CN1688795A - Apparatus, method and software for use with an air conditioning cycle - Google Patents
Apparatus, method and software for use with an air conditioning cycle Download PDFInfo
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Abstract
A turbine (21) used to generate electricity comprises a rotor (23) and at least one nozzle (22), wherein, the rotor (23) is positioned in a rotor chamber, and the nozzle (22) with a nozzle outlet is used to provide fluid to drive the rotor (23). At least one flow interrupter (7, 11) periodically interrupts the outflow of the fluid from the nozzle outlet (12) in order to increase the pressure of the fluid in the nozzle (22). Two turbines (21) can be used in a thermal circuit, the first turbine is positioned at the downstream of a compressor while being positioned at the upstream of a heat exchanger, and the second turbine is positioned at the downstream of an evaporator while being positioned at the upstream of the compressor.
Description
Technical field
Turbo machine that the present invention relates to heat pump, uses with heat pump and/or the generator that uses with heat pump, and the present invention especially, but not only relate to modified model refrigerating method or air-conditioning (air conditioning) method and equipment, and relate to turbo machine and/or the generator that is used for it.
Background technique
Current refrigeration cycle is put into hot type in the atmosphere.In some cases, can from circulation, reclaim a part otherwise, thereby improve whole efficiency the energy that is discharged.
Fig. 1 illustrates the graphic representation of the heat pump circuit of prior art.Heat, high pressure coolant enter the throttling device that is commonly called the Tx valve, and this throttling device is with low its pressure and temperature of constant enthalpy drop.The heat absorption steam is by heat exchanger or " vaporizer ", and this heat exchanger is from being blown over its surperficial environment temperature absorption of air heat by fan, cooling air, thus refrigeration is provided and its is expanded.The heat that obtains makes the liquid flash evaporation become steam and expands.
Then, the process fluid vapor of drawing heat enters accumulator, and the internal structure of this designed accumulator can make any remaining liq be gasified before entering compressor.
The high energy thermal technology enters compressor as fluid steam, utilizes input work (work input), this steam of this compressor compresses, thus its temperature and pressure is raise.Effective input work of importing this compressor partly is reproduced as the heat of compression, thus overheated process fluid vapor.
Therefore, the temperature of overheated process fluid vapor is elevated to more than the ambient, then, enters condenser, the similar of this structure of condenser and vaporizer.Then, in overheated process fluid vapor and be between the environment of low temperature heat exchange takes place.Heat exchange is proceeded, and up to remove enough heats from working fluid, causing from the heat steam state-transition is the hot liquid state.
Hot working solution enters reservoir, and this reservoir is commonly called " trap ", and its volume is enough big, can support the requirement of thermodynamic cycle and can bear high pressure in the discharge pipe of compressor.Then, the thermal high coolant enters the TX valve, thereby finishes thermodynamic cycle.
Many main cities in the world, air-conditioning system have become the huge person of benefiting from of electric power, and it is counted as the substantial section of many heavy constructions to keep certain environment controlling level in building.Meanwhile, because the quantity of air-conditioning system continues to increase, recognize that gradually electric power is limited resources, and supply falls short of demand in some place, perhaps supply falls short of demand in the near future in prediction.
Importantly, find the potential field of saving power consumption.If can on air-conditioning system, realize economize on electricity, then may totally save a large amount of power consumption.
The upgrading that economize on electricity also might be saved power distribution infrastructure.In order to handle the rise and peak load that causes because of the air-conditioning market that increases rapidly, this upgrading is essential.
Summary of the invention
A purpose of the preferred embodiment of the present invention provides a kind of equipment and/or a kind of current heat pump that can improve the utilization ratio of the useful power in this equipment that is used for heat pump.
Another purpose of the preferred embodiment of the present invention provides a kind of method of controlling heat pump, and is current, and this method can improve the efficient of this equipment.
Another purpose of the preferred embodiment of the present invention provides a kind of method of controlling turbo machine and generator, and is current, and this method can improve the efficient of this equipment.
Another purpose of the preferred embodiment of the present invention provides a kind of turbo machine and/or a kind of method that makes fluid be sent to turbo machine, and current, this method can improve the utilization ratio of the useful power in this fluid.
Another purpose is to be at least the public a kind of useful selection is provided.
According to the following explanation that only provides as an example, other purpose of the present invention is conspicuous.
According to a first aspect of the invention, provide a kind of turbo machine that is used to generate electricity, having comprised: rotor chamber; Rotor can rotate around axis in described rotor chamber; At least one ozzle comprises tube nozzle outlet, is used for fluid is delivered to described rotor from fluid source, thereby drives described rotor and generating; At least one tap hole in use, is used for discharging described fluid from described turbo machine;
Wherein
At least one flows the outflow of the described fluid of interrupting device periodic interruptions from described at least one tube nozzle outlet, thereby the pressure of the described fluid in described at least one outer ozzle is raise.
This turbo machine preferably includes at described fluid source and described at least one fluid storage device between the ozzle outside at least one.
Described at least one stream interrupting device preferably stops the outflow of described fluid from described at least one tube nozzle outlet substantially, and the pressure in described at least one ozzle is elevated to the preliminary election minimum pressure, and this preliminary election minimum pressure is lower than or equals the pressure of fluid source.
When using this turbo machine, described at least one interrupting device preferably made from the sufficiently long period of described flow disruption of the described fluid of described at least one ozzle outflow, thereby made the described fluid of the upstream of just arriving described at least one outer ozzle static substantially.
Described rotor preferably has a plurality of passages, this passage by moulding, locate and be processed into the size that needs, with when the refrigeration agent from described at least one ozzle enters described passage, form moment of rotation around described axis.
Described rotor preferably has a plurality of wheel blades, this wheel blade by moulding, locate and be processed into the size that needs, with when the refrigeration agent from described at least one ozzle contacts described wheel blade, form moment of rotation around described axis.
Described at least one interrupting device preferably includes at least one blade, this at least one blade can link to each other with the periphery of described rotor and therewith motion, and basic during at described at least one blade near described at least one tube nozzle outlet, it is suitable for interrupting the outflow that described fluid exports from described at least one outer ozzle.
Described stream interrupting device preferably includes a plurality of described blades that evenly separate basically around the described periphery of described rotor.
Described turbo machine preferably includes in heat pump circuit, and wherein said fluid source is a positive displacement compressor.
The capacity of described fluid storage device preferably equals the discharge capacity of described positive displacement compressor at least.
Described at least one tap hole preferably includes diffuser and expander part, reducing the speed of described fluid, in case and it decelerate to subsonic velocity, just keep the pressure of this fluid.
In use, described at least one ozzle is preferably delivered to described rotor with the velocity of sound or ultrasound velocity with described fluid.
According to a second aspect of the invention, provide a kind of fluid that is used for that the fluid source device is provided to be sent to the method for turbine rotor with the pressure of fluid source device, this method comprises: at least one ozzle is set, be used to make the described fluid that flows out from described fluid storage device to be sent to described turbine rotor, thereby drive described rotor, this method comprises that further at least one is set flows interrupting device, periodically to interrupt of the outflow of described fluid from described at least one ozzle, thereby make the pressure of the described fluid in described at least one ozzle be elevated to the preliminary election minimum pressure, then, recover the outflow of described fluid from described at least one ozzle, this preliminary election minimum pressure is lower than or equals the pressure of described fluid source device.
Described preliminary election minimum pressure preferably is enough to make this fluid to reach local sonic speed (local sonic velocity) in the throat of this ozzle.
This method preferably includes and makes the fluid that flows out from described at least one ozzle accelerate to ultrasound velocity.
According to a third aspect of the invention we, provide a kind of turbo machine, this turbo machine comprises: rotor comprises the rotor winding of two or more a plurality of separation; And stator, comprise a plurality of staor winding around described rotor, wherein at least two described staor winding are connected to controllable current source, and each controllable current source can move the staor winding to encourage it to be connected.
Each controllable current source is operation respectively preferably, after reaching predetermined speed at rotor, encourages the staor winding that it connects.
Predetermined speed is the final velocity under the current operating conditions of turbo machine preferably.
Preferably according to the numerical value of the power of staor winding output, each current source raises respectively or reduces electric current by its corresponding staor winding.
According to a forth aspect of the invention, provide a kind of method that is used to control turbo machine, this turbo machine comprises: rotor comprises the rotor winding of two or more a plurality of separation; And stator, comprise a plurality of staor winding around described rotor, wherein at least two described staor winding are connected to controllable current source, each controllable current source can move the staor winding to encourage it to be connected, this method comprises the power of duplicate measurements staor winding output, if the current numerical value of output power is greater than the previous numerical value of output power, electric current by this winding is raise, if and the current numerical value of output power then makes the electric current by this winding reduce less than the previous numerical value of output power.
According to a fifth aspect of the invention, provide a kind of thermodynamic cycle, this thermodynamic cycle comprises: compressor; First turbo machine is positioned at the compressor downstream; Heat exchanger is positioned at the downstream of first turbo machine, and can move so that this circuit heat is discharged in another thermodynamic cycle; Vaporizer is positioned at the downstream of heat exchanger; And second turbo machine, be positioned at the downstream of vaporizer, and be positioned at the upstream of compressor.
According to a sixth aspect of the invention, provide a kind of thermodynamic cycle, this thermodynamic cycle comprises: compressor; Condenser is positioned at the downstream of compressor; First turbo machine is positioned at the downstream of condenser; Vaporizer is positioned at the downstream of first turbo machine; And second turbo machine, be positioned at the downstream of vaporizer, and be positioned at the upstream of compressor.
This thermodynamic cycle preferably further comprises the heat exchanger between described first turbo machine and described vaporizer, and this heat exchanger operation is so that heat is discharged to another thermodynamic cycle.
First turbo machine and second turbo machine are preferably according to the described turbo machine of earlier paragraphs.
According to the arbitrary described thermodynamic cycle of claim 21 to 24, wherein first and second turbo machines are according to the described turbo machine of earlier paragraphs.
According to a seventh aspect of the invention, provide a kind of control system that is used for thermodynamic cycle, this thermodynamic cycle comprises compressor, and this control system comprises:
Detection device is used to provide the numerical value of the output of this thermodynamic cycle;
Control gear is used for this compressor, and wherein control gear is communicated by letter with described detection device, with the numerical value of the input work of the described numerical value of the output that receives this thermodynamic cycle and this compressor, as input;
Wherein control gear can move, and with the numerical value according to described input computational efficiency, and changes the speed of this compressor, thereby it is the highest that the described numerical value of efficient is elevated to, and perhaps makes the described numerical value of efficient remain on predeterminated level.
This control system preferably further comprises: second control device is used for TX valve or equivalent; And detection device, be used to provide the numerical value of the temperature of control zone, wherein second control device receives the described numerical value of the temperature of control zone, as another input, and second control device operation, with the variation of the temperature of the control zone detected of response, open or close TX valve or equivalent with respect to target value.
As input, second control device preferably further receives the numerical value of the quantity that is illustrated in the refrigeration agent in this circulation of gasifying after this circuit evaporation stage, and after evaporation stage, open or close TX valve or equivalent, to keep the refrigeration agent of gasification.
Be preferably in the temperature variation that responds described detection from control gear and open or close the TX valve and begin through after the predetermined delay, the operation second control device is to keep the vaporizing system cryogen after evaporation stage.
This control system preferably further comprises the 3rd control gear of the condenser that is used for this thermodynamic cycle, and this control system changes the operation of condenser so that condenser with refrigerant cools to the level that requires.
This control system is preferably moved controlling turbo machine according to claim 17, and this control system comprises the 4th control gear, is used for the direct current that control flows is crossed the staor winding of described turbo machine.
This control system is preferably moved, and crosses the direct current of staor winding with control flows, thereby when loading, makes described turbo machine keep transient equiliblium.
Control gear, second control device, the 3rd control gear and the 4th control gear are a microcontroller or microprocessor or a plurality of microcontroller or microprocessor, wherein microcontroller or the microprocessor of selecting at least communicated by letter mutually, manages with the timing to each function block of control system.
According to an eighth aspect of the invention, provide a kind of method that is used to control turbo machine, this turbo machine comprises: rotor comprises the rotor winding of two or more a plurality of separation; And stator, comprise a plurality of staor winding around described rotor, wherein at least two described staor winding are connected to controllable current source, each controllable current source can move the staor winding to encourage it to be connected, this method comprises regulates the electric current that flows through this winding, so that described rotor keeps transient equiliblium.
According to the following explanation of only being done with reference to the accompanying drawings as an example, the others of the present invention that should be counted as belonging to the whole novelties of the present invention aspect will become more obvious.
Description of drawings
Fig. 1 illustrates the thermodynamic cycle of prior art.
Fig. 2 illustrates first thermodynamic cycle according to one aspect of the invention.
Fig. 3 illustrates second thermodynamic cycle according to one aspect of the invention.
Fig. 4 illustrates the sectional view according to first turbo machine of one aspect of the invention.
Fig. 5 illustrates the sectional view according to second turbo machine of one aspect of the invention.
Fig. 6 illustrates the enlarged view of turbo machine passage shown in Figure 5.
Fig. 7 illustrates the 3rd thermodynamic cycle according to the control system of one aspect of the invention.
Fig. 8-10,12 illustrates the flow chart that is used to control the method for thermodynamic cycle according to one aspect of the invention.
Figure 11 illustrates the schematic representation according to the generator of one aspect of the invention.
Figure 13 illustrates the flow chart of the initialization subroutine of control system.
Figure 14 illustrates the flow chart of the scheduling sublayer routine of control system.
Embodiment
At this, will the present invention be described with reference to its application in refrigeration cycle.Those skilled in the art understand that described heat pump is sent the road back to can have various application, for example, and air-conditioning, refrigeration or heating.Those skilled in the art understand that also term " refrigeration agent " is used for description and is suitable for this loop or any working fluid of circuit.
The simple refrigerating circuit of prior art shown in Figure 1 can comprise in proper order: compressor, condenser, trap (receiver), throttle valve (TX valve), vaporizer and accumulator (accumulator).Some embodiment of prior art can be a device with two unit combination shown in Figure 1, and for example, some compressor can also comprise accumulator, but the function of each unit will appear in this loop usually.
At this, it is the device of kinetic energy and/or electric energy that term " turbo machine " is used for describing the power conversion that is used for liquid stream.Those skilled in the art understand that in the place of the energy that requires electric form, turbo machine can comprise suitable generator or alternator.
Then, with reference to figure 2, heat-pump apparatus of the present invention comprises first refrigerant circuit 10, and it comprises in proper order: first compressor 1, condenser 8, trap 2, TX valve, vaporizer 5 and turbo machine 21.Turbo machine 21 is kinetic energy and/or electric energy with the power conversion in the refrigeration agent, thereby reduces the temperature and pressure of first refrigeration agent.If this turbo machine is required to produce the refrigeration agent of suitable density and pressure, then can the expander (not shown) be set in one of the upstream side of turbo machine 21 and downstream side or the two.
In certain embodiments, turbo machine 21 can be designed to prevent that refrigerant cools is to forming the degree that liquid refrigerant drips, because may destroy the working surface of turbo machine 21 like this in this turbo machine 21.In conversion embodiment, for example,, can improve turbo machine 21, thereby allow condensating refrigerant, and not destroy turbo machine 21 by using suitable durable material structure rotor wheel blade.
Those skilled in the art understand, the quality influence of the refrigeration agent by first vaporizer 5 flows into the heat of first vaporizer 5.The refrigeration agent that flows out from first vaporizer 5 passes through first accumulator 6, then, returns first compressor 1.Those skilled in the art understand that trap 2 and accumulator 6 provide the refrigeration agent reservoir in this loop.Utilize accumulator 6 expressions that slightly illustrate to constitute the optional part of the part of compressor 1.
With reference to figure 3, Fig. 3 illustrates according to replacement heat pump of the present invention, and it comprises first refrigerant circuit 300 and second refrigerant circuit 400.In a preferred embodiment, second refrigerant cycle 400 can comprise vaporizer 405, accumulator, compressor, condenser, trap and TX valve (not shown), they are arranged with the order identical with the refrigerating circuit of prior art, and carry out essentially identical function.The boiling point of second refrigeration agent can be lower than 10 ℃, more preferably is about 0 ℃.Suitable second refrigeration agent can be R22, R134A or R123, but those skilled in the art are clear, also can use to have suitably lower boiling other refrigeration agent.
Utilization can be controlled second refrigerant cycle 400 below with reference to the control system that Fig. 7 describes.If desired, can utilize two refrigerant circuits of single controller control.
In a preferred embodiment, the temperature of refrigeration agent that enters the condenser of refrigerant circuit 400 can be higher than 30 ℃, and preferably is about 60 ℃.The temperature of refrigeration agent that enters the vaporizer of refrigerant circuit 400 is at least 10 ℃, is lower than the temperature of the refrigeration agent that enters condenser 304.
In certain embodiments, in order to produce electricity, one or more thermoelectric generator between compressor and condenser can be set.If employed refrigeration agent is R123, then thermoelectric generator is particularly useful, because condensing temperature can be up to 180 ℃, and evaporating temperature is between 35 ℃ and 10 ℃, and therefore, the temperature difference is big.
In order to reduce the density of the working fluid that enters turbo machine 302, and in order to help after working fluid is got back to subsonic velocity, keep low pressure at the output terminal of turbo machine 302, can comprise expander at the input end and the output terminal of turbo machine 302.In a preferred embodiment, expander can be guaranteed, in case this fluid decelerates to subsonic velocity, the pressure of this fluid just no longer raises.Otherwise if there is not expander, the pressure of turbo machine output terminal can raise, and destroys the performance of turbo machine.
Can also comprise the expander (not shown) at one of the input end of second turbo machine 306 and output terminal or the two.If refrigeration agent is recycled to outside the turbo machine 306 with ultrasound velocity, then this expander comprises diffuser.Enter at working fluid before the throat of turbo machine ozzle, be positioned at the essential density that reduces this working fluid of expander of the input end of turbo machine 302,306.When working fluid was in the velocity of sound, lower density allowed bigger throat dimension, and therefore kept critical minimum quality flow rate, thereby prevented that air-conditioner efficiency from reducing.Ideal situation is, the mass flowrate that this mass flowrate should stand when each turbo machine not being introduced thermodynamic cycle respectively is identical.Therefore, the volumetric expansion before the ozzle reduces the density of working fluid, and allows the large diameter ozzle of use throat, and does not weaken subsonic speed/supersonic speed transition or the mass flowrate at the working fluid of throat.
Replace in the circulation at two other, can omit refrigerant circuit 400 and condenser 304 the two one of.
Fig. 4 illustrates suitable with the turbo machine 21 that uses in conjunction with Fig. 1,2,3 heat-pump apparatus of describing.Turbo machine 21 can also be used for the prior art refrigerant circuit in all loops as shown in Figure 1, and perhaps other refrigerant circuit preferably immediately following in the upstream or the downstream of compressor, if desired, has the expander that is provided with around turbo machine 21.Turbo machine 21 comprises an outer ozzle 22 at least, and this outer ozzle 22 is installed on the shell (not shown) of turbo machine 21, has to be suitable for making the refrigeration agent that flows through it to accelerate to the velocity of sound or supersonic convergent/flaring part.
Below, with its part explanation turbo machine 21 as aforesaid heat pump circuit, on this heat pump circuit, working fluid is a refrigeration agent.Except generating, turbo machine 21 can also be realized the function of TX valve, and therefore, the TX valve can be omitted in this loop.Those skilled in the art understand that turbo machine 21 also has other application, and in these embodiments, and working fluid can be certain other suitable gaseous fluid.
Interrupting device periodically interrupts the outflow of ozzle 22 outside each.The following describes two preferred interrupting devices.Technician in the correlative technology field can find to be used to interrupt the alternate means from the outflow of outer ozzle 22.
First interrupting device can comprise one or more blade 7, and this blade 7 is positioned near the periphery of turbine rotor 23, and exports at this blade 7 at 12 o'clock near outer ozzle, and it is suitable for preventing substantially that refrigeration agent is from outer ozzle 22 outflows.Technician in the correlative technology field understands, Fig. 4 amplifies the outlet of outer ozzle 22 and the gap between the blade 7 are shown, and actual gap is enough little, when the close tube nozzle outlet 12 of blade 7, can interrupt or significantly forbids from the outflow of ozzle 22.
Second interrupting device 11 can comprise that being positioned at outer ozzle exports near 12 electronic control valves.Second interrupting device 11 can have the response that is exceedingly fast, and, for example, can carry out and electronically controlled common rail diesel engine oil sprayer similar operation.
Refrigeration agent storage 13 can be positioned at outer ozzle inlet 14 near.If refrigeration agent being delivered to the compressor of outer ozzle 22 is positive displacement compressors, then the internal volume of refrigeration agent storage 13 equals a discharge capacity (displacement) of first compressor at least.Refrigeration agent storage 13 can have the big any capacity of discharge capacity of ratio piston compressor.Refrigeration agent storage 13 preferably is positioned near the adiabatic spherical container the outer ozzle inlet 14 as far as possible.
The blade 7 and second interrupting device 11 can make the mobile of refrigeration agent stop efficiently and effectively, thereby the adiabatic pressure in the outer ozzle 22 is raise, and not corresponding increase enthalpy.Can make the sufficiently long period of flow disruption of refrigeration agent, so that the pressure in the outer ozzle 22, and better make the pressure in the refrigeration agent storage 13 that the low preliminary election minimum pressure of pressure that provides than first compressor is provided.Can select this pressure to guarantee that when blade 7 and second interrupting device 11 are all opened refrigeration agent flows out from outer ozzle 22 with the velocity of sound or ultrasound velocity.
The period that each blade 7 stops the outflow of outer ozzle 22 is depended on the girth of turbine rotor 23, the rotating speed and blade 7 length in a circumferential direction of rotor 23.In certain embodiments, this period long enough can not need second interrupting device 11.
In other embodiments, second interrupting device 11 can fully promptly cut out, and can not need blade 7, but in many cases, blade 7 only is provided with better simply interrupting device, and this simple interrupting device can be to cut out outer ozzle outlet 12 at a high speed.
Refrigeration agent storage 13, blade 7 and second interrupting device 11 help to increase the energy that obtains from refrigeration agent, still make enough flow of refrigerant simultaneously, to absorb enough heats from refrigerant circuit.Be convenient to like this or help from refrigerating circuit to omit trap and TX valve.
The applicant believes, when the interruption device is closed, outside ozzle 22 and can be reduced to 0 to the mass flow of the working fluid between the high-voltage power supply of 22 feed flows of ozzle outside this (being refrigeration agent in this case), in most of the cases, this high-voltage power supply is first compressor, and the pressure in refrigeration agent storage 13 and the outer ozzle inlet 14 can be elevated to the maximum pressure of the discharge pipe of first compressor.This unlifting pressure departs from the function of reduction of the mass flowrate that is this fluid.If mass flowrate is 0, the pressure reduction between then outer ozzle 22 two ends is 0 substantially, and therefore, the pressure of outer ozzle inlet 14 is maximum pressures, and the variation of the kinetic energy in the refrigeration agent is 0, and enthalpy change is 0.Therefore, when refrigeration agent stopped, the pressure of outer ozzle inlet 14 was elevated to the peak that compressor provides, and enthalpy change is 0.The applicant also believes, if compare with the time that allows flow of refrigerant, the interrupted period of refrigeration agent is short, and then turbo machine 21 is deterioration minimums of the total mass flow on the refrigerant circuit of the parts on it.
The applicant also believes, the advantage that the mass flow that flows through outer ozzle 22 is stopped is, raises if the period of flow disruption is enough short and the pressure of refrigeration agent is adiabatic basically, and enthalpy change does not take place then outer ozzle 22 interior static refrigeration agents.In addition, if the expansion of the rising compensation quality of the internal energy of and refrigeration agent compressed time durations static at refrigeration agent stream refrigeration agent during flowing time and power consumption thereof (this can realize by the correct time of flow of refrigerant and the ratio of interrupted time of refrigeration agent selected), then the enthalpy leaching process is continuous basically.The applicant believes that will cause comparing the enthalpy that extracts from working fluid with prior art system like this increases.
Those skilled in the art understand that also the treatment device (not shown) can be controlled the timing of second interrupting device 11.This treatment device can be from any appropriate device, but preferably receives information about the position, angle of turbine rotor 23 from the hall effect sensor etc. that is installed on the turbine casing (not shown), is used for the suitable scale mark (index mark) on the detection rotor 23.By changing opening the time of second relay 11, this treatment device can also change the speed of turbine rotor 23.
Although shown turbine rotor 23 has pusher vane construction, but the applicant finds that aforesaid relay also is particularly suitable for using with other radial-flow turbine design, for example, the radial-flow turbine design that automobile turbocharger uses, as shown in figure 11.
Now, with reference to figure 5, Fig. 5 illustrates and replaces turbine rotor 23A, and it has a plurality of portal roughly spirality channels 602 of 603 of central row of guiding to.Central row is portalled 603 can be at the center of rotor 23A, and extends in the central axis direction of rotor 23A basically.The sectional area of each passage 602 can continue to reduce between inlet 604 and outlet 605.
The area of inlet 604 preferably is 6: 1 with the ratio of the area of outlet 605 basically, so that under the situation that working fluid stream is had minimum restriction, help hypersonic work.
Then, with reference to figure 6, the center line 606 of each passage 602 at least respectively in inlet 604 and outlet 2: 608 between 605,609 and the radius 607 of rotor 23A crossing.
By entering the mouth 604, the fluid stream that arrow F represents can inlet passage 602.Because the direction of fluid F changes on passage 602, so the variation of the momentum of fluid F can produce rotating force to rotor 23A.Any other suitable mechanism that this rotating force can preferably be delivered to suitable generator or can be driven by rotating shaft.On the direction in passage 602, the variation near 180 ° preferably takes place as far as possible in fluid F, so that the variation of momentum increases to maximum, and therefore makes this energy be applied to rotor 23A.
Rotor 23A can use with aforesaid electronics second interrupting device, but those skilled in the art understand that in certain embodiments, the spacing 610 between the feeder connection 604 can be used as interrupting device.
Fig. 7 illustrates the air conditioning/refrigerating circulation that utilizes arrow 100 expressions according to a further aspect of the present invention usually.
Identical with circulation 300 shown in Figure 3, circulation 100 is with the air-conditioning of prior art or the difference of refrigeration cycle, can economizes slightly the TX valve and the trap that respectively circulate common of prior art.Utilize turbo machine 114 to replace the TX valve, in this embodiment, it is between condenser 105 and vaporizer 122.Optional thermoelectric generator 103 can be positioned at before the condenser 105.
The secondary heat pump circulation of arrow 200 expressions contains heat exchanger 201, it is in the back of expander 114c, and can 100 remove heats from once circulating, thereby the temperature and pressure of working fluid of guaranteeing to enter vaporizer 122 is enough low, effectively works can make vaporizer 122.Secondary cycle contains all main heat pump components of describing and has with reference to the figure 7 and the 100 additional controls of describing that circulate here in prior art circulation 10 shown in Figure 1.
By compressor discharge pipe 102, pressurized working fluid is discharged from compressor 101 with the gas phase form basically, then, enters thermoelectric generator 103, perhaps through to condenser 105.Thermoelectric generator 103 (if existence) can produce low-voltage direct output 103a, and by DC-DC converter 104, this low-voltage direct output 103a is transformed to high pressure output 104a.
The heat that condenser 105 is removed on the working fluid.By the heat that the speed controlling of the condenser fan 106 of condenser 105 blow air is discharged.Variable speed drive 107 can be determined the speed of condenser fan 106, by communication link 108, and main variable speed drive 109 control variable speed drive 107.Variable speed drive 107 comprises the suitable software of the speed that is used to control condenser fan 106.
Main variable speed drive 109 can comprise thermocouple input end 110,111 and 112, the information of the temperature (T4) of the air of discharging with the temperature (T2) of the refrigeration agent that temperature (T1) about the refrigeration agent that enters vaporizer is provided respectively, flows out from vaporizer and from vaporizer.Another thermocouple (T4a) and pressure transducer 115 can be measured the temperature and pressure of the working fluid that enters turbo machine 114.
Enter the temperature and pressure of working fluid of turbo machine and the temperature of the selection in this circulation by measurement, software on the main variable speed drive 109 can utilize software to look into the density that enters the working fluid of turbo machine 114 with the table estimation, then, regulate the speed of compressor 101 and/or condenser fan 106 and/or evaporator fan 126, to guarantee that this speed is enough low, the gas of can make throat by convergent/flaring ozzle 117, delivering to turbo machine 114 is in the velocity of sound substantially.Expander 114a further reduces the density of the working fluid that enters turbo machine 114.
Flaring part at ozzle 117 can continue to make the velocity of sound working fluid that flows out from turbo machine ozzle throat to quicken, and reaches ultrasound velocity up to it.
High speed operation fluid driven turbin machine rotor.By suitable connection 120, turbo machine can drive load 121, for example, and generator.
In ozzle 117, preferably make working fluid accelerate to the velocity of sound or ultrasound velocity, can reduce its temperature and pressure like this.Then, by flowing through turbo machine 114, remove energy from working fluid.
By expander 114, the mixture of the high-speed low temperature working fluid of gas phase and liquid phase flows into vaporizer 122, and when working fluid slowed down, this expander 114 was used to prevent that the pressure of working fluid from raising, and like this, utilizes turbo machine 114 to remove kinetic energy from it.If desired, expander 114c can also contain diffuser 114b, to enter at working fluid before the expander 114c, makes the speed of working fluid be reduced to subsonic velocity.
Main variable speed drive 109 can be controlled the speed of compressor 101, to optimize its coefficient of performance (COP), will do general description below, controls but will omit the TX valve, because 100 deleted the TX valve from circulating.
If turbo machine 114 drives generator 121, then this generator 121 can be an once-through type, or AC type.This generator 121 is the high tension direct current generator of 670 voltage magnitude output voltages preferably.In the preferred case, by diode and electric capacity buffer circuit, DC power output 114B can be coupled to the dc bus 109B of main variable speed drive 109, this diode and electric capacity buffer circuit can only make electric power flow with a direction, can prevent that like this power 150 from feeding back to generator 121.
Those skilled in the art understand, owing to control to optimize overall performance coefficient, the energy efficiency height of above-mentioned air-conditioning circuit energy effciency ratio prior art by the energy of turbo machine and thermoelectric generator (when using) recovery and to compressor speed.
Fig. 8 to 10 illustrates a series of illustrating and is used for air-conditioning circulation, for example, at this in conjunction with Fig. 1,2,3,7,8 circulations of describing and the flow chart that comprises the example of the computational process of the present invention that other circulation of circuit of prior art is controlled if desired.Can utilize its control to export these processes of control such as any suitable microcontroller of the drive signal of the electric machine controller that can control compressor, microprocessor.For the sake of brevity, in the following description, suppose to use microcontroller.
With reference to figure 8, when powering up, perhaps before carrying out control algorithm, can carry out initialization routine, need initialization if carry out specific control algorithm, then in this initialization routine, usually by zero setting, initialization selection marker, register and counter.
With reference to Figure 13, Figure 13 illustrates the flow chart of possible initialization subroutine.Input external devices (for example, compressor, TX valve, condenser, generator excitation) is used the time lag of (service)/optimization as DEL1 to DELn.For the specific heat pump of being controlled, determine to look into table, then, input is in the specific temperature difference ((T1-T3) (1) to (T1-T3) (the n)) clauses and subclauses of the target capabilities coefficient (COP3 to COPn) of the heat pump of work down at the vaporizer two ends.
Microprocessor can read switch SW1 state.Switch SW 1 points out whether microcontroller dispatches the use/optimization of heat pump Control Parameter automatically.Can also read the current state of sign, counter and the register of any requirement, then initialization they.
Then, according to the temperature difference of input ((T1-T3) (1) to (T1-T3) (n) and be used for the relevant target capabilities coefficient COP3 to COPn of heat pump uses/optimizations, formation is looked into showing (please refer to following content).At last, according to the state of switch SW 1, the still sign of automatic operation is pointed out manually in microcontroller set.
The temperature T 2 of the temperature T 1 of the refrigeration agent of microcontroller reception inflow evaporator, the refrigeration agent of outflow vaporizer and compressor electric motor power KW1 are as input.Also import the motor speed increment K2 of requirement of thermal load setting value T3, compressor and the motor speed decrement K3 and the air-conditioning refrigerant constant K1 of requirement.Utilize experimental technique, K1 is determined in specific air-conditioning circulation, K1 represents the heat increment that the every degree temperature variation between T1 and the T2 promotes.
After receiving these inputs, microcontroller calculates the difference between T1 and the T3.Then, utilize this difference from the looking into searching the respective performances coefficient of this heat pump the table of storage, wherein the coefficient of performance is represented the heat of the specific work lifting imported.
In conversion embodiment, replace COP work according to target, if this circuit COP is not only along with the speed of computer improves, then microcontroller can improve/reduce the speed of compressor, to bring up to COP the highest.Technician in the correlative technology field also knows, if desired, can also use the variable outside the temperature difference at vaporizer two ends.
If T1-T3 is less than or equal to 0, then heat pump is not worked, and microcontroller no longer works, and it returns the initial state of this algorithm.If T1-T3 greater than 0, then calculates based on the variable T1, the T2 that measure and the actual performance coefficient COP2 of KW1 according to equation 1:
COP2=K1|T1-T2|/KW1 equation 1
If desired, can also use circuit output other measured value relevant with the input work of compressor.As mentioned above, when being easier to obtain measured temperature, the preferred embodiment of current imagination uses the differential temperature survey value to measure the efficient heat that this system transmits.Yet, can use system's output and compressor to import the replacement measured value of relevant systematic function.
Then, coefficient of performance COP2 and the target capabilities coefficient COP1 that is calculated compared.If the value of COP1 less than COP2, then makes the speed of compressor improve K2.On the contrary, if target COP1 greater than the COP2 that is calculated, then makes the speed of motor reduce K3.Then, carry out delay subroutine (not shown), so that consider any hysteresis from this round robin to the speed that changes compressor.By with increment K2 and K3 forced adjustment compressor speed and measure air-conditioning circulation and return the required maximum duration of equilibrium condition, can utilize experimental technique to determine required time lag.Can utilize any suitable delay subroutine to realize this delay.Can be after having changed any one controlled variable, and before analyzing and changing another controlled variable, finish the delay subroutine, keep stable and/or guarantee to utilize equilibrium condition to guarantee this system, the measured value of each input is provided to control algorithm.Can between each control circle, have under the situation of appropriate time delay,, periodically carry out control algorithm continuously with predetermined time interval perhaps according to scheduling.
Fig. 9 illustrates when being provided with the TX valve in heat pump, the schematic diagram of the control algorithm of the operation of control TX valve.This control algorithm can also be applied to carry out with the TX valve any controllable devices of same or similar functions.
Controller receives from the constant T5 of the superheat temperature value of the temperature addition of the working fluid of the output terminal of the unsaturated temperature T 4 of the air of vaporizer outflow and expression and vaporizer and imports as temperature.It also receives the setting step-length K4 and the K5 with decrement operations of increasing progressively of the measured value of current state of pressure input P1, TX valve or equivalent TX1 of pressure of working fluid of expression vaporizer output terminal and TX valve respectively.
Microcontroller calculate as T4 and T5's and T6, then, calculate T7 as the product of P1 and constant K 6, be convenient to pressure is transformed to the temperature of working fluid like this.If temperature T 6 is lower than T7, then make the TX valve open increment K4, and if temperature T 6 greater than T7, then make the TX valve close increment K5.Otherwise the TX valve keeps its current state.The increment step-length may optionally be identical (K4=K5) with the decrement step-length.Then, carry out the delay subroutine,, make this circulation reach stable state, perhaps near stable state with before taking any other action.
If the setting of TX valve changes, then advantageously verification TX valve is still in work, so that after the vaporizer quilt is fully overheated, the interior refrigeration agent of the suction line of compressor is in gaseous state.Therefore, call when postponing subroutine after changing the TX valve, microcontroller can add verification to the operation of TX valve at every turn.Do not exist if control as the operational limit to the TX valve of the part of TX valve, if perhaps existing control algorithm is limited in the acceptable range of operation TX valve, then verification is essential.
If the aperture of the speed of compressor and TX valve changes, then the operation of condenser also changes.Therefore, this controller can also be controlled driving condenser fan.Figure 10 illustrates this process.
Temperature input to this algorithm is T1 and the T3 that as above determines; At the predetermined point of heat pump, usually immediately following the point after condenser, the liquid line temperature T 8 of measurement; And the target temperature T10 of liquid line temperature.The increment step-length K7 of condenser fan speed and the decrement step-length K8 of condenser fan speed and current condenser fan speed CFS1, condenser fan minimum speed CFSmin and condenser fan maximum speed CFSmax also are the inputs of this algorithm.Although the step-length of not shown use CFSmin and CFSmax among Figure 11, the allowable speed of the value limit compression machine fan of CFSmin and CFSmax.
Microcontroller at first calculates the T11 as the difference between T3 and the T1, then, if T3 is greater than or equal to T1, then stops the condenser fan speed control algorithm.If T3 is less than T1, heat is extracted in then this circular flow, and condenser.Then, microcontroller calculates the T12 as the difference of T10 and T8, then, if target temperature T10 less than true temperature T8, the current rotating speed CFS1 rising K7 of compressor then, and if T10 greater than T8, the current rotating speed CFS1 reduction K8 of compressor then.After the operation that has changed condenser fan, call another time lag.
Microprocessor can also change the timing of second relay 11, to optimize the selection parameter of each refrigerant circuit respectively.In certain embodiments, the heat that vaporizer absorbs can be to select parameter, and in other embodiments, the total output that is input to one or more compressor can be to select parameter.
Figure 14 illustrates the schematic diagram of the control algorithm that is used to dispatch control algorithm/optimized Algorithm described here.The time parameter table is stored in the storage, and when this time parameter table regulation carries out various algorithms.Can import this time parameter table by the heat pump caretaker.When powering up, pointer is set to the initial value of this time parameter table, then, picks up counting.This time parameter table is listed in proper order: all control algorithms; The time lag variable is used to point out in each time lag that should experience between this control algorithm of carrying out; And the address, be used to point out in storage, where can find this control algorithm.
Microcontroller reads the current time of real-time clock, then, makes the time lag addition of pointing out in it and the time parameter table, thereby provides current service time.Then, read this current service time, and it and real-time clock are compared.This process continues circulation around loop, with for every kind of algorithm, contrasts current verification real time service time, reaches the current service time of algorithm up to real-time clock.When this situation occurring, microprocessor withdraws from this loop, from the time parameter table, reads the initial address of this algorithm, then, carries out this algorithm.After having carried out this algorithm, microprocessor returns the loop that utilizes " returning " expression among Figure 14.
The rotor of heat pump generator can be with high rotation speed operation.For example, can design generator and heat pump, so that rotor is with 15000rpm or higher speed rotation.In order under high rotating speed, to keep the performance of generator, need make rotating part (turbo machine, rotor, main shaft and bearing arrangement) balance.In addition, rotor and generator being sealed in can avoid in the refrigerant cycle taking place transmitting generation loss of circuit power and integrity problem by main shaft.In addition, if use fixedly magnet rotor, then sensitive balance has become difficulty because center on the rotor of this outfit and the magnetic field of ferromagnetic component is energized, and if shock load be applied to this generator, then the power of Chan Shenging may make rotor unbalance.
Generator of the present invention comprises rotor nonmagnetic and that be not magnetized.For example, can produce this rotor by Lycore 150 electric furnace steel plates (electrical sheet steel).Be arranged on the electric field of epitrochanterian coil control rotor radiation, this coil is wrapped on the high permeability F5 ferrite clavate coil carrier.Can use other suitable material.
The turbine components of very close rotor and the shell of this rotor all can be by the suitable constructed in plastic material that can bear the strong stress that generator is applied.Therefore, these parts do not disturb the electric field that electric field that rotor produces or the staor winding that is energized produce.Staor winding is wrapped on the ring-shaped core of this plastic casing.This ring-shaped core can be Lycore 150 electric furnace steel plates, perhaps the high permeability ferrite coil frame of the specially-shaped of F5 ferrite or equivalent more preferably.
Figure 11 A-D illustrates the turbogenerator that utilizes arrow 500 expressions usually.Whole generating machine 500 can be sealed in the air-conditioning circulation.Figure 11 A illustrates the plan view of turbogenerator 500, wherein for the sake of clarity, unload lower cover plate, and Figure 11 B illustrates the sectional view by the line BB among Figure 11 A.Turbogenerator 500 comprises: turbine casing 501; Stator supporting shell 502 is used to support stator 504; And cover plate 503A-D.Figure 11 C and 11D illustrate the sectional view by timberline CC of Figure 11 B institute and DD respectively.Turbo machine 505 is arranged in the turbine casing 501, and this turbo machine 505 comprises rotor 506 and is remained on the ozzle 507 of appropriate location by ozzle retainer 508.By inlet duct 509, refrigeration agent is sent to ozzle 507.Generator amature 510 comprises 4 rotor coil 511-514 that are used to form four utmost point rotors 510.What can also make coil 511-514 respectively holds short circuit together, perhaps with the resistive element that temperature raises they is linked together by its impedance/resistance, to provide the restriction electric current with the protection rotor coil.For example, can utilize the copper cash of 1mm to form this coil, and this coil twine 135 circles around the F5 of 19mm ferrite coil frame.Yet, technician in the correlative technology field understands, can be according to requirement to generator 500, change the winding and the space between the staor winding of the quantity of the winding on generator amature 510 and the stator 504, the iron core that is used for this winding, generator amature 510 and be arranged on number of poles on the generator amature 510.Turbine rotor 506 preferably has the relay of as above describing with reference to figure 4, and can have at this with reference to figure 4 or 5 vane constructions of describing.
Can be with the form of the adjacent group of two or more a plurality of windings, each winding of the stator 504 that connects up together.For four utmost point rotors 510, the interchange of every group of winding output is connected to 90 degree another group winding at interval.Each is organized winding and is connected respectively to controlled DC generator (not shown), and this controlled DC generator can turn round, to provide Constant Direct Current by staor winding.Capacitor makes each winding and DC generator and exchanges output and isolate.The utilization son that rotates produces the right direct current of north and south poles alternately, and winding is respectively organized in excitation, and the north and south poles that replaces is to having the intervals of 90 degree, and wherein same electric field is right mutually with the intervals of 180 degree.Therefore, around rotor 510, electric field is a balance, and if desired, can respond the detected any imbalance of run duration, regulates this electric field, to proofread and correct any imbalance on the rotor 510.Other staor winding does not have DC generator to be connected to them.As an example, 18 groups of coils altogether can be arranged on the stator, wherein 4 are connected to DC generator.If desired, 2, winding more than 3 or 4 can be connected to DC generator.
Can periodically put upside down the polarity of direct current, not be subjected to permanent magnet bias to guarantee the ferromagnetic component on the turbo machine 500.
The turbo machine of prior art has running speed characteristic and torque characteristics fixing and that can not control under the situation of destructive characteristics not.Yet turbo machine 500 of the present invention can dynamically be controlled the field intensity of exciting field, thereby changes the characteristic of generator, and therefore, turbo machine 500 can be with optimal speed and torque operation, to operate in the preset parameter scope.About being applied to the turbo machine in the heat pump described here, turbo machine 500 of the present invention can be used to keep the ultrasound velocity operation.
When turbo machine 500 reaches its final velocity, activate DC generator, thereby make the staor winding that is connected to generator produce electric field, when rotor 510 rotations, in the coil of rotor 510, produce Ac like this.Then, produce Ac in staor winding, this Ac is sent to the output terminal of generator.Can carry out rectification to this interchange output, and if this generator constitute the part of heat pump, then can utilize this energy to provide a part of electric power to the compressor in the heat pump.
Figure 12 illustrates the schematic diagram of the control algorithm of staor winding.Raised speed at rotor 510, and when presenting direct current, adopted control algorithm shown in Figure 12 by staor winding.Measure the total current output IT and the total voltage output VT of stator.This can electric current be exported I1 to In and voltage output V1 to Vn realizes by every group of staor winding measured.Utilize the product of IT and VT, calculate total output output.Output of this total output and previous power output are compared.If previous power output, then makes the predetermined step-length of direct current rising by staor winding less than current power output.If previous power output greater than current power output, then makes the current DC by staor winding reduce predetermined step-length.Those skilled in the art understand that algorithm shown in Figure 12 can be used to control a plurality of target generators.
In the superincumbent description, each specific features of the present invention or the integral body with known equivalents is illustrated, but can comprises these equivalents, as they are set separately at this.
Although utilize example with reference to its possibility embodiment, describe the present invention,, obviously, under the situation that does not break away from the described scope of the invention of claims, can carry out various modifications or improvement to it.
Claims (34)
1, a kind of turbo machine that is used to generate electricity comprises:
Rotor chamber;
Rotor can rotate around axis in described rotor chamber;
At least one ozzle comprises tube nozzle outlet, is used for fluid is delivered to described rotor from fluid source, thereby drives described rotor and generating;
At least one tap hole in use, is used for discharging described fluid from described turbo machine;
Wherein
At least one flows the outflow of the described fluid of interrupting device periodic interruptions from described at least one tube nozzle outlet, thereby the pressure of the described fluid in described at least one outer ozzle is raise.
2, turbo machine according to claim 1 comprises at described fluid source and described at least one fluid storage device between the ozzle outside at least one.
3, turbo machine according to claim 1 and 2, wherein said at least one stream interrupting device stops the outflow of described fluid from described at least one tube nozzle outlet substantially, pressure in described at least one ozzle is elevated to the preliminary election minimum pressure, and this preliminary election minimum pressure is lower than or equals the pressure of fluid source.
4, according to the arbitrary described turbo machine of claim 1 to 3, wherein in use, described at least one interrupting device makes described fluid interrupt the sufficiently long period from the outflow of described at least one ozzle, thereby makes the described fluid of the upstream of just arriving described at least one outer ozzle static substantially.
5, according to the arbitrary described turbo machine of claim 1 to 4, wherein said rotor has a plurality of passages, this passage by moulding, locate and be processed into the size that needs, with when the refrigeration agent from described at least one ozzle enters described passage, form moment of rotation around described axis.
6, according to the arbitrary described turbo machine of claim 1 to 4, wherein said rotor has a plurality of wheel blades, this wheel blade by moulding, locate and be processed into the size that needs, with when the refrigeration agent from described at least one ozzle contacts described wheel blade, form moment of rotation around described axis.
7, according to the arbitrary described turbo machine of claim 1 to 6, wherein said at least one interrupting device comprises at least one blade, this at least one blade can link to each other with the periphery of described rotor and therewith motion, and basic during at described at least one blade near described at least one tube nozzle outlet, it is suitable for interrupting the outflow that described fluid exports from described at least one outer ozzle.
8, turbo machine according to claim 7, wherein said stream interrupting device comprise a plurality of described blades that evenly separate basically around the described periphery of described rotor.
9, according to the arbitrary described turbo machine of claim 1 to 8, in the time of in being included in heat pump circuit, wherein said fluid source is a positive displacement compressor.
10, turbo machine according to claim 9, based on claim 2 time, the capacity of wherein said fluid storage device equals the discharge capacity of described positive displacement compressor at least.
11, according to claim 9 or 10 described turbo machines, wherein said at least one tap hole comprises diffuser and expander part, reducing the speed of described fluid, in case and it decelerate to subsonic velocity, just keep the pressure of this fluid stream.
12, according to the arbitrary described turbo machine of claim 9 to 11, wherein in use, described at least one ozzle is delivered to described rotor with the velocity of sound or ultrasound velocity with described fluid.
13, a kind of fluid that is used for that the fluid source device is provided is sent to the method for turbine rotor with the pressure of fluid source device, this method comprises: at least one ozzle is set, be used to make the described fluid that flows out from described fluid storage device to be sent to described turbine rotor, thereby drive described rotor, this method comprises that further at least one is set flows interrupting device, periodically to interrupt of the outflow of described fluid from described at least one ozzle, thereby make the pressure of the described fluid in described at least one ozzle be elevated to the preliminary election minimum pressure, then, recover the outflow of described fluid from described at least one ozzle, this preliminary election minimum pressure is lower than or equals the pressure of described fluid source device.
14, method according to claim 13, wherein said preliminary election minimum pressure are enough to make this fluid to reach local sonic speed in the throat of this ozzle.
15, method according to claim 14 comprises making the fluid that flows out from described at least one ozzle accelerate to ultrasound velocity.
16, a kind of turbo machine comprises: rotor comprises the rotor winding of two or more a plurality of separation; And stator, comprise a plurality of staor winding around described rotor, wherein at least two described staor winding are connected to controllable current source, and each controllable current source can move the staor winding to encourage it to be connected.
17, turbo machine according to claim 16, wherein each controllable current source can move, and after reaching predetermined speed at rotor, encourages the staor winding that it connects.
18, turbo machine according to claim 17, wherein predetermined speed is the final velocity under the current operating conditions of turbo machine.
19, according to the arbitrary described turbo machine of claim 16 to 18, wherein according to the numerical value of the power of staor winding output, each current source raises respectively or reduces electric current by its corresponding staor winding.
20, a kind of method that is used to control turbo machine, this turbo machine comprises: rotor comprises the rotor winding of two or more a plurality of separation; And stator, comprise a plurality of staor winding around described rotor, wherein at least two described staor winding are connected to controllable current source, each controllable current source can move the staor winding to encourage it to be connected, this method comprises the power of duplicate measurements staor winding output, if the current numerical value of output power is greater than the previous numerical value of output power, electric current by this winding is raise, if and the current numerical value of output power then makes the electric current by this winding reduce less than the previous numerical value of output power.
21, a kind of thermodynamic cycle comprises: compressor; First turbo machine is positioned at the compressor downstream; Heat exchanger is positioned at the downstream of first turbo machine, and can move so that this circuit heat is discharged in another thermodynamic cycle; Vaporizer is positioned at the downstream of heat exchanger; And second turbo machine, be positioned at the downstream of vaporizer, and be positioned at the upstream of compressor.
22, a kind of thermodynamic cycle comprises: compressor; Condenser is positioned at the downstream of compressor; First turbo machine is positioned at the downstream of condenser; Vaporizer is positioned at the downstream of first turbo machine; And second turbo machine, be positioned at the downstream of vaporizer, and be positioned at the upstream of compressor.
23, thermodynamic cycle according to claim 22 further comprises the heat exchanger between described first turbo machine and described vaporizer, and this heat exchanger operation is so that heat is discharged to another thermodynamic cycle.
24, according to the arbitrary described thermodynamic cycle of claim 21 to 23, wherein first and second turbo machines are the arbitrary described turbo machines according to claim 1 to 11.
25, according to the arbitrary described thermodynamic cycle of claim 21 to 24, wherein first and second turbo machines are the arbitrary described turbo machines according to claim 17 to 20.
26, a kind of control system that is used for thermodynamic cycle, this thermodynamic cycle comprises compressor, this control system comprises:
Detection device is used to provide the numerical value of the output of this thermodynamic cycle;
Control gear is used for this compressor, and wherein control gear is communicated by letter with described detection device, with the numerical value of the input work of the described numerical value of the output that receives this thermodynamic cycle and this compressor, as input;
Wherein control gear can move, and with the numerical value according to described input computational efficiency, and changes the speed of this compressor, thereby it is the highest that the described numerical value of efficient is elevated to, and perhaps makes the described numerical value of efficient remain on predeterminated level.
27, control system according to claim 26 further comprises: second control device is used for TX valve or equivalent; And detection device, be used to provide the numerical value of the temperature of control zone, wherein second control device receives the described numerical value of the temperature of control zone, as another input, and second control device operation, with the variation of the temperature of the control zone detected of response, open or close TX valve or equivalent with respect to target value.
28, according to claim 26 or 27 described control system, wherein as input, second control device further receives the numerical value of the quantity that is illustrated in the refrigeration agent in this circulation of gasifying after this circuit evaporation stage, and after evaporation stage, open or close TX valve or equivalent, to keep the refrigeration agent of gasification.
29, according to the arbitrary described control system of claim 26 to 28, wherein opening or close the TX valve in the temperature variation that responds described detection from control gear begins through after the predetermined delay, the operation second control device is to keep the vaporizing system cryogen after evaporation stage.
30, according to the arbitrary described control system of claim 26 to 29, comprise the 3rd control gear of the condenser that is used for this thermodynamic cycle, this control system changes the operation of condenser so that condenser with refrigerant cools to the level that requires.
31, according to the arbitrary described control system of claim 26 to 30, this control system operation is to control turbo machine according to claim 17, and this control system comprises the 4th control gear, is used for the direct current that control flows is crossed the staor winding of described turbo machine.
32, control system according to claim 31, this control system operation is crossed the direct current of staor winding with control flows, thereby when loading, is made described turbo machine keep transient equiliblium.
33, control system according to claim 31, wherein control gear, second control device, the 3rd control gear and the 4th control gear are a microcontroller or microprocessor or a plurality of microcontroller or microprocessor, wherein microcontroller or the microprocessor of selecting at least communicated by letter mutually, manages with the timing to each function block of control system.
34, a kind of method that is used to control turbo machine, this turbo machine comprises: rotor comprises the rotor winding of two or more a plurality of separation; And stator, comprise a plurality of staor winding around described rotor, wherein at least two described staor winding are connected to controllable current source, each controllable current source can move the staor winding to encourage it to be connected, this method comprises regulates the electric current that flows through this winding, so that described rotor keeps transient equiliblium.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| NZ521263 | 2002-09-06 | ||
| NZ52126302A NZ521263A (en) | 2002-09-06 | 2002-09-06 | Apparatus, method and software for use with an air conditioning cycle |
| NZ521717 | 2002-09-30 | ||
| NZ523733 | 2003-01-21 | ||
| NZ524220 | 2003-02-17 |
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| Publication Number | Publication Date |
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| CN1688795A true CN1688795A (en) | 2005-10-26 |
| CN100374687C CN100374687C (en) | 2008-03-12 |
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| CNB038238101A Expired - Fee Related CN100374687C (en) | 2002-09-06 | 2003-09-05 | Apparatus, method and software for use with an air conditioning cycle |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN100374687C (en) |
| NZ (1) | NZ521263A (en) |
| ZA (1) | ZA200501739B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108692493A (en) * | 2017-04-04 | 2018-10-23 | 丹佛斯公司 | Low back pressure stream limiter |
| CN112361486A (en) * | 2020-11-16 | 2021-02-12 | 珠海格力电器股份有限公司 | Supercharging device, control method thereof and air conditioning system |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2475313A1 (en) * | 1980-02-05 | 1981-08-07 | Electricite De France | Automatic regulation of turbo-alternator sets - by sensing and processing alternator parameters, using reference circuit prior to supporting adjustable regulator |
| GB8325166D0 (en) * | 1983-09-20 | 1983-10-19 | Holset Engineering Co | Variable area turbine and control system |
| JP3080558B2 (en) * | 1995-02-03 | 2000-08-28 | 株式会社日立製作所 | Heat pump air conditioners for cold regions |
| JPH09178322A (en) * | 1995-12-22 | 1997-07-11 | Matsushita Refrig Co Ltd | Capacity control device of refrigerator |
| JP3843498B2 (en) * | 1996-08-22 | 2006-11-08 | 富士電機システムズ株式会社 | Power plant control system |
| JP3051678B2 (en) * | 1996-09-30 | 2000-06-12 | 三菱重工業株式会社 | Low temperature hydrogen combustion turbine |
| JP3679323B2 (en) * | 2000-10-30 | 2005-08-03 | 三菱電機株式会社 | Refrigeration cycle apparatus and control method thereof |
-
2002
- 2002-09-06 NZ NZ52126302A patent/NZ521263A/en unknown
-
2003
- 2003-09-05 CN CNB038238101A patent/CN100374687C/en not_active Expired - Fee Related
-
2005
- 2005-02-28 ZA ZA200501739A patent/ZA200501739B/en unknown
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108692493A (en) * | 2017-04-04 | 2018-10-23 | 丹佛斯公司 | Low back pressure stream limiter |
| CN108692493B (en) * | 2017-04-04 | 2022-03-01 | 丹佛斯公司 | Low back pressure flow limiter |
| CN112361486A (en) * | 2020-11-16 | 2021-02-12 | 珠海格力电器股份有限公司 | Supercharging device, control method thereof and air conditioning system |
| CN112361486B (en) * | 2020-11-16 | 2024-05-10 | 珠海格力电器股份有限公司 | Supercharging device, control method thereof and air conditioning system |
Also Published As
| Publication number | Publication date |
|---|---|
| NZ521263A (en) | 2005-04-29 |
| ZA200501739B (en) | 2008-10-29 |
| CN100374687C (en) | 2008-03-12 |
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