CN101680459A - Compression method and means - Google Patents
Compression method and means Download PDFInfo
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- CN101680459A CN101680459A CN200880018688A CN200880018688A CN101680459A CN 101680459 A CN101680459 A CN 101680459A CN 200880018688 A CN200880018688 A CN 200880018688A CN 200880018688 A CN200880018688 A CN 200880018688A CN 101680459 A CN101680459 A CN 101680459A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D23/00—Other rotary non-positive-displacement pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D21/00—Pump involving supersonic speed of pumped fluids
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- Structures Of Non-Positive Displacement Pumps (AREA)
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Abstract
The invention is a compression method having characteristics of smooth compression and internal cooling of the gas. Embodiments of the invention employ a cylindrical chamber and an orbiting rotor to create a moving duct or chamber whose walls converge, relative to a static gas packet drawn into the moving duct, at a 'pinch point'. Preferably the closing speed of the walls is subsonic and the speedof the pinch point is supersonic. This enables high pressure to co-exist, at the narrowing end of the duct, with low pressure elsewhere in the duct, because of the pressure information barrier produced by the supersonic advance of the pinch point. The invention also discloses means for adjusting the running clearance between the cylinder and the rotor, and means for counterbalancing the rotor.
Description
The application relates to the suction and the compression field of gas.
Background of invention
The gas compressing equipment that is used in refrigeration, air conditioning and the industry consumes the electric energy that most produces.The increase of gas pumping efficient (gas pumping efficiency) will cause the minimizing of CO2 emission.Depend on the proposal of the pressure isolation carbon dioxide of underground or ocean depth and to use following compression method, this compression method effectively and can also overcome for example phase transformation and the material corrosion problem of compressor components when compressing impure gaseous mixture.Whether the little variation of compressor efficiency can determine carbon to isolate in viable commercial.
Effectively compression requires the least possible kinetic energy to be applied to gas molecule.This hint gas bag (gaspacket) should move through compressor as far as possible lentamente, and does not have unexpected acceleration.Travel direction should be preferably straight line.Should there be possibility to cause forming the volume sudden change of vibration at high speed.Because gas noise is initiated by the kinetic energy of gas, therefore, smoothly and lightly compressor for compressing will be quiet at work.
The heat of compression that is diffused into the gas of less compression in inlet gas or the pressing chamber by leakage or transmission of heat backward is the reason that the compressor poor efficiency requires extra acting energy, and extra acting energy equals to enter before the compressor and the heat of any increase that the gas in compressor obtains.Some heats of compression flow in the wall of compressor.Because can not enough promptly remove this heat, thus wall to keep being hot, heat remains in the gas, and the merit that needs increases.Therefore expectation when compression and heated air, should be removed the heat of compression of some or all at gas motion during by compressor from gas.By convention, this finishes by the cooling compressor wall or by water filling.Yet in piston and cylinder compressors, gas is compressed in the volume that is limited by the constant surface of still reducing gradually, therefore, during process, may well not remove the heat of compression.What raise is high more, and loss in efficiency is big more.
The compressor of known type is typically trended towards the problem that lowers efficiency, this problem include but not limited to described herein these, just:
● a large amount of kinetic energy are applied to are compressed gas
● the unexpected acceleration of gas causes high noise levels and energy loss
● high gas flow rate causes being compressed the frictional heat of gas, causes increasing the acting demand
● the heat of compression feeds back to air inlet, causes increasing the acting demand
● variable inner surface area causes removing the reduction of the ability of the heat of compression from being compressed gas
● the high friction velocity between the inner member causes wearing and tearing and frictional loss
● low interstage compression (low inter-stage compression) is risen
● with respect to the big physical size of gas treatment speed
The invention summary
The present invention states in the claims.
In an embodiment of the invention, provide a kind of compressor that comprises cylinder and rotor, thus, rotor moves back and forth on the inner circumference of cylinder, and folder point (pinch point) forms at the some place of close cylinder inner wall in rotor periphery.Rotor moves back and forth on the inner circumference of cylinder, makes preferably, to move folder point high-speed motion with ultrasonic speed.In one embodiment, rotor rolls on the inner circumference of cylinder, makes rotor surface low or be zero with respect to the speed of cylinder wall, has therefore reduced parts and has been compressed the wearing and tearing or the frictional heat of gas, here be called " (rolling) rolls ", therefore help to improve compressor efficiency.Alternatively, the bar control valve unit on the rotor surface (strip valvearrangement) allows gas to enter in the chamber that forms between rotor and the cylinder.Alternatively, bar control valve unit on the cylinder wall allows gas to leave from the chamber, and alternatively, comprises that actuator (actuationmeans) controls its open position.
In another embodiment of the present invention, a kind of compressor that comprises cylinder and rotor is provided, thus, rotor moves back and forth on the inner circumference of cylinder, and folder point forms at the some place of close cylinder inner wall in rotor periphery.Rotor motion makes and folder point high-speed motion preferably, moves with ultrasonic speed.Rotor rotates on the inner circumference of cylinder, makes that the immovable point on the rotor periphery keeps being called " rotation (rotating) " here near the folder point.Alternatively, epitrochanterian import and export (port) allow gas to enter and leave via the path that is communicated with the axial end portion of cylinder.
In another embodiment, rotor around orbital motion, makes not rotation of rotor self to be called " orbital motion (orbiting) " here on cylinder.
Embodiments of the present invention comprise and are used to allow the pressurized gas inlet chamber and are used to allow pressurized gas to leave the control valve unit of chamber.
Embodiments of the present invention comprise the device of the running clearance between the inner circumference that is used to adjust rotor surface and cylinder.
Embodiments of the present invention comprise the device of the gyrating mass balance of the rotating part that is used to make rotor and is associated.This Equilibrator is adjustable alternatively.
In order to increase the efficient of compressor, embodiments of the present invention comprise rotor surface feature (rotorsurface feature).
Referring now to accompanying drawing, via example embodiments of the present invention are described, accompanying drawing is as follows:
The schematic representation of Fig. 1-compressor case and rotor
Fig. 2 a is to 2g-" rolling " rotor operation
Fig. 3 a is to 3g-" orbital motion " rotor operation
Fig. 4 a is to 4g-" rotation " rotor operation
Fig. 5-bar control valve unit
Fig. 6-rotor entrance device
Fig. 7-rotor surface feature
Fig. 8-helical pipe mode of execution
Fig. 9-balancing rotor/drive unit
Figure 10-bar valve and Equilibrator
Figure 11-bar valve actuating apparatus
Describe in detail
As shown in Figure 1, the invention provides a kind of compression method with desired characteristic of smooth compression and inner cooled gas.This method is used cylinder chamber (cylindrical chamber) (10) and rotor or orbiter (20), to generate motion tubes or chamber (40) of geometrical shape and size constancy, the wall of this motion tubes or chamber (40) is assembled with respect to the gas at rest bag that is drawn onto motion tubes (40) lining.The wall of pipeline (40) is to assemble along the slow speed of pipeline (40) motion than the point of close wall (hereinafter being called folder point (50)).In preferred operations, the closing speed of wall is a subsonic speed, and the speed of folder point (50) is supersonic speed.Along with folder point the advancing of (50), wherein the gas volume that is in maximum pressure/temperature also advances to the zone since the wall that has been cooled near high-temperature gas at last.When the operation of such compressor is: when folder point (50) move with supersonic speed, the information of the pressure rising that causes about narrowing down of pipeline (40) can not be propagated forward and promote gas forward.Because volume is pressed from both sides pressure information barrier (40) physical separation that the supersonic speed of point (50) and folder point (50) is advanced and made, this can coexist high pressure in the narrow end of pipeline (40) and the low pressure in pipeline (40) other places, lining.This provides a kind of compressor of the high pressure ratio ability with positive displacement compressor that flows out in conjunction with the level and smooth pulsating movement free of centrifugal and shaft type machine.
The pipeline (40) that generates between the inner circumference by using cylinder (10) and the wall (20) of shaping, the present invention can realize by various mode of executions, the wall (20) that is shaped is in the motion of cylinder (10) lining, so that locate to form the pipeline (40) that narrows down at the point (50) of the most close two members.
Three mode of executions of explanation rotor (20) in the variation of the motion of cylinder (10) lining will be described now.
, as use in the first kind mode of execution that is described below to shown in the 2g as Fig. 2 a, along with rotor (20) moves back and forth on the inner circumference of cylinder (10), " rolling " rotor (20) rolls on the inner circumference of cylinder (10).The orientation of rotor (20) is shown by corresponding arrow A, B and C among Fig. 2 a.Six order examples that Fig. 2 b shows in the 2g have continuously illustrated (seeing the arrow A among each figure), and along with rotor (20) rolls on the inner circumference of cylinder (10), how the orientation of rotor (20) changes with respect to cylinder (10).Rotor changes the orientation along with its rolling, make that rotor (20) surface in fact will be low with respect to the speed on the surface of the inner circumference of cylinder (10) or be zero.Rotor (20) can be arranged to contact in fact the internal surface of cylinder (10) or two surfaces can be separated a little and separated.Rotor (20) can be arranged to rely on the internal surface of contact cylinder (10) to roll, and maybe can pass through for example other devices of gear, or rotate by being compressed gas induced.This feature causes between the internal surface of the surface of rotor (20) and cylinder (10) low in fact or be zero friction velocity, and this causes the improved wear-resisting property on these surfaces again.Other results of this feature are lower frictional losses, are applied to the low kinetic energy that is compressed gas (low inducing) and are applied to the lower frictional heat that is compressed gas.These results have contribution to the bigger efficient of compressor.
, as use in the first kind mode of execution that is described below to shown in the 3g as Fig. 3 a, along with rotor (20) moves back and forth on the inner circumference of cylinder (10), the rotor of orbital motion (20) does not change the orientation with respect to cylinder (10).Fig. 3 a has shown the corresponding orientation that position 20a, 20b, 20c and arrow A, B, C in turn represents.Fig. 3 b has shown rotor-position in turn and corresponding orientation A to 3g.The rotor of orbital motion (20) causes rolling rotor (20) big of the relative velocity ratio Fig. 2 between the internal surface of the surface of rotor (20) and cylinder (10), but the relative velocity of the rotor of describing in the paragraph below than the general (20) is little.Therefore, when using the rotor (20) of orbital motion, loss in efficiency trends towards in the scope between the loss in efficiency of the loss in efficiency of rolling rotor (20) and rotor (20).
As Fig. 4 a to shown in the 4g, as use in the first kind mode of execution that is described below or the second class mode of execution, along with rotor (20) moves back and forth on the inner circumference of cylinder (10), rotor (20) changes the orientation, makes sequential position 20a, 20b in Fig. 4 a of the lip-deep immovable point A of rotor (20), B, C, 20c near folder point (50) by this way.The motion of point A can be seen in the sequential position that Fig. 4 b shows in the 4g.Rotor (20) causes orbital motion rotor (20) big of the rolling rotor (20) of the relative velocity ratio Fig. 2 between the internal surface of the surface of rotor (20) and cylinder (10) or Fig. 3.Therefore, when using rotor (20), loss in efficiency trends towards in the loss in efficiency scope of the orbital motion rotor (20) that is higher than the rolling rotor of Fig. 2 (20) or Fig. 3.The advantage of the rotor of Fig. 4 (20) is actually to use the valve bigger than other rotors of two types (20) to arrange scope.Can use than the compressor that comprises other rotors of two types moving parts still less, make the compressor that comprises rotor (20).
As shown in Figure 5, in the mode of execution of the first kind, pipeline (40) is the chamber that forms between two cylinders, and in two cylinders, one (10) are static relatively and take on stator, and another (20) take on rotor, rolling in stator, orbital motion or rotation.Use valve system described below, gas is by sparse pipeline (40) lining (just, when rotor near the opposite side of stator time) that is drawn onto that causes by an end of widening pipeline (40).Inlet in the wall of its process arbitrary cylinder (10,20) or end wall, and after the compression that narrows down relatively of the pipeline (40) that has caused near stator wall by the parts (20) by orbital motion, discharge with higher pressure at the other end of pipeline.By blade, the precompression that can acquire a certain degree being installed in rotor (20) the inside.In such mode of execution, rotor (20) can have rolling or surface of revolution maybe can not rotate and orbital motion.
In the equipment that the mode of execution of the such first kind of a kind of basis is set up, shown in Fig. 5 and 10, be provided with drum type rotor (cylindrical rotor) (20) in cylinder (10) lining.Rotor (20) is provided with surface channel (surface channel) (210), and its degree of depth equals to be installed in the thickness of the bar (220) of passage (210) lining.The circumference of bar (220) makes that greater than the circumference of rotor (20) it forms gas tight seal when bar (220) is pressed against on the rotor (20).Yet, because the circumference of bar (220) is greater than the circumference of rotor portion (20), so bar (220) will always be given prominence on the circumference on rotor (20) surface, since apply thereon extruding force and away from maximal end point, thereby allow the opening (230) of gas stream, flow to rotor (20) outside through passage (210) bottom.
Cylinder (10) is provided with passage (240) and the bar (250) that is positioned at the outside similarly, thereby allows gas to be positioned at the tube equipment in the outside from the internal delivery of cylinder (10).This goes out its width of pig's tongue (250) and is provided with girth member, to support its antagonism highpressure.
In operation, rotor (20) preferably with cause folder point (50) between rotor (20) and the cylinder (10) with the speed of supersonic speed rotation around orbital motion.Along with the rotation of folder point (50), low pressure is followed pressing from both sides point (50) (according to the direction of rotation) afterwards, and bar valve (220) is pulled away from rotor (20) and constantly induces gas inlet chamber (40) lining.The other end of (40) in the chamber, the gas of inducing before the compression of the convergence surface of rotor (20) and cylinder (10) also impels it to leave chamber (40) by going out pig's tongue (250), and this goes out the pressure that pig's tongue (250) pressed from both sides the gas of point (50) front and forces and remain on open position.Enter the low pressure volume in order to prevent out the overlapping folder point of pig's tongue (250) (50) and to allow gas to break away from high pressure volume, going out pig's tongue (250) can activate by mechanical, electric or magnetic device, to control the distance of its opening (270) apart from folder point (50).As shown in figure 11, cam (261) the operation push rod (260) on the live axle (660), push rod (260) moves to be lifted out pig's tongue (250).This activates for control beginning and closed condition also useful, and has provided volume controlled to a certain degree.In the mode of execution of rotation or rotor (face as follows), the high-pressure outlet side of wherein pressing from both sides point (50) can be by some distances of distance low-pressure inlet side separately, by motion opening (270) part through folder point (50), the actuating of bar (250) can be used to the restrict export zone and the therefore pressure ratio of control apparatus.Therefore, in one embodiment, bar can particularly by actuator, for example be connected to rotor, for example the cam of rotor drive shaft and push rod by mechanically actuated distortion.
As shown in Figure 6, in rotor, be provided with blind path (blind passage) (275) or path, stop at the axial vane surface opening and in inside near rotor surface.This path (275) communicates with the axial vane surface of rotor (20), makes that cooling liquid can be in the circulation of the circumferential surface back of rotor (20).For the circulation of cooling liquid, the wall and the end plate of chamber (10) additionally are provided with path.Can be provided with the device (finned means) (276) of radiating fin, flow to heat in the cooling liquid to increase from the wall of the chamber (10) that will cool off.
In operation, rotor (20) and entry conductor (330) guiding rotation make pipeline (40) and rotor with the preferred speed rotation that surpasses the local velocity of sound.The suitable curvature of entry conductor (330) path causes that gas is drawn onto conduit (330) lining with radial direction in fact from the axial vane surface of rotor (20).Along with the space between pipeline (40)-just rotor and the stator-rotate around stator, gas is by the convergence pipeline (40) that forms between the wall of the surface of the rotor of being kept in detention (20) and cylinder (10).Supersonic speed near folder point (50) does not provide the time of propagating about the information upstream of boost pressure.Along with folder point (50) arrives gas, gas is steadily compressed, up to its be allowed to high pressure by outlet (340) radial extremity that breaks away from rotor (20) of the path by rotor (20) lining also, it leaves equipment by line transportation therefrom.Between the compression period of pipeline (40), gas temperature increases.The heat of compression constantly shifts, and the wall by rotor (20) enters in wall back circuit cooling liquid and the wall by chamber (10) and enters circuit cooling liquid (277) there.
As shown in Figure 7, the surface of rotor (20) can be provided with helical groove (400) and/or path (410), turns back to the point (420) that pipeline (40) lining is selected or control with guiding by folder point (50) or along the pressurized gas of the axial end of chamber.This gas is cooled on the path of its return chamber, and this entry end of (330) returns more favourable to the efficient of equipment in the chamber than allowing it.In complex device, emit this gas to promote that laminar flow is possible by the micro pores in the rotor surface (430).
In the second class mode of execution, equipment can comprise rotor (20), assemble simultaneously between the surface that pipeline (40) is formed on the wall of cylinder (10) and rotor (20) (as shown in Figure 6), or converging duct (40) can be formed between the wall of cylinder (10) and the passage that reduces cross section (330) on the rotor (20) and forms its rotor and stator concentric (as shown in Figure 8).
For example with reference to figure 7 and 8, because the objective of the invention is to avoid accelerating gas, therefore, for the given cross section of pipeline (40), static ratio with motion tubes (40) surface should be high as much as possible very important.Use in passage (330) mode of execution in rotor (20) lining, pipeline (40) can be formed by groove (580), the circumferential surface of son (20) rotates under this groove (580) screw, make all parts of pipeline (40), the high pressure/high temperature end that comprises pipeline (40) constantly is exposed to new surface area, with from pipeline (40) heat conduction.In such mode of execution, the heat that upwards is delivered to the stationary wall of cylinder (10) can be reduced by the flange of surperficial (see figure 6) back (350).Rotor (20) can be further by internal liquid cooling along the side flow of the side of pipeline (40) and rotor (20).
As shown in Figure 8, the second class mode of execution uses rotor (20).In a kind of like this equipment, in cylinder (10) lining rotor (20) is set, the profile of rotor (20) is configured such that when it moves back and forth on inwall, and the part in fact of the circumferential surface of rotor (20) keeps rotatably closely the inwall near cylinder (10).The residue circumferential surface of rotor (20) is shaped or cuts away, so that generate the pipeline or the groove (40) of the narrow end (530) between the wall that has itself and cylinder (10).The end of the broad of pipeline (540) is provided with the entry conductor (520) of the core of the axial vane surface that is communicated with rotor (20).Separate with pipeline (40), the circumferential surface of rotor (20) is provided with the delivery channel (550) of another part of the axial vane surface that is communicated with rotor (20).In main equipment, be provided with a more than shaped pipe (40).
In the mode of execution of helical pipe (500), output pressure ratio can be by providing quill (510) to control between rotor (20) and cylinder (10).In operation, gas access (520) pass through another by an axial end of chamber (40) and export (550).Therefore will change discharge area with respect to rotor (20) axial motion sleeve (510), and change and the pressure ratio of control apparatus.
Above arbitrary mode of execution can be provided with adjusts rotor (20) and the biasing that comprises the central shaft of cylinder (10), and therefore is adjusted at the device that folder point (50) is located the gap between rotor (20) and the cylinder (10).This adjusts, reduces for wear compensation, at different rates of thermal expansion and leaks and the control capacity is favourable.
As shown in Figure 9, a kind of driven unit that is used for has been described here, and additionally adjust rotor (20) and comprise cylinder (10) central shaft biasing and therefore be adjusted at the device that folder point (50) is located the gap between rotor (20) and the cylinder (10).Generally speaking, rotor (20) has rotor shaft (670), every end of rotor shaft (670) is connected respectively to and drives rotor support and idler rotor support (idlerrotor support) (680,690), each that drives in rotor support and the idler rotor support (680,690) is connected respectively to live axle and idler shaft (idler axis) (660,650) again, live axle and idler shaft (660,650) are arranged such that they are positioned on the central shaft of cylinder (10), and each is all supported by bearing support (630).
More specifically, an end of rotor shaft (670) is connected to by shaft coupling (600) and drives rotor support (680), and the other end of rotor shaft (670) is connected to idler rotor support (690) by shaft coupling (600).Idler rotor support (690) is connected to stationary axle (650) by shaft coupling (600).Drive rotor support (680) and be connected to live axle (660) by shaft coupling (600).Live axle (660) and idler shaft (650) are arranged to be parallel to rotor shaft (670) and are positioned on the central shaft of cylinder (10).Each rotor support (680,690) is arranged to support rotor axle (670), makes the surface of rotor (20) in fact near the inner circumference of cylinder (10).Idler shaft (650) and live axle (660) are all supported by bearing support (630), and can rotate therein, and with respect to described bearing support (630) axial constraint.Each bearing support (630) is arranged such that the axial distance of itself and rotor shaft (670) equals the axial distance of other bearing supports (630) and rotor shaft (670), and can control.The distance at the center by Control Shaft bearing and rotor shaft (670), the position and the angle that change each rotor support (680,690) are possible, the running clearance that the result changes between rotor (20) and the casing (10) is possible.
In aforesaid device, can advantageously use three class shaft couplings (600).First kind shaft coupling (600) comprises the shaft coupling that is suitable for forming node, two axles between hinged two rotatingshafts of this node, but can not transmit any axial moment of torsion.The example that drops on the general known shaft coupling (600) in the first kind is a ball node.The second class shaft coupling (600) comprises the shaft coupling that is suitable for forming node, two axles between hinged two rotatingshafts of this node, and can transmission axle to moment of torsion.The example that drops on the general known shaft coupling (600) in second class is the rubber coupling of constant speed node, Hardy-Spicer universal joint, some type or the rubber pipe of compliance (compliant rubber tubing).The 3rd class shaft coupling comprises the shaft coupling that is suitable for forming node, this node can a hinged axle and can transmission axle to moment of torsion.The example of this node is a hinged joint.
Live axle (660) can be via driving shaft coupling (640) transmission rotation torque.Live axle (660) is connected to by the 3rd class shaft coupling (600) and drives rotor support (680).Driving rotor support (680) terminal that is connected to rotor shaft (670) therefore is constrained to around the axle of traction rotatingshaft (660) the mode orbital motion with circular movement.
In the mode of execution that uses rolling rotor, drive rotor support (680) and be connected to rotor shaft (670) by first kind shaft coupling (600).Rotor shaft (670) is connected to idler rotor support (690) by the first kind or the second class shaft coupling.In this embodiment, rotor shaft (670) is connected to the shaft coupling (600) of idler rotor support (690) and idler rotor support (690) is connected in the shaft coupling (600) of idler shaft (650) at least one be first kind shaft coupling, and/or idler shaft (650) rotates freely.Thereby rotor (20) freely rolls, and be independent of the orientation of live axle (640) and the orientation of idler shaft (650), but rotor (20) forces the inner circumference at cylinder (10) to move back and forth by be transferred to driving rotor support (680) driving force from live axle (640).
, in the mode of execution of the rotor of orbital motion, drive rotor support (680) and be connected to rotor shaft (670) in use by first kind shaft coupling (600).In this embodiment, rotor shaft (670) is connected to the shaft coupling (600) of idler rotor support (690) and all is second class shaft coupling (600) that idler rotor support (690) is connected to idler shaft (650), and idler shaft (650) is fixed, and makes it not rotate.Therefore retrain rotor (20), keep its orientation with respect to cylinder (10) so that rely on it to be connected to fixed idler axle (650).Rotor (20) forces the inner circumference at cylinder (10) to move back and forth by be transferred to the driving force that drives rotor support (680) from live axle (640).
In the mode of execution that uses rotor, drive rotor support (680) and be connected to rotor shaft (670) by second class or the 3rd class shaft coupling (600).Rotor shaft (670) is connected to idler rotor support (690) by the first kind or the second class shaft coupling.In this embodiment, rotor shaft (670) is connected to the shaft coupling (600) of idler rotor support (690) and idler rotor support (690) is connected in the shaft coupling (600) of idler shaft (650) at least one be the first kind, and/or idler shaft (650) rotates freely.Therefore retrain rotor (20) keeping it with respect to the orientation that drives rotor support (680), and unfettered with respect to the orientation of idler rotor support (690), the result, the lip-deep immovable point of rotor (20) is kept near folder point (50).Rotor (20) forces the inner circumference at cylinder (10) to move back and forth by be transferred to the driving force that drives rotor support (680) from live axle (640).
Though here with reference to the clearly combination of the shaft coupling that uses above-mentioned classification rolling has been described, around the restraint device of orbital motion and rotor, should be understood that rotor characteristics described herein can finish by other combinations of not describing.Therefore, described hereinly do not wish to be limited to scope of the present invention around orbital motion, fixing description with restraint device rotor, the present invention states in the claims.
As shown in Figure 9, provide a kind of device that is used to make rotor (20) balance.Driving rotor support (680) extends beyond on the direction away from rotor (20) driving the shaft coupling (600) that rotor support (680) is connected to live axle (660).Provide weight equalizer (620) integratedly individually or with the extension that drives rotor support (680).Similarly, idler rotor support (690) extends beyond the shaft coupling (600) that an idler rotor support (690) is connected to idler shaft (650) on the direction away from rotor (20).Provide weight equalizer (620) integratedly individually or with the extension of idler rotor support (690).Each weight equalizer (620) is arranged to have weight and apart from the distance of the central shaft of cylinder (10), makes the weight of the rotary component on the opposition side of central shaft of cylinder (10) be able to balance.Can adjust the quality and the position of weight equalizer (620) at the duration of work of compressor, with compensate for heat expansion or may otherwise upset other influences of balance of the rotary component of compressor.This can reach by the position of using actuator to adjust the weight equalizer (620) on the rotor support (680,690).Alternatively, can, for example, change the quality of weight equalizer (620) by fluid or gas pump being advanced or pumping the weight equalizer (620) that can comprise liquid container or gas holder.
Figure 10 has shown the option means that is used to make rotor (20) balance, and wherein live axle (660), rotor shaft (670) and weight equalizer (620) are included in cylinder (10) lining, are favourable like this, because help the chamber sealing.
Though in all situations, describe the mode that seals and pass through the various chambers of line transportation in detail, it should be understood that, in embodiments of the present invention, provide the common sliding seal of compressor field to prevent that gas from leaking into the low pressure volume from high pressure volume.The tube equipment of the equipment that leaves with pressurized gas in the guiding low-pressure gas access arrangement also is provided.
In above arbitrary mode of execution, the conventional control gear of related domain, for example valve can be used in combination with control and adjusting flow.
Though used static cylinder (10) and movable rotor (20) to describe mode of execution, other mode of executions can use motion cylinder (10) and static rotor (20) or be the rotor (20) and the cylinder (10) of motion.
The compressor that makes up according to the present invention can be reverse, is expander with suitable valve work.
Advantage of the present invention is a high efficiency of compression, and when giving a small amount of kinetic energy of gas and friction energy, reaches high-stage pressure by pressurized gas and rise.The present invention also allows at the compressed while cooled gas of gas.
In shaft type and centrifugal compressor, the multistage necessity that can use the low pressure in per stage to rise to cause provide between the stage in the middle of cooling.For efficient compression, all surface that centers on gas can be cooled, and gas and/or constantly change of surface, makes that gas is brought to the new cooling surface of contact between compression period.Preferably, gas should not flow with respect to wall, because cause frictional heat like this.
The present invention has several advantages on the prior art compressor.These advantages comprise:
By using the supersonic speed rotation of folder point, make simple and mechanical layout of the present invention become possibility, because high pressure can not propagate into the area of low pressure of chamber, so do not need mechanical separation between the area of low pressure of chamber and the high-pressure area.
Continuous rotary compressing device of the present invention allows level and smooth continuous compression.By using level and smooth and continuous compression set, the present invention has advantageously reduced the energy that is compressed gas.
By using adjustable running clearance device, and/or, reduced frictional loss on the inner circumference of cylinder, reduced the heating that is compressed gas like this and therefore increased efficient along with it moves back and forth and the rotor that rolls.
Fixing chamber volume of the present invention allows the heat transfer properties of enhancing, is compressed gas because maximum chamber surface area always contacts.This allows more effectively to cool off and is compressed gas, and this helps to improve the efficient of compressor again.
The gas flow of handling in each rotation is greater than the volume of the internal capacity of cylinder chamber and the volume of rotor.Swept volume is the volume of cylinder, less than the volume of rotor, its radius equals: { radius of rotor deducts the radial offset of rotor shaft and cylinder axis }.In other words, rotor surface with the folder spot diameter on opposed scanpath (sweep path) definition swept volume.
Compare with the shaft type or the centrifugal compressor of for example similar physical size, additional advantage of the present invention is that it has represented high flow properties.As a result, compression function of the present invention is made the volume less than known compressor.
Though explained the present invention, do not wished to limit the present invention about its preferred implementation.It will be understood by those skilled in the art that many other change and variations are possible and do not deviate from the scope of the present invention of requirement.The feature of mode of execution and mode of execution can be taken the circumstances into consideration and put or exchange mutually.
Claims (20)
1. gas compressor, it has rotor and stator, and one of them has and is used for carrying out the relative internal surface that moves back and forth with the closure that forms the folder point at hithermost some place with respect to another, and described gas compressor has the pressurized gas outlet.
2. gas compressor according to claim 1, wherein, described folder point is arranged to ultrasonic in fact speed motion.
3. gas compressor according to claim 1 and 2, wherein, in use, the lip-deep immovable point of described rotor remains on described folder point place in fact.
4. gas compressor according to claim 1 and 2, wherein, in use, the orientation of described rotor is constant with respect to cylinder in fact.
5. gas compressor according to claim 1 and 2, wherein, in use, described rotor rolls on the surface of described stator, makes the do not rub surface of described stator, the surface of described rotor.
6. according to the described gas compressor of arbitrary aforementioned claim, wherein, described rotor and/or stator comprise coolant path.
7. according to the described gas compressor of arbitrary aforementioned claim, wherein, described rotor and/or stator comprise cold sink.
8. according to the described gas compressor of arbitrary aforementioned claim, wherein, described rotor comprises described outlet.
9. according to the described gas compressor of arbitrary aforementioned claim, wherein, described outlet is in the upstream that is positioned at described rotor or stator on the direction that moves back and forth of described folder point.
10. according to the described gas compressor of arbitrary aforementioned claim, wherein, described stator comprises described outlet.
11. according to the described gas compressor of arbitrary aforementioned claim, wherein, described rotor comprises in the downstream that moves back and forth direction of described folder point and is used for the not inlet of pressurized gas.
12. according to the described gas compressor of arbitrary aforementioned claim, wherein, at least one in gas access and the gas outlet comprise in described stator and the rotor at least one move back and forth lip-deep aperture.
13. according to the described gas compressor of arbitrary aforementioned claim, wherein, at least one in gas access and the gas outlet comprises the circumferential strap of deformable away from described aperture, to allow the gas stream mistake.
14. according to the described gas compressor of arbitrary aforementioned claim, wherein, at least one in gas access and the gas outlet comprises the pipeline tapping on the circumferential surface that is positioned at described rotor.
15. according to the described gas compressor of arbitrary aforementioned claim, wherein, described rotor be supported for permission at described folder point place changeably near described stator.
16. control valve unit, it comprises main body, and described main body has outer wall casing, valve orifice and deformable circumferential strap, and described deformable circumferential strap is arranged on the described casing, so that closed described aperture under deformation-free state, and deformable comes said ports to allow gas flow.
17. the method for a pressurized gas, it comprises: cause that rotor relative to each other carries out relative moving back and forth with closed inner stator face, form the folder point with the tightst approaching some place betwixt, wherein, described folder point moves with ultrasonic in fact speed.
18. method as claimed in claim 17, wherein, described rotor be supported for permission at described folder point place changeably near described stator.
19. a gas compressor, it has first element and second element, and wherein at least one can carry out relative rotatablely moving with respect to another, and to form the folder point, described folder point is arranged at the tightst close some place pressurized gas.
20. one kind is installed or method, it is in fact as being described in the drawings here.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB0706637.6 | 2007-04-04 | ||
| GBGB0706637.6A GB0706637D0 (en) | 2007-04-04 | 2007-04-04 | Compression method and means |
| PCT/GB2008/001193 WO2008122781A1 (en) | 2007-04-04 | 2008-04-03 | Compression method and means |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101680459A true CN101680459A (en) | 2010-03-24 |
Family
ID=38090898
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200880018688A Pending CN101680459A (en) | 2007-04-04 | 2008-04-03 | Compression method and means |
Country Status (12)
| Country | Link |
|---|---|
| US (1) | US20100129192A1 (en) |
| EP (1) | EP2150703A1 (en) |
| JP (1) | JP2010523881A (en) |
| KR (1) | KR20100015695A (en) |
| CN (1) | CN101680459A (en) |
| AU (1) | AU2008235279A1 (en) |
| BR (1) | BRPI0809182A2 (en) |
| CA (1) | CA2682672A1 (en) |
| GB (1) | GB0706637D0 (en) |
| MX (1) | MX2009010530A (en) |
| RU (1) | RU2009137471A (en) |
| WO (1) | WO2008122781A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103620226A (en) * | 2011-05-27 | 2014-03-05 | 通用电气公司 | Supersonic compressor startup support system |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB0902792D0 (en) | 2009-02-20 | 2009-04-08 | Hammerbeck John P R | Variable flow compressor |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US496954A (en) * | 1893-05-09 | Rotary engine | ||
| US2623365A (en) * | 1947-07-14 | 1952-12-30 | Leonard J Daniel | Refrigerator pump |
| DE2837612A1 (en) * | 1978-08-29 | 1980-03-06 | Edmund Fahske | Pressure wave generator with tangential outlets - has rotor with vertical spindle in bearings top and bottom, and valves on top |
| JPS56143382A (en) * | 1980-04-07 | 1981-11-09 | Matsushita Electric Ind Co Ltd | Rotary fluid machine |
| US4898522A (en) * | 1988-04-07 | 1990-02-06 | Teledyne Industries, Inc. | System for cooling the rotary engine rotor |
-
2007
- 2007-04-04 GB GBGB0706637.6A patent/GB0706637D0/en not_active Ceased
-
2008
- 2008-04-03 WO PCT/GB2008/001193 patent/WO2008122781A1/en active Application Filing
- 2008-04-03 CN CN200880018688A patent/CN101680459A/en active Pending
- 2008-04-03 KR KR1020097021799A patent/KR20100015695A/en not_active Application Discontinuation
- 2008-04-03 AU AU2008235279A patent/AU2008235279A1/en not_active Abandoned
- 2008-04-03 MX MX2009010530A patent/MX2009010530A/en not_active Application Discontinuation
- 2008-04-03 BR BRPI0809182-0A patent/BRPI0809182A2/en not_active Application Discontinuation
- 2008-04-03 CA CA002682672A patent/CA2682672A1/en not_active Abandoned
- 2008-04-03 RU RU2009137471/06A patent/RU2009137471A/en unknown
- 2008-04-03 JP JP2010501591A patent/JP2010523881A/en active Pending
- 2008-04-03 US US12/594,360 patent/US20100129192A1/en not_active Abandoned
- 2008-04-03 EP EP08718991A patent/EP2150703A1/en not_active Withdrawn
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103620226A (en) * | 2011-05-27 | 2014-03-05 | 通用电气公司 | Supersonic compressor startup support system |
| CN103620226B (en) * | 2011-05-27 | 2016-08-17 | 通用电气公司 | Supersonic compressor starts support system and relevant startup method |
Also Published As
| Publication number | Publication date |
|---|---|
| GB0706637D0 (en) | 2007-05-16 |
| JP2010523881A (en) | 2010-07-15 |
| BRPI0809182A2 (en) | 2014-09-16 |
| MX2009010530A (en) | 2010-04-21 |
| CA2682672A1 (en) | 2008-10-16 |
| KR20100015695A (en) | 2010-02-12 |
| RU2009137471A (en) | 2011-05-10 |
| AU2008235279A1 (en) | 2008-10-16 |
| EP2150703A1 (en) | 2010-02-10 |
| WO2008122781A1 (en) | 2008-10-16 |
| US20100129192A1 (en) | 2010-05-27 |
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Application publication date: 20100324 |