CN104047706A - Integrated volumetric energy recovery and compression device - Google Patents
Integrated volumetric energy recovery and compression device Download PDFInfo
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- CN104047706A CN104047706A CN201410190416.4A CN201410190416A CN104047706A CN 104047706 A CN104047706 A CN 104047706A CN 201410190416 A CN201410190416 A CN 201410190416A CN 104047706 A CN104047706 A CN 104047706A
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- 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
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- 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
- F01C1/126—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 elements extending radially from the rotor body not necessarily cooperating with corresponding recesses in the other rotor, e.g. lobes, Roots type
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- 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
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- 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
- F01C13/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01C13/04—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby for driving pumps or compressors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B33/00—Engines characterised by provision of pumps for charging or scavenging
- F02B33/32—Engines with pumps other than of reciprocating-piston type
- F02B33/34—Engines with pumps other than of reciprocating-piston type with rotary pumps
- F02B33/36—Engines with pumps other than of reciprocating-piston type with rotary pumps of positive-displacement type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B33/00—Engines characterised by provision of pumps for charging or scavenging
- F02B33/32—Engines with pumps other than of reciprocating-piston type
- F02B33/34—Engines with pumps other than of reciprocating-piston type with rotary pumps
- F02B33/36—Engines with pumps other than of reciprocating-piston type with rotary pumps of positive-displacement type
- F02B33/38—Engines with pumps other than of reciprocating-piston type with rotary pumps of positive-displacement type of Roots type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Supercharger (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Power-generation system (14) including a power plant (16) and a power conversion unit (15) including an energy recovery device (20) and a volumetric compressor (50). The volumetric fluid compressor (50) has first and second meshed rotors (60,62) and is configured to generate a stream of relatively high-pressure fluid including oxygen to the power plant (16). The volumetric fluid energy recovery device (20) has third and fourth meshed rotors (30,32), operatively connected to the compressor (50), and configured to be rotated by the exhaust gas or other fluid deriving energy from the exhaust gas. The system can additionally include a set of timing gears (81,83) configured to operatively connect the first and second rotors (60,62) of the compressor (50) to the third and fourth rotors (30,32) of the energy recovery device (20), and prevent contact between the first and second rotors and between the third and fourth rotors. The system may also include a rotation transferring link for operative connection between the compressor (50) and the energy recovery device (20).
Description
The cross reference of related application
The application requires the U.S. Patent Application Serial Number No.61/787 submitting on March 15th, 2013,834 preference, and its disclosed full content is incorporated in this by reference.
Technical field
The present invention relates to a kind of power generation systems, it comprises the positive displacement energy recycle device that is attached to power plant.
Background technique
Fluid means, for example turboexpander, be often used in multiple power generation process and produce useful work.In this power generation process, pressurized working fluid conventionally expands and produces useful work in fluid means.Because this merit is taken at the high-pressure liquid of expansion, fluid expansion is similar to isentropic process, namely, and permanent constant entropy process.
Representational power production process can comprise Rankine cycle, and wherein, working fluid can be water, and rock gas, fuel oil or burning of coal are for generation of high pressure steam, and this high pressure steam is directed to fluid means subsequently.After the energy of hot operation fluid has been converted into useful work in fluid means, working fluid is discharged with low pressure form from this device conventionally, and in significantly reduced temperature, sometimes lower than-90 DEG C.
Summary of the invention
Power generation systems comprises the power plant that use power generation circulation, and wherein, power plant use oxygen to produce power and produce the by-product of exhausting air as power generation circulation.This system also can comprise displacement fluid compressor, and it has the first and second meshing rotors, and is configured to produce the steam of the relatively high pressure fluid that comprises oxygen, and this steam supply is to power plant.This system can also comprise displacement fluid energy recycle device, it has the third and fourth meshing rotors, is connected to described rotor operation compressor, and is constructed to be rotated by exhausting air, namely compensate energy from exhausting air, thus drive compression machine.This system can comprise one group of timing gear extraly, it is configured to operatively to connect the first and second rotors of compressor to the third and fourth rotor of energy recycle device, and prevents the contact between the first and second rotors and between the third and fourth rotor.This system can also comprise rotation transmission Transmitted chains (rotation transferring link), connects for operability between compressor and energy recycle device.This Transmitted chains can be constructed to make the rotational speed of energy recycle device and the rotational speed of power plant substantially to mate, and the rotational speed of power plant is that the amount of the oxygen that uses in order to produce power of power plant determines.
Another embodiment of the invention is about a kind of vehicle, and it has the power plant that produce the propelled vehicles that circulates with power.This vehicle can comprise displacement fluid compressor and the positive displacement energy recycle device of type mentioned above.
By reference to the accompanying drawings with appended claim, from below the detailed description of described working of an invention mode and optimal mode, clearly seeing above-mentioned feature and advantage of the present invention and further feature and advantage to implementing.
Brief description of the drawings
Accompanying drawing 1 is the schematic diagram of the first mode of execution of vehicular propulsion, and this vehicular propulsion comprises positive displacement energy recycle device and displacement fluid compressor, and it has the feature as the example of the each side according to principle of the present invention.
Accompanying drawing 2 is schematic diagram of the second mode of execution of vehicular propulsion, and this vehicular propulsion comprises positive displacement energy recycle device and displacement fluid compressor, and it has the feature as the example of the each side according to principle of the present invention.
Accompanying drawing 3 is schematic diagram of the 3rd mode of execution of vehicular propulsion, and this vehicular propulsion comprises positive displacement energy recycle device and displacement fluid compressor, and it has the feature as the example of the each side according to principle of the present invention.
Accompanying drawing 4 is the schematic diagram that comprise the first mode of execution of the positive displacement energy recycle device of the power plant that can be used for accompanying drawing 1-3 and the integrated device of displacement fluid compressor.
Accompanying drawing 5 is the schematic diagram that comprise the second mode of execution of the positive displacement energy recycle device of the power plant that can be used for accompanying drawing 1-3 and the integrated device of displacement fluid compressor.
Accompanying drawing 5A is the end elevation that can be used for the planetary gear set of the integrated device shown in accompanying drawing 5.
Accompanying drawing 6 is the schematic section side view that can be used for the energy recycle device of the power plant of accompanying drawing 1-3 and 8-9.
Accompanying drawing 7 is the perspective schematic view that can be used for the energy recycle device of the power plant of accompanying drawing 1-3 and 8-9.
Accompanying drawing 8 is schematic diagram of the 4th mode of execution of vehicular propulsion, and this vehicular propulsion comprises positive displacement energy recycle device and displacement fluid compressor, and it has the feature as the example of the each side according to principle of the present invention.
Accompanying drawing 9 is schematic diagram of the 5th mode of execution of vehicular propulsion, and this vehicular propulsion comprises positive displacement energy recycle device and displacement fluid compressor, and it has the feature as the example of the each side according to principle of the present invention.
Accompanying drawing 10 is the schematic diagram that can be used for the rotor geometry of the energy recycle device shown in accompanying drawing 6.
Accompanying drawing 11 is the schematic diagram that comprise the 3rd mode of execution of the integrated device of positive displacement energy recycle device in the power plant that can be used for accompanying drawing 1-3 and displacement fluid compressor.
Embodiment
Describe multiple mode of executions in detail with reference to accompanying drawing, wherein, in several figure, identical reference character represents identical parts and assembly.The reference of multiple mode of executions is not limited to the scope of this claim of be attached to.In addition, it is restrictive that any example of describing in this specification is not intended to, but only describes claims a lot of some mode of executions in may mode of executions.
Brought the development of mixed power generation and propulsion system for the modern needs of fuel efficient vehicle and power plant.Conventionally, this system for example, drives vehicle in conjunction with power plant (internal-combustion engine or fuel cell) and motor.Each in internal-combustion engine and fuel cell discharges high-temperature discharge gas and produces the by-product of circulation as the power being used in wherein.This high-temperature discharge gas forms the energy that produces circulation loss from power, if it is caught again, can be used to improve the efficiency of circulation, and thereby improves the efficiency of the propulsion system that uses this circulation.
With reference to accompanying drawing, wherein, in several figure, identical reference character is corresponding to same or analogous parts.Improvement that also need to be in other application, for example, in ocean agricultural and industry.Another example is stationary power generation unit.
Accompanying drawing 1-3 and 8-9 show the example of the power generation systems 14 that comprises power converting unit 15.Each disclosed power converting unit 15 includes energy recycle device 20 and compression set 50.As described in, the energy recycle device 20 in the future waste heat energy regenerating of ultromotivity device 16 is converted to rotating energy, this rotating energy can be used to drive compression device 50 directly or indirectly.Accompanying drawing 1-3 shows the example of integrated power converting unit 15, and therein, energy recycle device 20 is attached directly to compression set 50.For the use of term " compression set ", its mean comprise can pressurized gas fluid the device of any type of stream, for example positive displacement arrangements (for example, Roots blower) and on-positive displacement device is (for example, screw compressor, turbo machine, scroll compressor, etc.).For the use of term " integrated (integrated) ", it means the system that comprises that the output of device 20 and the input for compression set 50 are mechanically linked together.Accompanying drawing 8-9 shows the example of distributed-power converting unit 15, and therein, energy recycle device 20 and compression set 50 are all attached to power plant 16.For the use of term " distributed (distributed) ", it means the system between device 20 and compression set 50 without direct mechanical Transmitted chains that is included in.Power generation systems 14 can be used for vehicle, agricultural equipment and/or stationary power and produces system, for example generator set.
With reference to accompanying drawing 1, the vehicle 10 illustrating has wheel 12, for moving along suitable road surface.Vehicle 10 comprises power generation systems 14.System 14 comprises the power plant 16 that use power generation circulation.The oxygen of power plant 16 use specified quantitatives produces power, and this oxygen can be a part for the air stream 11 that enters.Power plant 16 also produce used heat, and this used heat is for example the form of the high-temperature discharge gas in discharge pipe line 18, are the by-products that power produces circulation.In one embodiment, power plant 16 are internal combustion type (IC) motors, the type of for example spark ignition or ignition by compression, and the mixture of its combustion fuel and air produces power.In one embodiment, power plant 16 can be fuel cells, and the chemical energy from fuel is converted into electric energy by the chemical reaction of its utilization and oxygen or other oxygenant.
In one embodiment, as shown in Figure 1, be directed to power converting unit 15 from whole exhausting air of power plant 16 by discharge pipe line 18.Along with exhausting air reclaims side 20 by the energy of system 15, exhausting air makes inner rotator 30,32 rotations, and this makes inner rotator 60,62 rotations of compression set 50 then.Gas can leave system at discharge pipe line 17 places subsequently.As shown in Figure 1, be provided with discharge bypass 18a and bypass valve 206, so that when needed, allow exhausting air to change its course around energy recycle device 20.The rotation of rotor 60,62 makes the air stream 11 that enters pressurized, and is transported to power plant 16 by intake manifold 13.As shown in Figure 1, air inlet bypass 13a and bypass valve 204 can be set, to allow pressurized air recirculation to get back to the compression set entrance at pipeline 11 places, thereby prevent the excessive pressurization of air inlet.Should point out, in paragraph below, will describe energy recycle device 20 and compression set 50 in detail, and the operation of bypass valve 202 and 204.
In one embodiment, as shown in Figure 2, only some exhausting air from power plant 16 is directed to power converting unit 15 by discharge pipe line 18a.As shown in the figure, in exhaust gas recirculation (EGR) configuration, pipeline 18a carrying will be recycled into the exhausting air of intake manifold 13 of power plant 16.Therefore, in exhausting air, by after energy recycle device 20, exhausting air can be transferred into exhausting air cooler 19 by pipeline 18b, and is fed into EGR mixer 21 by pipeline 18c subsequently, herein, exhausting air can with mix from the new charge of compression set 50.Should point out, energy recycle device 20 extracts energy from discharge gas stream, and can allow cooler for recycled exhaust gas 19 and manufacture than the situation that there is no energy recycle device 20 smaller.Energy recycle device also can be used to regulate the amount that is mixed into the EGR in new charge.Should point out, attached system shown in Figure 2 also can be provided with the bypass 13a shown in accompanying drawing 1 and/or 18a and bypass valve 202 and/or 204.
In one embodiment, as shown in Figure 3, organic Rankine circulation (ORC) is used to provide power to energy recycle device 20, instead of directly provides power by exhausting air.In this mode of execution, the pipe-line system 100 that comprises heat exchanger 102 is set, this heat exchanger 102 in the future heat of self-discharging gas line 18 is passed to working fluid, and it is transferred into energy recycle device 20 subsequently.Condenser 104 is also set, and it produces for the area of low pressure of working fluid, and thereby is provided for the position of working fluid condensation.Once condensation, working fluid can be passed to heat exchanger 102 by pump 106.Being described in more detail in Publication about Document of ORC system for driving-energy recovering device 20 provides: Patent Cooperation Treaty (PCT) International Application PCT/US13/28273, name is called " positive displacement energy recycle device and system ".The full content of PCT/US13/28273 is incorporated into this by reference.Should point out, attached system shown in Figure 3 also can be provided with the bypass 18a shown in accompanying drawing 1 and bypass valve 202.
With reference to accompanying drawing 8, it shows a mode of execution, and wherein compression set 50 and energy recycle device 20 are independent unit, thereby not integrated each other.Therefore, compression set 50 can be the Roots blower 50 of standard.In one embodiment, compression set 50 is the U. S. Patents 7,488 that are called " for the optimal helical angle rotor of Roots's pressure-increasing machine " in name, and shown in 164, with the type of describing, the full content of this patent is incorporated into this by reference.In one embodiment, energy recycle device 20 is shown in application mentioned above PCT/US13/28273 and the type of describing.As shown in the figure, the power outgoing position 16b drive compression device 50 of power plant 16, the output of energy recycle device 20 is simultaneously sent to the power input position 16a of power plant.In one embodiment, power input position 16a is the live axle of motor, and power outgoing position 16b is pulley, belt, gear or the chain that is directly or indirectly connected to the crankshaft of power plant 16.Alternatively or extraly, energy recycle device can send power to energy storing device 110, for example battery or storage battery.Should point out, attached system shown in Figure 8 also can be provided with the bypass 13a shown in accompanying drawing 1 and/or 18a and bypass valve 202 and/or 204.
Accompanying drawing 9 is similar to accompanying drawing 8, wherein shows distributed system, uses two energy recycle device 20A and 20B but show.For the exhausting air of the first energy recycle device 20A identical with shown in accompanying drawing 2 of configuration of flowing, and be the discharge gas stream not using at egr system for the discharge gas stream of the second energy recycle device 20B.As shown in the figure, the two provides the power of getting back to power plant 16 at position 16a energy recycle device 20A, 20B, and this position 16a can be a common location or (multiple) position separately.Should point out, attached system shown in Figure 9 also can be provided with the bypass 13a shown in accompanying drawing 1 and/or 18a and bypass valve 202 and/or 204.
With reference to accompanying drawing 4,5 and 11, show the schematic diagram of three mode of executions of the integrated power converting unit 15,115 that can be used for system mentioned above.Accompanying drawing 7 and 8 shows the further details about positive displacement energy recycle device 20.Should point out, a lot of features of positive displacement energy recycle device 20 and compression set 50 share.
power converting unit---energy recycle device
Conventionally dynamic power and static pressure that, positive displacement energy recycle device 20 depends on working fluid 12-1 carry out running shaft 38 or 40.Wherein, device 20 is used in expansion application, and for example, together with Rankine cycle, extra energy obtains from working fluid by fluid expansion.In this example, device 20 can be called as expander or expansion gear, as what explained in paragraph below.It should be understood, however, that device 20 is not limited to the application that wherein working fluid expands through this device, for example, the mode of execution of the exhaust gas-driven shown in attached Fig. 1 and 2.
Device 20 has housing 22, and this housing 22 has fluid input 24 and fluid output 26, and working fluid 12-1 bears pressure drop through this fluid input 24 and fluid output 26, with to axle 38 or 40 transferring energies.Axle 38 is driven by the first and second staggered mutually despun rotors 30,32 that are arranged in the synchronous connection in the cavity 28 of housing 22.Each rotor 30,32 all has blade, and its length along rotor 30,32 is reversed or helix shape.In the time of rotor 30,32 rotation, blade is against the inner side surface seal operation fluid 12-1 at least in part of housing, and now, the expansion of working fluid 12-1 only occurs to leak the degree allowing, and in ORC application, this represents the poor efficiency of system.Contrary with some expansion gears of volume that change working fluid in the time that fluid is sealed, be constant at working fluid 12-1 at the volume limiting between the inner side surface of the housing 22 of blade and device 20 during through the length of rotor 30,32.Therefore, device 20 can be called as " positive displacement arrangements ", because the volume of the working fluid of sealing or part sealing does not change.Should point out, as those skilled in the art will be clearly based on instruction of the present invention, the geometrical shape of described device 20 and structure are different from geometrical shape and the structure of typical Root's compressor.
Device 20 is shown specifically in accompanying drawing 7 and 8.Device 20 comprises housing 22.As shown in Figure 7, housing 22 comprises ingress port 24, and its working fluid 12-1 that is configured to the relatively high pressure that allows automatic heat-exchanger 18 (shown in accompanying drawing 1) enters.Housing 22 also comprises outlet port 26, and it is configured to discharge working fluid 12-2.Should point out, from the working fluid that exports 26 discharges in relatively high pressure, higher than using the pressure of working fluid at condenser 104 places of ORC system.Extraly, entrance and exit port 24,26 can have connector, for providing and the fluid-tight seal of other system unit, to guarantee that working fluid 12-1,12-2 (it can be ethanol) can jeopardously not leak into beyond device 20.
As illustrated in addition in accompanying drawing 7, each rotor 30,32 has four blades, the in the situation that of rotor 30, is 30-1,30-2,30-3 and 30-4, the in the situation that of rotor 32, is 32-1,32-2,32-3 and 32-4.Although show four blades for each rotor 30 and 32, each in two rotors can have any amount of blade equal to or greater than two, as long as the blade quantity of two rotors is identical just passable.Therefore, when a blade of rotor 30, for example blade 30-1 with respect to ingress port 24 guide/when leading, a blade of rotor 32, for example blade 30-2 is with respect to entrance 24 and thereby follow/delay with respect to the stream of pressurized working fluid 12-1.
As shown in the figure, the first and second rotors 30 and 32 are fixed to corresponding rotor shaft, and the first rotor is fixed to axle 38 and the second rotor is fixed to axle 40.Each rotor shaft 38,40 is mounted on one group of bearing (not shown) respectively around axis X 1, X2 rotation.Should point out, axis X 1 and X2 are substantially parallel to each other.Interlaced and the lasting engagement of the first and second rotors 30 and 32, for one rotation each other.Again with reference to accompanying drawing 6, device 20 also comprises the timing gear 42 and 44 of engagement, and wherein, timing gear 42 are fixed as rotation together with rotor 30, and timing gear 44 are fixed as rotation together with rotor 32.Timing gear 42,44 are configured to keep the special position of rotor 30,32, and prevent the contact between device operation period of 20 rotor.
Along with working fluid is converted to relatively low pressure working fluid 12-2 from relatively high pressure working fluid 12-1, axle 38 is rotated by working fluid 12.As seen in addition in accompanying drawing 6 and 7, axle 38 extends beyond the border of housing 22.Although the axle 38 illustrating is operatively connected to the first rotor 30, in replacement scheme, axle 38 can be operatively connected to the second rotor 32.As schematically shown in accompanying drawing 8-9, axle 38 can be attached to power plant 16, makes can again to be caught from the energy of exhausting air.Gear reducer can be set, to provide better coupling between power plant 16 and the rotational speed of axle 38.
Aspect of device 20 geometrical construction, each in rotor blade 30-1 to 30-4 and 32-1 to 32-4 all has a kind of blade geometry structure, wherein, the length 34 that the torsion of each in the first and second rotors 30 and 32 is mated substantially along them is constant.As schematically shown at accompanying drawing 10, a parameter of blade geometry structure is helix angle HA.By the mode of definition, it should be understood that at " helix angle (the helix angle) " of below mentioned rotor blade and refer to the helix angle of locating at the pitch diameter PD of rotor 30 and 32 (or pitch circle).Term " pitch diameter " and identification thereof are fine understanding to the technician in gear and rotor field, no longer further discuss at this.As used herein, helix angle HA can calculate as follows: helix angle (HA)=(180/.pi.*arctan (PD/ helical pitch)), wherein, the pitch diameter of PD=rotor blade; And helical pitch=blade completes 360 degree and reverses required length of blade.Should point out, helical pitch is the function of the corresponding torsion angle of blade 30,32 and length L 1, L2.Be known that for those skilled in the art torsion angle is the angle displacement of blade, to spend as unit, in the middle of it occurs in and " advances " to the front end edge length of blade of rotor from the rear end of rotor.As shown in the figure, torsion angle is approximately 120 degree, but torsion angle can be the smaller or greater number of degrees, for example 160 degree.
At expander geometrical construction on the other hand, ingress port 24 includes bicker 24-1, as can be schematically seen in accompanying drawing 6, and in the mode of execution shown in accompanying drawing 4-5.In one embodiment, Inlet cone angle 24-1 is defined as the overall or average angle of the internal surface 24a (example anterior internal surface as shown in Figure 6) of ingress port 24.In one embodiment, Inlet cone angle 24-1 is defined as the angle of the approximate centre line of ingress port 24, and example as shown in Figure 2.In one embodiment, Inlet cone angle 24-1 is defined as: owing to contacting with anterior internal surface 24a, enter the direction of the overall acquisition of the working fluid 12-1 of rotor 30,32, as visible in the two at accompanying drawing 2 and 8.As shown in the figure, Inlet cone angle 24-1 had both been not orthogonal to the spin axis X1, the X2 that are also not parallel to rotor 30,32.Therefore, the front inner surface 24a of ingress port 24 is shaped the major component of working fluid 12-1 in one direction, and this direction is with respect to spin axis X1, the X2 bevel of rotor 30,32, and thereby is roughly parallel to Inlet cone angle 24-1.
In addition, ingress port 24 can be configured as, and makes working fluid 12-1 be drawn towards the first axial end 30a, the 30b of rotor 30,32, and is drawn towards the guiding of rotor blade and follows surface (describing in detail below) from side direction.But, it should be understood that Inlet cone angle 24-1 can be roughly parallel to or be approximately perpendicular to axis X 1, X2, but can expect efficient loss for some rotor structure.In addition, should point out, ingress port 24 can be configured as towards entrance opening 24b and narrow, as at accompanying drawing 2 and 8 as shown in the two.Can find out with reference to accompanying drawing 10, ingress port 24 has width W, and it is slightly smaller than the combined diameter distance of rotor 30,32.Combined rotor diameter equals distance between axis X 1 and X2 and adds two times of distance from cener line X1 or X2 to the end of respective vanes.In some embodiments, width W is equal to or greater than combined rotor diameter.
At expander geometrical construction on the other hand, outlet port 26 comprises exit angle 26-1, as can be schematically seen in accompanying drawing 6, and in the mode of execution shown in accompanying drawing 4-5.In one embodiment, exit angle 26-1 is defined as the overall or average angle of the internal surface 26a of outlet port 26, and example as shown in Figure 8.In one embodiment, exit angle 26-1 is defined as the angle of the approximate centre line of outlet port 26, and example as shown in Figure 6.In one embodiment, exit angle 26-1 is defined as: owing to contacting with internal surface 26a, leave the direction of the overall acquisition of the working fluid 12-2 of rotor 30,32.As shown in the figure, exit angle 26-1 had both been not orthogonal to the spin axis X1, the X2 that are also not parallel to rotor 30,32.Therefore, the internal surface 26a of outlet port 26 receives with the angle tilting the working fluid 12-2 leaving from rotor 30,32, and this can be reduced in the back pressure at outlet port 26 places.In one embodiment, Inlet cone angle 24-1 is totally equal or parallel with exit angle 26-1, as shown in Figure 6.In one embodiment, Inlet cone angle 24-1 and exit angle 26-1 relative to each other tilt.It should be understood that exit angle 26-1 can be approximately perpendicular to axis X 1, X2, but can expect efficient loss for some rotor structure.Further should point out, exit angle 26-1 can be perpendicular to axis X 1, X2.As constructed, orientation and the size of outlet port 26-1 are asserted, and make the working fluid 12-2 leaving can as far as possible easily and promptly discharge each rotor cavity 28, thereby reduce as much as possible back pressure.The outputting power of axle 38 be maximized to the back pressure being caused by outlet can be minimum degree, make working fluid can be become by promptly discharge the operating on low voltage fluid at condenser place.
By coordinating the geometrical construction of Inlet cone angle 24-1 and the geometrical construction of rotor 30,32, the efficiency of device 20 can be optimized.For example, the helix angle HA of rotor 30,32 can construct with Inlet cone angle 24-1 together with complimentary fashion.Because ingress port 24 is guided working fluid 12-1 the guide surface of each rotor 30,32 into and follows face, working fluid 12-1 carries out forward and negative sense work on device 20.
In order to illustrate, accompanying drawing 7 illustrates that blade 30-1,30-4,32-1 and 32-2 are all exposed to working fluid 12-1 by ingress port opening 24b.Each blade all has guide surface and follows face, and the two is exposed to working fluid at multiple turning point place of associated rotor.Guide surface is the side of the forefront of blade in the time that rotor rotates along direction R1, R2, and the face of following is the side facing to guide surface of blade.For example, rotor 30 rotates on direction R1, thus cause side 30-1a as the guide surface of blade 30-1 and side 30-1b as the face of following.In the time that rotor 32 rotates on the direction R2 contrary with direction R1, guide surface and the face of following are mirror images, and making side 32-2a is the guide surface of blade 32-2, and side 32-2b is the face of following.
Put it briefly, working fluid 12-1 impinges upon following on face of blade in the time that they pass ingress port opening 24b, and carries out forward work on each rotor 30,32.For the use of term " forward work (positive work) ", it means that working fluid 12-1 makes rotor be used for rotor 32 along required direction rotation: direction R1 for rotor 30 and direction R2.As shown in the figure, working fluid 12-1 for example, implements forward work by being operating as on the face of the following 32-2b of rotor 32-2 (on surface portion 47).Also (for example, on surface portion 46) enforcement forward work on the face of the following 30-4b of rotor 30-1 of working fluid 12-1.But working fluid 12-1 also impinges upon on the guide surface of blade in the time that they pass ingress port opening 24b, for example surperficial 30-1 and 32-1, thereby make to carry out negative sense work on each rotor 30,32.For the use of term " negative sense work (negative work) ", it means that working fluid 12-1 rotates rotor on the opposite direction of required direction R1, R2.
Therefore, wish rotor 30,32 and ingress port 24 are shaped and are oriented to, make working fluid 12-1 as much as possible impinge upon following on face of blade, and the least possible working fluid 12-1 impinges upon on guide blades, work thereby can carry out the highest clean forward by device 20.
For the efficiency of optimization device 20 and the favourable configuration of one of clean forward work be the Inlet cone angle 24-1 of the rotor blade helix angle HA of about 35 degree and about 30 degree.This configuration is operating as the impingement region that maximizes the face of following on blade, the impingement region of the guide surface of simultaneous minimization blade.In one embodiment, helix angle is between about 25 degree and about 40 degree.In one embodiment, Inlet cone angle 24-1 is set as in (adding deduct) 15 degree in helix angle HA.In one embodiment, helix angle is between about 25 degree and about 40 degree.In one embodiment, Inlet cone angle 24-1 is set as in (adding deduct) 15 degree in helix angle HA.In one embodiment, in Inlet cone angle (adding deduct) 10 degree in helix angle.In one embodiment, Inlet cone angle 24-1 is set as in (adding deduct) 5 degree in helix angle HA.In one embodiment, Inlet cone angle 24-1 is set as in (the adding deduct) 1 15 in helix angle HA, and in one embodiment, Inlet cone angle 24-1 in helix angle 10 in.Inlet cone angle and helix angle can be also other values, and do not depart from the concept in this expression.But, have been found that in the case of the value of Inlet cone angle and helix angle do not have fully approaching, may there is significant decrease in efficiency (for example, the decline of 10-15%).
power converting unit---compression set
As arrived in prerequisite, compression set 50 can have and U. S. Patent 7,488, and the structure of describing in 164 is similarly constructed, and has a lot of features overlapping with above-described energy recycle device 20.Therefore, about the full content of the description of energy recycle device 20 by reference to being combined in this for compression set 50.
With reference to accompanying drawing 4,5 and 11, wherein show the schematic diagram of three mode of executions of the integrated power converting unit 15,115 that can be used for above-described system.In one aspect, power converting unit 15 comprises the compression set 50 with housing 52.As shown in the figure, housing 52 comprises ingress port 54, and it is configured to allow the ambient air 54-1 of relatively low pressure to enter.Housing 52 also comprises outlet port 56, and its air 56-1 that is configured to discharge relatively high pressure is to power plant 16.Should point out, the position of ingress port 54 and outlet port 56 can radially or axially arrange, for example, and axial entrance and radially outlet.
The housing 52 of compression set 50 also comprises rotor cavity 58.What as shown in the figure, be arranged in rotor cavity 58 inside is respectively the first and second torsion meshing rotors 60 and 62.Rotor 60 and 62 is mounted to synchronous rotary in rotor cavity 58, and is configured to compress the air 56-1 that the ambient air 54-1 of relatively low pressure is relatively high pressure.Therefore, the first and second meshing rotors 60 and 62 are configured to the stream of the air 56-1 that produces the relatively high pressure that comprises oxygen, and it is transported to power plant 14 subsequently, and the compressed oxygen that these power plant 14 are supplied with by use subsequently produces power.
As shown in the figure, each rotor 60,62 has respectively multiple blade 60-1,62-1.In one embodiment, each rotor 60,62 has three blade 60-1,62-1, and in another embodiment, each rotor 60,62 has four blade 60-1,62-1.Therefore, in the time that a blade, for example blade 60-1 of rotor 60 guide with respect to ingress port 54, a blade of rotor 62, for example blade 60-2 follow with respect to ingress port 64, and thereby follow with respect to the stream of the ambient air 54-1 of relatively low pressure.
In one embodiment, the length that the torsion of each in the first and second rotors 60 and 62 is mated substantially along them is constant.The first and second rotors 60 and 62 are fixed to corresponding rotor shaft, and wherein, the first rotor is fixed to input shaft 68 and the second rotor is fixed to axle 69.Each rotor shaft 68,69 is mounted on one group of bearing (not shown) and rotates.Axle 68 can be rotated by power plant 16, to produce the stream of relatively high pressure air 56-1.Although the input shaft 68 illustrating is operatively connected to the first rotor 60, in possibility, axle 69 can be operatively connected to the second rotor 62.Interlaced and the lasting engagement of the first and second rotors 60 and 62, for one rotation each other.
With reference to accompanying drawing 4 and 11, compressor 60 also comprises the timing gear 72 and 74 of engagement, and wherein, timing gear 72 are fixed as rotation together with rotor 60, and timing gear 74 are fixed as rotation together with rotor 62.Timing gear 72,74 are configured to maintain the specific relative position between rotor 60,62, and prevent the contact between the operation period of compressor 50 rotor.
Should point out, energy recycle device 20 and compression set 50 can comprise rotor and the housing with analog structure, but in the case of not utilizing the rotor of optimization and entrance some efficiency of possible loss.
power converting unit---transmission of power Transmitted chains
Power converting unit 15 can comprise transmission of power Transmitted chains 80 between energy recycle device 20 and compression set 50, make can be converted into rotating energy by energy recycle device 20 from the used heat of power plant 16, it is subsequently for drive compression device 50.Therefore, Transmitted chains 80 can be configured to make the rotational speed of device 50 substantially to mate with the rotational speed of power plant 16, and wherein, the rotational speed of power plant is that the amount of oxygen that is used to produce necessary power by power plant determines.Should point out, attached Figure 4 and 5 show integrated power converting unit 15, and wherein, energy recycle device 20, compression set 50 and Transmitted chains 80 are in common housing.
With reference to accompanying drawing 4 and 11, Transmitted chains 80 is arranged on the end relative with the timing gear 72,74 of compression set 50, and is positioned at the end relative with the timing gear 42,44 of recovering device 20.As shown in the figure, the axle 38 of recovering device 20 is configured to output shaft, and the axle 69 of compression set 50 is configured to input shaft.By by these shaft mechanicals be linked together, for example there is the gear train of the gear 81,83 that is connected to respectively axle 38,69 by use, torque can be passed between axle 38 and 69.This gear train can be configured to simple train of gearings, and it is configured to limit specific velocity ratio between compression set 50 and recovering device 20.Equally, when power plant 16 are in the situation of fuel cell, this direct mechanical drives or simple train of gearings can be used as Transmitted chains 80.Also be feasible for other device that mechanically connects these axles, for example, axle 38 or 40 can align with axle 68 or 69 respectively, and directly connects or be soldered to axle 68 or 69.In addition, axle 38 and 68 can be set to single common shaft, and axle 39 and 69 also can be set to single common shaft.
Should point out, by outrigger shaft 40, to gear 83 and outrigger shaft 68 to gear 81, Transmitted chains 80 can be configured to replace timing gear 42,44,72,74.In this structure, the two will complete transmission of power and rotor timing by identical gear train, make independent a pair of timing gear form one group of timing gear of system 14, and the rotation that is enough to the first and second rotors 30,32 that make compressor 20 is suitably synchronizeed with the third and fourth rotor 60,62 of device 50.
With reference to accompanying drawing 5, recovering device 20 and compression set 50 are oriented to and make the contiguous timing gear 42,44 of timing gear 72,74.In this mode of execution, recovering device 20 and compression set 50 are mechanically coupled to each other by variable speed drive 85, and this variable speed drive 85 is depicted as dual planetary gear group structure, and it has common or shared support element.This dual planetary gear group 85 can provide variable gear ratio, and it is configured to the operational condition experiencing based on power plant 16, and the speed of power plant 16 and device 20 is mated substantially.
With reference to accompanying drawing 5 and 5a, axle 68 can be attached to the sun gear 85a of planetary gear set 85, and axle 38 can be attached to support 87, and this support 87 is connected to the one group of planetary pinion 85b engaging rotatably with sun gear 85a.Also be provided with ring gear 85c, it is depicted as with planetary pinion 85b and engages rotatably.In the time that the position of ring gear 85c is fixed, the first gear ratio being limited with sun gear 85a and planetary pinion 85b from whole power of axle 38 is passed to axle 68.Be allowed to rotation in the situation that at ring gear 85c, power subsequently can from axle 38 be passed to axle 68 and ring gear 85c the two.This structure allows to obtain the required rotational speed of compression system 50, and meanwhile, any excessive power that recovering device 20 is produced is sent to ring gear 85c.
In one embodiment, generator/generator or pump 82 can be arranged to be connected with ring gear 85c operability by gear 89, and this gear 89 interacts with the tooth 85d on ring gear 85c.The drive system of other type is also feasible, for example belt and pulley.Therefore, generator 82 can be constructed to change as required the speed with selection device 20, to substantially mate the rotational speed of power plant 16 and device 50.Equally, generator 82 can be operating as the speed of break with modifier 20, makes in the time that generator provides zero braking force, and device 20 can be allowed to idle running.In addition, in the time that device 20 provides zero braking force to be allowed to dally due to generator 82, can be lowered from the parasitic drag on compression system 50 of this device, namely minimize, thus the operating efficiency of increase whole system 14.In the time that ring gear is allowed to dally, zero torque is passed, and is similar to the situation of open type clutch.This will reduce the wastage during idling mode, now can be too low and the forward energy input of getting back to motor 52 can not be provided with exhausting air energy.
With reference to accompanying drawing 4-6 and 11, system can also comprise drive system 90, so that in the situation that can not obtaining enough power from energy recycle device 20, allows power plant 16 drive compression devices 50.In one embodiment, drive system 90 comprises electric drive unit 91, and it can be independent of power operation and carry out drive compression device 50.In another embodiment, as shown at accompanying drawing 11, drive system 90 can comprise pulley 91, and it by power outgoing position (for example, pulley 16b and belt 16c) and power plant 16 power communication, as found in typical Roots blower.Gear reduction system is also feasible.The mode of execution of accompanying drawing 11 is also depicted as has clutch 93, makes drive system 90 can be when needed depart from and connect from compression set 50, for example, in the time that needs are only used the complete drive compression device of expansion gear 20 15.As substituting of clutch 93, unilateral bearing group also can be set at pulley place.The in the situation that of hope, Transmitted chains 80 also can comprise clutch, recovering device 20 can be closed hopefully and rotated by drive system 90.
system control and operation
Any in the system shown in accompanying drawing 1-3 with anyly can operate by control system in the structure shown in accompanying drawing 4,5 and 11.This system is present in accompanying drawing 1, and it shows electronic controller.Electronic controller 500 is shown schematically as and comprises processor 500A and non-temporality storage medium or storage 500B, for example RAM, flash disk or hard disk.Storage 500B is for store executable code, operating parameter and the input from operator's user interface 500D, and processor 500A is for run time version.Electronic controller is also depicted as and comprises transmission/reception port 500C, for example vehicle CAN bus.Can also arrange that user interface 500D starts and this system of stopping using, allow user manipulate specific setting or input to controller 500, and see the information about system operation.
Electronic controller 500 typically comprises the storage 500B of at least some forms.The example of storage 500B comprises computer readable medium.Computer readable medium comprises can be by any available media of processor 500A access.As example, computer readable medium comprises computer readable storage medium and computer readable medium of communication.
Computer readable storage medium is included in volatile and non-volatile, the erasable and not erasable medium in any device that is configured to the information of storing, realized, and described information is for example computer-readable instruction, data structure, program module or other data.Computer readable storage medium includes but not limited to: random access memory, ROM (read-only memory), electro-erasable programmable ROM (read-only memory), flash memories or other memory technology, compact disc read-only memory, digital universal disc or other optional storage, cassette, tape, disk storage or other magnetic storage device, or can be used for storing information needed and can be by any other medium of processor 500A access.
Computer readable medium of communication typically comprises other data in computer-readable instruction, data command, program module or molded data-signal, for example carrier wave or other transmission mechanism, and comprise any information transmitting medium.Term " molded data-signal (modulated data signal) " represents a kind of signal, its one or more characteristic settings or change into coded message in signal.As example, computer readable medium of communication comprises wired medium, and for example cable network or straight line connect, and wireless medium, for example sound, radio frequency, infrared rays and other wireless medium.Above-mentioned any combination is also contained in the scope of computer readable medium.
Electronic controller 500 is also depicted as the I/O with some, and it can be used to carry out the operator scheme of required power converting unit 15.For example, electronic controller 500 provides output, for instruction expander bypass valve 202, compressor bypass valve 204, and for example, for control-driven system 90 (, startup and inactive clutch 93 and/or drive motor 91).Similarly, the input that electronic controller 500 receives for controlling power converting unit 15, for example, from the input of the pressure transducer 206 of the upstream of expansion gear 20, from the input of the pressure transducer 208 in expansion gear downstream, and via multiple other input of vehicle CAN bus.Being also pointed out that the parts of above-described controller 500 can be embodied as a part for main vehicle operating SC system controller simply, must not be independent controller.
In operation, expander bypass valve 202 can be controlled as the pressure difference set point keeping across expansion gear 20, and it is to measure by the difference between the pressure signal from sensor 206 and 208 receptions.Across the pressure difference of expansion gear 20 directly corresponding to the torque being produced by expansion gear 20.In addition, the operation of expander bypass valve 202 allows the back pressure in power plant exhausting air to be controlled as, and makes can not produce too much back pressure by expansion gear 20, and too much back pressure will cause the remarkable Efficiency Decreasing of power plant 16.Similarly, compressor bypass valve 204 can be operating as and allow entering air and being transferred back to the entrance of compression set 50 of excess compression, thereby avoids the excessive pressurization of intake manifold 13.In the time that compressor bypass valve 204 is opened completely, the ability of the pressure reduction of the formation cross-pressure compression apparatus 50 of compression set 50 is greatly diminished, and this also has the effect of the brake horsepower that reduces compression set 50.
As previously described, clutch 93 can be engaged or separate.In the time that clutch 93 is separated, compression set 50 can not be driven by power plant 16.Therefore,, in the time that clutch 93 is separated, compression set 50 is only driven by expansion gear 20.This operator scheme (for example can be suitable for situation that power plant move under constant load, vehicle operates with cruising speed on highway), and be only just enough to drive compression device 50 by expansion gear 20 from the available waste heat of power plant 16.
In the time that clutch 93 is engaged, compression set 50 can be driven by power plant 16.In the time that compression set 50 is driven by power plant 16, can be opened to reduce for the bypass valve 202 of expansion gear 20 parasitic loss being caused by expansion gear 20.Alternately, as previously mentioned, can between expansion gear 20 and compression set 50, clutch be set so that device 20,50 is disengaged.Also possibly, expansion gear 20 and 16 the two while of power plant provide power to compression set 50.Equally, in the time that expansion gear 20 can produce than the required more power of compression set, or in the time that compression set 50 does not need to compress, clutch 93 can keep engaging, and the too much power being produced by expansion gear 20 can be passed and for example, get back to power plant 16 via drive system 90 (, the belt 16c of pulley 91,16b and connection) through compression set 50.Bypass valve 204 can be operating as, and makes transitions smooth by drive system 90 drive compression devices 50 with between by expansion gear 20 drive compression devices 50.Above-described control and configuration have increased power band (power band) scope, and by this power band scope, compression set 50 can be operating as raising engine power, thereby increase engine performance and efficiency.
Detailed explanation and accompanying drawing are to support of the present invention and description, but scope of the present invention is only defined by the claims.Although described some optimal modes and other mode of execution for the invention of execution requirements protection in detail, had multiple alternate design and mode of execution for being implemented in invention defined in the appended claims.
Claims (26)
1. integral compressor and an expander system, comprising:
Fluid compression engine, this fluid compression engine has the first and second contactless helical toothing rotors, and wherein, the first rotor has the blade of some, equals to be located at the quantity of the second epitrochanterian blade; And
Positive displacement energy recycle device, this positive displacement energy recycle device has the third and fourth contactless helical toothing rotor, and wherein, third trochanter has the blade of some, equals to be located at the quantity of the blade on fourth trochanter;
Wherein, be connected to the first and second rotor operation of displacement fluid compressor the third and fourth rotor of positive displacement energy recycle device, make the rotation of the third and fourth rotor cause the rotation of the first and second rotors.
2. integral compressor as claimed in claim 1 and expander system, wherein, the first rotor and third trochanter are installed to shared axle.
3. integral compressor as claimed in claim 1 and expander system, wherein, further comprises:
The first rotor is mounted to the first axle on it;
Third trochanter is mounted to the 3rd axle on it; And
Connect the transmission of power Transmitted chains of the first axle and the 3rd axle.
4. integral compressor as claimed in claim 3 and expander system, wherein:
Described transmission of power Transmitted chains comprises the first driving gear that is mounted to the first axle and the second driving gear that is mounted to the 3rd axle.
5. integral compressor as claimed in claim 4 and expander system, wherein:
The first driving gear engages with the second driving gear.
6. integral compressor as claimed in claim 3 and expander system, wherein:
Described transmission of power Transmitted chains comprises planetary gear set, and this planetary gear set comprises ring gear, is mounted to the sun gear of the first axle, and multiple planetary pinion, and described multiple planetary pinions are attached to the shared support that is installed on the 3rd axle.
7. integral compressor as claimed in claim 6 and expander system, wherein, further comprise: with the generator that the ring gear operability of planetary gear set is connected, this generator is configured to: the rotational speed that changes energy recycle device with respect to the rotational speed of displacement fluid compressor.
8. integral compressor as claimed in claim 6 and expander system, wherein, generator is operating as break, to change the rotational speed of energy recycle device, and wherein, in the time that generator provides zero braking force, the idle running of positive displacement energy recycle device, thereby be reduced in the resistance from positive displacement energy recycle device on displacement fluid compressor.
9. integral compressor as claimed in claim 1 and expander system, wherein, further comprises: one of pulley or gear drive, it is configured to be independent of positive displacement energy recycle device and receives the torque from power source, with rotary displacement type fluid compression engine.
10. integral compressor as claimed in claim 9 and expander system, wherein, further comprises: the electric drive unit that is configured to rotary compressor.
11. 1 kinds of power generation systems, comprising:
Use the power plant of power generation circulation, wherein, these power plant use oxygen to produce power, and produce the by-product of exhausting air as power generation circulation;
Displacement fluid compressor, this displacement fluid compressor has the first and second contactless meshing rotors, and the stream that is configured to produce the relatively high pressure fluid that comprises oxygen is to be supplied to power plant, wherein, the first rotor has the blade of some, equals to be located at the quantity of the second epitrochanterian blade;
Positive displacement energy recycle device, this positive displacement energy recycle device has the third and fourth contactless meshing rotors, and is configured to be rotated with drive compression machine, wherein by exhausting air, third trochanter has the blade of some, equals to be located at the quantity of the blade on fourth trochanter;
Transmission of power Transmitted chains between compressor and energy recycle device, wherein, the transmission of torque that this Transmitted chains is configured to energy recycle device to produce is to compressor.
12. power generation systems as claimed in claim 11, wherein, described transmission of power Transmitted chains is one of gear train and common shaft, described common shaft extends between displacement fluid compressor and positive displacement energy recycle device.
13. power generation systems as claimed in claim 12, wherein, described power plant are fuel cells.
14. power generation systems as claimed in claim 12, wherein, transmission of power Transmitted chains is the gear train that comprises planetary gear construction.
15. power generation systems as claimed in claim 14, wherein, this gear train comprises:
The first and second timing gear, it is fixed with respect to the first and second meshing rotors respectively, and is configured to prevent the contact between the first and second rotors; And
The third and fourth timing gear, it is fixed with respect to the third and fourth meshing rotors respectively, and is configured to prevent the contact between the third and fourth rotor; And
Wherein, the first and second timing gear are operatively connected to the third and fourth timing gear via planetary gear construction.
16. power generation systems as claimed in claim 15, wherein, further comprise: with the generator that planetary gear construction operability is connected, this generator is configured to change the rotational speed of energy recycle device, so that the rotational speed of power plant and energy recycle device is mated substantially.
17. power generation systems as claimed in claim 16, wherein, generator is operating as break, to change the rotational speed of energy recycle device, and wherein, in the time that generator provides zero braking force, energy recycle device idle running, thereby be reduced in the resistance from energy recycle device on compressor.
18. power generation systems as claimed in claim 17, wherein, these power plant are internal combustion type (IC) motors.
19. power generation systems as claimed in claim 18, wherein, further comprise: one of pulley or gear drive, it is configured to receive torque and the rotary compressor from IC motor.
20. power generation systems as claimed in claim 11, wherein, further comprise: the electric drive unit that is configured to rotary compressor.
21. 1 kinds of power converting units, comprising:
Power plant, these power plant receive air inlet and produce exhaust;
Fluid compression engine, this fluid compression engine is configured to provide the air inlet of pressurization to power plant;
Energy recycle device, this energy recycle device is attached to fluid compressing device, and the transformation of energy that is configured to the in the future exhaust of ultromotivity device is the rotating energy of driving fluid compression set; And
Drive system, this drive system is attached to fluid compressing device the power outgoing position of power plant, and this drive system comprises clutch, so that fluid compressing device engages with the power outgoing position selectivity of power plant; And
Compressor bypass valve, this compressor bypass valve is configured to make the air inlet of pressurization to be recycled to the entrance of fluid compression engine from the outlet of fluid compression engine.
22. power converting units as claimed in claim 21, wherein, this power converting unit at least has the first operator scheme and the second operator scheme:
The first operator scheme comprises that the clutch of drive system is disengaged, so that fluid compression engine separates from the power outgoing position of power plant;
The second operator scheme comprises that the clutch of drive system is engaged, to connect the power outgoing position of fluid compression engine and power plant.
23. power converting units as claimed in claim 22, wherein, further comprise:
Exhaust by-pass valve, this exhaust by-pass valve is configured to allow at least a portion exhaust of power plant to get around energy recycle device, and this exhaust by-pass valve is configured to keep the exhaust pressure reduction set point across energy recycle device.
24. power converting units as claimed in claim 24, wherein:
The first operator scheme also comprises that exhaust by-pass valve is in an open position.
25. power converting units as claimed in claim 22, wherein:
Described power converting unit is configured to, in the time that compressor bypass valve is opened completely, and in the first operator scheme, the power outgoing position by the transmission of power from energy recycle device to power plant.
26. power converting units as claimed in claim 22, wherein:
Described compressor bypass valve is configured to: in the time that power converting unit is converted to the first operator scheme from the second operator scheme, described compressor bypass valve is opened.
Applications Claiming Priority (2)
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| US201361787834P | 2013-03-15 | 2013-03-15 | |
| US61/787,834 | 2013-03-15 |
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| CN201420232275.3U Expired - Fee Related CN204060909U (en) | 2013-03-15 | 2014-03-17 | Integral compressor and expander system, power generation systems and power converting unit |
| CN201410190416.4A Pending CN104047706A (en) | 2013-03-15 | 2014-03-17 | Integrated volumetric energy recovery and compression device |
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| CN201420232275.3U Expired - Fee Related CN204060909U (en) | 2013-03-15 | 2014-03-17 | Integral compressor and expander system, power generation systems and power converting unit |
Country Status (4)
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| US (1) | US20160003045A1 (en) |
| EP (1) | EP2971510A1 (en) |
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|---|---|---|---|---|
| GB8925018D0 (en) * | 1989-11-06 | 1989-12-28 | Surgevest Limited | A rotary fluid device |
| US7488164B2 (en) | 2005-05-23 | 2009-02-10 | Eaton Corporation | Optimized helix angle rotors for Roots-style supercharger |
| WO2012108868A1 (en) * | 2011-02-10 | 2012-08-16 | Ingersoll-Rand Company | Compressor system including gear integrated screw expander |
-
2014
- 2014-03-14 EP EP14716198.8A patent/EP2971510A1/en not_active Withdrawn
- 2014-03-14 WO PCT/US2014/029223 patent/WO2014144701A1/en active Application Filing
- 2014-03-17 CN CN201420232275.3U patent/CN204060909U/en not_active Expired - Fee Related
- 2014-03-17 CN CN201410190416.4A patent/CN104047706A/en active Pending
-
2015
- 2015-09-15 US US14/854,319 patent/US20160003045A1/en not_active Abandoned
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105065266A (en) * | 2015-08-02 | 2015-11-18 | 衢州市易凡设计有限公司 | Compressor with sintered screw shaft |
| CN105569818A (en) * | 2016-02-03 | 2016-05-11 | 北京汽车股份有限公司 | Internal combustion engine exhaust gas utilizing device and automobile |
| CN105569818B (en) * | 2016-02-03 | 2018-01-16 | 北京汽车股份有限公司 | Engine exhaust gas utilizes device and automobile |
| CN106870659A (en) * | 2017-03-22 | 2017-06-20 | 山东潍坊鲁中拖拉机有限公司 | A kind of stepless speed variation device |
| CN110630476A (en) * | 2019-10-11 | 2019-12-31 | 上海孟宝机电工程有限公司 | Energy-efficient air compressor unit circulation system |
| CN110630476B (en) * | 2019-10-11 | 2024-05-03 | 上海孟宝机电工程有限公司 | Efficient energy-saving air compressor unit circulation system |
| CN113653687A (en) * | 2021-07-14 | 2021-11-16 | 天津科技大学 | Energy conversion module and rotary hydraulic converter thereof |
| CN113653687B (en) * | 2021-07-14 | 2023-09-22 | 天津科技大学 | Energy conversion module and rotary hydraulic converter thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2971510A1 (en) | 2016-01-20 |
| US20160003045A1 (en) | 2016-01-07 |
| WO2014144701A1 (en) | 2014-09-18 |
| CN204060909U (en) | 2014-12-31 |
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Application publication date: 20140917 |