Method and device for implementation air conditioning cycle (versions)

FIELD: heating, ventilation.

SUBSTANCE: invention refers to the device and method to be used with air conditioning cycle. A turbine for power generation includes a rotor, a chamber and at least one nozzle for supply of a fluid medium to activate the rotor. Flow of the fluid medium out of the nozzle output is periodically interrupted with at least one device of the flow brake to increase fluid medium pressure inside the nozzle. In a thermo dynamic cycle two such turbines can be used; at that the first turbine is located after a compressor and before a heat exchanger, and the second turbine is located after an evaporator and before the compressor. The invention facilitates upgrading of a total efficiency owing to recuperation of a portion of energy.

EFFECT: upgraded efficiency of an air conditioning device.

31 cl, 14 dwg

 

The technical field to which the invention relates

The present invention relates to a device, method, and software for use with cycle air conditioning and, in particular, but not exclusively, to improved methods of cooling or air conditioning device and the turbines and/or generators for use according to the method.

Description of the prior art

Existing cooling cycles emit heat into the atmosphere. In some cases, part of the energy that otherwise would be discarded, can be recovered from the cycle, which thus increases the overall efficiency.

Figure 1 shows a schematic view of a heat pump circuit of the prior art. Hot liquid refrigerant under high pressure enters the throttling device, often called a throttle valve, which reduces its pressure and temperature at constant enthalpy. Absorbing the warmth of the steam passes through the heat exchanger or evaporator", absorbing heat from the air, with ambient temperature, blown by the fan through the surface of the heat exchanger, the cooling air and thus providing a cooling effect and causing its expansion. Capture the heat causes the instantaneous evaporation of the liquid rasshirenie.

Bearing heat vaporous working fluid then passes into the battery, which has an internal structure designed to ensure evaporation of any remaining liquid before it enters the compressor.

Energy-rich warm vaporous working fluid enters the compressor, which results in the carrying out of the work compresses the vapor, thus increasing its temperature and pressure. A significant part of the work consumed by the compressor is converted into heat compression, thus causing overheating of the vaporous working medium.

Overheated vaporous working medium thus has a temperature greater than ambient temperature, and enters the condenser, which has a construction similar to the construction of the evaporator. Then there is the transfer of heat between the superheated vapor working fluid and the environment, which has a lower temperature. Heat transfer continues until the working fluid does not extract enough heat to change its state and the transformation of hot steam in the hot liquid.

Hot liquid working fluid held in the reservoir, usually called "collection", which has a large enough volume to maintain the conditions of thermodynamic cycle and to withstand the high pressure in the output line of the compressor. Hot LM is some working fluid under high pressure then passes to the throttle valve to complete thermodynamic cycle.

The air conditioning systems consume huge amounts of power in many major cities around the world and are considered as an integral component of many large buildings to maintain the required level of control of the environment inside the building. At the same time, since the amount of air conditioning systems continues to grow, increasing the understanding of that a resource of electricity is limited, and in some places the demand exceeds the supply, or is expected in the near future.

It became important to identify potential areas for savings in electricity consumption. If you can achieve any savings in air conditioning systems, the potential exists an enormous total savings in electricity consumption.

Saving energy can also lead to savings in the area of capacity resources infrastructure, energy distribution. Such capacity resources are required to work with increasing peak loads, make the fast growing market of air conditioning systems.

The purpose of the invention

Objective the preferred option of the invention is to provide a device for the heat pump and/or heat pump, which will increase the efficiency of use up the available energy in an existing device.

Alternative objective the preferred option of the invention is the provision of a method of controlling a heat pump, which will increase the efficiency of such an existing device.

Alternative objective the preferred option of the invention is the provision of a method of controlling the turbine and the generator, which will increase the efficiency of such an existing device.

Another alternative objective the preferred option of the invention is the provision of a turbine and/or a method of supplying fluid to the turbine, which provides a more effective use of available energy of the fluid at the present time.

Another alternative objective is at least to provide the public with a useful choice.

Other objectives of the present invention can be understood when reading the following description which is given for example only.

Brief description of the invention

According to the first variant of the invention provided with a thermodynamic cycle including a compressor, a first turbine, located after the compressor, a heat exchanger located after the first turbine and working to extract heat from cycle to another thermodynamic cycle, the evaporator is located the village of the e heat exchanger, and the second turbine located downstream of the evaporator and to the compressor.

According to the second variant of the present invention is provided with a thermodynamic cycle including a compressor, a condenser, located after the compressor, the first turbine, located after the condenser, the evaporator, located after the first turbine and the second turbine located downstream of the evaporator and to the compressor.

Preferably thermodynamic cycle includes a heat exchanger located between the first turbine and the evaporator, the heat exchanger operates to extract heat in another thermodynamic cycle.

Preferably, at least, or the first turbine, second turbine includes:

the camera of the rotor;

the rotor rotating around the Central axis inside the chamber of the rotor;

at least one nozzle including an outlet nozzle for feeding fluid from the means for supplying fluid to a thermodynamic cycle in the rotor to actuate the rotor and power generation;

at least one outlet for release when using the fluid from the turbine;

in which the flow of fluid from at least one nozzle is periodically interrupted by at least one means for interrupting the flow, thus increasing the pressure of the fluid HV is three, at least one nozzle.

Preferably, at least, or the first turbine, second turbine includes at least one means for storing the fluid, located between the means for supplying a fluid medium and at least one nozzle.

Preferably the means for storing fluid medium has a capacity at least equal to the volume of the compressor.

Preferably, at least one means of interrupting the flow essentially stops the flow of fluid from at least one outlet nozzle, until the pressure inside the at least one nozzle is increased to a predefined minimum pressure that is less than the pressure in the means for supplying the fluid or equal to.

Preferably when using a fluid flow from at least one nozzle is interrupted by at least one interrupting means during a period of time sufficient to bring the fluid immediately before at least one outer nozzle, essentially, in the quiescent state.

Preferably the rotor has multiple channels, which have the configuration, location, and dimensions, providing a torque around the Central axis when the refrigerant from at least one nozzle is included in the channel.

Preferably the mouth of the R. has many blades, which have the configuration, location, and dimensions, providing a torque around the Central axis when the refrigerant from at least one nozzle comes in contact with the blades.

Preferably, at least one means of interrupting the flow includes at least one blade, which can be connected to an external periphery of the rotor and can move with it and adapted to interrupt flow of fluid out of the at least one outlet nozzle, when at least one blade, essentially, is adjacent to at least one output nozzle.

Preferably the means to interrupt flow includes multiple blades, essentially equally spaced around the circumference of the outer periphery of the rotor.

Preferably, at least one nozzle when using a supply of fluid in the rotor with sonic or supersonic speeds.

Preferably, at least one outlet includes diffuser and the expansion section to reduce the velocity of the fluid and maintaining the pressure of the flow of the current environment after deceleration to subsonic speed.

Preferably, at least one of the first and second turbine includes a rotor, comprising two or more spaced apart windings of the rotor and the stator, including many which of botoc stator around the rotor, moreover, at least two of the windings are connected to an adjustable current source, each adjustable current source can work for excitation of the windings of the stator, with whom he is connected.

Preferably each regulated current source can work for excitation of the windings of the stator, with which it is connected, after the rotor reaches a predetermined speed.

Preferably preset speed is the speed limit for the current operating conditions of the turbine.

Preferably, each current source provides the increase and decrease in the current in their respective stator windings depending on the measured values of power output from the stator windings.

According to another object of the present invention is provided a method of controlling thermodynamic cycle described above, including repeated measurement of the power output from the stator windings and the increasing current in the windings if the current measured value of the output power more than the preceding measured output power, and reducing the current in the windings, if the measured value of the output power is less than the preceding measured values of power output.

According to another variant of the present invention is provided a method generated by the I power of thermodynamic cycle, including a compressor, a first turbine, located after the compressor, a heat exchanger located after the first turbine and providing the extraction of heat from cycle to another thermodynamic cycle, the evaporator, located after the heat exchanger, and a second turbine located downstream of the evaporator and to the compressor, in which the first and second turbines include a rotor and at least one nozzle for feeding fluid into the rotor to actuate the rotor and power generation;

the method includes providing at least one tool flow interruption for periodically interrupting the flow of fluid from at least one nozzle and pressure increase of the current environment within the at least one nozzle to a predefined minimum pressure that is less than the pressure in the means for supplying the fluid or equal to, before the resumption of the flow of the current environment of the at least one nozzle.

According to another variant of the present invention is provided a method of generating power in a thermodynamic cycle including a compressor, a condenser, located after the compressor, the first turbine, located after the condenser, the evaporator, located after the first turbine and the second turbine located downstream of the evaporator and to the compressor, in which lane the traveler and the second turbine includes a rotor, at least one nozzle for feeding fluid into the rotor to actuate the rotor and power generation; the method includes providing at least one tool flow interruption for periodically interrupting the flow of fluid from at least one nozzle and pressure increase of the current environment within the at least one nozzle to a predefined minimum pressure that is less than the pressure in the means for supplying the fluid or equal to, before the resumption of the flow of the current environment of the at least one nozzle.

Preferably preset minimum pressure sufficient to achieve a fluid environment of the local sound speed in the critical section of the nozzle.

Preferably the method includes the acceleration of the fluid exiting the at least one nozzle to supersonic speeds.

The control system for thermodynamic cycle described above, the control system includes:

sensitive means for measuring the output power of thermodynamic cycle;

management tool for compressor and management tool communicates with the sensing means for receiving, as input, the measured values of the output power of thermodynamic cycle and the measured values of work, need to change blaenau compressor;

this management tool provides the calculation of performance measurement based on the input data and changing the speed of the compressor to maximize performance measurement or for maintenance performance measurement at the specified level.

Preferably the control system also includes a second management tool for the second turbine and sensitive tool for measuring temperature controlled area in which the second management tool takes as additional input, the measured values of the temperature controlled region and provides the opening and closing of the passage for fluid flow through the second turbine in response to detected changes of temperature in a controlled area in relation to a specified value.

Preferably the second management tool optionally accepts, as input, measured value representing the amount of refrigerant in the cycle, which evaporated after phase evaporation in a loop, and provides the opening and closing of the passage for fluid flow through the second turbine to maintain the quantity of the vaporized refrigerant after phase evaporation.

Preferably, the second control means to maintain the quantity of the vaporized refrigerant after phase evaporation is carried who is after a specified delay after opening or closing a management tool passage for the current environment through the second turbine, in response to the detected temperature change.

Preferably the control system includes a third means of control for a capacitor in a thermodynamic cycle, and the control system provides for changing the operation of the condenser to maintain the required level of cooling of the refrigerant to the condenser.

Preferably, the first control, second control and the third control is one microcontroller, or microprocessor, or many microcontrollers or microprocessors, with at least selected microcontrollers or microprocessors communicate with each other to ensure bronirovania functions of the control system.

The control system for thermodynamic cycle described above, the control system includes:

sensitive means for measuring the output power of thermodynamic cycle;

management tool for compressor in communication with the sensing means for receiving, as input, the measured values of the output power of thermodynamic cycle and the measured values of the work consumed by the compressor;

this management tool provides the calculation of performance measurement based on the input data and changing the speed of the compressor to maximize measurement is effektivnosti or to maintain performance measurement at the specified level, moreover, the control system provides for the regulation of the DC current flowing in the windings of the stator of the turbine.

Preferably the control system provides for the regulation of the DC current flowing in the windings of the stator, for dynamic balancing of the turbine under load.

Other variants of the present invention, which should be considered with all its elements of novelty, will be understood when reading the following description given as an example only with reference to the accompanying drawings.

Brief description of drawings

Figure 1 - thermodynamic cycle of the prior art.

Figure 2 - the first thermodynamic cycle, corresponding to the present invention.

Figure 3 - the second thermodynamic cycle, corresponding to the present invention.

4 is a section of the first turbine, the corresponding variant of the present invention.

5 is a cross-section of the second turbine, the corresponding variant of the present invention.

6 is a magnified view of the channel of the turbine shown in figure 5.

Fig.7 - third thermodynamic cycle showing the control system, the corresponding variant of the present invention.

Fig-10, 12 - block diagram of the sequence control method of thermodynamic cycle, appropriate options this is the first invention.

11 diagram generator, the corresponding variant of the present invention.

Fig - block diagram of the initialization routine for the control system.

Fig - flowchart subroutine planning for system management.

Brief description of preferred embodiments of the invention

The present invention is described here in relation to its application in the refrigeration cycle. Specialists in the art will understand that the described circuit of the heat pump can be used in various ways, for example, for air conditioning, cooling or heating. Specialists in the art also will understand that the term "refrigerant" is used to describe any working fluid suitable for use in such circuit or loop.

A simple refrigeration cycle prior art, shown in figure 1, may include, in order, a compressor, a condenser, a collection, a throttle valve, an evaporator and an accumulator. In some embodiments, a prior art two of the elements shown in figure 1, can be combined into a single device, for example, some compressors may also include a battery, but the operation of each element usually occurs in the circuit.

The term "turbine" is used here to describe devices that convert the duty to regulate the energy of the fluid flow in the kinetic and/or electrical energy. Specialists in the art will understand that when energy is required in electric form, the turbine may include the electricity generator or an AC generator.

As shown in figure 2, the heat pump device corresponding to the present invention, includes a first refrigerant circuit 10, which includes on the order of the first compressor 1, a condenser 8, a battery 2, a throttle valve, an evaporator 5 and the turbine 21. Turbine 21 converts the energy of the refrigerant in the kinetic and/or electrical energy, thus reducing the temperature and pressure of the first refrigerant. If you want to get to the turbine refrigerant density and pressure on one or both of the front and rear sides of the turbine 21 can be placed expander (not shown).

In some embodiments of the invention, the turbine 21 may be arranged so as to prevent cooling of the refrigerant to the point at which the inside of the turbine 21 drops of liquid refrigerant, as they may damage the surfaces inside the turbine 21. In alternative embodiments, the turbine 21 may be adapted, for example, through the use of an appropriately solid materials for rotor blades, to ensure the condensation of the refrigerant without damaging the turbine 21.

Specially Islam in the art will understand, what qualities of the refrigerant passing through the first evaporator 5, will adversely affect the heat flow into the first evaporator 5. The refrigerant emerging from the first evaporator 5, passes through the first battery 6 before returning to the compressor 1. Specialists in the art will understand that the battery 2 and the battery 6 are reservoirs for the refrigerant circuit. The battery 6 is shown by a dashed line to indicate that it may form part of the compressor 1.

Figure 3 shows an alternative embodiment of the heat pump corresponding to the present invention, which includes a first refrigerant circuit 300 and the second refrigerant circuit 400. In a preferred embodiment of the invention the second refrigerant circuit 400 may include an evaporator 405, battery, compressor, condenser, collection and throttle valve MV (not shown)located in the same manner and performs essentially the same functions as in the cooling circuit of the prior art. The second refrigerant may have a boiling point component is less than 10°C, more preferably about 0°C. Suitable second refrigerant may be a refrigerant brands R22, R123, R134A or, although specialists in the art will understand that can be used with other refrigerants with suitable and low boiling points.

The second refrigerant circuit 400 can be controlled by a control system described below with reference to Fig.7. If required, both the refrigerant circuit can be controlled by one controller.

In a preferred embodiment of the invention the temperature of the refrigerant entering the condenser of the refrigeration circuit 400 can be more than 30°and preferably about 60°C. the temperature of the refrigerant entering the evaporator of the refrigeration circuit 400 may be at least 10°C lower than the temperature of the refrigerant entering the condenser 304.

In some embodiments of the invention between the compressor and the condenser may be located one or more thermoelectric generators to generate electricity. Thermoelectric generators can be especially useful if used refrigerant is the refrigerant brand R123, since the condensing temperature can reach 180°and the evaporation temperature between 35°and 10°providing greater temperature difference.

The circuit 300 includes, in order, clockwise compressor 301, capacitor 307, the first extender a, the first turbine 302, the second extender 302b, the heat exchanger 304, the evaporator 305 and the second turbine 306.

On both, the input and output sides of the turbine 302 in the circuit can be included the s extenders to reduce the density of the working fluid, coming into the turbine 302, and to maintain a low pressure at the outlet of the turbine 302 after returning the working fluid to subsonic speed. In a preferred embodiment of the invention, the extender can provide no increase in pressure of the fluid after its deceleration to subsonic speeds. Without using the expander pressure could increase and degrade the performance of the turbine.

Dilators (not shown) can also be included in the circuit on one or both of the inlet and outlet of the second turbine 306. The extenders will include a diffuser, if the refrigerant circulates supersonic speeds outside of the turbine 306. The extenders on the inputs turbines 302, 306 required to reduce the density of the working fluid before entering the critical section of the nozzle of the turbine. Lower density will provide a larger critical section at the point of the sound velocity of the working fluid and, consequently, to maintain a critical minimum specific mass flow rate to eliminate any reduction in the efficiency of air conditioning. In the ideal case, the specific mass flow rate must be the same what you would expect without the inclusion of each turbine thermodynamic cycle. Volumetric expansion in front of the nozzle, thus, reduces the density of the working fluid and lets you the th critical section of larger diameter without compromising the transition of the working fluid from subsonic to supersonic speed in the critical section or its specific mass flow.

In the other two alternative cycles or refrigeration cycle 400, or the capacitor 304 can be omitted.

Figure 4 shows a turbine 21, and suitable for use with heat pump device described in relation to figures 1, 2, 3. Turbine 21 can also be used in the cooling circuit of the prior art, such as the circuit shown in figure 1, or in another cooling circuit, preferably, or directly to the compressor, or immediately after it, using, if necessary, extenders, located near the turbine 21. Turbine 21 includes at least one outer nozzle 22 mounted in the housing (not shown) of the turbine 21, which has a converging/diverging section adapted to accelerate the refrigerant passing through it, until sonic or supersonic speeds.

The turbine 21 is described below in connection with its use as part of a heat pump circuit, such as described above, in which the working fluid is a refrigerant. Turbine 21 can perform the function of the throttle valve th in addition to generating electricity, allowing you to exclude from the path of the throttle valve th. Specialists in the art will understand that other choices are possible applications of the turbine 21 and that the working fluid in these embodiments may be any other suitable the th gaseous fluid medium.

The flow from each of the outer nozzle 22 periodically interrupts interrupting means. Below are described two preferred terminating means. Specialists in the art will be able to discover alternative means to interrupt flow from the outer nozzle 22.

First terminating means may include one or more blades 7 are located near the outer periphery of the rotor 23 of the turbine and adapted to essentially prevent the refrigerant from the external nozzle 22 when the blade 7 is located near exit 12 of the outer nozzle. Specialists in the art will understand that the gap between the output of the external nozzle 22 and the blades 7 is increased by 4 and that the actual gap will be small enough to interrupt or significant deterrence flow from the nozzle 22 when the blades 7 are adjacent to the outlet nozzle 12.

Second terminating means 11 may include an electronic valve, located near the outlet opening 12 of the outer nozzle. Second terminating means 11 can have a very fast response and can operate, for example, like electronic diesel injectors in the common rail.

The tank 13 for storing the refrigerant can be located near the external input 14 of the nozzle. If the compressor that supplies the refrigerant in the outer nozzle 22, is a volumetric compressor, reserves the Varos 13 for storing the refrigerant may have an internal volume, at least equal to the working volume of the first compressor. The tank 13 for storing the refrigerant can have any more capacity than the working volume of the compressor. The tank 13 for storing the refrigerant, preferably, can be isolated spherical container located as close as possible to the external input 14 of the nozzle.

The blades 7 and the second terminating means 11 can stop the refrigerant flow fast enough to create growth adiabatic pressure in the outer nozzle 22 without a corresponding increase in enthalpy. The refrigerant flow can be interrupted for a period of time that is long enough to ensure that the pressure inside the outer nozzle 22 and more preferably within the tank 13 for storing the refrigerant has reached a predefined minimum pressure that is less than the pressure supplied to the first compressor. This pressure can be set to ensure that, when both blades 7, and the second terminating means 11 are in the open position, the refrigerant exits the outer nozzle 22 with sonic or supersonic speeds.

The period of time during which each vane 7 stops the flow from the outer nozzle 22, depends on the length of the circumference of the rotor 23 of the turbine, the rotational speed of the rotor 23 and the length of the blade 7 in the circumferential direction. Not what which embodiments of the invention, this time period can be quite long, to the second terminating means 11 is not required.

In other embodiments of the invention, the second interrupting means can provide closing fast enough blade 7 is not needed, but in many cases the blades 7 can be a relatively simple terminating tool, which is able to close the outlet opening 12 of the outer nozzle at high speed.

The tank 13 for storing the refrigerant, the blades 7 and the second terminating means 11 can increase the amount of energy extracted from the refrigerant, and can still allow the passage of sufficient refrigerant to ensure adequate overall effect of the absorption of heat from the refrigerant circuit. This may facilitate or assist the exception of the refrigerant circuit of the collection and the throttle valve th.

It should be noted that, when interrupting means is closed, the mass flow rate of the working fluid, in this case, the refrigerant between the outer nozzle 22 and a source of high pressure, external supply nozzle 22, which in most cases may be the first compressor may be reduced to zero and the pressure in the tank 13 for storing the refrigerant at the inlet 14 of the outer nozzle may be increased up to the maximum pressure of the outlet line of the first compressor. This deviation of the pressure in the above is a function of reducing the mass flow of the fluid. When the specific mass flow rate is equal to zero, the differential pressure at the level of the outer nozzle 22 may be essentially equal to zero, thus, the pressure at the inlet 14 of the outer nozzle has a maximum value, and the change of the kinetic energy of the refrigerant is equal to zero, and the enthalpy change is zero. Thus, when the refrigerant is stopped, the pressure increases at the inlet 14 of the outer nozzle to the maximum value generated by the compressor, and the enthalpy change is zero. It is also assumed that, if the period of time when the flow of refrigerant is stopped short compared with the period of time during which the refrigerant is able to flow, the violation of the total mass flow in the cooling circuit, which is a turbine 21, will be minimal.

It should also be noted that the advantage of stopping the mass flow through the outer nozzle 22 is that, if the time period of interruption of the flow of relatively short and the increased pressure of the refrigerant is essentially o adiabatically change the fixed enthalpy of the refrigerant in the outer nozzle 22 will not. In addition, if the increase in internal energy during the time period when the stationary refrigerant and the refrigerant is compressed, is compensated by the expansion of the refrigerant and reducing its work during the time when m is snowy consumption exists, what can be achieved by appropriate selection of the ratio of time during which the refrigerant flows, and the time when the refrigerant flow is interrupted, the process of extracting heat may be essentially continuous. This can lead to increased extraction of heat from the working fluid in the systems of the prior art.

Specialists in the art will also understand that the synchronization of the second terminating means 11 can be controlled by means of data processing (not shown). The means of data processing can take information about the angular position of the rotor 23 of the turbine from any suitable means, but preferably from Hall sensor or similar means, is installed on the turbine housing (not shown)that can read suitable technological mark on the rotor 23. The processor may also change the frequency of rotation of the rotor 23 of the turbine by changing the frequency of opening of the second terminating means 11.

Although the rotor 23 of the turbine is shown as having vanes with the configuration of the active type, it should be understood that the terminating means, such as described above, is also particularly suitable for use with other designs of turbines of the radial type, such as used in automotive turbochargers, similar to the one shown n is 11.

Figure 5 shows an alternative embodiment of the rotor 23A of the turbine, with many essentially spiral channels 602, leading to the Central exhaust hole 603. The Central outlet 603 may be located in the center of the rotor 23A and can be carried out essentially in the direction corresponding to the Central axis of the rotor 23A. The cross-sectional area of each channel 602 can continuously decrease from the entrance 604 to the output 605.

Preferably the ratio of the area of the input 604 to the square of the output 605 may be essentially 6:1 to ensure work with hypersonic speed with minimum restriction of flow of the working fluid.

As shown in Fig.6, Central line 606 of each channel 602 can cross the radius 607 rotor 23A, at least in two points 608, 609 between the input 604 and the output 605.

The flow of the fluid is shown by arrows F, may enter the channel 602 through 604. Since the direction of the fluid F is changed inside the channel 602, the change of momentum of the fluid F can create a torque force acting on the rotor 23A. Preferably, the rotating force can be transmitted to any suitable generator of electricity, or any other suitable mechanism that can operate rotating shaft. Preferably fluid F changes the direction of motion is and the angle, as close as possible to 180°in direction within the channel 602 to maximize the changes of momentum and, thus, energy is transmitted to the rotor 23A.

The rotor 23A can be used with e second terminating means, which are described above, although specialists in the art will understand that in some embodiments of the invention the plot explode 610 between inputs 604 channels can act as a terminating agent.

7 shows cycle air-conditioning/cooling, generally indicated by arrow 100, corresponding to another variant of the present invention.

As the cycle 300 shown in figure 3, the loop 100 may vary from cycle to cycle air-conditioning or cooling prior art by the fact that the throttle valve th and collection, the usual cycles of the prior art can be eliminated. A throttle valve th replaced turbine 114, which in this embodiment of the invention is located between the condenser 105 and the evaporator 122. Before the capacitor 105 can be located thermoelectric generator 103.

The second turbine 130 is located between the outlet of the evaporator 122 and the battery 128. Extenders 130A and 130b, if they are used, are located on two sides of the turbine 130. This is done to ensure a sufficiently low PL is in the surrounding area of the working fluid, included in the turbine, which allows the use of the nozzle is sufficiently large diameter in the turbine 130 without deterioration of the turbine 130 at supersonic speed, specific mass flow rate of the system or its cooling efficiency.

The secondary heat pump cycle, indicated by arrow 200, comprises a heat exchanger 201, which follows the extender s and extracts heat from the primary loop 100 to ensure that the temperature and pressure of the working fluid entering the evaporator 122 will be low enough for efficient operation of the evaporator 122. The secondary loop contains all the essential elements of the heat pump described in relation to the cycle 10 of the prior art, shown in figure 1, with additional controls shown in Fig.7 and described here for the loop 100.

Working fluid under high pressure may come out of the compressor 101 to the output line 102 of the compressor, essentially in the vapor phase and may flow into thermoelectric generator 103, or may pass directly to the condenser 105. Thermoelectric generator 103, if used, can produce output DC 103A low voltage, which can be converted into an output current a high voltage through the inverter 104 DC.

The capacitor 105 provides from the treatment of heat from the working fluid. The amount of waste heat can be regulated by the speed of the fan capacitor 106, which blows air through the condenser 105. The speed of the fan 106 of the capacitor can be set by the actuator 107 with variable speed controlled motorized drive 109 with variable speed on line connection 108. The actuator 107 with variable speed includes suitable software for controlling the speed of the fan 106 of the capacitor.

Leading the drive 109 with variable speed may include inputs 110, 111 and 112 from thermocouples to obtain information about the temperature (T1) of the refrigerant entering the evaporator temperature (T2) of the refrigerant leaving the evaporator, and the temperature (T4) of the air leaving the evaporator, respectively. Another thermocouple (TA) and the sensor 115 pressure can measure the temperature and pressure of the working fluid entering the turbine 114.

By measuring the temperature and pressure of the working fluid entering the turbine, and the set temperature in the cycle software master drive 109 with variable speed can provide an assessment of the density of the working fluid entering the turbine 114, using a reference table of the software and may adjust the speed of the compressor 101 and/or fan capacitor 106 is/or fan evaporator 126, that it was low enough to ensure that the steam passing through the critical section of the converging/diverging nozzle 117, which feeds the turbine 114, had essentially sound speed. The extender a additionally provides a reduction in the density of the working fluid entering the turbine 114.

The working body, with sound speed and leaving a critical section of the nozzle of the turbine can continue the acceleration in the diverging section of the nozzle 117 until it reaches a supersonic speed.

High-speed working fluid drives the turbine rotor. The turbine may cause the load 121 such as a generator, by means of suitable connection 120. The acceleration of the working fluid in the nozzle 117 is preferably up to sonic or supersonic speeds can cause a drop in its temperature and pressure. In this case, the energy of the working fluid can be removed as a result of passing through the turbine 114.

The mixture of high-speed working fluid under high pressure in both the vapor and liquid phases takes place in the evaporator 122 through the extender s, which is intended to prevent an increase in pressure of the working fluid when the working fluid is slowed down by removing the kinetic energy of the turbine 114. If necessary, the extender s may also have a diffuser 114b to reduce the working speed is about the body to subsonic values before entering the expander s.

The coil 123 of the evaporator can absorb heat from the warmer air 124 on the outside of the evaporator 122. The cooled air 125 may be removed from the evaporator 122 fan evaporator 126. The fan speed evaporator 126 may change the additional actuator 130 with variable speed connected with a power input of the fan 126 evaporator and managed a leading actuator 109 with variable speed on line connection 108A. The fan speed evaporator 126 may change as a reaction to the drop in air temperature 124 passing through the evaporator 122.

The battery 128 may provide for the evaporation of any fluid remaining in the liquid phase, prior to the input 129 of the compressor. The battery 128 may also act as a reservoir for the working fluid to replace the collection used in some cycles conditioning/cooling systems of the prior art.

Leading the drive 109 with variable speed can provide speed control of the compressor 101 to optimize its efficiency, essentially as described herein below, although the throttle valve th is omitted due to the exclusion of the throttle valve th cycle of 100.

If the turbine 114 actuates a generator 121, elect the generator 121 may be a DC generator, and the alternator. Preferably the generator 121 may be a high voltage DC generator with output voltage up to 670 volts. In a preferred embodiment, the power output V DC can be connected to the bus 109B DC master drive 109 with variable speed through a dividing circuit of a diode and a capacitor, which can supply power only in one direction, thus eliminating the feedback of the power consumed from the mains, generator 121.

Specialists in the art will understand that the above cycle air-conditioning can be more energy efficient than the cycles of the prior art, due to the energy extracted by the turbine, and, when used thermoelectric generator, and the speed control of the compressor in order to optimize overall efficiency.

On Fig-10 shows several block diagrams illustrating an example of a calculation process corresponding to the present invention, which can be exercised to control the cycle air-conditioning, such as the cycles described herein in relation to Fig 1, 2, 3, 7, 8, or other cycles, including cycles prior art, if required. The process can be controlled through l is the God of suitable microcontroller, microprocessor or similar means, having a control output to control the excitation signal of the rotation speed regulator for compressor. For clarity in the following description assumes that you are using a microcontroller.

As shown in Fig, when the power is turned on or prior to the execution of the control algorithms can run the initialization program, under which can be set selected flags, registers and counters, in the typical case, by setting to zero, if required for a specific implementation of the control algorithms.

On Fig shows a block diagram illustrating a possible initialization routine. Time intervals that are serviced/optimized external device (for example, a compressor, a throttle valve MV, a condenser, an exciter generator)are entered as delay 1 - delay n. For a particular heat pump, through which the management, set reference table and enter records for the target efficiency (SOR-COPn) for a heat pump operating with defined temperature difference (T1-T3)(1) to (T1-T3)(n)) at the level of the evaporator.

The microprocessor can read the state of the switch SW1. The switch SW1 prescribes whether the microcontroller automatically PLA is activated maintenance/optimization of control parameters for the heat pump. Can also be read and then initialized to the current state of any desired flags, counters and registers.

Then create the reference table on the basis of the entered temperature difference (T1-T3)(1) to (T1-T3)(n) and the associated target efficiencies SOR-COPn for use in the maintenance/optimization of a heat pump (see below). Finally, the microprocessor sets a flag that instructs the manual or automatic mode of operation based on the status of the switch SW1.

The microprocessor receives as input data the values of the temperature T1 of the refrigerant entering the evaporator, the temperature T2 of the refrigerant leaving the evaporator, and power KW1 compressor motor. We also introduce the set value of the heat load T3, the desired increment K2 motor speed and the desired reduction K3 speed of the compressor motor and the constant K1 for the refrigerant of the air conditioning. The value of K1 can be determined experimentally for a particular cycle air-conditioning, and it represents the increment of heat extracted per degree temperature change between T1 and T2.

Taking these inputs, the microprocessor calculates the difference between T1 and T3. This difference is then used to find the corresponding coefficient is useful actions for the heat pump for the in-memory reference table, where efficiency is the heat extracted per unit consumed.

Alternatively, instead of working to a target value of the coefficient, the microprocessor can provide to increase/decrease the speed of the compressor to maximize efficiency, if the coefficient a for loop does not increase continuously with increasing speed of the compressor. Specialists in the art will also understand that, if necessary, you can use variables other than temperature difference at the level of the evaporator.

If T1-T3 is less than or equal to zero, the heat pump is not working and the microcontroller can do nothing else but return to the beginning of the algorithm. If T1-T3 is greater than zero, the actual efficiency SOR, which is based on measured variables T1, T2 and KW1, is calculated according to equation 1

COP2=K1|T1-T2|/KW1 equation 1

If you can use other criteria relating to the performance of the cycle depending upon the amount of compressor work. As described here, consider this preferred embodiment of the invention uses the measurement of the differential temperature to obtain the characteristics of useful heat transfer system, POSCO is ECU measurement of temperature can be carried out relatively easily. However, there may be used an alternative evaluation criteria of system characteristics that are related to the performance of the system relative to the work consumed by the compressor.

The calculated efficiency SOR is then compared with a target efficiency SOR. If the value SOR less than the value CAR, the speed of the compressor is increased by K2. Conversely, if the target SOR more calculated SAR, the motor speed is reduced to K3. It then executes the subroutine delay (not shown) to account for any delay reaction cycle for changing the speed of the compressor. Required delay time can be determined experimentally by force correction speed of the compressor to increment K2 and K3 and measuring the maximum time for the return cycle air-conditioning in the established state. To achieve this delay, you can use any suitable routine delays. The execution of the routine delay ends after any control variable is changed to analysis and change another control variable to ensure that the system remains stable and/or to ensure that to obtain these measurements as input for control algorithms used condition is I established state. Execution of control algorithms may be performed periodically at predetermined time intervals, continuously, with the proper time delay between cycles of the management or on the basis of the graph.

Figure 9 schematically shows a control algorithm to control the operation of the throttle valve, if it is used in a heat pump. The control algorithm may also be applied to any managed device that performs the same or a similar function as a throttle valve.

The microcontroller takes as input temperature data temperature data T4 unsaturated air exiting the evaporator, and a constant T5 representing the temperature of superheat added to the working fluid at the outlet of the evaporator. He also accepts the input pressure P1 representing the pressure of the working fluid at the outlet of the evaporator, the data about the current state of the throttle valve th or equivalent TX1 should be and sets the operation K4 and K5 for the strengthening and weakening of the operation of the throttle valve MV, respectively.

The microcontroller calculates T6 as the amount of T4 and T5 and calculates T7 as the product of P1 and constant K6, which facilitates the conversion of pressure in the temperature of the working fluid. If the temperature T6 is less than T7, the throttle valve t is opened increments K4, and if the temperature is T6 more T7, a throttle valve MV is closed increments K5. In another case, a throttle valve th remains in its current state. The magnitude of the increment and decrement can be the same (K4=K5). It then executes the subroutine delay to ensure that the cycle has reached steady state or near steady-state before it is taken any further action.

If the settings of the throttle valve th should preferably check that the throttle valve TX continues to operate so that the refrigerant in the suction line of the compressor downstream of the evaporator overheated enough so that he was in the form of vapour. Thus, each time the routine is activated delay following the status change of the throttle valve th, the microcontroller may perform additional verification of operation of the throttle valve th. Such verification may be required only if the control means limits the operation of the throttle valve th is not already included as part of the throttle valve and if the existing control algorithms do not keep the throttle valve MV in the valid operating range.

When the change speed of the compressor and the flow openings of the throttle valve th operation of the capacitor will change who I am. Thus, the controller may also control a working condenser fan. This process is shown in figure 10.

The input temperature data for the algorithm are above T1 and T3, the temperature T8 in the supply line of the fluid, measured at a given point of the heat pump, in the typical case, the point located after the condenser, and the target temperature T10 temperature in the supply line of the fluid. The magnitude of the increment K7 speed of the condenser fan and the magnitude of the increment K8 speed of the condenser fan are also input to the algorithm along with the current speed CFS1 condenser fan minimum speed of CFSmincondenser fan and a maximum speed of CFSmaxthe condenser fan. Although operations use a minimum speed of CFSmincondenser fan and a maximum speed of CFSmaxcondenser fan not shown in figure 11, the value of the minimum speed CFSmincondenser fan and a maximum speed of CFSmaxcondenser fan limit allowable fan speed compressor.

The first microcontroller calculates T11 as the difference between T3 and T1 and completes the control algorithm for the speed of the condenser fan, if T3 bol is above or equal to T1. If T3 is less than T1, the cycle works and the heat removed by the condenser. Then the microcontroller calculates T12 as the difference between the T10 and T8, and if the target temperature T10 is less than the actual temperature T8, the current speed CFS1 of the compressor is increased by C7, and if more T10 T8, the current speed of the compressor is reduced by K8. After changing the operation of the condenser fan is an additional time delay.

The microprocessor can also change bronirovanie second terminating means 11 for optimization of the chosen parameter of each refrigeration circuit. In some embodiments of the invention chosen parameter can be heat absorbed by the evaporator, while in other embodiments, the chosen parameter can be the total power consumed by one or more compressors.

On Fig schematically shows the control algorithm for the planning of the above-described control algorithms/optimization. In-memory temporary table is stored parameters, which determines when should be implemented each algorithm. This table is temporary settings will be entered by the administrator of the heat pump. At power-up the pointer is set to the original value in the temporary table settings and clock starts. The time parameters table contains the successor of the initial list of all control algorithms, a variable time delay, which represents the time delay, which should be performed between each execution of the control algorithm, and the address indicating where it can be found in the memory of the control algorithm.

The microcontroller reads the current time, measured real time clock, and adds the time delay specified in the table of temporary settings to set the current time of service. The current service time is then read and compared with the reference real time. The process continues uninterrupted cycles checking real-time relative to the current service time for each algorithm, while the countdown is real time will not reach the current service time for the algorithm. When this happens, the microprocessor exits the loop, reads the start address for the algorithm of table time parameters and executes the algorithm. After the execution of the algorithm, the microprocessor returns to the cycle that is designated as "return" on Fig.

The rotors of the generators of the heat pump can operate with high speeds. For example, the generators and the heat pump can be adapted to rotate the rotor with a frequency of 15,000 rpm or more. To maintain the performance of the generator at high speeds necessary in order to balance the rotating group (turbine, the rotor, shaft and bearing system). In addition, sealing of the rotor and generator in the refrigeration cycle can eliminate the problem of losses and reliability of power transmission cycle through the shaft. In addition, if you use a rotor with fixed magnets, precision balancing is difficult due to the magnetic field around the rotor and due to the fact that the ferromagnetic components of the installation are magnetized, and if the generator is attached to a sudden load, the resulting force can unbalance the rotor.

The generator corresponding to the present invention, includes a non-magnetic rotor, which cannot be magnetized. The rotor can be performed, for example, from electrical steel Lycore 150. The electric field radiated by the rotor is controlled by the coils of the rotor are wound on the bobbins of the ferrite cores F5 high permeability. You can use other suitable materials.

The elements of the turbine, located in close proximity to the rotor, and a casing for the rotor can be made of suitable plastic, resistant to strong stresses generated in the generator. Thus, these elements do not interact with proceeds from the rotor of the electric field or the electric field from the energized windings. Stator winding wound on the toroidal genial, OEM is key, located on the plastic case. The toroidal core may be made of electrical sheet steel Lycore 150 or, more preferably, from specially molded ferrite F5 or equivalent high permeability.

On figa-D shows the turbine generator, indicated generally by the arrow 500. The entire generator 500 may be sealed in the cycle air-conditioning. On figa shows a top view of the turbine generator 500 with remote covers for clarity, and figv shows a section along the line BB in figa. The turbine generator 500 includes a housing 501 of the turbine bearing housing 502 stator holding the stator 504, and a closing plate A-D. On figs and 11D shows a cross section along lines CC and DD on FIGU respectively. The housing 501 of the turbine includes a turbine 505 that includes a rotor 506 and the nozzle 507 held by the holder 508 nozzles. In the nozzle 507 input tube 509 is supplied to the refrigerant. The rotor generator 510 includes four coil 511-514 of the rotor, forming a four-pole rotor 510. Coil 511-514 may have short-circuited ends, or the ends are connected resistive element, the impedance/resistance of which increases with increasing temperature to provide current limiting to protect the windings of the rotor. Coils can be made, for example, from a copper wire of 1 mm in thickness and can have 135 Vitko is around 19 mm frame made of ferrite F5. However, experts in the art should understand that the number of windings of the rotor 510 generator and stator 504, the core used for the windings, the air gap between the windings of the rotor 510 generator and stator and the number of poles on the rotor 510 generator can be changed in accordance with the requirements for the generator 500. The rotor turbine 506 preferably has a terminating means described above with reference to figure 4, and may have the construction of the blades described with reference to figure 4 or 5.

The stator winding 504 can be connected to each other by groups of two or more adjacent windings. Conclusions alternating current of each winding group connected with other groups at intervals of 90° for a four-pole rotor 510. Each group of windings is connected to an adjustable direct current generator (not shown), which feeds a constant current in the stator winding. Capacitors isolate the windings and the DC generator from the findings of an alternating current. Groups of windings are excited by a constant current generating alternating pairs of North and South poles around the circumference of the rotor, which may be spaced at intervals of 90°, with the same fields are against each other at intervals of 180°. Thus, the electric field is balanced around the rotor 510 and may, if necessary, adjusted in order to find for the correction of any imbalance of the rotor 510 when it detects any imbalance in the course of work. Other stator winding will not have a connection to the DC generator. For example, the stator may be only 18 of the winding groups, four of which are connected with the DC. If you want, you can use two, three or more than four stator windings, connected by DC.

The polarity of the direct current can be periodically reversed to ensure that the ferromagnetic elements of the turbine 500 will not get a permanent bias.

The turbine of the prior art have characteristics operating speed and torque that is constant and cannot be adjusted without loss of performance. However, turbine 500, corresponding to the present invention allows dynamic adjustment of the field strength of the excitation-altering characteristics of the generator so that the turbine 500 can work with the best speed and torque for maintaining within regular parameters. For use as a turbine described here heat pumps turbine 500, corresponding to the present invention, can be used to maintain operation at supersonic speeds.

When the turbine reaches 500 speed limit, are driven DC generators, the gene is yousie electric field windings of the stator, connected to the generator, which generates a constant current in the coils of the rotor 510 when the rotor 510. In this case, the windings of the stator is generated by a constant current which is supplied to the generator output. Output DC current can be rectified, and if the generator forms part of a heat pump, the energy can be used to partially power the compressor of the heat pump.

On Fig schematically illustrates a control algorithm for stator windings. The control algorithm shown in Fig used after the rotor 510 communicated a certain speed, and in the windings of the stator is constant current. The total current IT on the output and the total voltage VT at the output of the stator is measured. This can be achieved through the implementation of the measurement current I1-In and out of the voltages V1-Vn at the output for each group of stator windings. Total output power is calculated as the product of IT and VT. Compared with the previous output. If its output power is less than the current output power DC current in the windings of the stator to increase with a given step size. If its output power is more than the current output power DC current in the windings of the stator is reduced with a given step size. Specialists in this field techniques is clear, the algorithm, shown in Fig that you can use to manage multiple target generators.

If in the foregoing description made with reference to specific items or entire device corresponding to the invention, the equivalents of which is known, it is assumed that such equivalents are included here as if they were described separately.

Although the present invention is described, for example, and with reference to possible variations in its implementation, it should be understood that they may be made of modifications and improvements without departing from the scope of the invention defined by the attached claims.

1. System for thermodynamic cycle including a compressor, a first turbine, located after the compressor, a heat exchanger located after the first turbine, and providing for the extraction of heat from cycle to another thermodynamic cycle, the evaporator, located after the heat exchanger, and a second turbine located downstream of the evaporator and to the compressor.

2. System for thermodynamic cycle including a compressor, a condenser, located after the compressor, the first turbine, located after the condenser, the evaporator, located after the first turbine and the second turbine located downstream of the evaporator and to the compressor.

3. The system according to claim 2, further what about including the heat exchanger, located between the first turbine and the evaporator, and heat exchanger extracts the heat in a different thermodynamic cycle.

4. The system according to claim 2, in which, at least, or the first turbine, second turbine includes

the camera of the rotor

the rotor rotating around the Central axis inside the chamber of the rotor, at least one nozzle including an outlet nozzle for feeding fluid from the means for supplying fluid to a thermodynamic cycle in the rotor to actuate the rotor and power generation,

at least one outlet for release, in use, fluid from the turbine,

thus the flow of fluid from at least one nozzle is periodically interrupted by at least one means for interrupting the flow to increase the pressure of the fluid inside the at least one nozzle.

5. The system according to claim 4, in which, at least, or the first turbine, second turbine includes at least one means for storing the fluid, located between the means for supplying a fluid medium and at least one nozzle.

6. The system according to claim 5 in which the means for storing fluid medium has a capacity at least equal to the volume of the compressor.

7. The system according to claim 4, in which, at measures which, one way of interrupting the flow essentially provides the stopping of the fluid flow from the at least one outlet nozzle, until the pressure within at least the nozzle is increased to a predefined minimum pressure that is less than the pressure in the means for supplying the fluid or equal to.

8. The system according to claim 4, in which, in use, the flow of fluid from at least one nozzle is interrupted by at least one interrupting means during a period of time sufficient to bring the fluid immediately before at least one outer nozzle essentially in a state of rest.

9. The system according to claim 4, in which the rotor has multiple channels, which have the configuration, location, and dimensions, providing a torque around the Central axis when the refrigerant from at least one nozzle is included in the channel.

10. The system according to claim 4, in which the rotor has many blades, which have the configuration, location, and dimensions, providing a torque around the Central axis when the refrigerant from at least one nozzle comes in contact with the blades.

11. The system according to claim 4, in which at least one tool flow interruption includes at least one blade, which is connected with the external periphery of the rotor and moves with it, prisposoblena for interrupting the flow of fluid out of, at least one outlet nozzle, when at least one blade is essentially adjacent to the at least one output nozzle.

12. The system according to claim 11 in which the means of interrupting the flow includes multiple blades, essentially equally spaced around the circumference of the outer periphery of the rotor.

13. The system according to claim 4, in which at least one nozzle, when used, allows flow of fluid into the rotor with sonic or supersonic speeds.

14. The system of item 13, in which at least one outlet includes diffuser and the expansion section to reduce the velocity of the fluid and maintaining the pressure of the fluid flow after deceleration to subsonic speed.

15. The system according to claim 1, in which at least one of the first and second turbine includes a rotor having two or more spaced apart windings of the rotor and the stator, with many windings of the stator around the rotor, and at least two of the windings are connected to an adjustable current source, each adjustable current source provides the excitation of the stator windings, with whom he is connected.

16. The system of clause 15, in which each regulated current source provides the excitation of the stator windings, with which it is connected, after the rotor reaches a pre-ass is Noah speed.

17. System according to clause 16, in which the predetermined speed is a speed limit for the current operating conditions of the turbine.

18. The system of clause 15 or 16, in which each current source provides the increase or decrease in current in their respective stator windings depending on the measured values of power output from the stator windings.

19. Control method for a system containing a thermodynamic cycle including a compressor, a condenser, located after the compressor, the first turbine, located after the condenser, the evaporator, located after the first turbine and the second turbine located downstream of the evaporator and to the compressor, in which at least one of the first and second turbine includes a rotor having two or more spaced apart rotor winding and a stator having multiple windings of the stator around the rotor, and at least two stator winding is connected to an adjustable current source, and each adjustable current source provides the excitation of the stator windings, with whom he is connected,

includes multiple measurement of the output power to the windings of the rotor system and the increasing current in the windings if the current measured value of the output power more than the preceding measured output power, and the reduction of the current in the windings, if the current measured value of the output power is less than the preceding measured values of power output.

20. Method of generating power in a thermodynamic cycle including a compressor, a first turbine, located after the compressor, a heat exchanger located after the first turbine, and working to extract heat from cycle to another thermodynamic cycle, the evaporator, located after the heat exchanger, and a second turbine located downstream of the evaporator and to the compressor, in which the first and second turbines include a rotor and at least one nozzle for feeding fluid into the rotor to actuate the rotor and power generation, including

providing at least one tool flow interruption for periodically interrupting the flow of fluid from at least one nozzle and increase the pressure of the fluid inside the at least one nozzle to a predefined minimum pressure that is less than the pressure in the means for supplying the fluid or equal to, before the resumption of the flow of fluid from the specified at least one nozzle.

21. Method of generating power in a thermodynamic cycle including a compressor, a condenser, located after the compressor, the first turbine, located after the condenser is, the evaporator is located behind the first turbine and the second turbine located downstream of the evaporator and to the compressor, in which the first and second turbines include a rotor and at least one nozzle for feeding fluid into the rotor to actuate the rotor and power generation, including the provision of at least one tool flow interruption for periodically interrupting the flow of fluid from at least one nozzle and increase the pressure of the fluid inside the at least one nozzle to pre-selected minimum pressure that is less than the pressure in the means for supplying fluid environment, or equal to, before the resumption of the flow of fluid from at least one nozzle.

22. The method according to item 21, in which a preset minimum pressure sufficient to achieve a fluid environment of the local sound speed in the critical section of the nozzle.

23. The method according to item 22, including the acceleration of the fluid exiting the at least one nozzle to supersonic speeds.

24. Control system for systems containing a thermodynamic cycle including a compressor, a condenser, located after the compressor, the first turbine, located after the condenser, the evaporator, located after the first turbine and the second turbine, located after the of sprites and to the compressor, including

sensitive means for measuring the output power of thermodynamic cycle,

management tool for compressor and management tool communicates with the sensing means for receiving, as input, the measured values of the output power of thermodynamic cycle and the measured values of the work consumed by the compressor,

this management tool provides the calculation of performance measurement based on the input data and changing the speed of the compressor to maximize performance measurement or for maintenance performance measurement at the specified level.

25. The control system according to paragraph 24, further comprising a second management tool for the second turbine and sensitive tool for measuring temperature controlled area in which the second management tool takes as additional input, the measured values of the temperature controlled region and provides the opening and closing of the passage for fluid flow through the second turbine in response to detected changes of temperature in a controlled area in relation to a specified value.

26. The control system according to paragraph 24, in which the second management tool optionally accepts, as input, measured the values, displays the amount of refrigerant in the cycle, which evaporated after phase evaporation in a loop, and provides the opening and closing of the passage for fluid flow through the second turbine to maintain the quantity of the vaporized refrigerant after phase evaporation.

27. The control system according to paragraph 24, in which the second control means to maintain the quantity of the vaporized refrigerant after phase evaporation, after a specified delay after opening or closing means to control passage of fluid through the second turbine in response to the detected temperature change.

28. The control system according to paragraph 24, which includes a third means of control for a capacitor in a thermodynamic cycle, and the control system provides for changing the operation of the condenser to maintain the required level of cooling of the refrigerant to the condenser.

29. Control system for p, in which the first control, second control and the third control is one microcontroller, or microprocessor, or many microcontrollers or microprocessors, with at least selected microcontrollers or microprocessors communicate with each other to ensure bronirovania functions of the control system.

30. The control system for the system, tereasa thermodynamic cycle, includes compressor, condenser, located after the compressor, the first turbine, located after the condenser, the evaporator, located after the first turbine and the second turbine located downstream of the evaporator and to the compressor, in which at least one of the first and second turbine includes a rotor having two or more spaced apart rotor winding and a stator having multiple windings of the stator around the rotor, and at least two stator winding is connected to an adjustable current source, and each adjustable current source provides the excitation of the stator windings, with whom he is connected, comprising

sensitive means for measuring the output power of thermodynamic cycle,

management tool for compressor and management tool communicates with the sensing means for receiving, as input, the measured values of the output power of thermodynamic cycle and the measured values of the work consumed by the compressor,

this management tool provides the calculation of performance measurement based on the input data and changing the speed of the compressor to maximize performance measurement or for maintenance performance measurement at a given level, and the control system provides for regulation the Finance DC flowing in the windings of the stator of the turbine.

31. The control system according to item 30, which provides regulation of the DC current flowing in the windings of the stator, for dynamic balancing, turbine under load.

The priority according to claim 2 and 3 of the claims set 30.09.2002 date of filing 521717 and priority p and 21 of the claims set 17.02.2003 date of filing 524220 in the patent office of New Zealand, other claims have priority 05.09.2003 on the date of filing of application PCT/AU 03/01144.



 

Same patents:

FIELD: heating, ventilation.

SUBSTANCE: invention refers to the device and method to be used with air conditioning cycle. A turbine for power generation includes a rotor, a chamber and at least one nozzle for supply of a fluid medium to activate the rotor. Flow of the fluid medium out of the nozzle output is periodically interrupted with at least one device of the flow brake to increase fluid medium pressure inside the nozzle. In a thermo dynamic cycle two such turbines can be used; at that the first turbine is located after a compressor and before a heat exchanger, and the second turbine is located after an evaporator and before the compressor. The invention facilitates upgrading of a total efficiency owing to recuperation of a portion of energy.

EFFECT: upgraded efficiency of an air conditioning device.

31 cl, 14 dwg

FIELD: power engineering.

SUBSTANCE: reversible electric turbo-expander plant comprises an electric machine, a turbo-expander, an electric heater installed upstream and connected to an accumulator battery, installed as capable of recharging from an electric machine, an additional system of natural gas heating. It is equipped with a centrifugal supercharger and a gas turbine, kinematically connected with a turbo-expander, with a centrifugal supercharger and with an electric machine equipped with a semiconductor converter. The additional heating system is made in the form of a heat recuperator installed in the gas turbine, and connected via a water pump with a water heater, installed upstream the electric heater, and the accumulator battery is connected with the electric machine via a semiconductor converter. The electric machine is made in the form of a synchronous electric motor as capable of its operation in the mode of an electric energy generator or in the mode of a controlled electric motor.

EFFECT: expansion of device capabilities and increased operational reliability.

2 cl, 5 dwg

Up!