JPH1123081A - Air conditioner having cooler for heat generating instrument - Google Patents

Air conditioner having cooler for heat generating instrument

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Publication number
JPH1123081A
JPH1123081A JP17613097A JP17613097A JPH1123081A JP H1123081 A JPH1123081 A JP H1123081A JP 17613097 A JP17613097 A JP 17613097A JP 17613097 A JP17613097 A JP 17613097A JP H1123081 A JPH1123081 A JP H1123081A
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JP
Japan
Prior art keywords
pressure
air
refrigerant
cooling temperature
intermediate pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP17613097A
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Japanese (ja)
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JP4006782B2 (en
Inventor
Takahisa Suzuki
隆久 鈴木
Original Assignee
Denso Corp
株式会社デンソー
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Application filed by Denso Corp, 株式会社デンソー filed Critical Denso Corp
Priority to JP17613097A priority Critical patent/JP4006782B2/en
Publication of JPH1123081A publication Critical patent/JPH1123081A/en
Application granted granted Critical
Publication of JP4006782B2 publication Critical patent/JP4006782B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Abstract

(57) [Problem] To stably cool a heat-generating device even if the load of an air conditioner and the heat generation amount of the heat-generating device vary greatly. SOLUTION: A cooler 25 configured to absorb a refrigerant at an intermediate pressure of a refrigeration cycle from a heating device 250 such as an inverter and evaporate. On the upstream side and the downstream side of the cooler 25, electric expansion valves 24 and 27 whose valve opening can be controlled by an external signal are arranged. The intermediate pressure is varied by controlling the valve opening of each of the electric expansion valves 24 and 27, and the amount of cooling from the heat generating device 250 is controlled.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner having a cooler for cooling a heat-generating device such as an electronic device, a motor, a battery, and the like by an air-conditioning refrigeration cycle. ) Is suitable for use in a vehicle air conditioner.

[0002]

2. Description of the Related Art Conventionally, various systems have been proposed for cooling a heat-generating device (for example, an electronic device such as an inverter for controlling the rotation speed of an air-conditioning compressor) by using a refrigerant of an air-conditioning refrigeration cycle. For example, there has been conventionally known a device that cools a heat-generating device with a low-temperature refrigerant on a low-pressure side of a refrigeration cycle. It may be cooled down to below and dew may be formed inside, causing problems such as electric leakage.

[0003] Japanese Patent Application Laid-Open No. 62-69066 proposes a device in which throttles are provided upstream and downstream of a heat-generating device cooler to cool the heat-generating device with an intermediate-pressure refrigerant.

[0004]

However, in this publication, since a fixed throttle is used, the temperature of the intermediate-pressure refrigerant, which is the cooling temperature of the heat-generating equipment, depends on the high and low pressures of the refrigeration cycle. The high and low pressures of the refrigeration cycle fluctuate greatly depending on the load of the air conditioner, and especially in the case of air conditioners for vehicles, the load fluctuates greatly due to the outside air temperature, the temperature in the cabin, etc. It will change greatly. Therefore, when the load on the air conditioner is small, the intermediate pressure also decreases with a decrease in the high and low pressures of the cycle, and the cooling temperature of the heat-generating equipment decreases excessively, which may cause dew condensation.

[0005] Further, since the cooling temperature cannot be adjusted according to the heat generation amount of the heat-producing equipment, there is a problem that when the heat generation amount is large, the cooling capacity becomes insufficient and the temperature of the heat-generating equipment rises. In view of the above, it is an object of the present invention to stably cool a heat generating device even if the load of an air conditioner and the heat generation amount of the heat generating device vary greatly.

Another object of the present invention is to achieve both good maintenance of the performance of the air conditioner and stable cooling of the heat-producing equipment. Still another object of the present invention is to make it possible to control an intermediate pressure for gas injection in a refrigeration cycle having a gas injection function so that system efficiency is optimized.

[0007]

To achieve the above object, according to the first aspect of the present invention, there is provided a cooling system in which a refrigerant at an intermediate pressure of a refrigeration cycle absorbs heat from a heating device (250) and evaporates. Electric expansion valves (24, 2) whose upstream and downstream sides of the cooler (25) can be controlled by an external signal, respectively.
7) is arranged, and the intermediate pressure is varied by controlling the valve opening of each of the electric expansion valves (24, 27) to control the cooling amount of the heat generating device (250). .

According to this, the intermediate pressure changes due to the valve opening control of the electric expansion valves (24, 27) arranged on the upstream side and the downstream side of the cooler (25) of the heat generating equipment (250), and the heat is generated. The cooling temperature of the device (250) can be varied. Therefore, even if the load of the air conditioner or the amount of heat generated by the heat-generating device fluctuates greatly, the cooling amount of the heat-generating device (250) can be appropriately controlled without being influenced by these.
Therefore, it is possible to stably cool the heat-generating device, and it is possible to avoid problems such as dew condensation due to excessive cooling of the heat-generating device and temperature rise due to insufficient cooling.

And, as in the invention according to claim 3,
Control means for controlling the number of revolutions of the compressor (21) (103,
105, 203, 206), and by controlling the number of revolutions of the compressor (21), the control of the air conditioning side capacity by the indoor heat exchanger (23) can be controlled by both electric expansion valves (24, 27).
If the control of the amount of cooling from the heat-generating device (250) is performed independently, the performance of the air conditioner is maintained by controlling the rotation speed of the compressor (21), and the cooling of the heat-generating device is performed by both electric expansion valves (2).
4, 27) can be performed stably.

Next, according to the present invention, a suction port (21b) for sucking a low-pressure refrigerant, a gas injection port (21c) for introducing an intermediate-pressure gas refrigerant,
And a discharge port (21a) for blowing out the compressed refrigerant
, A first decompression means (24) for decompressing the high-pressure refrigerant of the refrigeration cycle to a first intermediate pressure, and a refrigerant at the first intermediate pressure flows in and a refrigerant at the first intermediate pressure is supplied to the compressor. A cooler (25) configured to absorb heat and evaporate from the heat generating device (250), and the cooler (25)
A second decompression means (27) disposed downstream of the first decompression device and decompressing the refrigerant at the first intermediate pressure to a second intermediate pressure; and a refrigerant of the second intermediate pressure decompressed by the second decompression means (27). A gas-liquid separator (260) for separating a liquid;
A third pressure reducing means (29) for reducing the pressure of the liquid refrigerant separated by the gas refrigerant (60) to a low pressure, and a gas injection port (21c) of the compressor (21) using the gas refrigerant separated by the gas-liquid separator (260). ), And as first and second pressure reducing means, an electric expansion valve (24, 2) whose valve opening can be controlled by an external signal.
7) and the two electric expansion valves (24, 2
The first intermediate pressure is varied by controlling each of the valve opening degrees in 7), and the cooling amount of the heat generating device (250) is controlled.

[0011] According to this, by adopting gas injection to the compressor (21), the compression power of the compressor (21) can be reduced and the efficiency of the cycle can be improved. By controlling the opening degree of the two electric expansion valves (24, 27), the intermediate pressure changes, and the heating devices (25, 27)
0) The cooling temperature can be changed. for that reason,
Even if the load of the air conditioner or the amount of heat generated by the heating device fluctuates greatly, the heating device (250)
The amount of cooling can be controlled appropriately.

According to the fifth aspect of the present invention, the target pressure calculating means calculates the target pressure (Pmo) of the second intermediate pressure according to the discharge pressure (Pd) and the suction pressure (Ps) of the compressor (21). (204) and the actual second intermediate pressure (Pm)
Pressure reduction amount control means (207 to 209) for controlling the pressure reduction amount of the entire electric expansion valves (24, 27) so that the pressure becomes equal to the target pressure (Pmo), and the actual cooling temperature (Tr) of the cooler (25). ) For detecting the cooling temperature (37)
A target cooling temperature calculating means (205) for calculating a target cooling temperature (Tro); and both electric expansion valves (2) so that the actual cooling temperature (Tr) matches the target cooling temperature (Tro).
(4, 27), and a pressure reduction ratio control means (210 to 212) for varying the first intermediate pressure.

According to this, both electric expansion valves (24, 2
7) Since the actual second intermediate pressure (Pm) can be controlled to be equal to the target pressure (Pmo) by controlling the entire pressure reduction amount, in the refrigeration cycle having the gas injection function, the gas injection for gas injection is performed. It is possible to control the second intermediate pressure so that the system efficiency is optimized.

In addition, the amount of cooling of the heating device (250) can be appropriately controlled by the pressure reduction ratio of the two electric expansion valves (24, 27). In the invention according to claim 6, the compressor (21)
Control means (203, 206) for controlling the number of revolutions of the compressor, and by controlling the number of revolutions of the compressor (21), the capacity of the indoor heat exchanger (23) on the air conditioning side can be controlled by both electric expansion It is characterized in that the control is performed independently of the control of the cooling amount from the heating device (250) by the valves (24, 27) and the second intermediate pressure control.

According to this, the performance of the air conditioner is improved by the compressor (2
While maintaining the rotation speed control of 1), the heating device (25)
0) can be stably performed by controlling the pressure reduction ratio of the electric expansion valves (24, 27), and the second intermediate pressure can be optimized by controlling the pressure reduction amount of the entire electric expansion valves (24, 27). Control. In the invention according to claim 7, the target cooling temperature calculating means (104, 205)
Is characterized in that a value higher than the ambient temperature (Tam) of the heating device (250) by a predetermined temperature is calculated as a target cooling temperature (Tro).

According to this, the heat generating device (250) can be cooled to a temperature higher than its ambient temperature (for example, the outside air temperature) by a predetermined temperature. And the like can be reliably prevented.

[0017]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a block diagram showing a first embodiment of the present invention. (First Embodiment) FIG. 1 shows a system configuration of a first embodiment of the present invention. In FIG. 1, reference numeral 1 denotes a vehicle air conditioning unit, such as a hybrid vehicle (HV), an electric vehicle (EV), and the like. It is mounted on the lower part of the instrument panel of the vehicle interior. The air-conditioning duct 2 of the air-conditioning unit 1 constitutes an air-conditioning passage for guiding conditioned air into the vehicle interior. At one end of the air-conditioning duct 2, suction ports 4 and 5 for sucking inside and outside air are provided. The inside air suction port 4 and the outside air suction port 5 are selectively opened and closed by an inside / outside air switching door 6.

A blower 3 for blowing air into the air-conditioning duct 2 is installed adjacent to the suction ports 4 and 5, and the blower 3 is driven by a motor 3a and a centrifugal fan 3b driven by the motor 3a. It is configured. On the other hand, the other end of the air-conditioning duct 2 has a plurality of outlets 7 communicating with the vehicle interior,
8 and 9 are formed. These outlets 7, 8, 9 are switched open / closed by outlet switching doors 10, 11, 12, respectively.

Further, an evaporator (indoor heat exchanger) 23 of a refrigeration cycle is provided in the air conditioning duct 2 downstream of the blower 3 in the air. The evaporator 23 cools the air by absorbing and evaporating the low-pressure refrigerant of the refrigeration cycle from the air in the air conditioning duct 2. The refrigeration cycle is provided with the following devices in addition to the evaporator 23. That is, the refrigerant compressor 21, the condenser 22,
High pressure side electric expansion valve 2 for reducing high pressure refrigerant to intermediate pressure
4. a low-pressure side electric expansion valve 27 for further reducing the intermediate-pressure refrigerant to a low-pressure pressure; a cooler 25 installed between the two electric expansion valves 24 and 27 for cooling the vehicle-mounted heating device 250 with the intermediate-pressure refrigerant; The refrigerating cycle is provided with an accumulator 26 which performs gas-liquid separation of the refrigerant drawn into the compressor and has a function of storing the liquid refrigerant.

The heating device 250 is, for example, H
Motors for running V and EV vehicles, other motors, semiconductor switch elements (power transistors) of inverters for controlling the number of rotations of the motors, in-vehicle batteries, and the like. The cooler 25 has a refrigerant passage in contact with these heat generating devices 250, and the refrigerant flowing through the refrigerant passage and the heat generating device 250
This is a configuration in which heat exchange is performed between the heat exchanger.

The specific configuration of the cooler 25 is as follows.
It is set in various forms according to the type of 0. For example, when the heating device 250 is a semiconductor switch element of an inverter, the refrigerant passage of the cooler 25 is configured to be in contact with the radiation fins of the semiconductor switch element. In the refrigerating cycle, devices other than the evaporator 23 (21, 22, 2)
4, 25, 26, 27) are installed outside the vehicle compartment (the room where the traveling motor is mounted). The condenser 22 is an outdoor heat exchanger, and cools by exchanging heat with the outside air blown by the electric blower fan 22a. Both the electric expansion valves 24 and 27 can continuously control the valve opening (that is, the throttle amount) by an electric actuator such as a step motor.

The refrigerant compressor 21 is an electric compressor having a motor (not shown) built in the case and driven by the motor to perform suction, compression and discharge of the refrigerant. It is. An AC voltage is applied to the motor of the refrigerant compressor 21 by an inverter 33, and the frequency of the AC voltage is adjusted by the inverter 33 to continuously change the motor rotation speed. A DC voltage from a vehicle-mounted battery 34 is applied to the inverter 33.

The inverter 33 is connected to the air conditioning controller 31.
The air-conditioning control device 31 is an electronic control device including a microcomputer and its peripheral circuits, and controls the rotation speed of the blower 3 and the electric expansion valves 24 and 27. The valve opening and the like are also controlled. The air-conditioning control device 31 includes an evaporator temperature sensor 3 for detecting the air temperature immediately after the cooling evaporator 23 blows out.
5. Outside air temperature sensor 36 for detecting outside air temperature, heating device 2
A cooling temperature sensor (cooling temperature detecting means) 37 for detecting a cooling temperature of the 50 coolers 25 and an air conditioning operation signal from each lever and switch of the air conditioning control panel 32 are also input. The air-conditioning control panel 32 is installed around an instrument panel in the vehicle compartment, and operating members such as levers and switches are manually operated by an occupant.

Next, the operation of the above configuration will be described.
First, the operation of the refrigeration cycle will be described. The high-temperature and high-pressure gas refrigerant discharged from the compressor 21 is supplied to the condenser 22.
And heat exchange with the outside air blown by the cooling fan 22a to be cooled and condensed. The high-pressure liquid refrigerant flowing out of the condenser 22 is decompressed to an intermediate pressure by the high-pressure side electric expansion valve 24, enters a gas-liquid two-phase state, and then flows into a cooler 25 that cools a heating device 250 mounted on the vehicle. . In the cooler 25, a part of the liquid refrigerant in the two-phase refrigerant absorbs heat from the heating device 250 and evaporates, thereby cooling the heating device 250.

Next, the two-phase refrigerant flowing out of the cooler 25 is decompressed to a low pressure by the low pressure side electric expansion valve 27, and
And exchanges heat with the conditioned air blown by the blower 3 to evaporate the liquid refrigerant and cool the air, thereby cooling the passenger compartment. The evaporated gas refrigerant is sucked into the compressor 21 through the accumulator 26. Here, the relationship between the valve opening degree of the high-pressure side and low-pressure side electric expansion valves 24 and 27 and the cooling temperature of the heating device 250 will be described with reference to FIG. FIG. 2A is a Mollier diagram of the refrigeration cycle of FIG. 1, and FIG. 2B is a table showing a cooling temperature of the heating device 250 in the refrigeration cycle of FIG. 1.

First, when the valve opening of the high-pressure side electric expansion valve 24 is large and the valve opening of the low-pressure side electric expansion valve 27 is small, as in the operation mode of FIG.
4, the intermediate pressure increases because the amount of pressure reduction at the low-pressure side electric expansion valve 27 is large. Since the intermediate-pressure refrigerant that cools the heating device 250 is in a gas-liquid two-phase state, the refrigerant temperature is proportional to the intermediate pressure. Therefore, the heating device cooling temperature at this time becomes high.

Next, as in the operation mode of FIG. 2B, the valve opening of the high-pressure side electric expansion valve 24 and the low-pressure side electric expansion valve 27
When both valve openings are medium, the high pressure side flow path and the low pressure side flow path are both throttled, so that the intermediate pressure is about the middle between the high pressure and the low pressure, and the cooling temperature of the heating equipment also becomes the intermediate temperature. further,
When the valve opening of the high pressure side electric expansion valve 24 is small and the valve opening of the low pressure side electric expansion valve 27 is large,
Since the pressure reduction amount in the low pressure side electric expansion valve 27 is small and the pressure reduction amount in the low pressure side electric expansion valve 27 is small, the intermediate pressure is low and the cooling temperature of the heating device is low.

Therefore, by controlling the valve openings of the high-pressure side and low-pressure side electric expansion valves 24 and 27, the cooling temperature of the heating equipment can be freely controlled in the range from the high-pressure refrigerant temperature to the low-pressure refrigerant temperature. Next, a specific control method of the heating device cooling temperature will be described based on a flowchart shown in FIG.

The control routine shown in FIG. 3 is started by turning on an air-conditioning operation switch (not shown) provided on the air-conditioning control panel 32. First, in step 101, a set position (set temperature) of a temperature control lever of the air-conditioning control panel 32 is set. ) Is read, and in step 102, the outside air temperature Tam, the post-evaporator air temperature Te, and the heating device cooling temperature Tr are read from the outside air temperature sensor 36, the evaporator temperature sensor 35, and the heating device cooling temperature sensor 37.

In step 103, the temperature control lever position read in step 101 is
The target post-evaporator air temperature Teo is calculated as shown in FIG. 4 according to the outside air temperature Tam read in step 2. That is, the temperature control lever is moved between the maximum cooling position (Max Cool) and the maximum heating position (Max Ho) in FIG.
t), the set temperature increases from the maximum cooling position toward the maximum heating position, and accordingly, the target post-evaporator air temperature Teo increases, and the outside air temperature Tam increases. As the temperature becomes lower, the air temperature Teo after the target evaporator becomes higher.

In the next step 104, a target heating equipment cooling temperature Tro is calculated. Here, when the heat generating device 250 cooled by the cooler 25 is an electronic device such as an inverter, it is necessary to reliably prevent dew condensation on the surface of the electronic device in order to prevent leakage of the electronic device. Therefore, the target heating device cooling temperature Tro is calculated as a temperature that is higher than the outside air temperature (the ambient temperature of the heating device 250) Tam by a predetermined temperature α (for example, 5 ° C.), as shown in Expression 1 below.

[0032]

## EQU1 ## Next, in step 105, the actual post-evaporator air temperature Te detected in step 102 matches the target post-evaporator air temperature Teo calculated in step 103. Thus, the rotation speed of the compressor 21 is controlled by the inverter control.
This rotation speed control is performed, for example, by controlling the actual post-evaporator air temperature T.
It is controlled by a fuzzy control map (not shown) according to the deviation between e and the target evaporator air temperature Teo. This makes it possible to always control the cooling capacity to a value corresponding to the set temperature set by the temperature control lever.

Then, in step 106, the actual heating device cooling temperature Tr is compared with the target heating device cooling temperature Tro. Actual heating device cooling temperature Tr from target temperature Tro
If it is lower, the routine proceeds to step 107, where the valve opening of the high-pressure side expansion valve 24 is increased and the valve opening of the low-pressure side expansion valve 27 is reduced. As a result, the intermediate pressure of the cooler 25 increases, and the cooling temperature also increases.

On the other hand, if the actual cooling temperature Tr is higher than the target temperature Tro, the routine proceeds from step 106 to step 108, in which the opening degree of the high-pressure side expansion valve 24 is reduced.
The valve opening of the low pressure side expansion valve 27 is increased. This allows
The intermediate pressure of the cooler 25 decreases, and the actual cooling temperature Tr
Will also be lower. In the flowchart of FIG.
In the valve opening control of the low-pressure side expansion valves 24 and 27, the opening is increased or decreased by a predetermined amount per loop, but the deviation between the target heating device cooling temperature Tro and the actual heating device cooling temperature Tr is calculated. The valve opening control of both expansion valves 24 and 27 may be performed according to this deviation.

FIG. 5 shows a control map of the expansion valve opening. The vertical axis represents the high-pressure side and low-pressure side electric expansion valves 24 and 27.
The horizontal axis indicates the target heating device cooling temperature Tro and the actual heating device cooling temperature Tr in the air-conditioning control device 31.
This is the number of steps in the valve opening map calculated based on the deviation from. As shown in FIG. 5, a combination map of the valve opening degrees of the high-pressure side and the low-pressure side expansion valves 24 and 27 is set in advance, and the number of steps on this map is calculated according to the deviation. The valve openings of the high-pressure side and low-pressure side electric expansion valves 24 and 27 may be determined based on the numbers.
Although the number of steps on the horizontal axis is in the range of 0 to 100 in FIG. 5, this is merely an example and can be set arbitrarily.

As described above, the control is performed such that the actual cooling temperature Tr of the heating device always coincides with the target cooling temperature Tro of the heating device. Therefore, since the cooling capacity can be controlled independently by the compressor rotation speed, and the heating device cooling temperature can be independently controlled by the high-pressure side and the low-pressure side expansion valve opening degree, even when a large cooling capacity is required and the low-pressure pressure is reduced. In addition, the cooling temperature of the heat-generating device will not be lowered unnecessarily, and dew condensation will not occur. In addition, even when the heat generation amount of the heating device 250 is large, the heating device cooling temperature is controlled so as not to increase, so that the cooling of the heating device 250 does not occur.

(Second Embodiment) FIG. 6 shows a second embodiment, in which the present invention is applied to a heat pump cycle. The basic configuration of the refrigeration cycle is the same as that of the first embodiment in FIG. 1, and a four-way valve 28 for switching the flow direction of the refrigerant is added. The refrigerant flow direction during cooling is indicated by a solid line, and the refrigerant flow direction during heating is indicated by a broken line.

The electric expansion valves 24 and 27 have a reversible structure in the refrigerant flow direction. When controlling the valve opening, the first electric expansion valve 24 becomes a high pressure side expansion valve during cooling. Further, the second electric expansion valve 27 is a low pressure side expansion valve. on the other hand,
During heating, the second electric expansion valve 27 functions as a high-pressure side expansion valve,
It goes without saying that the first electric expansion valve 24 is a low pressure side expansion valve.

The vehicle air-conditioning unit 1 is of the first type.
Same as the embodiment, but because of the heat pump cycle, the heat exchanger 23 in the air conditioning unit 1 is an indoor heat exchanger that switches between an evaporator and a condenser, and a heat exchange installed outside the vehicle compartment. The unit 22 is an outdoor heat exchanger that switches to a condenser and an evaporator. All other points are the same as in the first embodiment.

(Third Embodiment) FIG. 7 shows a third embodiment, and the vehicle air conditioning unit 1 is the same as the second embodiment. On the other hand, the refrigeration cycle has a gas injection function added to the heat pump cycle of the second embodiment, and the following changes are made accordingly. That is, in this example, as the refrigerant compressor 21,
In addition to the discharge port 21a and the suction port 21b, a gas injection type having a gas injection port 21c for introducing a gas refrigerant during the compression process is used.

Then, on one end side of the outdoor heat exchanger 22,
The check valves 30a and 30d are connected in parallel so that they are in opposite directions, and at one end of the indoor heat exchanger 23, the check valves 30b and 30c are connected in parallel so that they are in opposite directions. Connected. Two check valves 30a, 3
0c, the connection points on the outlet side of each other and the remaining two check valves 30
b, 30d between the first electrical expansion valve 24, the cooler 25 of the heating device 250, the second electrical expansion valve 27, the gas-liquid separator 260, and the third expansion valve 2
9 are connected in series.

Here, the first electric expansion valve 24 is a first pressure reducing means for reducing the pressure of the high-pressure refrigerant to a first intermediate pressure.
The cooler 25 cools the heating device 250 mounted on the vehicle with the gas-liquid two-phase refrigerant having the first intermediate pressure. Second electric expansion valve 27
Is a second pressure reducing means for further reducing the first intermediate pressure refrigerant to the second intermediate pressure, and the gas-liquid separator 260 has a function of separating the gas-liquid two-phase refrigerant having the second intermediate pressure into gas and liquid and storing the liquid refrigerant. Fulfill.

Further, the third expansion valve 29 is connected to the gas-liquid separator 26.
This is a third pressure reducing means for reducing the pressure of the second intermediate pressure liquid refrigerant separated to zero to a low pressure. More specifically, the third expansion valve 29 has a temperature-sensitive cylinder (not shown) that senses the temperature of the suction refrigerant sucked into the suction port 21b of the compressor 21, and sets the degree of superheat of the suction refrigerant. It is a temperature-type expansion valve that adjusts to a value.

The gas-liquid separator 260 and the refrigerant compressor 21
Is connected to a gas injection port 21c by a gas injection passage 21d. In addition,
As in the first and second embodiments described above, the air-conditioning control device 31 includes an outside air temperature sensor 36 for detecting the outside air temperature, an air temperature sensor 35 for detecting the air temperature immediately after the air is blown from the indoor heat exchanger 23, A signal from a cooling temperature sensor 37 for detecting the cooling temperature of the cooler 25 is input.

Further, in addition to the above, a discharge pressure sensor 38 for detecting the compressor discharge pressure and an intermediate pressure sensor 39 for detecting the second intermediate pressure are provided on the discharge side of the compressor 21 of the refrigeration cycle. I have. This intermediate pressure sensor 39
Is provided in the gas injection passage 21d in the example of FIG. Next, the operation of the third embodiment in the above configuration will be described. First, the operation of the refrigeration cycle during cooling will be described.

The high-temperature and high-pressure gas refrigerant discharged from the compressor 21 passes through the four-way valve 28, is cooled by the outdoor heat exchanger 22, and condenses. The high-pressure liquid refrigerant flowing out of the outdoor heat exchanger 22 passes through the check valve 30a and the first electric expansion valve 24
The pressure is reduced to the intermediate pressure, and the gas-liquid two-phase state is established. In the cooler 25, a part of the liquid refrigerant in the two-phase refrigerant is generated by the heat generating device 250.
The heat-generating device 250 is cooled by absorbing heat from and evaporating.

The two-phase refrigerant flowing out of the cooler 25 flows into the gas-liquid separator 260 after being reduced to the second intermediate pressure by the second electric expansion valve 27. The gas-liquid separator 260 separates the two-phase refrigerant into gas and liquid, and the gas refrigerant passes through the gas injection passage 21d and is sucked from the gas injection port 21c during the compression process of the compressor 21. Since the average suction pressure of the compressor 21 is increased by the gas injection into the compressor 21 and the compression ratio can be reduced, the compression power can be reduced.

On the other hand, the liquid refrigerant from the gas-liquid separator 260 is reduced to a low pressure by the third expansion valve 29, and flows into the indoor heat exchanger 23 through the check valve 30b. Here, the refrigerant absorbs heat from the conditioned air blown by the blower 3, evaporates the refrigerant, cools the conditioned air, and cools the passenger compartment. The evaporated gas refrigerant passes through the four-way valve 28 and is sucked into the compressor 21 from the suction port 21b.

Next, during heating, the high-temperature and high-pressure gas refrigerant blown from the compressor 21 flows into the indoor heat exchanger 23 through the four-way valve 28. Here, heat exchange is performed with the conditioned air blown by the blower 3 to condense and liquefy the gas refrigerant and heat the conditioned air to heat the vehicle interior. The high-pressure liquid refrigerant flowing out of the indoor heat exchanger 23 is supplied to the check valve 30.
Then, the pressure is reduced to the first intermediate pressure by the first electric expansion valve 24 through the first electric expansion valve 24, and the gas enters the gas-liquid two-phase state. In the cooler 25, a part of the liquid refrigerant in the two-phase refrigerant absorbs heat from the heating device 250 and evaporates, thereby cooling the heating device 250.

The two-phase refrigerant flowing out of the cooler 25 is decompressed to a second intermediate pressure by the second electric expansion valve 27, and
Flow into 60. The two-phase refrigerant is separated into gas and liquid by the gas-liquid separator 260, and the gas refrigerant is supplied to the gas injection passage 2
The gas is sucked into the compressor 21 from the gas injection port 21c through 1d. On the other hand, the liquid refrigerant is reduced to a low pressure by the third expansion valve 29 and flows into the outdoor heat exchanger 22 through the check valve 30d.

Here, heat exchange is performed with the outside air, the liquid refrigerant evaporates and gasifies, and is sucked into the compressor 21 from the suction port 21b through the four-way valve 28. Next, a method for controlling the cooling temperature of the heating device in the third embodiment will be described with reference to the flowchart shown in FIG. First, in step 201, the set position (set temperature) of the temperature control lever of the air-conditioning control panel 32 is read.
02, the outside air temperature sensor 36, the outlet air temperature sensor 35,
The outside air temperature Tam, the blown air temperature Te, the cooling temperature Tr, the discharge pressure Pd, and the intermediate pressure Pm are read from the heating device cooling temperature sensor 37, the discharge pressure sensor 38, and the intermediate pressure sensor 39.

In step 203, the cooling mode is determined in the low temperature region and the heating mode is determined in the high temperature region, as shown in FIG. 9, based on the temperature control lever position (set temperature) read in step 101. You.
Then, the target outlet air temperature Teo in the cooling mode and the heating mode is calculated as shown in FIG. 9 according to the outside air temperature Tam and the position of the temperature control lever (set temperature).

In the next step 204, a target intermediate pressure Pmo at which the system efficiency of the refrigeration cycle is optimized is calculated. Here, the intermediate pressure at which the system efficiency in the gas injection cycle is optimized is generally near the intermediate pressure at which the compression ratio from low pressure to intermediate pressure and the compression ratio from intermediate pressure to high pressure are the same. Therefore, in this example, the evaporator outlet air temperature Te is set to the refrigerant saturation temperature during cooling, and the suction pressure Ps of the compressor 21 is calculated based on the refrigerant saturation temperature. The suction pressure Ps of the compressor 21 is calculated on the basis of the calculated suction pressure Ps, and the calculated suction pressure Ps and the discharge pressure sensor 38
The target intermediate pressure Pmo is calculated from the discharge pressure Pd detected by the following equation (2) and the following equation (2).

[0054]

## EQU2 ## Target intermediate pressure Pmo = (Pd * Ps) 1/2 In the next step 205, the target heating device cooling temperature Tro
Is calculated. Here, when the heating device 250 is an electronic device such as an inverter, the target heating device cooling temperature Tro is calculated by the above-described formula (1) in order to reliably prevent dew condensation on the surface of the electronic device.
As shown in the figure, the outside air temperature (the ambient temperature of the heating device 250)
Tam is calculated as a temperature higher than Tam by a predetermined temperature α (for example, 5 ° C.).

Next, in step 206, step 202
The rotational speed of the compressor 21 is controlled by the inverter control so that the blow-off air temperature Te read in step 2 matches the target blow-out temperature Teo calculated in step 203. This rotation speed control is performed according to the deviation between the blown air temperature Te and the target blown air temperature Teo as described above. Thus, the air conditioning capacity can be constantly controlled to a value set by the temperature control lever.

In step 207, the actual intermediate pressure Pm
Is compared with the target intermediate pressure Pmo. Actual intermediate pressure P
If m is lower than the target intermediate pressure, the process proceeds to step 208, and the total pressure reduction amount of the first and second electric expansion valves 24 and 27 is reduced. This means that the pattern of the opening degree of the expansion valve in FIG. 10 moves from the pattern indicated by the solid line to the pattern indicated by the broken line (the pattern on the valve opening increasing side).

Thus, the first and second electric expansion valves 2
Since the total amount of reduced pressure of the pressures 4 and 27 is reduced, the pressure loss between the condenser and the second intermediate pressure in the Mollier diagram of FIG. 11 is reduced, and the second intermediate pressure is increased. If the actual intermediate pressure Pm is higher than the target intermediate pressure Pmo, the process proceeds to step 209, where the first and second electric expansion valves 24,
Increase the total pressure reduction of 27. This means that the pattern of the opening degree of the expansion valve in FIG. 10 is shifted from the pattern indicated by the solid line to the pattern indicated by the dashed line (the pattern on the valve opening decreasing side). As a result, the first and second
Since the total pressure reduction amount of the electric expansion valves 24 and 27 increases, the pressure loss between the condenser and the second intermediate pressure in FIG. 11 increases, and the second intermediate pressure decreases.

On the other hand, the actual heating device cooling temperature Tr is compared with the target heating device cooling temperature Tro at step 210. If the actual heating device cooling temperature Tr is lower than the target temperature Tro, the process proceeds to step 211, where the first electric expansion valve 2
4, the valve opening of the second electric expansion valve 27 is decreased. This means that the number of steps in the valve opening map is moved in the zero direction in FIG. Thereby, the pressure loss between the condenser and the heat-generating device cooler 25 is small, and the pressure loss between the heat-generating device cooler 25 and the gas-liquid separator 260 increases, so that the first intermediate pressure in FIG. The cooling temperature also increases.

If the actual cooling temperature Tr of the heat generating device is higher than the target temperature Tro, the routine proceeds to step 212, where the opening degree of the first electric expansion valve 24 is reduced, and the opening degree of the second electric expansion valve 27 is reduced. Increase. This means that the number of steps in the valve opening map is moved in 100 directions in FIG. Thereby, the condenser and the heat-generating device cooler 25
11 is large, and the pressure loss between the heat-generating device cooler 25 and the gas-liquid separator 260 is small. Therefore, in FIG. 11, the first intermediate pressure is low and the cooling temperature is low. As described above, by controlling the ratio between the valve opening of the first electric expansion valve 24 and the valve opening of the second electric expansion valve 27 (that is, the pressure reduction ratio), the heating device cooling temperature Tr is always set to the target heating device cooling temperature. Control is performed so as to match the temperature Tro.

Therefore, also in the third embodiment, the air conditioning capacity can be controlled independently by the compressor rotation speed, and the cooling temperature of the heat generating equipment can be controlled independently by the opening degrees of the first and second expansion valves. Even when the capacity is required and the low pressure is lowered, the cooling temperature of the heat-generating device does not become lower than necessary and the occurrence of dew condensation can be prevented. In addition, even when the heat generation amount of the heating device 250 is large, the cooling is not performed because the cooling temperature of the heating device is controlled so as not to increase. Furthermore, in the gas injection cycle, the intermediate pressure can always be optimally controlled, so that the power consumption can be reduced with high efficiency.

Next, the correspondence between each step in the flowchart of FIG. 3 of the first embodiment and FIG. 8 of the third embodiment and each function realizing means in the claims will be described. Is a step 104 in FIG. 3 or a step 205 in FIG. The valve opening control means for controlling the valve opening of the two electric expansion valves 24 and 27 so that the actual cooling temperature Tr matches the target cooling temperature Tro according to the second aspect is as follows:
108 or steps 210 to 212 in FIG.

The control means for controlling the number of revolutions of the compressor 21 in claim 3 is step 103, 105 in FIG. 3 or step 203, 206 in FIG. The target pressure calculating means for calculating the target pressure Pmo of the second intermediate pressure according to the discharge pressure Pd and the suction pressure Ps of the compressor 21 in step 5 is step 204 in FIG.

The actual second intermediate pressure P according to claim 5
The decompression amount control means for controlling the decompression amount of the entire electric expansion valves (24, 27) so that m coincides with the target pressure (Pmo) is steps 207 to 209 in FIG. The electric expansion valves (24, 24) are arranged so that the actual cooling temperature (Tr) in claim 5 matches the target cooling temperature (Tro).
The pressure reduction ratio control means for varying the first intermediate pressure by controlling the pressure reduction ratio of 27) is Steps 210 to 212 in FIG.

In the above embodiment, the cooler 25
Although the case where the heat generating device 250 is directly cooled by the cooling device 25 has been described, a cooling medium such as water may be cooled by the cooler 25, and the heat generating device 250 may be cooled by the cooling medium. That is, the heat generating device 250 may be indirectly cooled by the cooler 25 via the cooling medium.

[Brief description of the drawings]

FIG. 1 is an overall configuration diagram showing a first embodiment of the present invention.

FIG. 2A is a Mollier diagram for explaining an operation of the first embodiment, and FIG. 2B is a table for explaining an operation of the first embodiment;

FIG. 3 is a flowchart showing an operation according to the first embodiment.

FIG. 4 is a characteristic diagram of a temperature control lever position and a target air temperature after an evaporator in the first embodiment.

FIG. 5 is a characteristic diagram showing a combination control map of an electric expansion valve opening degree in the first embodiment.

FIG. 6 is an overall configuration diagram showing a second embodiment of the present invention.

FIG. 7 is an overall configuration diagram showing a third embodiment of the present invention.

FIG. 8 is a flowchart showing an operation according to the third embodiment.

FIG. 9 is a characteristic diagram of a temperature control lever position and a target blown air temperature in the third embodiment.

FIG. 10 is a characteristic diagram showing a control map of an electric expansion valve opening degree in a third embodiment.

FIG. 11 is a Mollier diagram for explaining the operation of the third embodiment.

[Explanation of symbols]

2 ... air conditioning duct (air conditioning air passage), 3 ... blower, 4, 5
... Suction port, 7, 8, 9 ... Outlet, 21 ... Compressor, 22 ...
Condenser (outdoor heat exchanger), 23 ... Evaporator (indoor heat exchanger), 24, 27 ... Electrical expansion valve (first and second pressure reducing means), 25 ... Cooler, 29 ... Temperature expansion valve (No. (3) decompression means), 250: heating equipment, 260: gas-liquid separator.

Claims (7)

[Claims]
1. An air-conditioned air passage (2) having an air inlet (4, 5) at one end and an air outlet (5, 6, 7) at the other end. (2) a blower (3) for blowing air from the suction port (4, 5) side to the blowout port (5, 6, 7) through the conditioned air passage (2); An indoor heat exchanger (23) installed in the passage (2) to exchange heat with the air; and an outdoor heat exchanger installed outside the conditioned air passage (2) to exchange heat between the outside air and the refrigerant. An exchanger (22); a compressor (21) for compressing a refrigerant; the indoor heat exchanger (23); and the outdoor heat exchanger (22).
And a cooler (25) configured to absorb and evaporate a refrigerant at an intermediate pressure of the refrigeration cycle including the compressor (21) from the heat generating device (250), and an upstream side of the cooler (25). And electric expansion valves (24, 27) which are respectively arranged on the downstream side and whose valve opening can be controlled by an external signal, by controlling the valve opening of both electric expansion valves (24, 27), respectively. An air conditioner characterized by varying the intermediate pressure and controlling the amount of cooling of the heating device (250).
2. A cooling temperature detecting means (37) for detecting an actual cooling temperature (Tr) of said cooler (25), and a target cooling temperature calculating means (104, 205) for calculating a target cooling temperature (Tro). And the actual cooling temperature (Tr) is equal to the target cooling temperature (Tr).
o) The two electric expansion valves (24, 27)
Opening control means (106 to 108,
210 to 212).
An air conditioner as described.
3. A control means (103, 105, 203, 206) for controlling the number of revolutions of the compressor (21), wherein the control of the capacity of the air conditioning side by the indoor heat exchanger (23) is performed. Independently of the cooling amount control of the heating device (250),
The air conditioner according to claim 1, wherein the control is performed by controlling a rotation speed of the compressor.
4. An air-conditioned air passage (2) having an air inlet (4, 5) on one end and an air outlet (5, 6, 7) on the other end. (2) a blower (3) for blowing air from the suction port (4, 5) side to the blowout port (5, 6, 7) through the conditioned air passage (2); An indoor heat exchanger (23) installed in the passage (2) to exchange heat with the air; and an outdoor heat exchanger installed outside the conditioned air passage (2) to exchange heat between the outside air and the refrigerant. Exchanger (22), a suction port (21b) for sucking low-pressure refrigerant, and a gas injection port (21) for introducing gas refrigerant of intermediate pressure.
c) and a discharge port (2
1a), the indoor heat exchanger (23), and the outdoor heat exchanger (22).
And first decompression means (2) for decompressing the high-pressure refrigerant of the refrigeration cycle including the compressor (21) to a first intermediate pressure.
4), the refrigerant at the first intermediate pressure flows in and the first
A cooler (25) configured to absorb and evaporate the intermediate-pressure refrigerant from the heat-generating device (250); and a cooler (25) disposed downstream of the cooler (25), and A second pressure reducing means (27) for reducing the pressure to an intermediate pressure; a gas-liquid separator (260) for separating the gas and liquid of the refrigerant having the second intermediate pressure reduced by the second pressure reducing means (27); A third decompression means (29) for decompressing the liquid refrigerant separated by the liquid separator (260) to a low pressure, and a gas refrigerant separated by the gas-liquid separator (260) to the compressor (21) Gas injection port (21
c) a gas injection passage (21d) leading to the first and second pressure reducing means, wherein the first and second pressure reducing means use electric expansion valves (24, 27) whose valve opening can be controlled by an external signal. An air conditioner, wherein the first intermediate pressure is varied by controlling the valve opening of each of the valves (24, 27), and the amount of cooling of the heat generating device (250) is controlled.
5. A target pressure calculating means (204) for calculating a target pressure (Pmo) of said second intermediate pressure according to a discharge pressure (Pd) and a suction pressure (Ps) of said compressor (21).
And the actual second intermediate pressure (Pm) is equal to the target pressure (Pmo).
Pressure reduction amount control means (207 to 209) for controlling the pressure reduction amount of the entire electric expansion valves (24, 27) so as to correspond to
A cooling temperature detecting means (37) for detecting an actual cooling temperature (Tr) of the cooler (25); a target cooling temperature calculating means (205) for calculating a target cooling temperature (Tro); The cooling temperature (Tr) is equal to the target cooling temperature (Tr).
o) The two electric expansion valves (24, 27)
5. The air conditioner according to claim 4, further comprising a pressure reducing ratio control unit (210 to 212) that controls the pressure reducing ratio to vary the first intermediate pressure. 6.
6. A control means (203, 206) for controlling the number of revolutions of the compressor (21), wherein the control of the air conditioning side capacity by the indoor heat exchanger (23) is performed by the heating device (250). The air conditioner according to claim 4 or 5, wherein the control is performed by controlling the rotation speed of the compressor (21) independently of the cooling amount control and the second intermediate pressure control.
7. The target cooling temperature calculating means (104, 2)
05) is the ambient temperature (Ta) of the heating device (250).
m) is a value higher than the predetermined temperature by the target cooling temperature (Tro).
The air conditioner according to claim 2, wherein the air conditioner is calculated as:
JP17613097A 1997-07-01 1997-07-01 Air conditioner having a cooler for heat generating equipment Expired - Fee Related JP4006782B2 (en)

Priority Applications (1)

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Application Number Priority Date Filing Date Title
JP17613097A JP4006782B2 (en) 1997-07-01 1997-07-01 Air conditioner having a cooler for heat generating equipment

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