressor).
  • the expansion of the compressed gas results in the rotation of the main rotor 14 and subsequently the rotor shaft 26.
  • the rotor shaft 26 provides a rotating output that can be coupled to the input of other machines, in this manner, the apparatus 10, when configured to operate as an expander, can be used to drive various other machines.
  • FIG, 3 illustrates the flow path of the compressed gas as it enters the apparatus 10, configured to operate as an expander, and proceeds through the channels 40.
  • the gas then proceeds into the sides 44 ( iiitake sides at high pressure) of the gas chambers 35, wherein the gas expands as it passes to the sides 48 (discharge sides at low pressure), providing a rotational motion of the main rotor 14.
  • the injected oil provides lubrication and sealing between the gear teeth 32 and the main rotor 14 during the expansion process.
  • the gas then proceeds through the discharge channels 50 to exit the expander.
  • oil injection ports 54 are situated within close proximity to the channels 40, and the high pressure seal ) . This allows the oil to be directed to a space formed by the high pressure seal 1. and the main rotor 14, which in turn lim its leakage of the gas.
  • oil injection ports 54 are located adjacent to each of the sides 44 of the gas chambers 35. To conserve the use of oil, oil that exits gas chambers 35 and flows oat of the channels, such as channels SO, and is recovered and recirculated. Further, to facilitate proper injection of oil at injection ports 54, the oil. can. be pressurized to exceed the pressure of the gas in the channels 40.
  • FIG. 4 is a Mollier diagram depicting a theoretical, expansion process for an expander.
  • Line A indicates a wet-wet condition
  • line B indicates a dry-wet condition
  • line C indicates a dry-dry condition.
  • a single screw expander in accordance with, at least some embodiments of the present invention, is capable of maintaining the compressed gas in a wet- wet condition inside the gas expansion chambers. In such cases, the expander requires less cooling than when the compressed gas is in a dry-wet or dry-dry condition,
  • FIG. 5 shows a schematic view of a portion of the apparatus shown in FIG. 3, when the apparatus is configured to operate as an expander, and further illustrating i) exemplary intake and discharge flow paths,, and ii) exemplary intake and discharge sides, but utilizing a conventional sealing arrangement.
  • FKI 6A shows an enlarged schematic view of a portion of the apparatus shown in FIG. 3 and similar to FIG. 5, with the apparatus again configured to operate as an expander, and illustrating a sealing arrangement in accordance with alternative embodiments of the present invention;
  • compressed gas flows through the portion of the apparatus 10 (FIGS. 1-3), configured, to operate as an expander (FIG, 3), and more specifically, through the channels 40 (one of which is shown) which are located opposite each one another in the apparatus 10.
  • the gas flowing in the illustrated channel 40 follows and diverges among at least two possible paths 42a and 68.
  • One of these paths is merely a portion of the path 42.
  • the other mentioned flow of gas moves through the leakage path 68 via a labyrinth space 74 that is created by a combination of a conventional labyrinth seal ⁇ , teeth l a * of the conventional labyrinth seal, and a running surface of the rotor 14a.
  • the leakage path 68 provides a pathway for leakage of compressed gas to the discharge channels 50; and thus reducing efficiency of the operation of the apparatus 10 when configured to operate as an expander.
  • Oil (or other lubricant) is injected by the oil (lubricant) injection ports 54 into the gas flowing in channel 40. It will be appreciated that oil (lubricant) would similarly be injected into the channel 40 located on the opposite side of the expander.
  • high pressure oil seating structure 1 comprises a conventional labyrinth seal but with the structure modified to include one more oil (lubricant ⁇ injection channels formed therein.
  • the high pressure seal .1 is used to seal the low-pressure side, for example, on a side adjacent to or near the channels 50 (discharge channels), from the high-pressure side, for example, on a side adjacent to or near the channels 40 (intake channels).
  • the high pressure seal 1 has many grooves and threads la and it encircles the main rotor 14 with a small gap between the grooves and threads la and the running surface of the main rotor 14.
  • the high pressure seal 1 is fixed in relation to the housing 12 and is held in place by the bearing assemblies 28.
  • the bearing assemblies 28 house bearings 55a and 55b that connect the rotor shall 26 and facilitate rotation of the main rotor 14 that rotates in between, at least partially, the high pressure seal 1.
  • the high pressure seal 1 leaks, by way of the path 68, compressed gas to the low-pressure area 50, typically by way of the channels 51, of which one is shown. Further description regarding embodiments of the high pressure seal 1 is provided with respect to FIGS. 6B and 7 and associated description which follows.
  • leakage is addressed, remedied, or is at least reduced, by injecting, and as such forcing, an amount of oil into the space 74.
  • an amount of oil or other lubricant
  • FIG. 6 A an amount of oil (or other lubricant) is injected or forced into the space 74 and such oil injection creates a film or cushion, schematically represented by arrows 76, that substantially limits the leakage depicted by flow of gas along die path 68.
  • die cushioning effect of oil 76 also lubricates the naming end of the main rotor 14a and, in so doing, serves at least in part to decrease wear to the rotor 14.
  • Another benefit cushioning effect 76 provided by the oil (or other lubricant) injection into the space by way of the lubrication injection channels 56, is a decrease in thermal shock during startup and transition periods of running the apparatus 10,
  • the apparatus during such periods and when configured to operate as an expander, permits hot (or warmer) gas to enter the apparatus and cold (or cooler) gas to be discharged from the apparatus. Since the main rotor 14 is constructed from a different materia!
  • FIG. 6B shows an enlarged schematic view of a portion of the apparatus shown in FIG. 3 and similar to FIG. 6A, with the but with apparatus 10 (FIGS. 1 and 2 ⁇ configured to operate as a single screw compressor, in which it cold (or cooler) gas typically enters the compressor and hot (or warmer) gas is typically discharged from the compressor.
  • the high pressure sealing arrangement previously described with reference to FIG. 6A is again illustrated.
  • injection of oil by way of high pressure seal i particularly by way of lubrication injection channels 56 from oil injection ports 54 and into space 74, is accomplished in a compressor, such as a single screw compressor, the same or similar ' benefit is achieved as in an expander.
  • FIG. 6B is a partially schematic cross-sectional view taken along line 7-7 of FIG.
  • oil or other lubricant is provided, as noted before, from passages 54 (FIGS. 6A and 6B) and is injected, or otherwise forced, into the oil or lubrication injection channels 56 of the seal 1 , which is shown to comprise an generally annular body that completely or at least substantially entirely encircles or surrounds the main rotor 14.
  • Channels 40 are shown for reference purposes. It is again noted that channels 40 are intake channels when the apparatus 10 (FIG .
  • FIGS. 8 and 9 depicted are cross- sectional views of a portion of a main rotor of an apparatus, such as the apparatus 10 (FIG. I ) which can comprise, by way of example, a single screw compressor or single screw expander.
  • a groove, for example, a groo ve 804, of a mam rotor 805 facilitates ' compression of gas, which follows a path 806 from a low-pressure side of the compressor to a high-pressure side of the compressor, generally referenced by numerals 807 and 808.
  • main rotor portion includes a discharge angle (when the rotor is used with an expander), indicated by angle 802, as measured from the edge or surface of the main rotor (or main rotor portion) to a main rotor axis of rotation 803.
  • the discharge angle can comprise thirty-nine (39) degrees, however, other discharge angles are contemplated.
  • a discharge angle indicated by reference numeral 902
  • the discharge angle 802 when the rotor of FIG. 8 is utilized hi an apparatus configured for use as an expander
  • a discharge portion 90S of a groove 904 is reduced, and is particularly reduced in comparison to the discharge portion 809 of FIG. 8.
  • the reduced discharge angle can comprise twenty-six (26) degrees, although again other discharge angles are contemplated, to provide an angled main rotor structure in which recompression, is substantially reduced, or eliminated.
  • the groove 904 or a shortened plurality of grooves
  • a narrower discharge angle such as the angle 902
  • potential recompression of the gas is at least substantially reduced, or possibly even eliminated, at the discharge portion 908 of the groove 904.
  • apparatuses configured to operate as expanders provide a versatile energy converter that can be powered by a multitude of heat sources and provides a rotating drive source that can power various machines.
  • a heat source that can be used to create the compressed gas is the exhaust of an electric generator. This generator exhaust may be used to heat a liquid such as ammonia in a condenser unit, thereby creating the pressurized/compressed, gas.
  • the pressure of the compressed gas can vary depending on the heat source, the size of the condensing unit, etc., a typical 240 millimeter size expander can provide enough rotational power at the rotor output shaft 26 to drive sufficiently a 300-kilowatt electric generator.
  • the rotor shaft 26, when configured to operate as an output shaft, can drive various machines that are capable of utilizing a rotational input drive source, for example, an electric generator.
  • the apparatuses configured, to operate as an expander as disclosed herein can utilize compressed gas generated from the exhaust of an electric generator to provide an output to drive another electric generator. Therefore, at least some of the wasted energy of driving one power generation source is recycled to provide the driving force for another power source.
  • an apparatus that can be configured to operate as a single screw expander, or a single screw compressor, is disclosed.
  • the apparatus includes a housing having a cylindrical bore; one or more bearing assemblies, wherein the one or more bearing assemblies are mounted to the housing; a pair of gate rotors mounted for rotation in.
  • the housing each, having a plurality of gate rotor teeth; a main rotor rotatab!y mounted at least partially within the cylindrical bore, the main rotor including a plurality of grooves ihat meshingiy engage at least one of the plurality of gear teeth from each gate rotor; a plurality of gas chambers, each of the gas chambers formed by a respective portion, of one of the plurality of gate rotors, a respective portion of one of the plurality of .main rotor grooves, and a portion of the cylindrical bore, wherein each of the plurality of gas expansion chambers; and a high pressure sealing structure situated within the housing and including at least one channel formed therein, for injecting a flow of lubricant into a space formed by at least a portion of the high pressure seal and a running surface of the .main rotor.
  • the high pressure sealing structure can include a conventional labyrinth sea! ihat has been modified in accordance with embodiments of the present disclosure.
  • the apparatus is configured to operate as one of a single screw expander or a single screw compressor.
  • the high pressure sealing structure includes an arcuate structural body thai at least partially surrounds a portion of the main rotor and includes a plurality of channels formed in the body and spaced about the body for injection of lubricant into the space at a plurality of locations, in at least some embodiments, the high pressure sealing structure is a labyrinth seal that has been modified and the space is a labyrinth space.
  • the high pressure sealing structure includes an arcuate structural body that at least partially surrounds a portion of the main rotor and includes a plurality of channels formed in the body and spaced about the body for injection of lubricant into the space at a plurality of locations, hi at least, some embodiments, the high pressure sealing structure is a labyrinth, seal that has been modified, and the space is a labyrinth space.
  • the apparatus is configured to operate as a single screw expander, and wherein, whe» so configured, at least a portion of at least one of the plurality of grooves of the main rotor is shaped to prevent gas that expands within one or more of the plurality of gas chambers from recompressing within the one or more of the plurality of gas chambers. Still furt her, in at. least s o me em bod;3 ⁇ 4 men i s , at least a portion of each of the plurality of grooves of the main rotor is shaped to prevent gas that expands within, each of the plurality of gas chambers from recompressmg within the each of the plurality of gas chambers. And in at least, some embodiments, the injecting of a flow of lubricant into the space provides lubrication of the high pressure seal without adding any lubrication into an internal expansion process taking place using, or by way of, the main, rotor.
  • a method of generating power from a single screw expander comprises; flowing compressed gas from at least one intake channel into the intake side of at least one gas expansion chamber, the gas expansion chamber including at least a portion of a grooved main rotor and a plurality of teeth from at least one gate rotor; expanding the gas in the at least one gas expansion chamber as the gas moves from the higher pressure intake side of the gas expansion chamber to a lower pressure discharge side of the gas expansion chamber, thereby rotating the at least one gate rotor and the grooved main rotor, wherein the main, rotor thereby is configured to operate as a rotational drive source; and injecting a flow of lubricant into a space formed by a surface of high pressure sealing structure and a running surface of the main rotor using a channel formed in the high pressure sealing structure, which at least partially prevents leakage of the gas.
  • the lubricant includes an amount of oil and the injecting takes place via a plurality of channels positioned in relation to, but not within, discharge areas of the expander. Further, in at least some embodiments, the method further includes discharging an expanded gas via. a discharge portion of a groove of the at least a portion of the grooved main rotor, and wherein discharge portion is shaped to prevent the expanded gas from reeompressing in the at least one gas expansion chamber.
  • a single screw expander comprising: a housing including a cylindrical bore; a plurality of bearing assemblies mounted to the housing; a pair of gate rotors mounted for rotation in the housing, each having a plurality of gate rotor teeth; a main rotor rotafably mounted at least partially in the cylindrical bore, wherein the main rotor has one or more grooves that meshmgiy engage at least one of the plurality of gate rotor gear teeth from each of the pair of gate rotors; a pair of gas expansion chambers each at least partially created by a portion of a respective one of the pair of gate rotors, a portion of the main rotor groove, and a portion of the cylindrical bore, wherein each of the respective one of the pair of gas expansion chambers includes an intake side and a discharge side to provide, associated with each gate rotor; and a high pressure sealing structure situated at least partially between the housing and the bearing assemblies, and at least partially between the housing and the main rotor
  • the one or more channels formed or otherwise provided in the high pressure seal is or are situated, adjacent to an intake side of the at least one of the gas expansion chambers.
  • the rotor shaft is configured to serve as a drive source of a machine.
  • at least a portion of each, of the plurality of grooves of the main rotor is shaped to prevent gas that expands within each of the plurality of gas chambers from rec-ompressing within the each of the plurality of gas chambers.
  • lubrication of the high pressure seal occurs without adding any lubrication into an interna! expansion process taking place using the main rotor.
  • the h igh pressure sealing structure is a labyrinth seal that has been modified and the space is a labyrinth space.
  • a method of operating a single screw compressor as a single screw expander comprises; flowing compressed gas into a discharge end of the compressor; expanding a higher pressure compressed gas as it passes through a gas compression chamber to a lower pressure suction end, the expansion of the gas thereby rotating a main rotor situated at least partially in the compression chamber; and injecting oil into a space between a high pressure seal and a running surface of the main rotor via at least one channel formed or otherwise provided in a high pressure seal; and discharging the gas through the suction end, in at least some embodiments, the injecting of oil into the space provides lubrication of the high pressure seal and such lubrication occurs without adding any lubrication into an internal expansion process taking place using, or by way of, the main rotor.
  • the present invention »ot be limited to the embodiments and IS lustrations contained herein, but include modified forms of those embodiments including portions of the embodiments and combinations of elements of different

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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Abstract

Cette invention concerne un appareil qui peut être configuré pour fonctionner comme un détendeur monovis ou comme un compresseur monovis. L'appareil comprend un carter comportant un alésage cylindrique, un ou plusieurs ensembles de roulements, une paire de rotors femelles montés pour tourner dans le carter, un rotor principal monté rotativement au moins partiellement à l'intérieur de l'alésage cylindrique, une pluralité de chambres à gaz, et une structure d'étanchéité à haute pression située à l'intérieur du carter et comprenant au moins un canal formé à l'intérieur de celui-ci pour injecter un flux de lubrifiant dans un espace formé par au moins une partie du joint d'étanchéité à haute pression et une surface de roulement du rotor principal. Selon un aspect de l'invention, la structure d'étanchéité à haute pression peut être composée d'un joint d'étanchéité à labyrinthe classique qui a été modifié conformément aux modes de réalisation de la présente invention. L'invention concerne également des procédés d'utilisation et de fonctionnement de l'appareil.
PCT/US2012/065853 2011-11-22 2012-11-19 Appareil de detente/compression monovis Ceased WO2013078132A1 (fr)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105114305A (zh) * 2015-07-16 2015-12-02 上海理工大学 一种带链式星轮的单螺杆压缩机
WO2018042197A1 (fr) * 2016-09-02 2018-03-08 Lontra Limited Dispositif de piston rotatif et cylindre
WO2018052463A1 (fr) 2016-09-16 2018-03-22 Vilter Manufacturing Llc Compresseur à vis unique à haute pression d'aspiration avec charge d'équilibrage de poussée utilisant une pression de joint d'arbre et procédés associés
RU2675639C2 (ru) * 2017-02-14 2018-12-21 Евгений Михайлович Пузырёв Роторно-винтовая машина
WO2024207125A1 (fr) 2023-04-03 2024-10-10 Green-Y Energy Ag Système à vis unique bidirectionnel et procédé de compression et d'expansion d'un gaz

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US6685191B2 (en) * 2000-02-11 2004-02-03 A. W. Chesterton Company Mechanical seal for rotating shaft
JP2004162540A (ja) * 2002-11-11 2004-06-10 Kobe Steel Ltd スクリュ圧縮機
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Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105114305A (zh) * 2015-07-16 2015-12-02 上海理工大学 一种带链式星轮的单螺杆压缩机
WO2018042197A1 (fr) * 2016-09-02 2018-03-08 Lontra Limited Dispositif de piston rotatif et cylindre
CN109906308A (zh) * 2016-09-02 2019-06-18 隆特拉有限责任公司 旋转活塞和缸体装置
CN109906308B (zh) * 2016-09-02 2021-05-25 隆特拉有限责任公司 旋转活塞和缸体装置
WO2018052463A1 (fr) 2016-09-16 2018-03-22 Vilter Manufacturing Llc Compresseur à vis unique à haute pression d'aspiration avec charge d'équilibrage de poussée utilisant une pression de joint d'arbre et procédés associés
CN109690087A (zh) * 2016-09-16 2019-04-26 维特制造有限公司 具有利用轴密封压力推力平衡负载的高吸入压力单螺杆式压缩机及相关方法
US11136978B2 (en) 2016-09-16 2021-10-05 Vilter Manufacturing Llc High suction pressure single screw compressor with thrust balancing load using shaft seal pressure and related methods
US11530702B2 (en) 2016-09-16 2022-12-20 Vilter Manufacturing Llc High suction pressure single screw compressor with thrust balancing load using shaft seal pressure and related methods
RU2675639C2 (ru) * 2017-02-14 2018-12-21 Евгений Михайлович Пузырёв Роторно-винтовая машина
WO2024207125A1 (fr) 2023-04-03 2024-10-10 Green-Y Energy Ag Système à vis unique bidirectionnel et procédé de compression et d'expansion d'un gaz

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