Air-conditioning apparatus

Description of the invention

The present invention relates to an air-conditioner that enables heat exchange between a plurality of heating media, which allows the air temperature to be regulated based on the amount of heat exchange.

An air conditioner used in vehicles is generally designed to control the temperature inside the vehicle using a refrigeration cycle that circulates refrigerant. An air conditioner of this type is disclosed in Japanese Patent No. 2000-142078. According to this design of a vehicle air conditioner, a compressor, condenser, receiver, expansion valve, evaporator and other components are arranged in the refrigerant circulation circuit. In turn, the blower and evaporator are arranged in the housing of the air conditioner. In addition, the housing is equipped with an air inlet and outlet.

An example of how the above-mentioned air conditioner works is shown below. First, when the blower is turned on, air is introduced through the air inlet into the housing. On the other hand, when the compressor is driven by the motor, the refrigerant is compressed by the compressor, thereby obtaining the refrigerant under high pressure. The compressed high pressure refrigerant is then concentrated using a condenser and passed through the receiver. As a result, the refrigerant is converted into a high temperature liquid refrigerant under high pressure. The liquid refrigerant is expanded using an expansion valve and passed to the evaporator as a low temperature, low pressure liquid refrigerant. Inside the evaporator, the heat contained in the air is transferred to the refrigerant due to the temperature difference between the air inside the housing and the refrigerant, which causes the liquid refrigerant to evaporate. The air at the reduced temperature (chilled) is then introduced through the outlet opening into the interior of the vehicle cabin. The refrigerant, in turn, passes through the evaporator to the compressor again. The temperature inside the vehicle cabin is regulated as described herein.

The "refrigerant flow rate" is one of the factors that affect the efficiency of the heat transfer process for the refrigerant circulating within the circuit. In the case of the air conditioner disclosed in the aforementioned solution - since the compressor is driven to transport the refrigerant - the operation of the air conditioner is highly dependent on the operation of the compressor. This in turn means the possibility that the desired functionality of the air conditioner may not be achieved.

The air conditioner according to the invention serves to cool or heat air and to supply heated or cooled air in predetermined amounts, comprising a first circulation circuit for a first heating medium, a second circulation circuit for a second heating medium, and a first heat exchanger for heat exchange between the first and second heating medium and air, and a second heat exchanger for heat exchange between the second heating medium and air.

The air conditioner according to the invention is characterized in that it further comprises a first heat storing device provided with a heat storing material, heated or cooled using a first heating medium to effect heat exchange between the first heating medium, the second heating medium and the heat storing material. the second circulation circuit comprising a first circuit for passing the second heating medium through the first heat exchanger and a second circuit for passing the second heating medium through the first heat storing device and a selector selectively connecting the second heat exchanger to the first circuit and the second circuit.

Preferably, the selector is further connected to a controller that switches it based on the air conditioning demand.

The controller preferably comprises means for carrying out a selector switching operation by guiding the second heating medium through one of the devices, i.e. the first heat exchanger and the first heat storing device, which has more favorable heat transfer characteristics, as long as the efficiency demand of the air-conditioning system is high.

The first heat exchanger preferably comprises a first flow channel for passing the first heating medium and a second flow channel formed adjacent to parallel to the first flow channel for passing the second heating medium, the flow direction of the first heating medium inside the first flow channel and the flow direction of the second heating medium within the second flow passage is opposite to each other.

The first heat exchanger may be placed upstream of the first heat storing device in a flow direction of the first reduced temperature heating medium, and furthermore the selector is preferably adapted to connect the flow of the second heating medium to the first heat exchanger through the first circuit in case of rapid cooling demand. and is adapted to switch the second heating medium to the first heat storing device via the second circuit when normal cooling is required.

Preferably, a second heat storing device is arranged in the first circuit, provided with a material with heat storing properties, receiving and storing heat from the high-temperature heated heating medium.

Preferably, at least one of the heat storing devices is provided with a heat source mechanism for heating or cooling the first heating medium and a controller for activating said heat source mechanism when the temperature of the heat-storing material in at least one of the heat storing devices is at a temperature. level or lower, and there is a need for air conditioning to operate.

The first circulation circuit is preferably controlled by a controller in accordance with the temperature of at least one of the heat storing devices and controls the operation of the second circulation circuit in accordance with the air temperature.

Optionally, the air conditioner further comprises a pump for compressing and delivering the second heating medium and a controller that has means for adjusting the pump capacity based on the difference between the air temperature and the target temperature at a predetermined position downstream of the second heat exchanger.

One of the heat storing devices, i.e. the first heat storing device or the second heat storing device, may comprise a pipe led through a heat storing material for carrying the first heating medium or second heating medium and furthermore a number of ribs embedded in the material having heat storing properties. heat accumulation properties and integrated into the pipe.

The second heat storing device is preferably arranged upstream of the first heat storing device in a flow direction of the heated first heating medium with high temperature.

In addition to the second heat storing device, the air-conditioning unit is preferably further provided with a fourth heat exchanger for the heat exchange selectively with air, a third heating medium circulating between the second heat storing device and the fourth heat exchanger in the third circuit, which also serves for applying heat to the third heating medium in the second heat storing device.

Optionally, the first heat storing device is connected in series with the first heat exchanger, a compressor for compressing the first heating medium, a heat radiator for radiating heat from the first heating medium, and an expander for adiabatic expansion of the pressurized first heating medium.

The compressor is preferably provided with a controller for actuating it or not depending on the temperature of a heat-storing material in any of the heat storing devices, the hysteresis being set for the allowable temperature and the unacceptable operating temperature of the compressor.

Preferably, the controller is a defrosting device according to step S616 for temporarily heating the first heat storing device, where energy for cooling is stored in the first heat storing device and energy for heating is stored in the second heat storing device.

Optionally, the controller which constitutes the defrosting device in step S616 has means for determining the amount of heat for heating the first heat storing device based on at least one of the information about the road traveled by the vehicle, the prevailing weather, the speed of the vehicle, the engine speed, outdoor temperature, required heat quantity 4

To provide air conditioning inside the room, the air conditioner also includes the car in which it is mounted.

Preferably, the controller is a pre-heating device according to step S618, during which heat is collected in the heat-storing device or radiated by driving the compressor with an inertia force, the air conditioner further comprising a driving motor for expending energy for vehicle movement. and driving a compressor, wherein in the preheating mode the drive motor is force driven by the inertia force.

Optionally, the air conditioner further comprises a diverter valve for diverting the first heating medium to a direction from the compressor through the heat radiator and an expander to the first heat storing device, and from the heater through the first heat storing device and an expander to the radiator.

A second heat storing device receiving and storing heat from the first heating medium is preferably arranged between the diverter valve and the outlet of the compressor.

Preferably, in addition to the second heat-storing device, the air-conditioning unit is furthermore provided with a fourth heat exchanger for heat exchange selectively with air, the third heating medium circulating between the second heat-storing device and the fourth heat exchanger in a third circuit which serves also for applying heat to the third heating medium in the second heat storing device.

Preferably, the air conditioner further comprises air mixing means including a fourth heat exchanger and a third circuit for applying heat of the second heat storing device to the air cooled by the second heat exchanger, thereby heating the air.

Optionally, the air conditioner further comprises any internal combustion engine and an oil drive unit, and a controller for supplying heat stored in the second heat storing device to any of the internal combustion engine or drive unit, thereby warming up the internal combustion engine. or heating the oil.

Optionally, the air conditioner further comprises means for heating the internal combustion engine using heat from the second heat storing device, the internal combustion engine then remaining stationary.

According to the present invention, the operation of the air conditioner is less influenced by the operation of the compressor regarding the circulation of the first heating medium in the first circuit.

The proposed design of the air conditioner allows you to improve the amount of fuel consumption by reducing the engine load related to the demand from the air conditioner, if it is installed in the vehicle.

In the air conditioner according to the invention, the first circulation circuit of the first heating medium and the second circulation circuit of the second heating medium are arranged independently of each other. The heat exchange between the first and second heating medium takes place in the first heat exchanger, and the heat exchange between the second heating medium and air takes place in the second heat exchanger.

The first heating medium is heated or cooled using a drive unit such as a motor and the like, with no heat exchange between it and air. Consequently, the first heating medium can be heated or cooled independently of the demand of the air conditioning system. This reduces the direct impact on the power package load associated with the air conditioning system demand.

Moreover, according to the present invention, a third heat exchanger, different from the first heat exchanger with regard to the heat transfer characteristics, is arranged in a circuit within which the first heating medium is transferred. Accordingly, it is possible to pass the second heating medium independently through the first heat exchanger or the third heat exchanger, which allows heat exchange with the first heating medium. This flow path selection is made by the controller using a selector. Especially - when the demand from the air conditioning system is high - the second

The heating medium is led through to a heat exchanger with more favorable heat transfer characteristics.

Therefore, cooling or heating for the second heating medium can be regulated so that the air conditioning system operates according to the demand.

In the case of a first heat exchanger, the flow path of the first heating medium and the flow path of the second heating medium are disposed adjacent to and parallel to each other, and the flow directions of the two heating mediums may be opposite to each other. Thanks to the use of such a structure, the efficiency of the heat exchange process between heating agents can be improved.

The third heat exchanger may be a heat storing device having a heat storing material that is heated or cooled by the first heating medium. In this case, the heat capacity of the third heat exchanger is higher than that of the first heat exchanger. Accordingly, the second heating medium is passed through the first heat exchanger to perform cooling in response to the rapid cooling demand, and the second heating medium is passed through the third heat exchanger to perform cooling in response to the usual cooling demand, which allows use the accumulated heat efficiently.

Moreover, according to the present invention, it is possible to provide a second heat storing device which is heated by receiving heat from the first heating medium and then holding the stored heat therein. For example, a fluid may be used as the first heating medium, the temperature of which is lowered using the compression pressure followed by adiabatic expansion. In this case - as the amount of heat of the first heating medium increases due to compression - the heat is not released to the outside but recovered by the second heat storing device.

According to this invention, the first heat storing device is able to store heat for cooling and the second heat storing device is able to store heat for heating. Accordingly, it is possible to provide a control unit for the heat source mechanism used to cool or heat the first heating medium on the basis that the amount of heat stored inside one or both of the heat storing devices is reduced.

As described above, the first circuit acts as a circuit for generating heat for the air conditioning system, and the second circuit serves as a circuit for cooling or heating the air. Accordingly, according to the present invention, it is possible to provide a regulating unit for operating the first circuit based on the temperature of the first heat storing device and for operating the second circuit based on air temperature.

In this case, the regulation of the capacity of the pump for transferring the second heating medium may be based on the deviation between the air temperature on the outlet side of the second heat exchanger and the target temperature.

In the case of the heat storing device according to the invention, a number of ribs are integrated with the pipe through which the heating medium flows, the pipe with the ribs being embedded in a material with heat storing properties.

The second heat storing device is heated by the first heating medium, thereby increasing its temperature. According to the invention, it is possible to arrange a third circuit for circulating a third heating medium between the second heat storing device and the fourth heat exchanger for transferring the heat stored in the second heat storing device.

In order to heat or cool the first heating medium, it is possible according to the invention to provide a mechanism including a compressor to compress the first heating medium, a heat radiator to radiate heat from the pressurized first heating medium at an elevated temperature, and an expander to adiabatically expand the first heating medium. A compressor, heat radiator and expander may be connected in series with the first heat exchanger and the first heat storing device. The second heat storing device is preferably connected immediately downstream of the compressor discharge. Thus, the heat of the first heating medium is recovered to a greater extent by the second heat storing device. As a result, the load on the radiant heater has been reduced to such

A way that the heat radiator can be made smaller. Moreover, the energy consumed by the blower can be saved when cooling is required.

As each heat storing device is designed to store thermal energy for the purpose of cooling or heating a compressor, it may be decided on the basis of its temperature whether it is allowed or disabled. In this case, the hysteresis is set for the acceptable temperature and for the unacceptable temperature.

The first heating medium is compressed to raise its temperature and adiabatically expanded to limit its temperature. The second heat storing device stores the heat of the first heating medium at an elevated temperature. The first heat storing device is cooled by the adiabatically expanded and depressurized first heating medium, whereby energy is stored for cooling. Accordingly, in the event that the heat storage capacity of the first heat storing device is fully exploited, the compressor becomes blocked in operation even if the heat storage capacity of the second heat storing device has not been fully utilized. According to the present invention, it is possible to use a defrosting device to periodically heat the first heat storing device.

The defrost period can be determined based on road conditions or the operating mode of the vehicle equipped with an air conditioning system.

A drive motor may be used to drive the compressor. In this case, when the drive motor is positively driven by an inertia force, it is possible to select a pre-heat accumulation mode in which the inertia force can be used to drive the compressor to accumulate heat.

The heat stored in the second heat storing device according to the invention finds many different applications. For example, to regulate the temperature of the air, the heat may be used for air mixing to transfer heat to the air after it has been cooled by the second heat exchanger. The heat, on the other hand, is used to warm the internal combustion engine and to heat the oil, relative to keeping the temperature at a certain level. In the case where the heat is used to warm up the internal combustion engine or to maintain its temperature at a certain level, heat is supplied from the second heat storing device to the internal combustion engine while the internal combustion engine remains stationary.

The invention is illustrated in an embodiment in the drawing, in which Fig. 1 is a schematic diagram showing a selected example of an air conditioner according to the invention; 2 is a cross-sectional view showing the structure of the heat storing device in FIG. 1; Fig. 3 is an exploded perspective view showing the structure of the heat exchanger shown in Fig. 1; fig. 4 - a schematic diagram showing the flow directions of the brine and the refrigerant inside the heat exchanger shown in Fig. 3; Fig. 5 is a block diagram showing the control flow of the air conditioner shown in Fig. 1; Fig. 6 is a diagram showing the main part of the control diagram used for the air conditioner of Fig. 1; Fig. 7 is a diagram showing a part leading to the diagram shown in Fig. 6; fig. 8 - a diagram showing a selected example of a plan used in the example of the control process shown in Figs. 6 and 7; Fig. 9 is a diagram showing a temperature threshold applicable to the example of the control process shown in Figs. 6 and 7; Fig. 10 is a diagram showing another temperature threshold applicable to the example of the control process shown in Figs. 6 and 7; fig. 11 - a diagram showing another temperature threshold applicable to the example of the control process shown in figures 6 and 7; Fig. 12 is a diagram showing another example of a plan applicable to the example of the control process shown in Figs. 6 and 7; Fig. 13 is a diagram showing another temperature threshold applicable to the example of the control process shown in Figs. 6 and 7; fig. 14 - a diagram showing another temperature threshold applying to the example of the control process shown in figures 6 and 7; Fig. 15 is a diagram showing another temperature threshold applicable to the example of the control process shown in Figs. 6 and 7; Fig. 16 is a diagram showing another temperature threshold applicable to the example of the control process shown in Figs. 6 and 7.

The present invention will be described below with reference to the accompanying drawings. Fig. 1 is a schematic diagram showing the construction of an air conditioner A1 used in vehicles. The air conditioner A1 comprises a first circuit B1, a second circuit C1, and a third circuit D1. In particular, each of the circulation circuits is a fluid path with respective conduits. Inside the first circuit B1, a refrigerant (for example a chlorofluorocarbon or a chlorine-free refrigerant gas) flows, and brine (for example, salt water or water) flows inside the second circuit C1 and the third circuit D1.

The construction of the first circuit B1 will be described first. A compressor 1 is arranged in the first circuit B1, in which there can be a suction port 2 and an outlet port 3. The compressor 1 is driven by an internal combustion engine (described below) or an electric motor (described below). In turn, an external heat exchanger 4 is arranged in the second part of the first circuit B1. The external heat exchanger 4 is here, for example, a condenser mounted in front of the engine distribution area. The external heat exchanger 4 has a first flow port 4A and a second flow port 4B.

A fan 5 is provided for the external heat exchanger 4. The fan 5 is driven by an internal combustion engine or an electric motor. Inside the first circuit B1, also a pressure reduction unit 6 and a reservoir 7 are arranged. The pressure reduction unit 6 performs adiabatic expansion of the refrigerant, an expansion valve being used, for example. In the pressure reduction unit 6, a first flow opening 6A and a second flow opening 6B can be distinguished. The first flow opening 6A is connected to the second flow opening 4B of the external heat exchanger 4. The reservoir in turn has an inlet 7A and an outlet 7B.

Also provided are a first heat storing device 8 which is part of the first circuit B1 and part of the second circuit C1, and a second heat storing device 9 which is part of the first circuit B1 and part of the third circuit D1. An example of the construction of the first heat-storing device 8 and the second heat-storing device 9 is shown exhaustively in FIG. 2.

The first heat storing device 8 has a housing 10 and is further provided with pipes 11 and 12 routed inside the housing 10. The pipe 11 is part of the first circuit B1 and the tube 12 is part of the second circuit C1. The pipes 11 and 12 are tied together or closely spaced within the housing 10. Thus, the flow paths of the two coolants are adjacent - parallel to each other.

The tube 11 includes a first flow port 8A and a second flow port 8B defining an inlet and an outlet of the housing 10. The tube 12, in turn, includes a first flow port 8C and a second flow port 8D defining an inlet and an outlet port of the housing 10. The pipes 11 and 12 are formed. of a metal with extremely favorable heat-conducting properties, for example aluminum, copper or the like.

Plate-shaped radiant fins 13 are provided on the outer surface of the tubes 11 and 12. A material 14 with heat-storing properties is placed inside the housing 10. For example, water or the like may be used as the heat-storing material 14. The heat-storing material 14 contacts the tubes 11 and 12 and each of the radiant fins 13. The outer surface of the casing 10 is covered by a heat-insulating material 15.

As the structure of the second heat storing device 9 is very similar to that of the first heat storing device 8, similar elements are indicated by analogous symbols. The second heat storing device 9 has pipes 11 and 16 arranged inside the casing 10. The pipe 11 forms part of the first circuit B1, and the pipe 16 forms part of the third circuit D1. The pipe 16 is made of a metal with extremely favorable heat-conducting properties, for example aluminum, copper or the like, and includes an inlet 9A and an outlet 9B constituting the inlet and outlet of the housing 10. Inlet 9A of the second heat storing device 9 remains in contact with the outlet 3 of the compressor 1. Moreover, the pipe 11 comprises an inlet 9C and an outlet 9D constituting the inlet and outlet of the housing 10.

A four-way valve 17 is located in the first circuit B1. The four-way valve 17 selectively opens or closes the flow path between the first flow port 8A of the first heat storing device 8 or the first flow port 4A of the external heat exchanger 4 and the inlet 7A of the reservoir 7 or the second flow port 9B. a second heat storage device 9.

Moreover, there is provided a heat exchanger 18 which is part of circuit B1 and part of second circuit C1. In particular, in the first circuit B1, the heat exchanger 18 is arranged between

A pressure reduction unit 6 and a first heat-storing device 8. Figs. 3 and 4 show an embodiment of a heat exchanger 18. When a number of plates 19 with heat transfer properties are arranged in the direction along their thickness, the heat exchanger 18 is a portion of the first circuit B1 and a portion of the second circuit C1 between the plates 19 with adjacent heat transfer characteristics.

Moreover, in the case of the heat exchange device 18, a first flow opening 18A and a second flow opening 18B are provided for the first circuit B1, the openings being connected to each other. The second flow port 18B is in turn communicating with the second flow port 6B of the pressure reduction unit 6, and the first flow port 18A is communicating with the first flow port 8B of the first heat storing device 8. Moreover, the heat exchanger 18 includes a first flow port 18C and a second flow port 18D for the second circuit C1.

An air conditioner unit 20 is used for the second circuit C1 and the third circuit D1. The air conditioner unit 20 includes a conduit 23 in which an air inlet 21 and an air outlet 22 can be distinguished. Inside the conduit 23 is a fan 24, an internal heat exchanger (or evaporator) 25, and heater 26. The heater 26 has a heating core 35 and a humidifier 36. The degree of opening of the humidifier 36 is adjustable. An internal heat exchanger 25 is disposed between the fan 24 and the heater 26 inside the conduit 23.

The fan 24 is disposed closer to the air inlet 21 than the internal heat exchanger 25 and the heater 26, and the heater is disposed closer to the air outlet 22 than the fan 24 and the internal heat exchanger 25. The internal heat exchanger 25 is part of the second circuit C1 and includes the inlet 25A and outlet 25B. The first flow opening 18C of the heat exchanger 18 and the first flow opening 8C of the first heat storing device 8 communicate in parallel with the inlet 25A. On the other hand, the second flow opening 18D of the heat exchanger 18 and the second flow opening 8D of the first heat storing device 8 communicate in parallel with the outlet 25B. The heater 26 forms part of the third circuit D1 and includes an inlet 26A and an outlet 26B. The heater inlet 26A is connected to the outlet 9D of the second heat storing device 9.

Moreover, a three-way valve 27 is arranged in the second circuit C1 to direct the flow path by branch towards the second flow opening 18D of the heat exchanger 18 and towards the second flow opening 8D of the first heat storing device 8. The three-way valve 27 selectively opens or closes the flow path between the outlet 25B of the internal heat exchanger 25 and the second flow port 8D of the first heat storage device 8 or the second flow port 18D of the heat exchanger 18. Moreover, a first pump 28 is provided inside the second circuit C1. outlet 25B of internal heat exchanger 25 and a three-way valve 27. First pump 28 includes a suction port 28A and an outlet port 28B. Suction opening 28A is connected to outlet 25B and outlet 28B is connected to three-way valve 27.

Within the third circuit D1, a second pump 29 is disposed between the outlet 26B of the heater 26 and the inlet 9C of the second heat storing device 9. The first pump 28 and the second pump 29 are both an adjustable pump. The second pump 29 includes a suction port 29A and an outlet port 29B. Suction opening 29A is connected to the outlet 26B of the heater 26, and the outlet 29B is connected to the inlet 9C of the second heat storing device 9. In addition, there are provided a temperature sensor 30 for measuring the internal temperature of the first heat storing device 8, a temperature sensor 31 for measuring the internal temperature of the second heat storing device 9, and a temperature sensor 32 arranged inside the conduit 23.

A vehicle in which an air conditioner of the above type is installed includes, for example: a vehicle equipped with an internal combustion engine as a propulsion engine; a vehicle (ie, a hybrid vehicle) having a plurality of prime mover with different modes of power generation; a vehicle (i.e. an electric vehicle) incorporating an electric motor as its power source. For example, in a vehicle equipped with an internal combustion engine, and in particular with a power source engine, the engine power is transferred to the wheels by means of a transmission. A vehicle of this type is steered using the steering process shown in Fig. 5. For the sake of simplicity, the controller 33 is a controller for controlling the operation of the entire vehicle, it is a microcomputer equipped primarily with a main processor (CPU or MPU), a memory module (RAM and ROM) and an input / output connector. The data recorded by the temperature sensors 30, 31 and 32 are entered into the controller 33, and the individual types of sensors 34 receive information on the

The topic of accelerator opening, engine speed, fuel injection, suction pump vacuum, outside air temperature, vehicle speed, air conditioning switch mode, insolation, gear position, ignition key operating mode and so on. The individual signals of the sensors 34 are routed to the controller 33.

In turn, signals are emitted from the controller 33 for controlling the operation of the motor 51 and the three-way valve 27, signals for controlling the degree of opening of the humidifier 36, signals for controlling the efficiency of the first pump 28 and the second pump 29, and so on. In the case where the compressor 1, fans 5 and 24 are driven using an electric motor 50 instead of an internal combustion engine 51, the controller 33 provides signals for controlling the operation of the motor 50, compressor 1 and fans 5 and 24.

For the A1 air conditioner discussed above, you can set three operating modes: quick cooling mode, normal cooling mode (including pre-accumulation of cold) and heating mode. The operation of the A1 air conditioner in each of the selected operating modes will be discussed below.

Quick cooling mode

The quick cooling mode is selected when a rapid cooling of the interior is required because of its very high temperature or when the amount of heat stored inside the first heat storing device 8 is lower than the amount anticipated. When the quick cooling mode is selected, the operation of the four-way valve 17 is adjusted so as to connect between the first flow port 8A of the first heat storing device 8 and the inlet 7A of the reservoir 7 and blocking the connection between the second flow port 9B of the second heat storing device 9 and the first flow port 4A. external heat exchanger 4.

In operation of the compressor 1, the refrigerant in the first circuit B1 is compressed and discharged through the outlet 3 in the form of high-temperature pressurized gas. The pressurized refrigerant is transferred to the second heat storing device 4, as a result of which the temperature of the refrigerant is lowered. In particular, the heat of the refrigerant is transferred along the tube 11 and, by means of the radiant fins 13, to the heat-storing material 14, where it is stored. The second pump 29 is responsible for the flow of brine within the third circuit D1 in the direction of circulation G1.

In turn, the refrigerant released from the second flow opening 9B of the second heat storing device 9 is passed to the external heat exchanger 9. As the air flow is generated by the fan 5, the heat is radiated due to forced circulation in the external heat exchanger 4, as a result, the temperature of the refrigerant is lowered and the refrigerant is liquefied. The refrigerant thus cooled inside the external heat exchanger 4 is released through the second flow opening 4B and led to the pressure reduction unit 6. The refrigerant is adiabatically depressed by passing it through the pressure reduction unit 6 and passed to the heat exchanger 18.

The course of the heat exchange between the refrigerant and brine inside the heat exchanger 18 will be described below. The refrigerant is expanded and its temperature drops inside the pressure reduction unit 6 in the first circuit B1. In the second circuit C1 - as the flow paths of the refrigerant and brine are separated by a plate 19 - the heat of the brine is taken by the refrigerant with the desired cooling. In particular, the heat exchanger 8 is formed by a number of plates 19 arranged at a predetermined distance in the chassis, the spaces between the plates 19 being flow channels. The channels are interconnected, allowing refrigerant to flow through any of the adjacent channels across the plate 19 and to allow brine to flow through the other. This means that the flow channels are arranged adjacent - parallel to each other. There is a flow inlet and a flow outlet in the undercarriage which are connected to the refrigerant flow conduit, and further, a flow inlet and flow outlet connected to the brine flow conduit.

The heat exchanger 18 makes the flow directions of the refrigerant and brine opposite to each other. In other words, the flow direction of the refrigerant in the first circuit B1 and the brine in the second circuit C1 are opposite to each other. The purpose of this type of structure is to increase the brine cooling effect by positioning it in the flow path of the medium

The cooling effect of the refrigerant, where its cooling effect may be particularly effective, at the point where the brine leaves the heat exchanger 18, considering that the cooling effect of the refrigerant is gradually reduced and heat is lost in the heat exchanger 18 when the brine leaves the heat exchanger 18. refrigerant is passed through second flow port 18B to first flow port 18A.

As described above, the refrigerant passed through the heat exchanger 18 is introduced into the compressor 1 through the first heat storing device 8. The refrigerant circulates inside the first circuit B1. When the quick cooling mode is selected, the refrigerant flows inside the first circuit B1 in the direction F1.

On the other hand, the operation of the three-way valve 27 is adjusted to connect the outlet 28B of the first pump 28 and the second flow opening 18D of the heat exchanger 18 with each other. With the help of the first pump 28, the brine inside the second circuit C1 is cooled by the refrigerant by being passed through it. heat exchanger 18. Then the brine inside the second circuit C1 is led to the internal heat exchanger 25 in the air conditioning unit 20. When the quick cooling mode is selected, the refrigerant is passed inside the second circuit C1 towards E1.

In the case of the air conditioner 20, on the other hand, a fan 24 is driven, with the air supplied from the air intake opening 21 being fed into the interior of the vehicle XI through the exhaust port 22 via the conduit 23. When the air contained in the conduit 23 is passed through the interior heat exchanger 25, the heat contained in the air is transferred to the brine, thereby cooling the air and increasing the temperature of the brine. Thus, the temperature inside the X1 vehicle is lowered. The brine circulates inside the third circuit D1 also using the quick cooling mode; however, as the humidifier 36 of the heater 26 is closed, no heat is exchanged between the brine in the third circuit D1 and the air passed inside the conduit 23.

Normal cooling mode

The normal cooling mode is selected when cooling is required after heat has been stored inside the first heat storing device 8 in an amount above the predicted value. When the normal cooling mode is selected, the first circuit B1 and the third circuit D1 are subject to the same effects as for the quick cooling mode. Within the second circuit C1, a three-way valve 27 is controlled to connect between the outlet 28B of the first pump 28 and the second flow port 8D of the first heat storing device 8 and to close the flow path between the outlet 28B of the first pump 28 and the second flow port 18D of the heat exchanger 18. As a result, the brine released from the first pump 28 is conducted through the three-way valve 27 to the first heat storing device 8. In the first heat storing device 8, the heat exchange takes place between the refrigerant having a reduced temperature in the first circuit B1 and the brine circulating inside the second circuit C1.

As shown in Fig. 2, the first heat-storing device 8 has a material 14 with heat-storing properties. The heat of the brine is absorbed by the material 14 with heat-storing properties, whereby the brine is sufficiently cooled. Moreover, as shown in Fig. 2, the refrigerant and brine are led in opposite directions. In other words, the flow direction F1 of the refrigerant in the first circuit B1 and the flow direction H1 of the brine in the second circuit C1 are opposite to each other. The purpose of such a structure is to increase the cooling effect of the brine by positioning in the flow path of the refrigerant, where its cooling effect may be particularly effective, at the point where the brine leaves the heat exchanger 18, taking into account that the cooling effect of the refrigerant is gradually diminished. and heat is lost in the heat storing device 8 then, when the refrigerant is led through the second flow port 8B to the first flow port 8A.

According to this embodiment of the invention, even in the normal cooling mode, the refrigerant in the first circuit B1 is introduced into the first heat storing device 8 through the heat exchanger 18. However, in the normal cooling mode, the refrigerant inside the first circuit B1 can be introduced into the first heat-storing device. storing heat 8 without having to pass it through the heat exchanger 18 (i.e. bypassing the heat exchanger 18). By using a structure of this type, the flow path of the refrigerant is shortened, whereby the energy required to run the compressor 1 for generating the force required to transfer the refrigerant can be saved, which in turn allows a reduction in fuel consumption.

Accordingly, the brine cooled by the first heat-storing device 8 is released through the first flow opening 8C of the first heat-storing device 8 and is then transferred to the air-conditioning unit 20. Other actions not described here are the same as for quick cooling mode. In other words, when the normal cooling mode is selected, the brine flows inside the second circuit C1 towards H1. Descriptions of the initial cold accumulation mode will be omitted here.

Heating mode

When the heating mode is selected, the operation of the four-way valve is controlled so as to establish communication between the first flow opening 8A of the first heat storing device 8 and the second flow opening 9B of the second heat storing device 9, and to establish communication between the inlet 7A of the reservoir 7 and the second. 4A flow opening of the external heat exchanger 4. The operation of the three-way valve 27 is controlled to establish communication between the discharge port 28B of the first pump 28 and the second flow port 8D of the first heat storing device 8 and to establish communication between the discharge port 28B of the pump 28 and the second flow port 18D of the heat exchanger 18. The first pump 28 and the second pump 29 are in operation and the humidifier 36 of the heater 26 is open.

When the heating mode is selected, the refrigerant in the first circuit B1 is compressed using compressor 1 and converted to pressurized gas at an elevated temperature. The refrigerant is then passed to the second heat storing device 9. When the refrigerant is transferred to the second heat storing device 9, the heat of the refrigerant will be transferred to the brine in the third circuit D1. In particular, the heat of the refrigerant is transferred to the brine via a pipe 11, a radiant rib 13 of a heat-storing material 14 and a pipe 16. Moreover, the refrigerant is drawn into the compressor 1 via a heat exchanger 18, a pressure reduction unit 6, an external exchanger. heat 4 and tank 7. When selecting the heating mode as described above, the refrigerant is passed inside the first circuit B1 towards J1.

In turn, in the second circuit C1, the brine is transferred from the outlet port 28B of the first pump 28 towards the first heat storing device 8 by the operation of the first pump 28. Then, in the first heat storing device 8, the heat of the refrigerant is transferred to the brine inside the second circuit C1. as a result, the brine is heated. In particular, the heat of the refrigerant is transferred to the brine via the pipes 11 and 12, the radiant fin 13 and the heat-storing material 14. The brine at elevated temperature is released from the first flow opening 8C of the first heat storing device 8 and transferred to the internal heat exchanger 25 in the air conditioning unit 20. When the air conveyed inside the conduit 23 is passed through the internal heat exchanger 25, the heat of the brine is transferred to the air inside the conduit 23 and the heated air is introduced through the outlet 22 into the interior of the vehicle X1. In this way, the interior of the X1 is heated. The heat released from the outlet 25B of the internal heat exchanger 25 is then sucked through the suction port 28A of the first pump 28.

When a heating mode is selected inside the third circuit D1, the second pump 29 is operational and the brine flows inside the third circuit D1 towards G1. Accordingly, the brine, the temperature of which has increased in the second heat storing device 9, is led to the heater 26. In the heater 26, the heat of the brine is transferred to the air inside the conduit 23, as a result of which the air in the conduit 23 is additionally heated. The heat released by the outlet 26B of the heater 26 is sucked through the suction opening 29A of the second pump 29.

A control example will be described below, showing the selection of the above-mentioned three operating modes based on the flow diagrams shown in Figs. 6 and 7. Each of the parts of the diagram indicated with a circled number in Fig. 6 is expanded in Fig. 7 with reference to analogous reference numbers. in Circle. Thus, starting with the flow diagram in Fig. 6, attention is drawn to step S601 where a choice is made as to whether to activate the air conditioner A1. At12

For example, when the air conditioner is turned on, the answer in step S601 is YES, and then, in step S602, a selection is made as to whether to activate the quick cooling mode.

The decision in step S602 is made, for example, on the basis of the plan in Fig. 8 and the diagram in Fig. 9. The plan in Fig. 8 shows the relationship between the temperature of the material 14 having heat-storing properties in the first heat-storing device 8 and the current state (cooling). / heating) of the material 14 with heat storage properties. The plan shown in Fig. 8 shows that: the heat-storing material 14 is in solid form when its temperature is below T2; the heat-storing material 14 is in a mixed form (solid and liquid) when its temperature is T2; the heat-storing material 14 is in liquid or mixed form (liquid and gas) when its temperature is above T2.

As shown in the diagram in Fig. 9, when the temperature of the heat accumulating material 14 in the first heat accumulating device 8 increases, the quick cool command is OFF, as long as the temperature of the heat accumulating material 14 is is T6 or less. When the temperature of the heat-storing material 14 in the first heat storing device 8 becomes T6 or higher, the quick cooling command is activated (ON). On the other hand, when the temperature of the heat-storing material 14 in the first heat-storing device 8 drops, the quick cooling command is activated (ON) when the temperature of the heat-storing material 14 exceeds T2, and remains OFF. provided the temperature of the heat-storing material 14 is T2 or less. Thus, the hysteresis is set for the temperature thresholds T2 and T6. It is also possible to judge if there is a need for rapid cooling by measuring the ambient temperature around or inside the vehicle and compare if the measured value is above a predetermined value.

While the answer of step S602 is YES, the quick cool mode is selected. Then, the operation of the four way valve 17 and the three way valve 27 is adjusted in a manner corresponding to the quick cooling mode, and further the first pump 28 and the second pump 29 are activated (step S604) followed by step S605.

In step S605, an assessment is made as to whether insufficient cold accumulation has been recorded in the first heat storing device 8 according to Figs. 8 and 10. "Insufficient cold accumulation" means that "the temperature of the heat-storing material 14 has not been lowered to the prescribed value or lower ". As shown in the diagram in Fig. 10, when the temperature of the material 14 with heat accumulation properties increases, insufficient accumulation of cold is not signaled (OFF option), as long as the temperature of the material 14 with heat accumulation properties is T5 or less, and it is signaled when (option ON), when the temperature of the heat-storing material 14 will exceed the value of T5. On the other hand, when the temperature of the heat-storing material 14 decreases, insufficient cold accumulation is signaled (ON option) when the temperature of the heat-accumulating material 14 exceeds T2, and not signaled (OFF) as long as the material temperature is 14 with heat storage properties is T2 or less.

In the case where the answer in step S605 is YES (YES), the amount of heat stored in the material 14 with heat-storing properties is insufficient. In step S606, the air conditioning priority request is turned ON and the routine continues to step S608. On the other hand, when the answer in step S605 is negative (NO), the stored heat in the material 14 with heat-storing properties is sufficient. The air conditioning priority request is turned OFF in Step S607, and the procedure continues to Step S608. "A / C Priority Request" means that "compressor 1 is allowed to operate regardless of the engine load," provided that the amount of heat stored in the first heat storing device 8 in the case of performing a cooling operation using the first heat storing device 8 as the heat source or the amount of heat stored in the second heat storing device 9 in the case of performing a heating operation using the second heat storing device heat 9 as a heat source is insufficient in relation to the demand, as a result, the desired air conditioning cannot be provided. '

In step S608, it is checked that the cold accumulation in the first heat storing device 8 has been completed according to the plan shown in Fig. 8 and the diagram in Fig. 11. "Completion of cold accumulation" means that the "temperature of the material 14 with accumulation properties is complete.

The heat was lowered to the intended temperature or lower. " For example, when the temperature of the material 14 with heat accumulation properties increases, the end of the accumulation of cold is signaled (option ON) when the temperature of the material 14 with heat accumulation properties is T2 or less, and it is not signaled (option OFF) when the temperature of the material is 14 with heat accumulation properties exceeds T2. On the other hand, when the temperature of the material 14 with heat accumulation properties is lowered, the completion of the accumulation of cold is not signaled (option OFF), as long as the temperature of the material 14 with heat accumulation properties exceeds T1, and the completion of the accumulation of cold is signaled (option ON), provided the temperature of the heat-storing material 14 is T1 or less. Thus, the hysteresis is set for the temperature thresholds T1 and T2.

While the answer of step S608 is YES, in step S609 it is judged whether the completion of heat accumulation in the second heat storing device 9 is signaled (ON) based on the design in Fig. 12 and the diagram in Fig. 13. "Completion of heat storage" means that "the temperature of the heat-accumulating material 14 rises above a predetermined value". The plan shown in Fig. 12 shows the relationship between the temperature of the material 14 with heat storage properties when the sensible heat of the liquid phase is applied and under cooling / heating conditions. In particular, the target temperature for the accumulation of cold is set at a level between T8 and T9, i.e. between the melting point and the boiling point of the material 14 with heat accumulation properties.

When the temperature of the material 14 with heat accumulation properties increases, the end of the accumulation of cold is not signaled (option OFF) when the temperature of the material 14 with heat accumulation properties is T9 or less, and it is signaled (option ON) when the temperature of the material 14 with heat accumulation properties exceeds T9. On the other hand, when the temperature of the heat-storing material 14 is lowered, the completion of the accumulation of cold is signaled (option ON), as long as the temperature of the material 14 with heat-accumulation properties exceeds T8, and the completion of heat accumulation is not signaled (option OFF), provided the temperature of the heat-storing material 14 is T8 or less. Thus, the hysteresis is set for the temperature thresholds T8 and T9.

While the answer of step S609 is YES, compressor 1 is not allowed to operate (OFF) at step S610, whereupon the routine continues to step S618. On the other hand, when the answer to step S608 is NO (NO), compressor 1 is allowed to operate (option ON) at step S611, whereupon the procedure continues to step S618.

On the other hand, while the answer to step S609 is NO (NO), compressor 1 is allowed to operate (ON option) in step S612, and in step S613 it is judged whether the heat-storing material 14 in the second device is heat accumulation 9 is thawed (i.e. under defrosting conditions). While the answer to step S613 is NO, defrosting starts in step S616 and timer 1 is started in step S617. As shown in Fig. 1, when the thawing operation is started, the material 14 with thawing properties is melted by temporarily diverting the circulation of the refrigerant inside the first circuit B1 to that of the heating mode (i.e., the circulation direction J1 shown in fig. 1), provided that the cooling load is low and the heat-storing material 14 in the first heat-storing device 8 is completely solid and the accumulation of cold is completed, while the refrigerant is transferred inside the first circuit B1 towards circulation F1 to carry out the cooling process.

While the answer of step S613 is YES (YES), in step S614 it is judged as to whether timer 1 is finished. For example, the time required until the heat-storing material 14 turns into a liquid is determined from the temperature of the heat-accumulating material 14 in the second heat-storing device 9, after which timer 1 is set based on the obtained data.

While the answer of step S614 is YES, the defrost process is not enabled (OFF) in step S615. The direction of circulation of the refrigerant inside the first circuit B1 returns to that corresponding to the cooling mode (i.e., the direction of circulation F1 shown in Fig. 1), and the procedure continues to step S618. On the other hand, if the answer of step S614 is NO (NO), the process continues to step S618 with no titers.

PL 209 334 B1

As long as the answer of step S618 is YES (YES), operation continues to step S619. First pump 28 is stopped and it returns to step S601. In turn, when the answer of step S618 is NO (NO), the first pump 28 is activated after its capacity is adjusted as described below. First, the first pump 28 is adjusted and the heat capacity is adjusted by adjusting the degree of opening of the humidifier 36 of the heating core 35. The capacity of the first pump 28 is adjusted so that the air temperature TE downstream of the outlet 22 in the flow direction reaches the target temperature TEO. Accordingly, during the cooling operation, when the principal interior air temperature of the vehicle X1 is higher than the target temperature, adjustment is performed to increase the flow rate for the first pump 28. On the other hand, when the vehicle interior air temperature X1 is at or below the target value, adjustment is made to limit the flow rate of the first pump 28. Conversely, during the heating operation, when the vehicle interior air temperature X1 is above the target temperature adjustment is performed to limit the flow rate for the first pump 28. Then, when the air temperature inside the vehicle X1 is at or below the target value, adjustment is made to increase the flow rate for the first pump 28.

Accordingly, when flow rate control is performed for the first pump 28, a PI check may be performed to provide feedback on the air temperature inside the vehicle X1 with a target temperature. An example of the formula for calculating the flow rate for each of the pumps used for PI control is shown below.

During the cooling process:

En = TE-TEO

P1out = P1out (n-1) + Kp ((E (n) -E (n-1)) + (T / Ti * E (n))

During the heating process:

En = TE-TEO

P1out = P1out (n-1) -Kp ((E (n) -E (n-1)) + (T / Ti * E (n))

Where for both formulas:

P1out is the capacity of the first pump 28; TE is the air temperature; TEO is the target temperature; E is the difference between air temperature and target temperature; KP is the proportionality constant; Ti is an integer constant; T is the sampling time.

On the other hand, when the air conditioner switch is turned off by making the decision in step S601 in Fig. 6, the answer in step S601 is NO (NO) and the procedure continues as shown in Fig. 7. Then, in step S601, S621, judging if the heating request is active (ON option). The judging in step S621 is performed according to the diagram in Fig. 14. For example, when the target temperature of the air flow from the air outlet 22 of the air conditioner unit 20 (ie, the desired TAO temperature) increases, the heating request is disabled (OFF) as long as the desired temperature is T45 or below. On the other hand, the heating request is active (ON option) when the desired temperature exceeds T45. On the other hand, when the desired temperature drops, the heating request is active (ON option) when the desired temperature exceeds T45. On the other hand, the heat request is not active (OFF) when the desired temperature is T35 or less. Thus, the hysteresis is set for the threshold values ​​T35 and T45 for the temperature.

If the answer of Step S621 is in the affirmative (S621), the heating mode is selected and the first pump 28 and the second pump 29 are activated in Step S622. Then, in step S624, it is judged whether there is insufficient heat accumulation for the first heat storing device 8 (ON option) from the design in Fig. 8 and the diagram in Fig. 10. "Insufficient heat storage" means that "the temperature of the heat-accumulating material 14 has not risen above the intended temperature." As shown, for example, in Fig. 15, when the temperature of the material 14 with heat accumulation properties increases, insufficient heat accumulation is signaled (ON option), provided that the temperature of the material 14 with heat accumulation properties is T4 or less, and insufficient heat accumulation is not signaled (OFF option), as long as the temperature of the heat-storing material 14 exceeds T4. On the other hand, when the temperature of the heat-storing material 14 drops, insufficient heat accumulation is not signaled (OFF option), as long as the temperature of the heat-storing material 14 exceeds T7 and insufficient heat accumulation.

The PL 209 334 B1 is signaled (ON option) as long as the temperature of the heat-storing material 14 is T7 or less. Thus, the hysteresis is set for the threshold values ​​42 and T7 for the temperature.

While the answer of step S624 is YES, the air conditioning priority request is turned ON at step S625, whereupon the procedure continues to step S627. On the other hand, when the answer of step S624 is NO, the air conditioning priority request is not activated (OFF) in step S626, and the procedure continues to step S627. In step S627, it is judged whether the completion of heat accumulation for the first heat storing device is signaled (ON) based on the design in Fig. 8 and the diagram in Fig. 16.

As shown in Fig. 16, for example, when the temperature of the heat accumulating material 14 increases, the completion of heat accumulating is not signaled (OFF) as long as the temperature of the heat accumulating material 14 is T4 or less, and completion of heat accumulation is signaled (option ON) as long as the temperature of the heat accumulating material 14 exceeds T4. On the other hand, in the event that the temperature of the heat accumulating material 14 drops, the completion of heat accumulation is signaled (option ON), as long as the temperature of the heat accumulating material 14 exceeds T3, and the completion of heat accumulation is not signaled (option OFF). provided that the temperature of the heat-storing material 14 is T3 or less.

If the answer of step S627 is YES, the compressor is allowed to run OFF at step S628, whereupon the procedure continues to step S630. Then, when the answer of step S627 is NO (NO), the compressor is allowed to run (ON) at step S629, and the procedure continues to step S630.

The following relationship is established for step S630:

TEO = TAO

TAO is the target temperature (desired) of the air released from the air exhaust port 22. After step S630, the efficiency of the first pump 28 and the second pump 29 is calculated in step S631, and the process returns to step S601 in Fig. 6. Negative answer in step S621 means that under these conditions neither cooling nor heating is required.

In this case, the precooling mode is selected in step S623, and the routine continues to step S607 in Fig. 6. After the pre-cooling mode has been selected, an adjustment is carried out to collect heat inside the heat storing device or to radiate heat from the heat storing device by starting the compressor 1 with a portion of the torque of the combustion engine 51 at idle, provided the fuel consumption in in the case of the internal combustion engine 51 it hardly changes; for example, when the engine is operated by an inertia force and an adjustment is made to stop the fuel delivery, the kinetic energy generated by the inertia of the vehicle is transferred to the engine 51, thereby causing the engine 51 to idle.

By providing such control, the heat of the first heat storing device 8 is radiated without adversely affecting the fuel consumption of the engine 51, and the heat is stored in the second heat storing device 9. Therefore, it is possible to prepare while waiting for a new request regarding not only the operation of the air conditioner, but also the heating system.

At each stage when the ignition key is turned, that is, when the system is activated, various judgments are made regardless of the temperature value in the respective diagrams. For example, in the diagram shown in Fig. 9, when the system is activated, the fast cooling request is active (ON option). On the other hand, as shown in the diagram in Fig. 10, when the system is activated, insufficient cooling is signaled (ON option) for the first heat accumulation device 8. In the case of the diagram shown in Fig. 11, when the system is activated, insufficient cold accumulation is not signaled (OFF option) in the case of of the first heat storing device 8. In the case of the diagram shown in Fig. 13, when the system is activated, the completion of heat storage is not signaled (option OFF) for the second heat storing device 9. In the case of the diagram shown in Fig. 14, when the system is activated, the heating request is signaled (option ON). In the case of the diagram shown in Fig. 15, when the system is activated, insufficient heat accumulation is indicated (option ON) in the case of the first heat storing device 8. In the case of the diagram shown in Fig. 16, when the system is activated, the accumulation is completed

Heat is not signaled (OFF) in the case of the first heat storing device 8. At step S601 in Fig. 6, it can also be judged from the outside air temperature whether it is desired to start the air conditioner A1.

Accordingly, in the air conditioner A1 of Fig. 1, the heat exchange is performed between a refrigerant conducted inside the first circuit B1 and a brine conducted inside the second circuit C1 to heat or cool the air. Moreover, according to this embodiment of the invention, there are some differences between the heat exchanger 18 and the first heat storing device 8 in terms of heat transfer; for example, regarding the heat transfer coefficient, heat flux, heat transfer coefficient, heat resistance and the like. In particular, the heat exchange between the refrigerant and brine in the heat exchanger 18 is higher than that of the first heat storing device 8. The rationale for this is that the heat-storing material 14 has not been placed inside the heat exchanger 18, so that the heat capacity of the first heat-storing device 8 is higher than that of the heat exchanger 18 in which the heat-storing material 14 is placed.

For the above reasons, in the air conditioner A1, as shown in Fig. 1, the heat transfer (or heat transfer characteristic) between the refrigerant in the first circuit B1 and the brine in the second circuit C1 can be varied without changing the refrigerant transfer function. in the case of compressor 1, by selecting the first heat storing device 8 or heat exchanger 18. Consequently, the desired air conditioning operation can be achieved independently of the current operating mode of compressor 1, which allows the interior temperature to be adjusted arbitrarily.

Moreover, it is not so important to adjust the drive system of the compressor 1 in accordance with the required blower temperature. In other words, the impact on the engine load from air conditioning demand has been reduced. When the compressor 1 is driven by the internal combustion engine 51, it is possible to favorably influence the fuel consumption of the internal combustion engine 51. On the other hand, when the engine is powered by an electric generator and the electric motor 50 is supplied with electricity to drive the compressor 1, the consumption of electric energy is limited for the electric motor 50 in such a way that the fuel consumption can be favorably influenced. in the case of an internal combustion engine 51. In other words, the load on the engine can be equalized regardless of changes in the required blast temperature. Moreover, it is possible to limit the consumption of part of the energy used to drive the compressor 1 when the motor torque is low, thereby reducing the effect of limiting its power supply.

Moreover, in the first heat storing device 8 or heat exchanger 18 - in the case where the heat accumulation characteristic 45 for the first heat storing device 8, including the temperature, amount of heat and the like, allows to adapt to the required blowing temperature - exchange heat is transferred between the brine and the refrigerant using the first heat storage device 8. Accordingly, a mismatch between the required blowing temperature and the heat accumulation characteristics is avoided, as a result of which the operation of the air conditioner A1 can be further improved.

Moreover, the heat of the heating medium conducted inside the first circuit B1 can be stored inside the second heat storing device 9, and the heat can be transferred to the air passed along the conduit 23. Accordingly, it is possible to increase the usability of the excess heat energy that is generated during compression with the compressor 1 and that is not transferred to the heat exchanger 18 and the first heat storing device 8, which allows the operation of the air conditioner A1 to be further improved.

Typically, the heat of the condenser 4 is radiated into the surrounding air. According to this embodiment of the invention, the heat from the condenser 4 is collected inside the second heat storing device 9, and the heat energy obtained can be used in the air-mixing process during the cooling operation, as a heat source during the heating operation and as a heat source during the heating of the internal combustion engine. 51, oil heating and the like. By "air mixing" it is meant that the air cooled by the internal heat exchanger 25 is heated by a heater 26 to maintain the temperature of the interior of the vehicle X1 at the target temperature. If this heat is used as a heat source for warming up an internal combustion engine 51 or heating oil and the like, the following solutions are possible, for example:

1. Requirements are met (for example: the vehicle is stopped, the accelerator opening is at zero and the brake pedal is pressed (ON)) and the idle stop adjustment is performed to immobilize the combustion engine 51.

2. A hybrid vehicle equipped with an internal combustion engine 51 and an electric motor as driving motors moves under the influence of the torque of the electric motor, and the internal combustion engine 51 is stationary.

Moreover, the heat of the high-temperature compressed refrigerant gas compressed by the compressor 1 is taken by the second heat storing device 9, after which the refrigerant is introduced into the condenser, whereby a reduced amount of refrigerant heat is radiated through the condenser. This allows the speed of operation of the fan 5 to be lowered, thereby reducing the electrical energy required to operate the fan 5. Moreover, it is also possible to improve the fuel consumption of the internal combustion engine 51 for driving an electric generator producing electricity.

According to the air conditioning system shown in Fig. 1, when the quick cooling mode or the cooling mode is selected, the direction of the refrigerant flow inside the circuit B1 and the direction of the brine flow inside the second circuit C1 are opposite to each other. In particular, when a quick cooling mode is selected, the flow directions of the refrigerant and brine are opposite to each other inside the heat exchanger 18, and when the cooling mode is selected, the flow directions of the refrigerant and brine are opposite to each other inside the first heat storing device 8. Therefore, the temperature difference between refrigerant and brine can be kept as high as possible inside the entire area in accordance with the flow directions of the refrigerant and brine. Such a solution makes it possible to increase the efficiency of the heat exchange process inside the heat exchanger 18 and the first heat storing device 8.

Inside the first heat storing device 8 and the second heat storing device 9 a radiant fin 13 are provided. Accordingly, the heat transfer mode can be standardized for all material 14 with heat storing properties. This allows the load on the material 14 with heat accumulating properties to be reduced, thereby increasing the durability of the heat accumulating devices. Moreover, the use of the radiant rib 13 increases the heat transfer area between the refrigerant and brine, which in turn increases the efficiency of the heat exchange process.

Moreover, when the quick cooling mode or the cooling mode is selected, it is possible to store the heat of the refrigerant in the second heat storing device 9 before passing the refrigerant to the external heat exchanger 4. Accordingly, the speed of the fan 5 for cooling the refrigerant can be reduced. . In the embodiment shown in Fig. 1, the heat of the second heat storing device 9 is transferred to the air conditioning unit 20. However, if the heat of the second heat storing device 9 is used to warm up the internal combustion engine 51 when it is started, the reduction of emissions can be improved. This example applies to a vehicle equipped with an engine only as propulsion engine, a hybrid vehicle having a combustion engine and an electric motor as a propulsion engine, and in the case of an economy vehicle that allows engine start and stop adjustments based on predetermined guidelines outside of the ignition key operating mode. and others.

Moreover, according to the embodiment shown in figure 1, it is possible to store cold inside the first heat storing device 8 and to store heat inside the second heat storing device 9. Provided that both cooling and heating are permitted (i.e. in spring or autumn), the heat previously stored in the second heat storing device 9 can be used when heating is required and the heat pre-stored in the first heat storing device heat storage 8 can be used when cooling is required. This solution allows you to protect against heat loss.

Moreover, when the heat is pre-stored in the second heat storing device 9 and in the first heat storing device 8 using a drive for the compressor 1, it is possible to supply the air conditioner A1. In this case, the stored heat can be used by activating only the first pump 28 and the second pump 29, but not the compressors

1. Accordingly, the fuel consumption and the power characteristics of the internal combustion engine 51 can be improved.

Since the stored heat inside the second heat storing device 9 can be used for air stirring during cooling, dehumidification, heating and the like, it is preferable that the second heat storing device 9 has the maximum amount of stored heat. In the above-mentioned diagram shown in Fig. 6, for example, when the procedure is carried out to step S612 via step S608 and S609, it is preferable to store heat in the second heat storing device 9, which allows more heat to be stored. However, when the cold accumulation process inside the first heat storing device 8 has been completed, the heat contained in the first heat storing device 8 cannot be transferred to the refrigerant circulating inside the first circuit B1 using the compressor 1.

In that case, in step S616, the heat storing material 14 contained in the first heat storing device 8 is temporarily thawed to transfer the heat contained in the first heat storing device 8 to the refrigerant inside circuit B1. Moreover, it is preferable to set the time for timer 1 in step S617 so as to obtain the expected heat capacity.

The expected heat capacity is determined from road gradient data, infrastructure data (road traffic, weather, etc.), vehicle speed, outside temperature, and the amount of heat required for air conditioning inside the vehicle. The expected heat capacity can also be determined from the amount of heat stored in the second heat storing device 9.

In the following, the relationship between the structure of the various embodiments and the present invention will be described. The refrigerant corresponds to the first heating medium according to the invention; the brine corresponds to the second heating medium according to the invention; the controller 33 corresponds to the control unit according to the invention; "The situation where the temperature of the heat storing material 14 exceeds the predetermined temperature" corresponds to "the situation where the predetermined heat value is stored in the first heat storing device"; The "direction of circulation F1 of the refrigerant inside the first circuit B1" corresponds to the "direction of circulation of the first heating medium in the first circuit" and the directions of circulation H1 and E1 of the brine in the second circuit C1 correspond to the "direction of circulation of the second heating medium in the second circuit".

The characteristic constructions presented in the case of individual execution methods are, for example: in particular, the air conditioner control unit responsible for the heat exchange between the heating medium and the first heat transfer object by moving the heating medium using the transfer unit or pressure unit, characterized by comprising temperature control demand evaluation means for evaluating the temperature control demand on the part of the facility inside which the air conditioning is to operate, as well as means of choice for selecting - when the heat exchange is to be carried out between the heating medium and the first heat transfer object - which of the heat exchangers with different heat transfer performance and located at different points in the direction of the heating medium to be used.

Moreover, the selection means further offers the function of selecting any one of a plurality of heat exchangers in case the temperature of the first heat transfer object changes to a value higher than a predetermined value to improve the heat transfer between the heating medium and the first heat transfer object. Moreover, the selection means has the function of selecting any one of a plurality of heat exchangers with a predetermined function, whereby the temperature of the heat transferring object can be set at a predetermined level.

Moreover, a heat exchanger is provided here to effect a heat exchange between the heating medium and the second heat transfer object, as long as the heating medium is influenced by mechanical energy using a transfer or pressure unit, as a result of which the temperature of the heating medium changes. Moreover, the direction of movement of the heating medium and the direction of movement of the first heating object are opposite to each other. Moreover, the heat transferred between the heating medium and the first heat transfer object and the heat transferred between the heating medium and the second heat transfer object are transferred in the same part of the object with the use of a temperature control system.

PL 209 334 B1

Steps S601, S602 and S621 in Figures 6 and 7 correspond to the means of assessing the need for temperature control, and steps S603, S604, S622 and S623 correspond to the means of selection.

The temperature control demand evaluation means as described herein may be understood as a temperature control demand indicator or controller for temperature control demand evaluation, and the selection means may be a selector or controller for selection making. In this case, the controller 33 shown in Fig. 5 corresponds to a temperature control demand indicator, a controller for a temperature control demand assessment, a selector or a controller for a selection. Moreover, the temperature control demand estimation means as described herein may be a temperature control demand determination step, while the selection means may be regarded as a selecting step, and the air conditioner control unit may be understood as an air conditioner control step.

As described above, in the air conditioner of the invention, the first heating medium is heated or cooled using a power unit, such as a motor, and the first heating medium does not directly exchange heat with air. This allows the first heating medium to be heated or cooled independently of the air conditioning demand, which means it is possible to limit the direct influence of the air conditioning demand on the load on the power unit. As a result, the fuel consumption of the vehicle's engine can be improved.

Moreover, a plurality of heat exchangers with different heat transfer characteristics are arranged in the circuit where the first heating medium is carried out. The second heating medium is selectively transferred to any of these heat exchangers where heat is exchanged with the first heating medium. Thanks to the use of this type of design, it is possible to switch between the option of cooling and heating the second heating medium, which allows the air conditioning to be activated according to the demand.

When the flow directions of the first heating medium and the second heating medium inside the heat exchanger are opposite to each other, it is possible to obtain a higher temperature difference between the heating factors at the outlet of the second heating medium, which allows efficient heating or cooling of the second heating medium. In other words, the efficiency of heat transfer between the individual heating factors can be improved.

According to the present invention, instead of a heat exchanger inside the first circuit, a heat exchanger having a heat storing function or a heat storing device may be used. In other words, the above-mentioned third heat exchanger may be replaced by an exchanger having such a heat-storing function. By using this type of design, since the heat transfer efficiency of the first heat exchanger is high, the demand for rapid cooling is fully met. Moreover, as the heat for cooling can be stored inside the third heat exchanger, the energy efficiency of the solution can be improved.

According to the present invention, a second heat storing device can also be used. The second heat storing device is heated by receiving heat from the first heating medium and thereafter it stores the heat inside. For example, the first heating medium may be a liquid that adiabatically decompresses when it is compressed, thereby reducing its temperature. In this case, since the amount of heat of the first heating medium increases due to compression, the heat is not released to the outside but recovered by the second heat storing device. As a result, the energy efficiency of the solution can be improved, while improving the fuel consumption rate of the vehicle.

The heat storing device according to the invention is constructed in such a way that the pipe through which the heating medium flows is integrated with a plurality of ribs, the pipe and the ribs being embedded in a material with heat storing properties. Accordingly, it is possible to increase the heat transfer efficiency between the heat-storing material and each of the heating media, and furthermore, to prevent or reduce thermal stress in the heat storing device.

According to the present invention, the heat of the second heat storing device can be transferred to air by means of a third circuit, which allows increasing the thermal efficiency during the heating process, and an air mixing operation can be carried out in a simple and efficient manner.

PL 209 334 B1

The second heat storing device is positioned directly downstream of the compressor which is responsible for applying pressure and compressing the first heating medium. Accordingly, the amount of heat from the first heating medium that is recovered by the second heat storing device increases. As a result, the load on the radiant device decreases, which in turn allows the dimensions of the radiant device to be reduced and energy consumption to be reduced in the event of cooling being required.

The drive motor can be used to drive the compressor. In this case - as long as the driving motor is positively driven by the inertia force - it is possible to select the pre-heat accumulation mode when the heat accumulation is carried out by driving the compressor with the inertia force. As a result, the amount of energy recovered is further increased, which helps to improve fuel consumption.

The liquid collected inside the second heat storing device according to the invention finds various applications. In order to control the air temperature, it is possible, for example, to use this type of heat in an air-mixing process in order to transfer the heat to the air previously cooled in the second heat exchanger. On the other hand, heat may be used to heat or keep warm an oil or an internal combustion engine. Thus, the recovered heat can be used efficiently in such a way as to improve the fuel consumption rate and reduce the emission rate.

The present invention finds industrial application in those fields where air conditioning systems for interiors, work spaces and others are used; an air-conditioning system is manufactured to meet the needs of this type. Moreover, the invention allows use wherever a stationary air conditioning system or a portable air conditioning system inside a vehicle is used or manufactured.