DE112017006293T5 - Vehicle air conditioning device - Google Patents

Abstract

In a dehumidifying and cooling mode, a temperature spread (temperature fluctuation) generated in a heat absorber is prevented or suppressed. The dehumidifying and cooling mode is performed which causes a refrigerant discharged from a compressor 2 to radiate heat in a radiator 4 and an outdoor heat exchanger 7, decompressing heat-radiating refrigerant through an indoor expansion valve 8 and then allowing the refrigerant to absorb heat in a heat absorber 9. A controller controls a capacity of the compressor based on the temperature of the heat absorber and controls a valve position of an outdoor expansion valve based on the temperature or the pressure of the radiator. A minimum valve opening degree of an outdoor expansion valve is changed so that no temperature dispersion is generated in the heat absorber or the temperature dispersion becomes low.

Description

Technical area

The present invention relates to a vehicle air conditioning apparatus of a heat pump system that conditions the air of a vehicle interior of a vehicle.

State of the art

The update of environmental problems in recent years has spread to hybrid and electric vehicles. Consequently, an air conditioning apparatus applicable to such a vehicle has been developed, which includes a compressor for compressing and discharging a refrigerant, a radiator provided on the side of a vehicle interior to radiate the refrigerant heat, a heat absorber is provided on the side of the vehicle interior to allow the refrigerant to absorb heat, and an outdoor heat exchanger, which is provided outside the vehicle interior to radiate heat or heat to absorb the heat, and which changes a heating mode and performs to the from the Compressor discharged refrigerant to radiate heat in the radiator and to let the refrigerant from which the heat was radiated in this radiator to absorb heat in the outdoor heat exchanger, a dehumidifying and heating mode to radiate the discharged refrigerant from the compressor heat in the radiator and the cold ttel, from which the heat was radiated in the radiator, heat only in the heat absorber or in the heat absorber and outdoor heat exchanger record, a dehumidifying and cooling mode to radiate the refrigerant discharged from the compressor heat in the radiator and outdoor heat exchanger and the refrigerant heat in the heat absorber, and a cooling mode for allowing the refrigerant discharged from the compressor to radiate heat in the outdoor heat exchanger and allowing the refrigerant to absorb heat in the heat absorber (see, for example, Patent Document 1).

Then, the number of revolutions of the compressor in the dehumidifying and cooling mode is controlled based on the temperature of the heat absorber to control a cooling capability (dehumidification) of the heat absorber. Further, a valve position of the outdoor expansion valve for decompressing the refrigerant flowing into the outdoor heat exchanger is controlled based on the temperature of the radiator to control a heating capability of the radiator.

CITATION

Patent documents

Patent Document 1: Japanese Patent Application Publication No. Hei. 2014-205563

Summary of the invention

Problems to be solved by the invention

That is, in the dehumidifying and cooling mode, the valve position of the outdoor expansion valve is lowered to allow the temperature of the radiator to rise. However, a problem arises because a refrigerant circulation amount of the heat absorber is reduced as the valve position of the outdoor expansion valve becomes small, a temperature dispersion (indicating that a change in temperature occurs depending on a portion of the heat absorber) becomes large, and the dehumidifying performance deteriorates as well a target output temperature is difficult to produce.

The present invention has been developed to solve such conventional problems, and an object thereof is to provide a vehicle air conditioning apparatus which prevents or suppresses temperature variations (changes in temperature) generated in a heat absorber in a dehumidifying and cooling mode To improve the air conditioning performance of a vehicle interior.

Means of solving the problems

A vehicle air conditioning apparatus of the present invention includes a compressor for compressing a refrigerant, an air flow passage through which the air to be supplied to a vehicle interior flows, a radiator for radiating the heat, thereby heating the air to be supplied to the vehicle interior from the air flow passage, a heat absorber for allowing the refrigerant to absorb heat, thereby cooling the air to be supplied to the vehicle interior from the air flow passage, an outdoor heat exchanger disposed outside the vehicle cabin to radiate the heat, an outdoor expansion valve to supply the refrigerant flowing into the outdoor heat exchanger decompressing, an inner expansion valve to decompress the refrigerant flowing into the heat absorber, and a control device, wherein the control device has at least one dehumidifying and cooling mode a causes the refrigerant discharged from the compressor to heat into the radiator and the outdoor heat exchanger to decompress the refrigerant from which heat was radiated, through the inner expansion valve, and then to let the refrigerant absorb heat in the heat absorber. The vehicle air conditioning apparatus is characterized in that, in the dehumidifying and cooling mode, the controller controls a capacity of the compressor based on a temperature of the heat absorber and controls a valve position of the outdoor expansion valve based on a temperature or a pressure of the radiator and changes a minimum valve opening degree of the outdoor expansion valve to prevent the occurrence of a temperature dispersion in the heat absorber or to reduce the temperature dispersion.

The vehicle air conditioning apparatus of the invention of claim 2 is characterized in that in the above invention, the control device changes the minimum valve opening degree of the outdoor expansion valve so that the temperature dispersion of the heat absorber maintains a predetermined limit value allowed for the temperature dispersion of the heat absorber.

The vehicle air conditioning apparatus of the invention of claim 3 is characterized in that, in the above related inventions, the vehicle air conditioning apparatus includes an indoor blower for flowing the air into the air flow passage, and the control apparatus based on a volume of the air passing through the heat absorber through the indoor blower is intended to change the minimum valve opening degree of the outdoor expansion valve in a direction of increase as the air volume increases.

The vehicular air-conditioning apparatus of the invention of claim 4 is characterized in that in the above-mentioned inventions, the control apparatus changes the minimum valve opening degree of the outdoor expansion valve toward a decrease based on a valve position of the indoor expansion valve as the valve position increases / increases.

The vehicle air conditioning apparatus of the invention of claim 5 is characterized in that in the above-mentioned inventions in the dehumidifying and cooling mode, the control device controls the capacity of the compressor based on the temperature of the heat absorber and a target temperature of the heat absorber and the minimum valve opening degree of the outdoor expansion valve in the direction decreases as the target temperature of the heat absorber is reduced.

The vehicle air conditioning apparatus of the invention of claim 6 is characterized in that in the above-mentioned inventions, the control device provides a predetermined hysteresis when the minimum valve opening degree of the outdoor expansion valve is changed.

Advantageous Effects of the Invention

According to the present invention, in a vehicle air conditioning apparatus including a compressor for compressing a refrigerant, an air flow passage through which the air to be supplied to a vehicle interior flows, a radiator for radiating the heat, thereby cooling the air to be supplied from the air flow passage to the vehicle interior an outside heat exchanger disposed outside the vehicle interior for radiating the heat, an outside expansion valve for decompressing the refrigerant flowing into the exterior heat exchanger, an inside expansion valve for decompressing the refrigerant flowing into the heat absorber, and a control device; wherein the control device performs at least one dehumidifying and cooling mode for radiating heat released from the compressor into the radiator and the outdoor heat exchanger, the refrigerant, from which heat has been radiated, decompressing through the inner expansion valve, and thereafter allowing the refrigerant to absorb heat in the heat absorber, and in the dehumidifying and cooling mode, the control device controls a capacity of the compressor based on a temperature of the heat absorber and a valve position of the outer expansion valve Controlling based on a temperature or a pressure of the radiator and a minimum valve opening degree of the outer expansion valve changes to prevent the occurrence of a temperature dispersion in the heat absorber or to reduce the temperature dispersion. It is therefore possible to prevent the disadvantage that the valve position of the outer expansion valve is reduced to reduce a refrigerant circulation amount to the heat absorber and to generate the temperature dispersion in the heat absorber or to increase the temperature dispersion of the heat absorber.

Thus, while maintaining the dehumidifying performance of the heat absorber in the dehumidifying and cooling modes, the temperature of the radiator can also help conserve energy because the allowable range of the temperature can be increased. In addition, it is generally possible to increase the air conditioning capacity of the vehicle interior and also to improve the comfortableness of an occupant, since a target exit temperature of the air to be supplied to the vehicle interior will also be easy to manufacture.

In this case, as in the invention of claim 2, when the control device changes the minimum valve opening degree of the outdoor expansion valve so that the temperature dispersion of the heat absorber satisfies the predetermined limit value allowed for the temperature dispersion of the heat absorber, it is possible to reduce the valve position of the outdoor expansion valve Accompanying temperature dispersion of the heat absorber in a suitable manner to prevent or u nterd back.

When an internal blower is provided to let the air flow in the air flow passage, and the air passes through the heat blower through the indoor blower, the refrigerant actively evaporates as the volume of the air to be flowed increases, and thus the heat absorber temperature dispersion becomes large. Thus, as in the invention of claim 3, when the control device changes the minimum valve opening degree of the outdoor expansion valve in a direction of increase based on a volume of the air to be passed through the heat absorber by the indoor blower when the air volume increases, it is possible to to effectively prevent or suppress the temperature dispersion of the heat absorber accompanying a reduction in the valve position of the outer expansion valve.

Also, the temperature dispersion of the heat absorber becomes small as the refrigerant circulation amount of the heat absorber increases when a valve position of the indoor expansion valve to decompress the refrigerant flowing into the heat absorber is increased. Consequently, as in the invention of claim 4, when the control device based on a valve position of the inner expansion valve changes the minimum valve opening degree of the outer expansion valve toward decrease as the valve position increases, it is possible to raise the temperature of the radiator unhindered while the temperature dispersion of the Heat absorber is prevented or suppressed.

Further, the controller controls the compressor based on the temperature of the heat absorber and its target temperature in the dehumidifying and cooling modes. Therefore, when the target temperature of the heat absorber is reduced, the capacity of the compressor is increased, and the refrigerant circulation amount of the heat absorber also increases. Consequently, as in the invention of claim 5, when the control device changes the minimum valve opening degree of the outdoor expansion valve in the direction of a decrease, when the target temperature of the heat absorber is reduced, it is possible to increase the temperature of the heat absorber unhindered, while the temperature dispersion of Heat absorber is prevented or suppressed.

Then, as in the invention of claim 6, since the control device provides a predetermined hysteresis when the minimum valve opening degree of the outdoor expansion valve is changed, it is possible to prejudge in advance the disadvantage that hunting occurs when the minimum valve opening degree of the outdoor expansion valve is changed, to avoid.

list of figures

• 1 Fig. 13 is a constitutional view of a vehicle air conditioning apparatus of an embodiment to which the present invention is applicable;
• 2 FIG. 10 is a block diagram of a control device of a vehicle air conditioning apparatus of FIG 1 ;
• 3 FIG. 14 is a typical diagram of an air flow passage of the vehicle air conditioning apparatus of FIG 1 ;
• 4 FIG. 13 is a control block diagram relating to the compressor control in a heating mode of a heat pump controller of FIG 2 ;
• 5 FIG. 10 is a control block diagram regarding the compressor control in a dehumidifying and heating mode, a dehumidifying and cooling mode, a cooling mode, and a MAX cooling mode of the heat pump control of FIG 2 ;
• 6 is a control block diagram relating to the control of the auxiliary heater (auxiliary heater) in the dehumidifying and heating mode of the heat pump control of 2 ;
• 7 FIG. 15 is a graph showing a relationship between the valve position of an outside expansion valve and the temperature of a radiator in the dehumidifying and cooling mode of the vehicle air conditioning apparatus. FIG 1 shows;
• 8th FIG. 12 is a graph showing a relationship between a valve position of the outside expansion valve and a temperature dispersion of a heat absorber in the dehumidifying and cooling mode of the vehicle air conditioning apparatus. FIG 1 shows;
• 9 FIG. 12 is a graph showing a relationship between a valve position of the outer expansion valve and a temperature dispersion of the heat absorber, wherein the volume of the air passing through the heat absorber is changed in the dehumidifying and cooling mode of the vehicle air conditioning apparatus 1 shows;
• 10 FIG. 12 is a graph showing a hysteresis when the minimum valve opening degree of the outdoor expansion valve is determined by the volume of the air passing through the heat absorber in the dehumidifying and cooling mode of the vehicle air conditioning apparatus. FIG 1 is changed to describe.
• 11 FIG. 15 is a diagram for explaining the control of the change of the minimum valve opening degree of the outside expansion valve by a valve position of an inside expansion valve in the dehumidifying and cooling mode of the vehicle air conditioning apparatus. FIG 1 to describe;
• 12 FIG. 10 is a time chart for describing a situation when a target temperature of the heat absorber in the dehumidifying and cooling mode of the vehicle air conditioning apparatus is the 1 is reduced;
• 13 FIG. 15 is a diagram for showing the control of the change of the minimum valve opening degree of the outside expansion valve at a target temperature of the heat absorber in the dehumidifying and cooling mode of the vehicle air conditioning apparatus. FIG 1 to describe; and
• 14 Fig. 10 is a basic view of a vehicle air conditioning apparatus of another embodiment of the present invention.

Molds for carrying out the invention

Hereinafter, the embodiments of the present invention will be described in detail with reference to the drawings.

[Embodiment 1]

1 shows a basic view of a vehicle air conditioning device 1 an embodiment of the present invention. A vehicle of the embodiment to which the present invention can be applied is an electric vehicle ( EV ) in which no engine (internal combustion engine) is installed, and is operated with an electric motor for driving, which is driven by a power charged in a battery (both are not shown in the figure), and the vehicle air conditioning device 1 The present invention is also powered by the performance of the battery.

That is, in the electric vehicle that is unable to perform heating by engine waste heat, the vehicle air conditioning apparatus performs 1 of the embodiment, a heating mode by a heat pump operation in which a refrigerant circuit is used. In addition, the vehicle air conditioning device performs 1 selectively selects the respective modes of a dehumidification and heating mode, a dehumidifying and cooling mode, a cooling mode, a MAX cooling mode (maximum cooling mode), and an auxiliary heating mode.

Incidentally, the vehicle is not limited to the electric vehicle, and the present invention is also effective for a so-called hybrid vehicle in which the engine is used together with the electric motor for driving. In addition, it goes without saying that the present invention is also applicable to a conventional vehicle running with the engine.

The vehicle air conditioning apparatus of the embodiment performs air conditioning (heating, cooling, dehumidifying, and ventilating) of a vehicle interior of an electric vehicle. An electrical type of a compressor 2 To compress a refrigerant, a radiator 4 in an air flow channel 3 a HVAC unit 10 in which vehicle interior air is ventilated and circulated to that of the compressor 2 discharged high-temperature and high-pressure refrigerant via a refrigerant line 13G allowing the refrigerant to radiate heat to heat the air supplied to the vehicle interior, an outdoor expansion valve 6 (a pressure reducing unit), which is formed of an electrovalve that decompresses and expands the refrigerant during heating, an outdoor heat exchanger 7 provided outside the vehicle interior space and performing heat exchange between the refrigerant and outside air to function as the radiator during cooling and to function as a vaporizer during heating, an interior expansion valve 8th (a pressure reducing unit) formed of an electric valve to decompress and expand the refrigerant, a heat absorber 9 which is in the air flow channel 3 is provided to allow the refrigerant to absorb heat during cooling and dehumidification to cool sucked from the interior and exterior of the vehicle and supplied to the vehicle interior air, an accumulator 12 and others are sequentially via the refrigerant pipe 13 connected, creating a refrigerant circuit R is formed.

Then the refrigerant circuit R filled with a predetermined amount of a refrigerant and oil for lubrication. Incidentally, in the outdoor heat exchanger 7 an outdoor fan 15 intended. The outdoor fan 15 forcibly passes the outside air through the outdoor heat exchanger 7 so as to perform the heat exchange between the outside air and the refrigerant, the outside air also during the stopping of the vehicle (ie its Speed is 0 km / h) through the outdoor heat exchanger 7 is directed.

Furthermore, the outdoor heat exchanger 7 a collector dryer section 14 and a subcooling section 16 successively on a refrigerant downstream side. A refrigerant line 13A arising from the outdoor heat exchanger 7 extends out, is via a solenoid valve 17 , which is opened during cooling, with the collector dryer section 14 connected. A refrigerant line 13B on an outlet side of the subcooling section 16 is via the interior expansion valve 8th with an inlet side of the heat absorber 9 connected. Incidentally, form the Sammilertrocknerabschnitt 14 and the subcooling section 16 structurally a part of the outdoor heat exchanger 7 ,

In addition, the refrigerant line 13B between the subcooling section 16 and the indoor expansion valve 8th in a heat exchange relationship with a refrigerant line 13C on an outlet side of the heat absorber 9 provided, and both lines form an indoor heat exchanger 19 , Consequently, the refrigerant passing through the refrigerant line 13B into the interior expansion valve 8th flows through the heat absorber 9 emerging low-temperature refrigerant cooled (undercooled).

In addition, the refrigerant line branches 13A extending from the outdoor heat exchanger 7 out to a refrigerant line 13D off and this branching refrigerant line 13D is in exchange and connects to the refrigerant line 13C on a downstream side of the indoor heat exchanger 19 via a solenoid valve 21 which is opened during heating. The refrigerant line 13C is with the accumulator 12 connected, and the accumulator 12 is with a refrigerant suction side of the compressor 2 connected. Furthermore, a refrigerant pipe 13E on an outlet side of the radiator 4 via the outdoor expansion valve 6 with an inlet side of the outdoor heat exchanger 7 connected.

In addition, in the refrigerant line 13G between a discharge side of the compressor 2 and an inlet side of the radiator 4 a solenoid valve 30 (which constitutes a flow channel changing device) which is closed during dehumidifying and heating and MAX cooling, as will be described later. In this case, the refrigerant line branches 13G to a bypass line 35 on an upstream side of the solenoid valve 30 from. This bypass line 35 is in exchange and connects to the refrigerant line 13E on a downstream side of the outdoor expansion valve 6 via a solenoid valve 40 (which also represents a flow channel changing device) which is opened during dehumidification and heating and MAX cooling. A bypass device 45 gets out of this bypass line 35 , the solenoid valve 30 and the solenoid valve 40 educated.

The bypass device 45 gets out of such a bypass line 35 , a solenoid valve 30 and a solenoid valve 40 thereby allowing a smooth change of the dehumidifying and heating mode and the MAX cooling mode, so that the compressor 2 discharged refrigerant directly into the outdoor heat exchanger 7 can flow, and so that the heating mode, the dehumidifying and cooling mode and the cooling mode it from that of the compressor 2 allow released refrigerant into the radiator 4 to flow, as described later.

In addition, in the air flow channel 3 on an air upstream side of the heat absorber 9 corresponding intake ports, such as an outside air intake port and an inside air intake port, are formed (represented by a suction port 25 in 1 ). In the intake opening 25 is a suction change flap 26 provided to the in the air flow channel 3 air to be introduced in indoor air, the air of the vehicle interior is (an indoor air circulation mode), and outdoor air that is air outside the vehicle interior (an outdoor air introduction mode) is to be changed. In addition, on an air downstream side of the intake change flap 26 an inside fan (a blower fan) 27 is provided to communicate the introduced inside or outside air to the air flow passage 3 to feed her and pass her through the heat absorber 9 to enable.

In addition, referred to in 1 23 shows an auxiliary heater as an auxiliary heater used in the vehicle air conditioning apparatus 1 the embodiment is provided. The auxiliary heating 23 The embodiment is formed of a PTC heater, which is an electric heater, and is in the air flow passage 3 on a windward side (air upstream side) of the radiator 4 to the air flow in the air flow channel 3 intended. If then the auxiliary heating 23 is activated to generate heat, the air in the air flow channel 3 passing over the heat absorber 9 in the radiator 4 flows, warms. That is, the auxiliary heater 23 becomes a so-called Heater core to perform or supplement the heating of the vehicle interior.

Here is the air flow channel 3 on a leeward side (one air downstream side), more than the heat absorber 9 the HVAC unit 10 through a partition 10A divided to a heating heat exchange channel 3A and a bypass channel 3B to avoid him, to form. The aforementioned radiator 4 and the auxiliary heating 23 are in the heating heat exchange channel 3A arranged.

In addition, in the air flow channel 3 on a windward side of the auxiliary heater 23 an air mix door 28 provided to set a ratio at which the air (the inside air or outside air) in the air flow channel 3 entering the airflow channel 3 flows in and through the heat absorber 9 passed through the heating heat exchange channel 3A in which the auxiliary heating 23 and the radiator 4 are arranged to be directed.

Furthermore, the HVAC unit 10 on the leeward side of the radiator 4 with corresponding outlets of a foot outlet "FOOT" 29A (first outlet), one vent outlet "VENT" 29B (a second outlet in relation to the foot outlet 29A and a first outlet with respect to a disc outlet 29C) , the disc outlet "DEF" 29C (a second outlet) formed. The foot outlet 29A is an outlet for blowing out the air to the foot of the vehicle interior and is in the lowest position. In addition, the ventilation outlet 29B an outlet for blowing air close to the chest or face of a driver in the vehicle interior and located above the foot outlet 29A , Consequently, the disc outlet 29C an outlet for blowing the air to an inner surface of a windshield of the vehicle and is located at the highest position above other outlets 29A and 29B ,

Then the foot outlet 29A , the ventilation outlet 29B and the disc outlet 29C each with a Fußauslassklappe 31A , a ventilation outlet flaps 31 B and a Scheibenauslassklappen 31C for controlling a blow-out amount of the air.

Next shows 2 a block diagram of a control device 11 the vehicle air conditioning device 1 the embodiment. The control device 11 is from an air conditioning control 20 and a heat pump controller 32 , both of which are formed from a microcomputer as an example of a computer with a processor. These are with a vehicle communication bus 65 which represents a CAN (Controller Area Network) or a LIN (Local Interconnect Network). Further, the compressor 2 and the auxiliary heating 23 also with the vehicle communication bus 65 connected. This air conditioning control 20 , Heat pump control 32 , this compressor 2 and this auxiliary heater 23 are for sending and receiving data via the vehicle communication bus 65 set up.

The air conditioning control 20 is a higher-level controller that performs the vehicle interior air-conditioning control of the vehicle. An input of the climate control 20 is with the respective outputs of an outside air temperature sensor 33 that detects an outside air temperature Tam of the vehicle, an outside air humidity sensor 34 detecting outside air humidity of an HVAC intake temperature sensor 36 a temperature (an intake air temperature Tas) of the air to be sucked from the suction port 25 to the air flow channel 3 , and those in the heat absorber 9 flows, detects, an inside air temperature sensor 37 which detects a temperature (an internal temperature Tin) of the air (the inside air) of the vehicle interior, an inside air humidity sensor 38 detecting a humidity of the air of the vehicle interior, an inside air CO ₂ concentration sensor 39 detecting a carbon dioxide concentration of the vehicle interior, an outlet temperature sensor 41 detecting a temperature of the air to be exhausted into the vehicle interior, a discharge pressure sensor 42 that supplies a discharge refrigerant pressure Pd of the compressor 2 detected, a solar radiation sensor 51 For example, a photosensor system for detecting a quantity of solar radiation into the vehicle and a speed sensor 52 to detect a moving speed (a speed) of the vehicle and an air conditioning operating section 53 to set the change of a predetermined temperature or mode.

Furthermore, an output of the air conditioning control 20 with the outside fan 15 , the internal fan (the blower fan) 27 , the intake change flap 26 , the air mixing valve 28 and the respective outlet flaps 31A to 31C connected and these are from the air conditioning control 20 controlled.

The heat pump control 32 is a controller that mainly controls the refrigerant circuit R performs. An input of the heat pump control 32 is with respective outputs of a dispensing temperature sensor 43 that a temperature td that of the compressor 2 emitted refrigerant detected, a suction pressure sensor 44 that a pressure ps of the compressor 2 to be sucked refrigerant, an intake temperature sensor 55 that a temperature ts of the compressor 2 to be sucked refrigerant, a radiator temperature sensor 46 , which is a refrigerant temperature (a radiator temperature TCI ) of the radiator 4 detected, a Radiatordrucksensors 47 , which has a refrigerant pressure (a radiator pressure PCI) of the radiator 4 detected, a heat absorber temperature sensor 48 indicating a refrigerant temperature (a heat absorber temperature Te ) of the heat absorber 9 detected, a heat absorber pressure sensor 49 , the one Refrigerant pressure of the heat absorber 9 detected, an auxiliary heating temperature sensor 50 which has a temperature (an auxiliary heating temperature TPTC ) of the auxiliary heater 23 detected, an outdoor heat exchanger temperature sensor 54 indicating a refrigerant temperature (an outdoor heat exchanger temperature TXO ) of an outlet of the outdoor heat exchanger 7 detected, and an outdoor heat exchanger pressure sensor 56 , which is a refrigerant pressure (an outdoor heat exchanger pressure PXO ) of the output of the outdoor heat exchanger 7 detected, connected.

In addition, an output of the heat pump control 32 with respective solenoid valves of the outdoor expansion valve 6 , the interior expansion valve 8th , the solenoid valve 30 (for reheating), of the solenoid valve 17 (for cooling), the solenoid valve 21 (for heating) and the solenoid valve 40 (for the bypass), and these are controlled by the heat pump 32 controlled. Incidentally, the compressor point 2 and the auxiliary heating 23 each integrated therein controls, and the controls of the compressor 2 and the auxiliary heating 23 carry out the sending and receiving of data to and from the heat pump control 32 via the vehicle communication bus 65 out and over the heat pump control 32 controlled.

The heat pump control 32 and the air conditioning control 20 alternately carry out the sending and receiving of the data via the vehicle communication bus 65 and control corresponding devices based on the output of the respective sensors and the set input of the air conditioning operating section 53 , In the embodiment, however, in this case, a volumetric air volume Ga (calculated by the air conditioning controller 20 ) in the outside air temperature sensor 33 , the discharge pressure sensor 42 , the speed sensor 52 and the air flow channel 3 flowing air, an air volume ratio SW (calculated by the air conditioning controller 20 ) through the air mix door 28 and the output of the air conditioning operation section 53 from the air conditioning control 20 via the vehicle communication bus 65 to the heat pump control 32 transmitted and provided for control by the heat pump controller 32 adapted.

From the above embodiment, an operation of the vehicle air conditioning apparatus will next be described 1 the embodiment described. In the embodiment, the control device changes and guides 11 (the air conditioning control 20 and the heat pump control 32 ) the respective modes of heating mode, dehumidifying and heating mode, dehumidifying and cooling mode, cooling mode, MAX cooling mode (maximum cooling mode) and auxiliary heating mode. First, an overview of a flow and the control of the refrigerant is given in each mode.

heating mode

When the heating mode via the heat pump control 32 (an automatic mode) or manual operation to the air conditioning operation section 53 (a manual mode) is selected, the heat pump control opens 32 the solenoid valve 21 (for heating) and closes the solenoid valve 17 (for cooling). The heat pump control 32 also opens the solenoid valve 30 (for reheating) and closes the solenoid valve 40 (for the bypass). The air conditioning control 20 operates the respective blowers 15 and 27 , and the air mix door 28 basically has a state in which all the air in the air flow channel 3 coming from the indoor fan 27 is blown out and then over the heat absorber 9 through the auxiliary heating 23 and the radiator 4 in the heating heat exchange channel 3A flows, but can adjust an air volume.

Consequently, one of the compressor flows 2 discharged high-temperature high-pressure gas refrigerant from the refrigerant line 13 G via the solenoid valve 30 in the radiator 4 , The air in the air flow channel 3 goes through the radiator 4 , and thus the air in the air flow channel 3 over the high-temperature refrigerant in the radiator 4 (via the auxiliary heater 23 and the radiator 4 when the auxiliary heater 23 operated) is heated. On the other side, the refrigerant points in the radiator 4 the heat absorbed by the air and is cooled to condense and liquefy.

That in the radiator 4 liquefied refrigerant flows out of the radiator 4 and then flows through the refrigerant line 13E to the outdoor expansion valve 6 to reach. The in the outdoor expansion valve 6 flowing refrigerant is decompressed in it and flows into the outdoor heat exchanger 7 , That in the outdoor heat exchanger 7 flowing refrigerant vaporizes and the heat is dissipated by the outdoor air or outdoor fan passing during operation 15 pumped out. In other words, the refrigerant circuit works R like a heat pump. Thereafter, this flows out of the outdoor heat exchanger 7 emerging low-temperature refrigerant through the refrigerant line 13A , the solenoid valve 21 and the refrigerant line 13 , and flows from the refrigerant line 13C in the accumulator 12 to perform a gas-liquid separation there, and then the gas refrigerant is introduced into the compressor 2 sucked, whereby this circulation is repeated. The through the radiator 4 (the auxiliary heater 23 and the radiator 4 when the auxiliary heater 23 working) heated air is from the respective outlets 29A to 29C blown out and thus carried out the heating of the vehicle interior.

The heat pump control 32 calculated from a target radiator temperature TCO (a setpoint of the radiator temperature TCI ) coming from a target outlet temperature TAO through the air conditioning control 20 is calculated, a target radiator pressure PCO (a setpoint of the radiator pressure PCI ), and controls the number of revolutions NC of the compressor 2 based on the target radiator pressure PCO and the refrigerant pressure (the radiator pressure PCI , which is a high pressure of the refrigerant circuit R is) of the radiator 4 by the radiator pressure sensor 47 is detected, to the heating by the radiator 4 to control. In addition, the heat pump control controls 32 a valve position of the outer expansion valve 6 based on the refrigerant temperature (the radiator temperature TCI ) of the radiator 4 by the radiator temperature sensor 46 and the radiator pressure sensor 47 detected radiator pressure PCI is detected, and controls a degree of supercooling SC of the refrigerant in the outlet of the radiator 4 ,

When the heating capacity of the radiator 4 is shorter than a heating capacity required for the vehicle interior air conditioning in the heating mode controls the heat pump control 32 also the energy supply of the auxiliary heater 23 to its lack by the heat generation by the auxiliary heating 23 to complete. As a result, a comfortable heating of the vehicle interior is achieved and also a freezing of the outdoor heat exchanger 7 suppressed. Because the auxiliary heating 23 on the air upstream side of the radiator 4 is arranged, passes through the through the air flow channel 3 flowing air at this time the auxiliary heater 23 in front of the radiator 4 ,

Here, when the auxiliary heater 23 on the downstream side of the radiator 4 is arranged, the temperature rises in the auxiliary heater 23 flowing air through the radiator 4 on, with the auxiliary heating 23 from the PTC Heating, as in the embodiment, is formed. Thus, a resistance of the PTC Heating large and a current value is also low, so that their amount of heat generated is reduced, but the performance of the PTC Heating auxiliary heating formed 23 As in the embodiment, the arrangement of the auxiliary heater 23 on the air upstream side of the radiator 4 be presented sufficiently.

Dehumidification and heating mode

In dehumidification and heating mode, the heat pump control opens 32 Next, the solenoid valve 17 and closes the solenoid valve 21 , In addition, the heat pump control closes 32 the solenoid valve 30 and opens the solenoid valve 40 and closes the valve position of the outdoor expansion valve 6 Completed. Then the heat pump control operates 32 the compressor 2 , The air conditioning control 20 operates the respective blowers 15 and 27 and the air mix door 28 basically has a state in which all the air in the air flow channel 3 that of the indoor fan 27 is blown out and then over the heat absorber 9 flows, the auxiliary heating 23 and the radiator 4 in the heating heat exchange channel 3A goes through, but also performs an air volume adjustment.

Consequently, this flows from the compressor 2 to the refrigerant line 13G discharged high-temperature high-pressure gas refrigerant in the bypass line 35 without going to the radiator 4 to flow, and reaches the refrigerant line 13E on the downstream side of the outdoor expansion valve 6 through the solenoid valve 40 , At this time, the refrigerant flows into the outdoor heat exchanger 7 because the outdoor expansion valve 6 is completely closed. That in the outdoor heat exchanger 7 flowing refrigerant is flowing through it or the outside fan 15 passing outside air cooled to condense. That from the outdoor heat exchanger 7 flowing refrigerant flows from the refrigerant line 13A through the solenoid valve 17 to successively into the header dryer section 14 and the subcooling section 16 to stream. In this case, the refrigerant is undercooled.

That from the subcooling section 16 of the outdoor heat exchanger 7 flowing refrigerant enters the refrigerant line 13B and passes through the inner heat exchanger 19 in the expansion valve 8th , After decompressing the refrigerant in the internal expansion valve 8th the refrigerant flows into the heat absorber 9 to evaporate. The from the indoor fan 27 blown air is cooled by the heat absorbing operation at this time and the water in the air is coagulated to the heat absorber 9 to adhere, and thus the air in the air flow channel 3 cooled and dehumidified. That in the heat absorber 9 Evaporated refrigerant flows through the indoor heat exchanger 19 to get over the refrigerant line 13C to the accumulator 12 and gets through it into the compressor 2 sucked, whereby the circulation is repeated.

As the valve position of the outdoor expansion valve 6 is completely closed, it is possible at this time, the disadvantage that that of the compressor 2 discharged refrigerant in the reverse direction of the outdoor expansion valve 6 in the radiator 4 flows, suppress or avoid. Thus, the reduction of a refrigerant circulation amount is suppressed or prevented to ensure the To enable air conditioning performance. In dehumidification and heating mode the heat pump control activates 32 also the auxiliary heating 23 to generate heat. Consequently, the heat absorber 9 cooled and dehumidified air while passing through the auxiliary heater 23 further heated and the temperature rises, so that the dehumidification and heating of the vehicle interior is performed. The heat pump control 32 controls the number of revolutions NC of the compressor 2 based on a through the heat absorber temperature sensor 48 detected temperature (the heat absorber temperature Te ) of the heat absorber 9 and a desired absorber temperature TEO , which is a setpoint (a target temperature of the heat absorber 9 ) of the heat absorber temperature Te via the air conditioning controller 20 is calculated, and controls the activation (heating by heat generation) of the auxiliary heater 23 based on the via the auxiliary heating temperature sensor 50 detected auxiliary heating temperature Tptc and the above-described target heating temperature TCO (which in this case a target value of the auxiliary heating temperature TPTC ), reducing the temperature of the respective outlets 29A to 29C to be blown out to the vehicle interior air by heating by the auxiliary heater 23 is suitably prevented while cooling and dehumidifying air through the heat absorber 9 is carried out in a suitable manner. Accordingly, it is possible to control the temperature of the air blown into the vehicle interior to an appropriate heating temperature while dehumidifying the air, and to achieve comfortable and efficient dehumidification and heating of the vehicle interior.

Because the auxiliary heating 23 on a Luftstromwaufwärtigen side of the radiator 4 is arranged, passes through in the auxiliary heater 23 heated air, moreover, the radiator 4 but the refrigerant is not caused in the dehumidifying and heating mode, in the radiator 4 to stream. This also prevents the disadvantage that the radiator 4 Heat from that through the auxiliary heater 23 absorbed heated air. That is, the reduction of the temperature of the air blown into the vehicle interior through the radiator 4 is suppressed and a COP is also improved.

Dehumidifying and cooling mode

In the dehumidification and cooling mode, the heat pump control opens 32 Next, the solenoid valve 17 and closes the solenoid valve 21 , In addition, the heat pump control opens 32 the solenoid valve 30 and closes the solenoid valve 40 , Then the heat pump control operates 32 the compressor 2 , The air conditioning control 20 operates the respective blowers 15 and 27 , and the air mix door 28 basically has a state in which all the air in the air flow channel 3 that of the indoor fan 27 is blown out and then over the heat absorber 9 flows, the auxiliary heating 23 and the radiator 4 in the heating heat exchange channel 3A goes through, but also performs an air volume adjustment.

Thus, that flows from the compressor 2 discharged high-temperature high-pressure gas refrigerant from the refrigerant line 13 G via the solenoid valve 30 in the radiator 4 , Because the air in the air flow channel 3 the radiator 4 passes through, the air in the air flow channel 3 by the high-temperature refrigerant in the radiator 4 heated, with the refrigerant in the radiator 4 has the heat absorbed by the air and is cooled to condense and liquefy.

That from the radiator 4 flowing refrigerant flows through the refrigerant line 13E to go to the outdoor expansion valve 6 to arrive, and flows through the outdoor expansion valve 6 , which is controlled so that it is slightly open to enter the outdoor heat exchanger 7 to stream. That in the outdoor heat exchanger 7 flowing refrigerant is passing through it or the outside fan 15 passing outside air cooled to condense. That from the outdoor heat exchanger 7 flowing refrigerant flows from the refrigerant line 13A through the solenoid valve 17 to successively into the header dryer section 14 and the subcooling section 16 to stream. In this case, the refrigerant is undercooled.

That from the subcooling section 16 of the outdoor heat exchanger 7 flowing refrigerant enters the refrigerant line 13B and flows through the indoor heat exchanger 19 to go to the interior expansion valve 8th to get. The refrigerant is in the inner expansion valve 8th decompresses and then flows into the heat absorber 9 to evaporate. The water in the from the indoor fan 27 blown air coagulated by the heat absorption operation at this time on the Werbeabsorber 9 to adhere, and thus the air is cooled and dehumidified.

That in the heat absorber 9 Evaporated refrigerant flows through the indoor heat exchanger 19 to pass through the refrigerant line 13C to the accumulator 12 to pass through and flows through it to enter the compressor 2 to be sucked, whereby the circulation is repeated. As the heat pump control 32 in dehumidifying and cooling mode, no activation of the auxiliary heater 23 is performed by the heat absorber 9 cooled and dehumidified air during the passage of the radiator 4 reheated (the heating capacity is lower than that during heating). Thus, will carried out the dehumidification and cooling of the vehicle interior.

The heat pump control 32 controls the number of revolutions NC (Performance of the compressor 2 ) of the compressor 2 based on the temperature (the heat absorber temperature Te) of the heat absorber 9 passing through the heat absorber temperature sensor 48 is detected, and the desired heat absorber temperature TEO (transmitted by the air conditioning controller 20 ), which is its setpoint (a desired temperature of the heat absorber 9 ). That is, when the heat absorber temperature Te is greater than the desired heat absorber temperature TEO , the number of revolutions NC of the compressor 2 increases, and when the heat absorber temperature Te is less than the desired heat absorber temperature TEO , the number of revolutions NC reduced. In addition, the heat pump control calculates 32 a desired radiator pressure PCO from the above-described target heating temperature TCO and controls the valve position of the outdoor expansion valve 6 based on the target radiator pressure PCO and the refrigerant pressure (the radiator pressure PCI , which is a high pressure of the refrigerant circuit) of the radiator 4 by the radiator pressure sensor 47 is detected, to the heating by the radiator 4 to control.

In the embodiment, here controls the heat pump control 32 the valve position of the outdoor expansion valve 6 On the basis of the target radiator pressure PCO, which is calculated from the target heating temperature TCO, which is the setpoint of the radiator temperature TCI, and the radiator pressure PCI, but also the valve position of the outdoor expansion valve 6 on the basis of the radiator temperature TCI and the target heating temperature TCO. In both cases, the heat pump control decreases 32 the valve position of the outdoor expansion valve 6 when the pressure (or temperature) of the radiator is lower than the set point. Since the supercooling degree SC of the refrigerant in the radiator 4 becomes large when the valve position of the outdoor expansion valve 6 is decreased, the temperature of the radiator increases, so that a heating efficiency becomes large. On the other hand, if the pressure (or temperature) is greater than a setpoint, the heat pump control increases 32 the valve position of the outdoor expansion valve 6 to the temperature of the radiator 4 to reduce and reduce the Heizleistungsfähigkeit.

cooling mode

In cooling mode, the heat pump control opens 32 the valve position of the outdoor expansion valve 6 in the above state of dehumidifying and cooling mode next completely. The heat pump control 32 then operates the compressor 2 and does not activate the auxiliary heater 23 out. The air conditioning control 20 operates the respective blowers 15 and 27 , and the air mix door 28 has a state where a ratio in which that of the indoor blower 27 blown out and the heat absorber 9 traversed air in the air flow channel 3 through the auxiliary heating 23 and the radiator 4 in the heating heat exchange channel 3A is set, is set.

As a result, this flows from the compressor 2 discharged high-temperature high-pressure gas refrigerant from the refrigerant line 13G through the solenoid valve 30 in the radiator 4 , and that from the radiator 4 flowing refrigerant flows through the refrigerant line 13E to go to the outdoor expansion valve 6 to get. At this time, the outdoor expansion valve is 6 completely open, and thus the refrigerant passes through this and flows as it is in the outdoor heat exchanger 7 where the refrigerant passes through here or through the outdoor blower 15 Guided outdoor air is air cooled to condense and liquefy. That from the outdoor heat exchanger 7 flowing refrigerant flows from the refrigerant line 13A through the solenoid valve 17 to successively into the header dryer section 14 and the subcooling section 16 to stream. In this case, the refrigerant is undercooled.

That from the subcooling section 16 of the outdoor heat exchanger 7 flowing refrigerant enters the refrigerant line 13B and reached through the indoor heat exchanger 19 the inner expansion valve 8th , The refrigerant is in the inner expansion valve 8th decompresses and then flows into the heat absorber 9 to evaporate. The from the indoor fan 27 blown air is cooled by the heat absorbing operation at this time. In addition, the water in the air coagulates to the heat absorber 9 to stick.

That in the heat absorber 9 Evaporated refrigerant flows through the indoor heat exchanger 19 to the accumulator 12 through the refrigerant line 13C to reach, and thereby flows through to the compressor 2 to be sucked, whereby this circulation is repeated. The in the heat absorber 9 chilled and dehumidified air is emitted from the respective outlets 29A to 29C blown into the vehicle interior (a part of which passes through the radiator 4 to perform a heat exchange), whereby the cooling of the vehicle interior is carried out. In this cooling mode, the heat pump control also controls 32 the number of revolutions NC of the compressor 2 based on the temperature (the heat absorber temperature Te) of the heat absorber 9 passing through the heat absorber temperature sensor 48 is detected, and the above described setpoint Heat absorber temperature TEO, which is its nominal value.

MAX cooling mode (maximum cooling mode)

In MAX cooling mode as the maximum cooling mode, the heat pump control opens 32 Next, the solenoid valve 17 and closes the solenoid valve 21 , Furthermore, the heat pump control closes 32 the solenoid valve 30 and opens the solenoid valve 40 and closes the valve position of the outdoor expansion valve 6 Completed. The heat pump control 32 then operates the compressor 2 and does not activate the auxiliary heater 23 out. The air conditioning control 20 operates the respective blowers 15 and 27 , and the air mix door 28 has a state in which it has a ratio in which that of the indoor blower 27 blown out and through the heat absorber 9 directed air in the air flow channel 3 through the auxiliary heating 23 and the radiator 4 in the heating heat exchange channel 3A is set.

Thus, this flows from the compressor 2 to the refrigerant line 13G discharged high-temperature high-pressure gas refrigerant into the bypass line 35 without getting into the radiator 4 to flow, and reaches the refrigerant line 13E on the downstream side of the outdoor expansion valve 6 through the solenoid valve 40 , Because the outdoor expansion valve 6 is completely closed at this time, the refrigerant flows into the outdoor heat exchanger 7 , That in the outdoor heat exchanger 7 flowing refrigerant is passing through it or through the outdoor fan 15 directed outside air is air cooled to condense. That from the outdoor heat exchanger 7 flowing refrigerant flows from the refrigerant line 13A through the solenoid valve 17 to successively into the header dryer section 14 and the subcooling section 16 to stream. In this case, the refrigerant is undercooled.

That from the subcooling section 16 of the outdoor heat exchanger 7 flowing refrigerant enters the refrigerant line 13B and reaches the interior expansion valve 8th through the indoor heat exchanger 19 , The refrigerant is in the inner expansion valve 8th decompresses and then flows into the heat absorber 9 to evaporate. The from the indoor fan 27 blown air is cooled by the heat absorbing operation at this time. As the water in the air coagulates to the heat absorber 9 to adhere, the air in the air flow channel 3 it also dehumidifies. A circulation is repeated in which the heat absorber 9 evaporated refrigerant through the indoor heat exchanger 19 flows over to the refrigerant line 13C to the accumulator 12 to enter, and thereby flows to enter the compressor 2 to be sucked. At this time, since the outdoor expansion valve 6 is completely closed, it is possible the disadvantage that that from the compressor 2 discharged refrigerant in reverse direction from the outdoor expansion valve 6 to the radiator 4 flows, also to suppress or prevent. Thus, the reduction of a refrigerant cycle amount is suppressed or prevented to allow the ensuring of an air conditioning performance.

Because here the high-temperature refrigerant in the above-described cooling mode in the radiator 4 flows, there is not least a direct heat conduction from the radiator 4 to the HVAC unit 10 , However, since the refrigerant is not in the radiator in the MAX cooling mode 4 flows, the air in the air flow channel 3 from the heat absorber 9 not by the radiator 4 to the HVAC unit 10 heat transmitted transferred. Therefore, the high cooling of the vehicle interior is performed, and under such an environment that, in particular, the outside air temperature Tam is high, the vehicle interior is rapidly cooled to make it possible to achieve comfortable vehicle interior air conditioning. Furthermore controls the heat pump control 32 also in MAX cooling mode the number of revolutions NC of the compressor 2 based on the temperature (the heat absorber temperature Te) of the heat absorber 9 from the heat absorber temperature sensor 48 is detected, and the above-described desired heat absorber temperature TEO, which is the target value.

Auxiliary heating mono mode

Otherwise, the control device 11 of the embodiment, an auxiliary heater monomode which, when, for example, excessive frost formation in the outdoor heat exchanger 7 occurs, etc., the compressor 2 and the outdoor fan 15 in the refrigerant circuit R stops and the auxiliary heater 23 activated to the vehicle interior only by the auxiliary heater 23 to heat. Also in this case controls the heat pump control 32 the activation (heat generation) of the auxiliary heating 23 based on the auxiliary heater temperature sensor 50 detected auxiliary heating temperature Tptc and the above-described target heating temperature TCO.

In addition, operates the air conditioning control 20 the indoor fan 27 , and the air mix door 28 has a state in which the air in the air flow channel 3 coming from the indoor fan 27 blown out, the auxiliary heating 23 of the heating heat exchange channel 3A goes through to adjust an air volume. The by the auxiliary heating 23 heated air is from respective outlets 29A to 29C blown into the vehicle interior and thus performs the heating of the vehicle interior.

Change of operating mode

wobei Tset eine vorbestimmte Temperatur des Fahrzeuginnenraums ist, die durch den Klimatisierungsbetriebsabschnitt 53 gesetzt wird, Tin eine durch den Innenlufttemperatursensor 37 detektierte Innentemperatur ist, K ein Koeffizient ist und Tbal ein Ausgleichswert ist, der sich aus dem vorbestimmten Wert Tset, der durch den Sonneneinstrahlungssensor 51 detektierten Sonneneinstrahlungsmenge SUN und der durch den Außenlufttemperatursensor 33 detektierten Außenlufttemperatur Tam berechnet. Darüber hinaus gilt generell, dass je niedriger die Außenlufttemperatur Tam ist, desto höher die Soll-Auslasstemperatur TAO wird, und die Soll-Auslasstemperatur TAO wird mit Anstieg der Außenlufttemperatur Tam verringert.The air conditioning control 20 calculates the aforementioned target outlet temperature TAO from the following equation (I). The target outlet temperature TAO is a set value of the temperature of the air blown into the vehicle interior. $$\text{TAO}=\left(\text{tset}-\text{Tin}\right)\times \text{K}+\text{Tbal}\left(\text{f}\left(\text{tset}\text{, SUN}\text{, Tam}\right)\right)$$

wherein Tset is a predetermined temperature of the vehicle interior caused by the air conditioning operation section 53 is set, Tin a through the indoor air temperature sensor 37 detected internal temperature, K is a coefficient and Tbal is a compensation value resulting from the predetermined value tset by the solar radiation sensor 51 detected solar radiation amount SUN and by the outside air temperature sensor 33 detected outside air temperature Tam calculated. In addition, in general, the lower the outside air temperature Tam, the higher the target outlet temperature TAO and the target outlet temperature TAO is decreased with increase of the outside air temperature Tam.

The heat pump control 32 selects an operation mode from the above respective operation modes based on the outside air temperature Tam (detected by the outside air temperature sensor 33 ) and that of the air conditioning control 20 via the vehicle communication bus 65 transmitted target outlet temperature TAO during the boot process and sends the respective operating modes via the vehicle communication bus 65 to the air conditioning control 20 , Furthermore, the heat pump control changes 32 after starting the respective operating modes based on parameters such as the outside air temperature Tam, the humidity of the vehicle interior, the target outlet temperature TAO , a heating temperature to be described later TH (a temperature of the air on the leeward side of the radiator 4 , which is an estimated value), the target heating temperature TCO , the heat absorber temperature Te , the desired heat absorber temperature TEO , the presence or absence of a dehumidification request for the vehicle interior, etc., and accordingly changes the heating mode, the dehumidifying and heating mode, the dehumidifying and cooling mode, the cooling mode, the MAX cooling mode, and the auxiliary heating mode mode according to the environmental conditions or the dehumidifying request the temperature of the blown into the vehicle interior air to the target outlet temperature TAO in order to achieve a comfortable and efficient vehicle interior air conditioning.

Control of the compressor 2 in the heating mode by the heat pump controller 32nd

Next is the control of the compressor 2 in the aforementioned heating mode based on 4 described in detail. 4 is a control block diagram of the heat pump control 32 , which is a target speed (a compressor target speed) TGNCh of the compressor 2 intended for heating mode. An F / F (Feedforward) control amount calculation section 58 the heat pump control 32 calculates an F / F control amount TGNChff of the compressor target number of revolutions based on the outside air temperature Tam detected by the outside air temperature sensor 33 can be obtained, a blower voltage BLV of the internal fan 27 , an air volume ratio SW through the air mix door 28 , which is obtained by SW = (TAO - Te) / (TH - Te), a target supercooling degree TGSC, which is a target value of a subcooling degree SC in the outlet of the radiator 4 is, the above-mentioned target heating temperature TCO (transmitted from the air-conditioning control 20), which is the target value of the temperature of the radiator 4 is, and the target radiator pressure PCO, the setpoint of the pressure of the radiator 4 is.

wobei INTL eine Berechnungsperiode (konstant) ist, Tau eine Zeitkonstante einer Verzögerung erster Ordnung ist, TH0 ein stationärer Wert der Heiztemperatur in einem stationären Zustand vor einer Verzögerungsberechnung erster Ordnung ist und THz ein vorheriger Wert der Heiztemperatur TH ist. Durch die Abschätzung der Heiztemperatur TH in dieser Weise ist es nicht erforderlich, einen speziellen Temperatursensor vorzusehen.The above TH used for calculating the air volume ratio SW is here a temperature (hereinafter called heating temperature) of the air on the leeward side of the radiator 4 , The heat pump control 32 estimates TH from a first-order delay calculation formula (II) from: $$\text{TH}=\left(\text{INTL}\times \text{TH0}+\text{dew}\times \text{THz}\right)/\left(\text{dew}+\text{INTL}\right)$$

in which INTL is a calculation period (constant), Tau is a time constant of a first-order delay, TH0 a steady state value of the heating temperature is in a steady state before a first-order lag calculation, and THz a previous value of the heating temperature TH is. By estimating the heating temperature TH in this way it is not necessary to provide a special temperature sensor.

Incidentally, the heat pump control changes 32 the above time constant Tau and the stationary value TH0 according to the aforesaid operation modes, thereby the above-described estimation formula (II) depending on the operation mode for estimating the heating temperature TH different shape. Subsequently, the heating temperature TH via the vehicle communication bus 65 to the air conditioning control 20 transmitted.

The target radiator pressure PCO is determined by a target value calculation section 59 based on the above target supercooling degree TGSC and the target heating temperature TCO calculated. In addition, an F / B (feedback) control amount calculation section calculates 60 an F / B control amount TGNChfb of a compressor target number of revolutions based on the target radiator pressure PCO and the radiator pressure PCI , which is a refrigerant pressure of the radiator. Subsequently, the one from the F / F control amount calculation section 58 calculated F / F control amount TGNCnff and that from the F / B control amount calculation section 60 calculated TGNCnfb in an adder 61 and its result with the limits of an upper limit of the control and a lower limit of the control in a limit setting section 62 is added, followed by the determination as the compressor target number of revolutions TGNCh. In heating mode, the heat pump control controls 32 the number of revolutions NC of the compressor 2 based on the compressor set number of revolutions TGNCh.

Control of the compressor 2 in the dehumidifying and heating mode, dehumidifying and cooling mode, cooling mode and MAX cooling mode by the heat pump controller 32

The other is 5 a control block diagram of the heat pump control 32 , which is a target speed (a compressor target speed) TGNCc of the compressor 2 for the above described dehumidification and heating mode, dehumidifying and cooling mode, cooling mode and MAX cooling mode. An F / F control amount calculation section 63 the heat pump control 32 calculates a F / F control amount TGNCcff of the compressor target speed based on the outside air temperature Tam, volumetric air volume Ga, into the air flow passage 3 flowing air, the desired compressor pressure PCO , which is a nominal value of the pressure (of the radiator pressure PCI ) of the radiator 4 is, and the desired heat absorber temperature TEO , which is a set point of the temperature (the heat absorber temperature Te ) of the heat absorber 9 is.

In addition, the F / B control calculation section 64 calculates an F / B control amount TGNCcfb the desired compressor speed based on the desired heat absorber temperature TEO (transmitted from the climate control 20 ) and the heat absorber temperature Te. Subsequently, the one of the F / F control amount calculation section 63 calculated F / F control amount TGNCccff and that of the F / B control amount calculating section 64 calculated F / B control amount TGNCcfb in an adder 66 and its result with the limits of an upper limit of the control and a lower limit of the control in a limit setting section 67 and then determined as the compressor target speed TGNCc. In dehumidification and heating mode, the heat pump control system controls 32 the speed NC of the compressor 2 based on the compressor target speed TGNCc.

Control of the auxiliary heater 23 in the dehumidifying and heating mode by the heat pump controller 32nd

Next, FIG. 6 is a control block diagram of the heat pump controller 32 Having an auxiliary heating demand capability TGQPTC of auxiliary heating 23 determined in dehumidifying and heating mode. The target heating temperature TCO and the auxiliary heating temperature Tptc become a subtractor 73 the heat pump control 32 entered a deviation ( TCO - Tptc) between the target heating temperature TCO and the auxiliary heating temperature Tptc to calculate. The deviation ( TCO - TPTC ) becomes an F / B control section 74 entered. The F / B control section 74 eliminates the deviation ( TCO Tptc) and calculates an auxiliary heater demand performance F / B control amount such that the auxiliary heater temperature TPTC the target heating temperature TCO becomes.

The in the F / B control section 74 calculated auxiliary heater demand performance F / B control amount becomes with an upper limit of control and a lower limit of control in a limit setting section 76 added and then as the auxiliary heating need efficiency TGQPTC certainly. In dehumidification and heating mode, the controller controls 32 the activation of the auxiliary heater 23 based on the auxiliary heating demand performance TGQPTC to thereby generate the heat (heating) of the auxiliary heater 23 so that the auxiliary heating temperature Tptc is the target heating temperature TCO becomes.

Thus, the heat pump control controls 32 in the dehumidifying and heating operation, the operation of the compressor based on the heat absorber temperature Te and the target heat absorber temperature TEO and controls the heat generation of the auxiliary heater 23 based on the target heating temperature TCO , whereby the cooling and dehumidifying by the heat absorber 9 and heating by the auxiliary heater 23 is controlled in the dehumidifying and heating mode in a suitable manner. As the air blown into the vehicle interior is dehumidified more adequately, the temperature of the air can be controlled to a more accurate heating temperature, and a more comfortable and efficient dehumidification and heating of the vehicle interior can be achieved.

Control of the air mix door 28

Subsequently, the control of the air mix door 28 through the air conditioning control 20 with reference to 3 described. In 3 Ga is a volumetric air volume in the air flow channel described above 3 flowing air, Te is a heat absorber temperature, and TH is the above-described heating temperature (the temperature of the air on the leeward side of the radiator 4 ).

On the basis of that calculated by the equation (the following equation (III)) and by the radiator as described above 4 and the auxiliary heating 23 in the heating heat exchange channel 3A guided air volume ratio SW controls the air conditioning control 20 the air mix door 28 such that the air is brought to an air volume of the corresponding ratio, and thereby a quantity of the through the radiator 4 (and the auxiliary heater 23 ) directed air. $$\text{SW}=\left(\text{TAO}-\text{Te}\right)/\left(\text{TH}-\text{Te}\right)$$

That is, the air volume ratio SW in which the air passes through the radiator 4 and the auxiliary heating 23 in the heating heat exchange channel 3A 0 changes within a range of 0 ≤ SW ≤ 1. "0" indicates a fully closed air mix condition in which all the air in the air flow channel 3 through the bypass channel 3B should be directed without them through the heating heat exchange channel 3A and "1" indicates a fully open air mix condition in which all air in the air flow channel 3 through the heating heat exchange channel 3A should be directed. That is, the volume of air to the radiator 4 becomes Ga x SW.

Change and control of the minimum valve opening degree of the outdoor expansion valve 6 in the dehumidifying and cooling mode by the heat pump controller 32 (part 1)

Next, an example of the change and control of the minimum valve opening degree ECCVpcmin of the outside expansion valve will be described 6 in dehumidification and cooling mode by the heat pump control 32 based on 7 to 10 described. As described above, controls the heat pump control 32 a valve position ECCVpc of the outer expansion valve 6 on the basis of the target radiator pressure PCO and the radiator pressure PCI in the dehumidifying and cooling mode in the embodiment. In this case, the heat pump control controls 32 however, the valve position ECCVpc of the outer expansion valve 6 between a predetermined maximum valve opening degree ECCVpcmax and the minimum valve opening degree ECCVpcmin.

Then, when the valve position ECCVpc of the outdoor expansion valve 6 is low (the outdoor expansion valve 6 is limited), the temperature (the radiator temperature TCI) of the radiator 4 , as in 7 shown, high and the heating power is increased. However, if the valve position ECCVpc of the outdoor expansion valve 6 becomes low, a refrigerant circulation amount of the heat absorber becomes 9 decreased accordingly, and thus the refrigerant is at an early stage, in which the refrigerant in the heat absorber 9 flows, completely evaporate. Therefore, the heat absorber points 9 Sections on which the temperature becomes low and high, so that a temperature dispersion is generated (temperature fluctuation). As in 8th the lower the valve position ECCVpc of the outdoor expansion valve 6 , the greater the temperature dispersion.

When the temperature dispersion in the heat absorber 9 occurs and becomes large, the dehumidifying performance deteriorates, and the air passed therethrough will be difficult to cool depending on the portions, and the target outlet temperature TAO will be hard to reach, thereby deteriorating the air conditioning capability of the vehicle cabin.

On the other hand, there is a correlation between the volume of air, that of the internal fan 27 through the heat absorber 9 is passed, and the temperature dispersion detected. With increasing volume of the air to be passed through the temperature will be easy to reach (by the way, as the whole of the internal fan 27 blown air through the heat absorber 9 is passed, the aforementioned volumetric air volume Ga to the volume of the heat absorber 9 air to be passed through). This behavior is in 9 shown. For example, in the embodiment, the volume of the heat absorber 9 air to be diverted divided into three stages. In 9 shows L1 a temperature dispersion of the heat absorber 9 if the volume of air to be passed through is a high volume of air, L2 indicates a temperature dispersion when the volume of the air to be passed through is an average air volume, and L3 indicates a temperature spread when the volume of the air to be passed through is a small volume of air. For example, if the valve position ECCVpc of the outdoor expansion valve 6 is assumed to be B ( 9 ), the refrigerant evaporates in the heat absorber 9 active with increasing volume of heat through the absorber 9 air to be passed through. This will also the temperature dispersion of the heat absorber 9 big, and the difference between the temperature dispersion L1 at high Air volume and temperature dispersion L2 at medium air volume becomes too X1 ( 9 ).

Thus, in the embodiment, a predetermined limit value X2 set that for the temperature dispersion of the heat absorber 9 is permissible. In the embodiment, the limit is X2 is defined as a temperature dispersion when the difference between the temperature of the air blown to a driver's seat side of the vehicle interior and the temperature of the air blown out to a passenger's seat side is a predetermined value (eg, 5 degrees). It is assumed that this is obtained by previous experiments. Incidentally, this is not limited thereto. For example, the temperatures of several sections of the heat absorber 9 measured in advance and the limit X2 can be set directly from their difference.

Assuming that, as in 9 shown, the valve position of the outdoor expansion valve 6 in which the temperature dispersion L1 of the heat absorber 9 to the limit X2 is increased when the volume of the heat absorber 9 to air being conductive is the high volume of air, A is the valve position of the outdoor expansion valve 6 in which the temperature dispersion L2 of the heat absorber 9 to the limit X2 is increased when the volume of the heat absorber 9 to conductive air is the mean air volume, B is and the valve position of the outdoor expansion valve 6 in which the temperature dispersion L3 of the heat separator 9 to the limit X2 is increased when the volume of the heat absorber 9 conductive air is the small volume of air, C is, changes the heat pump control 32 the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 such that when the volume of heat released by the heat absorber 9 To conductive air is the high volume of air, the valve position A ( 9 ) of the outdoor expansion valve 6 in which the temperature dispersion L1 of the heat absorber 9 to the limit X2 is used as the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 is taken when the volume of the heat absorber 9 air to be conducted is the mean air volume, the valve position B ( 9 ) of the outdoor expansion valve 6 in which the temperature dispersion L2 of the heat absorber 9 to the limit X2 is used as the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 is taken, and if the volume of the heat absorber 9 to conductive air is the small volume of air, the valve position C ( 9 ) of the outdoor expansion valve 6 in which the temperature dispersion L3 of the heat absorber 9 to the limit X2 is used as the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 is taken. By the way, like out 9 As can be seen, the relationship between the respective valve positions (minimum valve opening degree ECCVpcmin) A>B> C. Further, in the embodiment, the volume of the air to be transmitted is judged in the three stages but may be judged in two stages. Conversely, the volume of air to be transmitted can be judged in more stages (greater than or equal to four stages).

Thus, in each volume of the air to be passed through the valve position of the outer expansion valve 6 not reduced to the value at which the temperature dispersion of the heat absorber 9 gets bigger than the limit X2 , That is, the heat pump control 32 changes the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 based on the volume of the heat absorber 9 to conducting air (volumetric air volume Ga) so that the temperature dispersion of the heat absorber 9 the limit X2 complies (the temperature dispersion becomes the limit X2 Or less). When the heat pump control 32 however, the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 according to the volume of the heat absorber 9 changes to conductive air causes the heat pump control 32 in that the volume of the air to be passed through has a predetermined hysteresis, as in 10 shown. Incidentally, in 10 but the lines indicated by arrows, each indicating a change in direction, shown obliquely, but actually change in the vertical direction.

As the heat pump control 32 so the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 according to the volume of the heat absorber 9 air to be conducted in increasing direction when the volume of the air to be transmitted is large (the high air volume), and in a decrease direction when the volume of the air to be passed is small (the small air volume), the temperature dispersion does not change in the heat absorber 9 generated or the temperature spread becomes small. Thus, it is possible to prevent the disadvantage that the valve position ECCVpc of the outer expansion valve 6 is reduced to the refrigerant circulation amount to the heat absorber 9 reduce and the temperature dispersion in the heat absorber 9 to generate or the temperature dispersion of the heat absorber 9 to increase. Maintaining the dehumidifying performance of the heat absorber 9 In the dehumidifying and cooling mode, the temperature (the radiator temperature TCI ) of the radiator 4 contribute to energy savings, as the permissible temperature range can be extended. As is also the target outlet temperature TAO It is generally possible to increase the air-conditioning capacity of the vehicle interior and also to improve the comfort of an occupant.

As the heat pump control 32 in this case, in the embodiment, the minimum valve opening degree ECCVpcmin of the outside expansion valve 6 so that changes the temperature dispersion of the heat absorber 9 the predetermined limit X2 for the permissible temperature dispersion of the heat absorber 9 It is possible, the temperature dispersion of the heat absorber 9 associated with the reduction of the ECCVpc valve position of the outer expansion valve 6 is accompanied, in a suitable way to prevent or suppress. Also, it is possible in the present embodiment, the temperature dispersion of the heat absorber 9 associated with the reduction of the ECCVpc valve position of the outer expansion valve 6 goes along with effectively preventing or suppressing heat pump control 32 based on the volume of the internal fan 6 through the heat absorber 9 conducted air, the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 increases in increasing direction when the air volume becomes large.

As the heat pump control 32 it allows the air volume to be passed through to have the predetermined hysteresis when the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 is changed, in addition, in the embodiment can be avoided in advance the disadvantage that chasing occurs when the minimum valve opening degree ECCVpc of the outdoor expansion valve 6 will be changed.

Change and control of the minimum valve opening degree of the outdoor expansion valve 6 in the dehumidifying and cooling mode by the heat pump controller 32 (part 2)

Furthermore, if a valve position TXV of the inner expansion valve 8th that in the heat absorber 9 decompressed refrigerant flowing, is increased, the refrigerant circulation amount of the heat absorber 9 increases, and thus the temperature dispersion of the heat absorber 9 small. Thus, the heat pump control changes 32 the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 based on the valve position TXV of the inner expansion valve 8th instead of the above embodiment (part 1 ) or in addition.

11 FIG. 15 is a diagram to show an example of the control of the change of the minimum valve opening degree ECCVpcmin of the outside expansion valve 6 also depending on the valve position TXV of the inner expansion valve 8th in addition to the above embodiment (part 1 ) to describe. In the present embodiment, the valve positions A, B, and C, respectively, are the minimum valve opening degree ECCVpcmin based on the volume described above by the heat absorber 9 To conductive air (the high air volume, average air volume and low air volume) are, in addition, changed, depending on whether the valve position TXV of the inner expansion valve 8th is an open side (large in the valve opening degree), a reference or a narrow side (small in the valve opening degree).

That is, when the valve position TXV of the inner expansion valve 8th the open side is large (in valve opening degree) and the volume through the heat absorber 9 To high-volume air to be conducted, the minimum valve opening degree becomes ECCVpcmin of the outdoor expansion valve 6 assumed as A-α smaller than the aforementioned valve position A. When the volume of the air to be passed therethrough is the average air volume, the minimum valve opening degree ECCVpcmin is assumed to be smaller than the aforementioned valve position B as B-β. When the volume of the air to be passed therethrough is the low air volume, the minimum valve opening degree ECCVpcmin as C-γ is assumed smaller than the aforementioned valve position C (while α, β and γ are positive numbers).

When the valve position TXV of the inner expansion valve 8th is the reference value, the minimum valve opening degree ECCVpcmin of the outdoor expansion valve becomes 6 further than the valve positions A . B and C assumed that from the aforementioned volume of the heat absorber 9 are put to conductive air.

On the other hand, if the valve position TXV of the inner expansion valve 8th the narrow side is (small in valve opening degree), and the volume through the heat absorber 9 To high-volume air to be conducted, the minimum valve opening degree becomes ECCVpcmin of the outdoor expansion valve 6 assumed to be greater than the aforementioned valve position A as A + δ. When the volume of the air to be passed therethrough is the average air volume, the minimum valve opening degree ECCVpcmin as B + ε becomes larger than the aforementioned valve position B accepted. When the volume of the air to be passed therethrough is the low air volume, the minimum valve opening degree ECCVpcmin as C + ζ becomes larger than the aforementioned valve position C assumed (while δ, ε and ζ are positive numbers).

Thus, the heat pump control changes 32 based on the valve position TXV of the inner expansion valve 8th the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 in decreasing direction, when the valve position TXV becomes large, and thus allows an unhindered increase in the temperature of the radiator 4 while the temperature dispersion of the heat absorber 9 prevented or suppressed.

Incidentally, the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 only based on the valve position TXV of the inner expansion valve 8th be changed without depending on the present embodiment and the change based on the volume of the heat absorber 9 to conduct conductive air. In this case, for example, only based on the aforementioned valve position B, when the valve position TXV of the inner expansion valve 8th the open side is the ECCVpcmin minimum valve opening degree of the outdoor expansion valve 6 assumed as B-β when the valve position TXV is the reference, the minimum valve opening degree ECCVpcmin is assumed to be B, and when the valve position TXV is the narrow side, the minimum valve opening degree ECCVpcmin is assumed to be B + ε, etc.

Change and Control of the Minimum Valve Opening Degree of the Outdoor Expansion Valve 6 in the Dehumidifying and Cooling Mode by the Heat Pump Controller 32 (Part 3)

Furthermore, as described above, since the heat pump control 32 the speed NC of the compressor 2 based on the temperature (the heat absorber temperature Te) of the heat absorber 9 and the target heat absorber temperature TEO , which is its set temperature in dehumidifying and cooling mode, as in 12 shown, controls, the speed is NC of the compressor 2 high when the desired heat absorber temperature TEO (the target temperature of the heat absorber 9 ) and its performance is increased, so that the refrigerant circulation amount of the heat absorber 9 is increased. This will cause the temperature dispersion of the heat absorber 9 small (one through X3 in 12 given section) and the temperature (the radiator temperature TCI ) of the radiator 4 also increased.

So even if the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 is reduced (a section through X4 in 12 is specified, and the radiator temperature TCI is also increased), the temperature dispersion of the heat absorber 9 only increased to a state before the target heat absorber temperature TEO is lowered (a section passing through X5 in 12 is specified).

Consequently, the heat pump control changes 32 the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 based on the target heat absorber temperature TEO instead of the above embodiment (part 1 ) and (part 2 ) or in addition.

13 FIG. 15 is a diagram for an example of the control of the change of the minimum valve opening degree ECCVpcmin of the outer expansion valve 6 also in dependence on the target heat absorber temperature TEO in addition to the above embodiment (part 1 ) to describe. In the present embodiment, the valve positions become A . B and C , each of which is the minimum valve opening degree ECCVpcmin based on the above-described volume of heat released by the heat absorber 9 to conductive air (the high air volume, average air volume and low air volume) are also changed, depending on whether the target heat absorber temperature TEO low, medium or high. Although in 13 only the valve position A is shown at high air volume, by the way, the valve position B assuming medium air volume and the valve position C at low air volume as similar to change.

That is, when the volume of the heat absorber 9 For example, when the air to be air is the high air volume at which the target heat absorber temperature TEO is low, the minimum valve opening degree ECCVpcmin of the outdoor expansion valve becomes 6 assumed as A-η smaller than the aforementioned valve position A. In addition, at medium target heat absorber temperature TEO, the minimum valve opening degree ECCVpcmin of the outdoor expansion valve becomes 6 assumed as the valve position A, from the aforementioned high volume through the heat absorber 9 is put to conductive air. When the volume of the heat absorber 9 In addition, when the air-volume to be conducted is the high air volume at which the target heat-absorber temperature TEO is high, it is assumed that the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6A + θ is greater than the aforementioned valve position A (while η and θ are positive numbers).

Thus, the heat pump control changes 32 the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 in the decrease direction, when the target temperature (the target heat absorber temperature TEO) of the heat absorber 9 becomes low, whereby it is possible the temperature (the radiator temperature TCI) of the radiator 4 increase unhindered while the temperature dispersion of the heat absorber 9 prevented or suppressed ( 12 ).

Incidentally, even in the case of the present embodiment, the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 based only on the desired heat absorber temperature TEO be changed without depending on the above and the change based on the volume of the heat absorber 9 to conduct conductive air. In this case, only based on the aforementioned valve position A , as in 13 For example, when the desired heat absorber temperature is shown TEO is low, the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 assumed as A-η when the target heat absorber temperature TEO mean, the minimum valve opening degree ECCVpcmin is assumed as A and when the desired heat absorber temperature TEO is high, the minimum valve opening degree ECCVpcmin is assumed to be A + θ, etc.

[Embodiment 2]

Next shows 14 a basic view of a vehicle air conditioning device 1 another embodiment to which the present invention is applied. Incidentally, in this drawing, components having the same reference numerals as in FIG 1 be designated, the same or similar function. In the case of the present embodiment, an outlet is a subcooling section 16 with a shut-off valve 18 connected. An outlet of the check valve 18 is with a refrigerant pipe 13B connected. Incidentally, the check valve 18 a refrigerant line 13B (an interior expansion valve 8th ) Side which serves as a forward direction.

Furthermore branches a refrigerant pipe 13E on an outlet side of a radiator 4 in front of an outdoor expansion valve 6 and this branching refrigerant pipe (hereinafter referred to as a second bypass pipe) 13F exchanges and connects to a refrigerant pipe 13B on a downstream side of the check valve 18 via a solenoid valve 22 (for dehumidification). In addition, there is an evaporation pressure control valve 70 with a refrigerant line 13C on an outlet side of a heat absorber 9 on a refrigerant downstream side of an indoor heat exchanger 19 and on a refrigerant upstream side as a junction with a refrigerant line 13D connected.

Then this solenoid valve 22 and this evaporation pressure control valve 70 also with an output of a heat pump control 32 connected. Incidentally, the out of the bypass line 35 , the solenoid valve 30 and the solenoid valve 40 in 1 The bypass device formed in the aforementioned embodiment 45 not provided. Because other things are similar as in 1 , their description is omitted.

With the above configuration, an operation of the vehicle air conditioning apparatus becomes 1 this embodiment described. In this embodiment, the heat pump control changes and performs 32 the respective operation modes of a heating mode, a dehumidifying and heating mode, an internal cycle mode, a dehumidifying and cooling mode, a cooling mode, and an auxiliary heating monomode (a MAX cooling mode is not provided in this embodiment). Incidentally, the operation and flow of a refrigerant in selecting the heating mode, the dehumidifying and cooling mode, and the cooling mode and the auxiliary heating mode mode are the same as those in the above-described embodiment (embodiment 1 ) are similar, their description is omitted. In the present embodiment (embodiment 2 ), however, it is assumed that the solenoid valve 22 is closed in heating mode, dehumidifying and cooling mode and cooling mode.

Dehumidifying and heating mode of the vehicle air conditioning apparatus 1 in FIG. 14

If, on the other hand, the dehumidifying and heating mode is selected, the heat pump control opens 32 in this embodiment, a solenoid valve 21 (for the heater) and closes a solenoid valve 17 (for cooling). In addition, the heat pump control opens 32 the solenoid valve 22 (for dehumidification). Subsequently, the heat pump control operates 32 a compressor 2 , An air conditioning control 20 operates the respective blowers 15 and 27 , and an air mix door 28 has a substantially state in which all the air into an air flow channel 3 is directed from the indoor fan 27 is blown out and then over the heat absorber 9 by an auxiliary heater 23 and the radiator 4 in a heating heat exchange channel 3A flows, but also performs an air volume adjustment.

Consequently, one of the compressor flows 2 discharged high-temperature high-pressure gas refrigerant from a refrigerant line 13G in the radiator 4 , Because the air in the air flow channel 3 entering the heating heat exchange channel 3A flows through the radiator 4 is passed, the air in the air flow channel 3 by the high-temperature refrigerant in the radiator 4 heated while the refrigerant in the radiator 4 has the heat absorbed by the air and is cooled to condense and liquefy.

That in the radiator 4 liquefied refrigerant flows out of the radiator 4 and then passes through the refrigerant line 13E to the outdoor expansion valve 6 , The in the outdoor expansion valve 6 flowing refrigerant is decompressed therein and then flows into an outdoor heat exchanger 7 , That in the outdoor heat exchanger 7 flowing refrigerant evaporates, and the heat is dissipated by the passing outside air through the operation or the external fan 15 pumped up. In other words, a refrigerant circuit functions R as a heat pump. Subsequently, a circulation is repeated in which the from the outdoor heat exchanger 7 flowing low-temperature refrigerant via a refrigerant line 13A , the solenoid valve 21 and the refrigerant line 13D from the refrigerant line 13C into an accumulator 12 flows, where it is subjected to gas-liquid separation, and then the gas refrigerant in the compressor 2 is sucked.

Furthermore, part of the condensed refrigerant passing through the radiator 4 to Refrigerant line 13E flows, distributes and flows through the solenoid valve 22 to from the second bypass line 13F and the refrigerant line 13B to the inner expansion valve 8th through the indoor heat exchanger 19 to get. The refrigerant is passed through the internal expansion valve 8th decompresses and then flows into the heat absorber 9 to evaporate. The water in the from the indoor fan 27 blown air coagulates to heat absorber by a heat absorbing process at this time 9 to adhere, and thus the air is cooled and dehumidified.

It is repeated a circulation in which the heat absorber 9 evaporated refrigerant with the refrigerant from the refrigerant line 13D on the refrigerant line 13C through the indoor heat exchanger 19 and the subsequent evaporation pressure control valve 70 meets and then through the accumulator 12 in the compressor 2 is sucked. The in the heat absorber 9 Dehumidified air is flowing through the radiator 4 reheated, whereby the dehumidification and heating of the vehicle interior is performed.

The air conditioning control 20 transfers a set heating temperature TCO (a setpoint of a radiator outlet temperature TCI ) coming from a target outlet temperature TAO is calculated to the heat pump control 32 , The heat pump control 32 calculated from the target heating temperature TCO a desired radiator pressure PCO (a setpoint of a radiator pressure PCI ) and controls the speed NC of the compressor 2 based on the target radiator pressure PCO and the refrigerant pressure (a radiator pressure PCI, the high pressure of the refrigerant circuit R is) of the radiator 4 that of a radiograph pressure sensor 47 is detected, to the heating by the radiator 4 to control. In addition, the heat pump control controls 32 a valve position of the outer expansion valve 6 based on one of a heat absorber temperature sensor 48 detected temperature Te of the heat absorber 9 and one of the air conditioning controller 20 transmitted desired heat absorber temperature TEO. Further, to increase a flow path, the heat pump control opens (to flow a slight refrigerant) 32 the evaporation pressure control valve 70 based on the heat absorber temperature sensor 48 detected temperature Te of the heat absorber 9 To prevent the inconvenience that the heat absorber 9 freezes due to excessive temperature drop.

Internal cycle mode of the vehicle air conditioning apparatus 1 of FIG. 14

Furthermore, the heat pump control closes 32 in internal cycle mode, the outdoor expansion valve 6 in the state of the above dehumidifying and heating mode (fully open) completely and closes the solenoid valve 21 , With the closing of the outdoor expansion valve 6 and the solenoid valve 21 is the inflow of the refrigerant in the outdoor heat exchanger 7 and the outflow of the refrigerant from the outdoor heat exchanger 7 prevented, and thus all this flows through the radiator 4 into the refrigerant line 13E flowing condensed refrigerant through the solenoid valve 22 in the second bypass line 13F , That through the second bypass line 13F flowing refrigerant then passes from the refrigerant line 13B to the inner expansion valve 8th through the indoor heat exchanger 19 , The refrigerant is passed through the internal expansion valve 8th decompresses and then flows into the heat absorber 9 to evaporate. The water in the from the indoor fan 27 blown air coagulates to heat absorber by a heat absorbing process at this time 9 to adhere so that the air is cooled and dehumidified.

It is repeated a circulation in which the heat absorber 9 evaporated refrigerant through the indoor heat exchanger 19 and the subsequent evaporation pressure control valve 70 into the refrigerant line 13C flows and over the accumulator 12 in the compressor 2 is sucked. The in the heat absorber 9 Dehumidified air is passing through the radiator 4 reheated, whereby the dehumidification and heating of the vehicle interior is performed. However, as the refrigerant between the radiator 4 (Heat radiation) and the heat absorber 9 (Heat absorption), in the air flow channel 3 lying on the inside, is circulated in the internal cycle operation, the conveyance of heat from the outside air is not carried out and the power consumption of the compressor 2 corresponding heating power shown. Because the total amount of refrigerant through the heat absorber 9 When a dehumidifying operation is performed, a dehumidifying ability is high as compared with the above dehumidifying and heating mode, but the heating performance becomes low.

The air conditioning control 20 transmits the target heater temperature TCO (the target value of the radiator outlet temperature TCI) calculated from the target outlet temperature TAO to the heat pump controller 32 , The heat pump control 32 calculates from the transmitted target heating temperature TCO a target radiator pressure PCO (a target value of a radiator pressure PCI) and controls the rotational speed NC of the compressor 2 Based on the target radiator pressure PCO and the refrigerant pressure (the radiator pressure PCI, the high pressure of the refrigerant circuit R is) of the radiator 4 , by the radiograph pressure sensor 47 is detected, to the heating by the radiator 4 to control.
Since the flow and the control of the refrigerant in the dehumidifying and cooling mode of the vehicle air conditioning device 1 the embodiment 2 those of the aforementioned embodiment 1 are similar, the heat pump control leads 32 the change and control (part 1 ) to (part 3 ) of the minimum valve opening degree of the outdoor expansion valve 6 in the aforementioned (12) to (14) in the dehumidifying and cooling mode, whereby the occurrence of a temperature dispersion in the heat absorber 9 prevents or reduces the temperature dispersion in a similar manner as above. Thus, it is possible to have the disadvantage that the valve position ECCVpc of the outer expansion valve 6 is reduced to a refrigerant circulation amount to the heat absorber 9 decrease and a temperature dispersion in the heat absorber 9 to produce or the temperature dispersion of the heat absorber 9 increase in a similar way.

Also in this case can then while maintaining the dehumidifying capacity of the heat absorber 9 in the dehumidifying and cooling mode, the temperature (the radiator temperature TCI) of the radiator 4 then contribute in a similar way to energy saving, since the allowable temperature range can be extended. Moreover, since the target outlet temperature TAO of the air to be supplied to the vehicle interior can be easily displayed, it is also generally possible to increase the air-conditioning capacity of the vehicle interior and also to improve the comfort of an occupant.

Incidentally, the numerical values and the like shown in the respective embodiment are not limited thereto and should be set according to the device to be used. In addition, the auxiliary heater is not on the auxiliary heater shown in the embodiment 23 but may be a Heizmittelzirkulationskreislauf for circulating a heating medium heated by a heater for heating air in the air flow channel 3 , use a heater core of circulating cooling water heated by a motor, etc.

LIST OF REFERENCE NUMBERS

1

Vehicle air conditioning device

2

compressor

3

Air flow channel

4

radiator

6

Outdoor expansion valve

7

Outdoor heat exchanger

8th

Indoor expansion valve

9

heat absorber

10

HVAC unit

11

control device

20

air conditioning control

27

Internal fan (blower fan)

28

Air mixing door

32

Heat pump control

41

outlet temperature

65

vehicle communication

R

Refrigerant circulation

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• JP 2014205563 [0004]

Claims (6)

A vehicle air conditioning apparatus comprising: a compressor for compressing a refrigerant; an air flow passage through which the air to be supplied to a vehicle interior flows; a radiator to radiate heat to the refrigerant, thereby heating the air to be supplied from the air flow passage to the vehicle interior; a heat absorber for allowing the refrigerant to absorb heat, thereby cooling the air to be supplied to the vehicle interior from the air flow passage; an outdoor heat exchanger disposed outside the vehicle interior to radiate heat to the refrigerant; an outdoor expansion valve for decompressing the refrigerant flowing into the outdoor heat exchanger; an inner expansion valve for decompressing the refrigerant flowing into the heat absorber; and a control device, wherein the control device performs at least one dehumidifying and cooling mode to radiate the refrigerant discharged from the compressor into the radiator and the outdoor heat exchanger, decompressing the refrigerant from which heat is radiated through the indoor expansion valve, and thereafter the refrigerant heat in the heat absorber to record, wherein the control device in the dehumidifying and cooling mode controls a capacity of the compressor based on a temperature of the heat absorber and controls a valve position of the outdoor expansion valve based on a temperature or a pressure of the radiator, and wherein the control device changes a minimum valve opening degree of the outer expansion valve to prevent the occurrence of a temperature dispersion in the heat absorber or to reduce the temperature dispersion. The vehicle air conditioning device according to Claim 1 wherein the control device changes the minimum valve opening degree of the outdoor expansion valve so that the temperature dispersion of the heat absorber maintains a predetermined limit value permissible for the temperature dispersion of the heat absorber. The vehicle air conditioning device according to Claim 1 or 2 comprising an indoor blower for flowing the air into the air flow passage, the control device changing the minimum valve opening degree of the outdoor expansion valve in a direction of increase based on a volume of the air to pass through the heat absorber by the indoor blower as the air volume increases , The vehicle air conditioning apparatus according to any one of Claims 1 to 3 wherein the control device changes the minimum valve opening degree of the outer expansion valve toward a decrease based on a valve position of the inner expansion valve as the valve position increases. The vehicle air conditioning apparatus according to any one of Claims 1 to 4 wherein in the dehumidifying and cooling mode, the control device controls the capacity of the compressor based on the temperature of the heat absorber and a target temperature of the heat absorber, and wherein the control device changes the minimum valve opening degree of the outdoor expansion valve toward a decrease when the target temperature of the heat absorber is reduced. The vehicle air conditioning apparatus according to any one of Claims 1 to 5 wherein the control device provides a predetermined hysteresis when the minimum valve opening degree of the outdoor expansion valve is changed.

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