DE10355190A1 - Compressor system and air conditioning system - Google Patents

Abstract

It is determined that a displacement of a compressor device (1) is equal to or greater than a predetermined displacement, i.e. H. is equal to the maximum displacement when an output pressure (Pd) of the compressor device (1) becomes equal to or greater than a predetermined value. In the determination, the fan deceleration control process is initiated. In this way, it is possible to effectively prevent blowing uncooled air into a room.

Description

The present invention relates to a compressor system, which is a variable compressor device contains and is effectively applicable to a vehicle air conditioning system.

Right after activating the climate system, i.e. immediately after activation of a compressor device the temperature of a passenger compartment heat exchanger is not sufficient reduced. Thus, if the activation of the Compressor a blower is activated, the air which has not been cooled sufficiently is blown into a passenger compartment.

That is why in a conventional Vehicle air conditioning system the blower only after a specified period of time has elapsed from the time of activation the compressor, i.e. the time of energizing an electromagnetic Coupling for transmission a driving force on the compressor device activated to To blow air into the passenger compartment. Such is a climate system for example in Japanese Examined Patent Publication No. 5-9285.

The patent publication examined in Japanese No. 5-9285 disclosed invention is a climate system, which a Fixed displacement compressor device used which their displacement not changed. Therefore, when the patent publication examined in Japanese No. 5-9285 disclosed invention is applied to a climate system which has a variable displacement compressor device which can change its displacement, the following problem occurs.

Here the displacement is as a theoretical geometric displacement of one from the compressor device refrigerant output per rotation of a shaft of the compressor device to understand.

That in a variable compressor device Swashplate type, which can change the stroke of a piston, becomes a balance between a force acting on a piston exerted by the pressure in a swashplate chamber and a counter pressure force that is exerted on the piston, changed by controlling the pressure in the swash plate chamber. The Change of Equilibrium then causes a change in an angle of rotation pulse to tilt the swash plate to change the stroke of the piston to thereby the repression to change the compressor device.

In addition, the swash plate chamber is more normal Always with a refrigerant inlet side the compressor device by a throttle device, such as an opening, and is also connected to a refrigerant outlet side of the compressor device through a control valve, which can change the degree of opening. The pressure in the swashplate chamber is controlled by controlling the degree of opening of the control valve regulated.

Usually when maximizing of repression the compressor device the control valve closed to the pressure to reduce the swash plate chamber to a level which is substantially equal to the suction pressure of the compressor device. On the other hand, when reducing the displacement, the control valve is opened by the Increase the pressure of the swash plate chamber. If the displacement of the Compressor device is reduced, therefore flows a large part of the refrigerant dispensed into the swashplate chamber.

If at this time the compressor device is activated in this state in which a relatively large amount refrigerant is collected in the swash plate chamber, the swash plate because of a relatively small pressure difference between the suction pressure and the output pressure of the compressor device and a need to Rotating the inclined swash plate in the liquid phase refrigerant, which resists swashplate rotation, not immediately be rotated. As a result, the displacement of the compressor cannot immediately increased become.

Therefore, if the blower after Elapse of a predetermined period of time from the time of activation the compressor device, i.e. the time of issuing a Signals to increase of repression the compressor device is activated to the control valve the repression not raised enough and the climate system is not really activated. So the air which are not chilled is unfavorably blown into the passenger compartment.

The present invention is concerned deal with the above disadvantage. It is therefore an object of the present Invention to provide a new compressor system, which of the previously proposed compressor systems is different. It is one further object of the present invention, a climate system with to provide such a compressor system. It's another job of the present invention to suggest a way to do the above To dedicate disadvantage.

To achieve the objects of the present invention, a compressor system is provided which contains a variable compressor device, a control valve, a pressure measuring device and a signal output device. The compressor device includes a refrigerant inlet, a refrigerant outlet, a piston and a control pressure chamber. The refrigerant is drawn into the compressor device through the refrigerant inlet. The refrigerant is discharged from the compressor device through the refrigerant outlet. The piston is reciprocally driven when the compressor device rotates to compress the refrigerant supplied from the refrigerant inlet mieren. The control pressure chamber is connected to the refrigerant inlet and the refrigerant outlet and receives the refrigerant pressure from the refrigerant inlet and / or the refrigerant outlet. The refrigerant pressure in the control pressure chamber regulates a stroke of the piston to regulate displacement of the compressor device. The control valve changes a degree of connection between the refrigerant inlet and the control pressure chamber and / or a degree of connection between the control pressure chamber and the refrigerant outlet. The pressure measuring device is used to measure a refrigerant suction pressure of the compressor device and / or a refrigerant discharge pressure of the compressor device. The signal output device is used to output a signal when it is determined based on the refrigerant suction pressure and / or the refrigerant output pressure, which are measured by the pressure measuring device, that the displacement of the compressor device is equal to or greater than a predetermined displacement.

Instead of the pressure measuring device a temperature measuring device can be provided. The temperature measuring device is used to measure a temperature of an intake refrigerant, which in the Compressor device is sucked, and / or a temperature of one issued refrigerant, which is output from the compressor device. In one Case, the signal output device outputs the signal when based on the temperature of the intake refrigerant and / or the temperature of the output refrigerant, which by the Temperature measuring device are measured, it is determined that the displacement of the compressor device is equal to or greater than a predetermined displacement.

To the tasks of the present To solve invention an air conditioning system is also provided, which includes a vapor compression cooling system, a blower and a blower start control device contains. In the vapor compression cooling system becomes a refrigerant through the above-described compressor system sucked in and compressed. The blower blows air with the refrigerant Exchanges heat and being blown into a room. The blower start control device serves activating the fan, when the signal is received by the signal output device.

The invention is together with other objects, Characteristics and advantages thereof best from the following description, the attached claims and the accompanying drawings understandable. In it show:

1 is a schematic representation of a vehicle air conditioning system (vapor compression cooling system) according to a first embodiment of the present invention;

2 a cross-sectional view of a variable displacement compressor device of a swash plate type according to the first embodiment of the present invention;

3 a flowchart of the control process of a compressor system according to the first embodiment of the present invention;

4 a flowchart of a control process of a compressor system according to a second embodiment of the present invention;

5 a flowchart of a control process of a compressor system according to a third embodiment of the present invention;

6 a flowchart of a control process of a compressor system according to a fourth embodiment of the present invention;

7 a flowchart of a control process of a compressor system according to a fifth embodiment of the present invention;

8th a flowchart of a control process of a compressor system according to a sixth embodiment of the present invention;

9 a flowchart of a control process of a compressor system according to a seventh embodiment of the present invention; and

10 a flowchart of a control process of a compressor system according to an eighth embodiment of the present invention.

First embodiment

In the present embodiment, a compressor system of the present invention is used in a vehicle air conditioning system, and 1 is a schematic illustration of the vehicle air conditioning system.

A vapor compression cooling system, which is a main component of the vehicle air conditioning system, includes a compressor device 1 , a cooler 2 , a receptacle 3 , a pressure reducer 4 and an evaporator 5 , The cooler 2 cools the refrigerant by heat exchange between the outside air and the high temperature / high pressure refrigerant, which is through the compressor device 1 is compressed. The collecting vessel 3 separates the refrigerant from the radiator 2 is outputted into a liquid-phase refrigerant and a vapor-phase refrigerant and stores excess refrigerant as a liquid-phase refrigerant. The pressure reducer 4 reduces the pressure of the collection vessel 3 supplied liquid phase refrigerant. The evaporator 5 serves as a passenger compartment heat exchanger, which evaporates the liquid-phase refrigerant by heat exchange between the low-temperature refrigerant with reduced pressure and the air to be discharged into a passenger compartment of a vehicle.

The compressor device 1 is driven by a driving force, which is used by an internal combustion engine (serves as a vehicle drive source, ie an engine 8th Will be received. The compressor device 1 is mechanical with the engine 8th through a V-belt and a pulley 9 connected and is synchronized with the start and stop of the engine 8th driven.

A heater 10 uses an engine coolant 8th as a heat source and heats the air to be released into the passenger compartment. A heater output 10 becomes by adjusting a flow rate of the to the heater 10 supplied high-temperature coolant by operating a flow rate control valve 11 set. A blower 12 blows air to be released into the passenger compartment.

In the present embodiment, a reheating type is applied. In the reheating type, air passing through the evaporator 5 is flowed, reheated and the heating level of this air is adjusted to adjust the temperature of the air to be discharged into the passenger compartment.

However, the present invention is not limited to this. It goes without saying that an air mixing type can also be used instead of the reheating type. In the air mixing type, the flow rate of hot air flowing through the heater 10 flows, and the flow rate of cold air flowing to the heater 10 flows past, adjusted to adjust the temperature of the air blown into the passenger compartment.

2 is a cross-sectional view of the variable compressor device 1 of a swashplate type. As is known, the compressor device 1 their displacement by changing an inclination angle of a swash plate 1a, ie a stroke of a piston 1c by regulating the pressure in a swash plate chamber (crankcase) 1b , which serves as a control pressure chamber.

In particular, there is an inlet side 1d the compressor device 1 and the swashplate chamber 1b always connected by a throttle (not shown), such as an opening or a capillary tube, which induces a predetermined pressure loss. There is also a pressure control valve 6 provided, which controls a connection state in a pressure line channel (not shown), which is between a refrigerant outlet side 1e the compressor device 1 and the swash plate chamber 1b combines. When increasing the displacement of the compressor device 1 the pressure line channel through the pressure control valve 6 throttled or closed to the pressure in the swash plate chamber 1b to diminish. On the other hand, in reducing the displacement of the compressor device 1 the pressure control valve 6 opened to the pressure in the swashplate chamber 1b to increase.

Therefore, when the displacement is maximized, the pressure is in the swash plate chamber 1b substantially equal to the suction pressure of the compressor device 1 at the entrance 1d , If, on the other hand, the displacement of the compressor device 1 is minimized, the pressure in the swash plate chamber 1b substantially equal to the discharge pressure of the compressor device 1 at the outlet 1e ,

As in 1 shown, the pressure control valve 6 by an electronic control unit (ECU) 7 controlled. In normal operation, the pressure control valve 6 by the ECU 7 turned on in such a way that the pressure (evaporating temperature) in the evaporator 5 is essentially kept at a correspondingly predetermined value.

It is difficult to measure the evaporating temperature directly. Therefore, in the present embodiment, the pressure control valve 6 based on the temperature of the air immediately after flowing through the evaporator 5 , more precisely the measured temperature of a temperature sensor 7a controlled.

The ECU 7 receives measurement signals from various climate sensors 7b next to the temperature sensor 7a , such as an outside air temperature sensor for measuring the outside air temperature outside the passenger compartment, an inside air temperature sensor for measuring the inside air temperature inside the passenger compartment, and a solar radiation sensor. The ECU 7 receives setting values of a control console 7c which is operated and set by a passenger. The ECU 7 also receives measurements from compressor device control parameter sensors 7d , such as an output pressure sensor (serves as an output pressure measuring device), an output refrigerant temperature sensor (serves as a temperature measuring device of the discharged refrigerant), an intake pressure sensor (serves as an intake pressure measuring device), and an intake refrigerant temperature sensor (serves as a temperature measuring device of the sucked-in refrigerant). It goes without saying that the output pressure measuring device and the intake pressure measuring device can be referred to collectively as a pressure measuring device. Likewise, the temperature measuring device of the refrigerant output and the temperature measuring device of the drawn-in refrigerant can be referred to collectively as the temperature measuring device. The output pressure sensor measures the refrigerant output pressure of the compressor device 1 , The output refrigerant temperature sensor measures the temperature of the compressor device 1 issued refrigerant. The intake pressure sensor measures the refrigerant intake pressure of the compressor device 1 , The intake refrigerant temperature sensor measures the temperature of the intake refrigerant that is in the compressor device 1 is sucked.

Next, characteristic operation of the present embodiment will be described with reference to FIG 3 described flowchart described.

This control sequence is in cooling mode executed. When you turn on a start switch (air conditioning switch) to start the air conditioning system or when you turn on a blower switch to activate the blower 12 becomes the measurement (monitoring) of the refrigerant discharge pressure Pd of the compressor device 1 initiated (S11). If the output pressure Pd is equal to or greater than a predetermined pressure P1 (e.g., about 0.7 MPa or +0.1 MPa in the case of a saturated pressure at an outside air temperature of 20 ° C), a cooling fan delay control process is initiated (S12, S13). On the other hand, when the refrigerant discharge pressure Pd is lower than the predetermined pressure P1, the blower is kept off (S16).

Here, the fan deceleration control process delays the activation of the fan 12 by a predetermined period of time T1 to prevent the uncooled air from being blown into the passenger compartment. A measurement of the predetermined time T1 is initiated when the output pressure Pd becomes equal to or greater than the predetermined pressure P1.

When the air conditioning switch or the blower switch is disconnected or turned off, the air conditioning system is kept in the stopped state. Therefore, normally, when the air conditioner switch or the blower switch is turned on, a signal for increasing the displacement of the compressor device becomes 1 to the maximum displacement simultaneously from the ECU 7 to the pressure control valve 6 issued so that the pressure control valve 6 is pressed to change the displacement to the maximum displacement.

Then when the elapsed measurement time reaches the predetermined time T1, the blower becomes 12 started to initiate air blowing into the passenger compartment (S14, S15). If the elapsed measurement time is less than the specified time T1, the blower will 12 not started (repeat S14). Here the ECU serves 7 as a blower start control device for activating the blower 12 ,

Next are the benefits of the present embodiment described.

In the present embodiment, when the output pressure Pd is equal to or larger than the predetermined value P1, it is assumed that the displacement of the compressor device 1 equal to or greater than a given displacement, ie becomes the maximum displacement. Then the fan deceleration control process is initiated. This effectively prevents the uncooled air from being blown into the passenger compartment.

Second embodiment

In the first embodiment, the fan deceleration control process is initiated when the output pressure Pd becomes equal to or greater than the predetermined value P1. In the present embodiment, however, as in 4 is shown, the fan deceleration control process is initiated when the currently measured refrigerant discharge pressure shows a pressure rise ΔP from the discharge pressure Pd that occurs when the pressure control valve is activated 6 to increase the displacement of the compressor device 1 , ie when the signal is output from the ECU 7 to the pressure control valve 6 to increase the displacement of the compressor device 1 measured to the maximum displacement, is equal to or greater than a predetermined value ΔP1 (for example about 0.1 MPa at an outside air temperature of 20 ° C).

This way, this too embodiment blowing uncooled Air in the passenger compartment can be effectively prevented.

In the in 4 shown flowchart, the steps except step S22 are the same as those of the first embodiment.

Third embodiment

In the second embodiment, the fan deceleration control process is initiated when the pressure rise ΔP from the output pressure Pd is that when the pressure control valve is activated 6 to increase the displacement of the compressor device 1 is measured is equal to or greater than the predetermined value ΔP1. In the present exemplary embodiment, however, as described in 5 is shown, the fan deceleration control process is initiated when a pressure difference ΔPs between the refrigerant suction pressure Ps and the refrigerant discharge pressure Pd of the compressor device 1 becomes equal to or greater than a predetermined value ΔPs1 (eg 0.15 MPa).

In this way, the present embodiment blowing uncooled air effectively prevented into the passenger compartment.

In the in 5 shown flowchart, the steps except step S32 are the same as those of the first embodiment.

Fourth embodiment

In the first embodiment, the fan deceleration control process is initiated when the output pressure Pd becomes equal to or greater than the predetermined value P1. In the present exemplary embodiment, however, as described in 6 is shown, the fan deceleration control process is initiated when the suction pressure Ps becomes equal to or lower than a predetermined value P2.

In this way, also in the present embodiment blowing uncooled Air in the passenger compartment can be effectively prevented.

In the in 6 shown flowchart, the steps except step S72 are the same as those of the first embodiment.

Fifth embodiment

In the present embodiment, the fan deceleration control process becomes due to the existence of a correlation between the discharge pressure Pd and the discharge refrigerant temperature Td of the compressor device 1 performed using the output refrigerant temperature Td as a parameter. A characteristic control operation of the present embodiment will be described with reference to FIG 7 described.

When the air conditioner switch or the blower switch is turned on, the measurement (monitoring) of the discharge refrigerant temperature Pd of the compressor device becomes simultaneous 1 initiated (S41). Then, when the discharge refrigerant temperature Td becomes equal to or higher than a predetermined temperature Td1 (for example, about 30 ° C at an outside air temperature of 20 ° C), the fan deceleration control process is initiated (S42, S43).

Then, when the elapsed measurement period becomes equal to or larger than the predetermined period T1, the blower becomes 12 started to start blowing air into the passenger compartment (S44, S45). If the elapsed measurement period is less than the specified period T1, the blower will 12 not activated (repeat S44).

Next are the benefits of the present embodiment described.

In the present embodiment, when the discharge refrigerant temperature Td is equal to or larger than the predetermined value, it is assumed that the displacement of the compressor device 1 equal to or greater than the specified displacement, ie becomes the maximum displacement. Then the fan deceleration control process is initiated. This effectively prevents the uncooled air from being blown into the passenger compartment.

Sixth embodiment

In the fifth embodiment, the blower deceleration control process is initiated when the output refrigerant temperature Td is equal to or greater than the predetermined value. In the present exemplary embodiment, however, as described in 8th is shown, the fan deceleration control process is initiated when the currently measured temperature of the output refrigerant shows a temperature rise .DELTA.T from the output refrigerant temperature Td, which occurs when the pressure control valve is activated 6 to increase the displacement of the compressor device 1 , ie when the signal is output from the ECU 7 to the pressure control valve 6 to increase the displacement of the compressor device 1 measured on the maximum displacement shows, which is equal to or greater than a predetermined value ΔT1 (for example about 10 ° C at an outside air temperature of 20 ° C).

This way, this too embodiment blowing uncooled Air in the passenger compartment can be effectively prevented.

In the in 8th shown flowchart, the steps except step S52 are the same as those of the fifth embodiment.

Seventh embodiment

In the sixth embodiment, the fan deceleration control process is initiated when the temperature rise ΔT from the discharge refrigerant temperature Td is that when the pressure control valve is activated 6 to increase the displacement of the compressor device 1 is measured, is equal to or greater than the predetermined value ΔT1. In the present exemplary embodiment, however, as described in 9 is shown, the fan deceleration control process is initiated when the temperature difference ΔTs between the intake refrigerant temperature Ts and the discharge refrigerant temperature Td becomes equal to or larger than a predetermined value ΔTs1 (e.g., about 15 ° C at an outside air temperature of 20 ° C).

This way you can also in the present embodiment blowing uncooled air effectively prevented into the passenger compartment.

In the in 9 shown flowchart, the steps except step S62 are the same as those of the fifth embodiment.

Eighth embodiment

In the fifth embodiment, the blower deceleration control process is initiated when the output refrigerant temperature Pd is equal to or greater than the predetermined value. In the present exemplary embodiment, however, as described in 10 is shown, the fan deceleration control process is initiated when the intake refrigerant temperature Ts is equal to or lower than a predetermined value Ts1.

This way, this too embodiment blowing uncooled Air in the passenger compartment can be effectively prevented.

In the in 10 shown flowchart, the steps except step S82 are the same as those of the fifth embodiment.

modifications

In the above embodiments, the control unit is for controlling the blower 12 and the control unit for controlling the compressor device 1 integrated. However, the present invention is not limited to this. For example, the compressor system, which is the compressor device 1 contains, separate from the climate control unit, which the blower 12 controls, be provided. The fan deceleration control process can be initiated when a signal indicating that the displacement of the compressor device 1 is equal to or greater than the specified displacement, is received by the air conditioning control unit from the compressor system.

In the above embodiments, the ECU corresponds 7 a "signal output device" of the present invention.

In the above embodiments, the pressure regulating valve is provided in the channel which is between the outlet 1e the compressor device 1 and the swash plate chamber 1b combines. However, the present invention is not limited to this. For example, the pressure control valve 6 be provided in a channel which is between the inlet 1d the compressor device 1 and the swash plate chamber 1b combines.

Other advantages and modifications are for the Expert obviously. The invention is in its generality not to the special details shown and described here, representative devices and illustrative examples limited.

Claims (11)

Compressor system with a variable compressor device ( 1 ), the compressor device ( 1 ) contains: a refrigerant inlet ( 1d ) through which a refrigerant enters the compressor device ( 1 ) is sucked; a refrigerant outlet ( 1e ) through which the refrigerant from the compressor device ( 1 ) is issued; a piston ( 1c ) which, when the compressor device ( 1 ) is driven back and forth to move from the refrigerant inlet ( 1d ) compress supplied refrigerant; and a control pressure chamber ( 1b ), which with the refrigerant inlet ( 1d ) and the refrigerant outlet ( 1e ) is connected and a refrigerant pressure of the refrigerant inlet ( 1d ) and / or the refrigerant outlet ( 1e ) receives, with the refrigerant in the control pressure chamber ( 1b ) a stroke of the piston ( 1c ) regulated to displace the compressor device ( 1 ), the compressor system being characterized by: a control valve ( 6 ), which is a degree of connection between the refrigerant inlet ( 1d ) and the control pressure chamber ( 1b ) and / or a degree of connection between the control pressure chamber ( 1b ) and the refrigerant outlet ( 1e ) changed; a pressure measuring device ( 7d ) for measuring a refrigerant suction pressure of the compressor device ( 1 ) and / or a refrigerant discharge pressure of the compressor device ( 1 ); and a signal output device ( 7 ) for outputting a signal, if based on the refrigerant suction pressure and / or the refrigerant outlet pressure, which are generated by the pressure measuring device ( 7d ) are measured, it is determined that the displacement of the compressor device ( 1 ) is equal to or greater than a given displacement. Compressor system according to claim 1, characterized in that the pressure measuring device ( 7d ) the refrigerant discharge pressure of the compressor device ( 1 ) measures; and that the signal output device ( 7 ) outputs the signal when the refrigerant discharge pressure by the pressure gauge 17d ) is measured, is equal to or greater than a predetermined value. Compressor system according to claim 1, characterized in that the pressure measuring device ( 7d ) the refrigerant discharge pressure of the compressor device ( 1 ) measures; and that the signal output device ( 7 ) outputs the signal when a currently measured refrigerant discharge pressure that is currently being measured by the pressure measuring device ( 7d ) is measured with respect to a previously measured refrigerant discharge pressure, which is measured by the pressure measuring device ( 7d ) when activating the control valve ( 6 ) to increase the displacement of the compressor device ( 1 ) is measured, shows a pressure rise that is equal to or greater than a predetermined value. Compressor system according to claim 1, characterized in that the pressure measuring device ( 7d ) both the refrigerant suction pressure of the compressor device ( 1 ) as well as the refrigerant discharge pressure of the compressor device ( 1 ) measures; and that the signal output device outputs the signal when a pressure difference between the refrigerant discharge pressure and the refrigerant suction pressure, which is caused by the pressure measuring device ( 7d ) are measured to be equal to or greater than a predetermined value. Compressor system according to claim 1, characterized in that the pressure measuring device ( 7d ) the refrigerant suction pressure of the compressor device ( 1 ) measures; and that the signal output device ( 7 ) outputs the signal when the refrigerant suction pressure, which is determined by the pressure measuring device ( 7d ) is measured to be equal to or lower than a predetermined value. Compressor system with a variable compressor device ( 1 ), the compressor device ( 1 ) contains: a refrigerant inlet ( 1d ) through which a refrigerant enters the compressor device ( 1 ) is sucked; a refrigerant outlet ( 1e ) through which the refrigerant from the compressor device ( 1 ) is issued; a piston ( 1c ) which, when the compressor device ( 1 ) is driven back and forth to move from the refrigerant inlet ( 1d ) compress supplied refrigerant; and a control pressure chamber ( 1b ), which with the refrigerant inlet ( 1d ) and the refrigerant outlet ( 1e ) is connected and a refrigerant pressure from the refrigerant inlet ( 1d ) and / or the refrigerant outlet ( 1e ), whereby the refrigerant pressure in the control pressure chamber ( 1b ) a stroke of the piston ( 1c ) regulated to displace the compressor device ( 1 ) to regulate, the compressor system being characterized by a control valve ( 6 ), which is a degree of connection between the refrigerant inlet 11d ) and the control pressure chamber ( 1b ) and / or a degree of connection between the control pressure chamber ( 1b ) and the refrigerant outlet ( 1e ) changed; a temperature measuring device ( 7d ) for measuring a temperature of an intake refrigerant which is fed into the compressor device ( 1 ) is sucked, and / or a temperature of an output refrigerant, which is discharged from the compressor device ( 1 ) is issued; and a signal output device ( 7 ) for outputting a signal if based on the temperature of the intake refrigerant and / or the temperature of the output refrigerant, which is determined by the temperature measuring device ( 7d ) are measured, it is determined that the displacement of the compressor device ( 1 ) is equal to or greater than a given displacement. Compressor system according to claim 6, characterized in that the temperature measuring device ( 7d ) measures the temperature of the refrigerant dispensed; and that the signal output device ( 7 ) outputs the signal when the temperature of the output refrigerant, which is determined by the temperature measuring device ( 7d ) is measured, is equal to or greater than a predetermined value. Compressor system according to claim 6, characterized in that the temperature measuring device ( 7d ) measures the temperature of the refrigerant dispensed; and the signal output device ( 7 ) outputs the signal when a currently measured temperature of the output refrigerant, which is currently measured by the temperature measuring device ( 7d ) is measured with respect to a previously measured temperature of the output refrigerant, which is measured by the temperature measuring device ( 7d ) when activating the control valve ( 6 ) to increase the displacement of the compressor device ( 1 ) is measured, shows an increase in temperature that is equal to or greater than a predetermined value. Compressor system according to claim 6, characterized in that the temperature measuring device ( 7d ) measures both the temperature of the intake refrigerant and the temperature of the refrigerant being dispensed; and that the signal output device outputs the signal when a temperature difference between the temperature of the intake refrigerant and the temperature of the output refrigerant, which is determined by the temperature measuring device ( 7d ) are measured to be equal to or greater than a predetermined value. Compressor system according to claim 6, characterized in that the temperature measuring device ( 7d ) measures the temperature of the intake refrigerant; and that the signal output device ( 7 ) outputs the signal when the temperature of the intake refrigerant, which is determined by the temperature measuring device ( 7d ) is measured to be equal to or lower than a predetermined value. Air conditioning system, characterized by a vapor compression cooling system in which a refrigerant is sucked in and compressed by the compressor system according to one of claims 1 to 10; a blower ( 12 ) that blows air, which exchanges heat with the refrigerant and is blown into a room; and a blower start control device ( 7 ) to activate the fan ( 12 ) if the signal from the signal output device ( 7 ) Will be received.