WO2017094172A1

WO2017094172A1 - Air conditioning device

Info

Publication number: WO2017094172A1
Application number: PCT/JP2015/084075
Authority: WO
Inventors: 孝史福井; 雅史冨田; 和樹岡田
Original assignee: 三菱電機株式会社
Priority date: 2015-12-03
Filing date: 2015-12-03
Publication date: 2017-06-08
Also published as: JP6537629B2; JPWO2017094172A1

Abstract

Provided is an air conditioning device capable of performing normal air conditioning operations by eliminating excessive temperature increase of a discharging refrigerant. An air conditioning device of the present invention is provided with: an internal heat exchanger, which is disposed to an intake pipe connected to the intake side of a compressor, and which exchanges heat between a refrigerant flowing in the intake pipe, and the refrigerant between a condenser and a decompression device; a bypass pipe, one end of which is connected to the intake pipe disposed on the inlet side of the internal heat exchanger, and the other end of which is connected to the intake pipe disposed on the outlet side of the internal heat exchanger; a first flow rate regulation valve disposed in the bypass pipe; a discharging refrigerant temperature detection means that detects the discharging refrigerant temperature of the compressor; and a control unit that controls opening of the first flow rate regulation valve on the basis of the discharging refrigerant temperature detected by means of the discharging refrigerant temperature detection means.

Description

Air conditioner

The present invention relates to an air conditioner capable of performing normal air-conditioning operation while avoiding an excessive increase in the discharge refrigerant temperature.

Conventionally, a receiver circuit that realizes high controllability and high-efficiency operation has been adopted in an air conditioner. For example, an air conditioner disclosed in Patent Documents 1 to 3 below is a refrigerant circuit in which a compressor, a four-way valve, a condenser, a first expansion valve, a second expansion valve, and an evaporator are sequentially connected by a refrigerant pipe. A receiver is installed on the refrigerant pipe between the first expansion valve and the second expansion valve.
Inside the receiver, a part of a suction pipe connecting the four-way valve and the suction side of the compressor is disposed, and an internal heat exchanger for exchanging heat between the refrigerant flowing through the suction pipe and the refrigerant in the receiver is set up. By installing the receiver, the liquid back in which the liquid refrigerant flows into the suction side of the compressor is suppressed, and the efficiency of the refrigeration cycle is improved.

JP 2001-174091 A Japanese Patent Laid-Open No. 2015-078800 JP 2014-202385 A

In Patent Documents 1 to 3, the discharge temperature of the compressor is controlled by opening and closing the first expansion valve and the second expansion valve installed between the receiver and the evaporator. It is not the structure which adjusts the heat exchange amount of a medium pressure refrigerant | coolant or a low pressure refrigerant | coolant with the internal heat exchanger installed in. For this reason, for example, when R32 is used as the refrigerant circulating in the refrigerant circuit, the internal heat exchanger cannot control the amount of heat exchange appropriate for the operating conditions, and the refrigerant heating degree on the suction side of the compressor is excessive. There has been a problem that an abnormal stoppage of operation of the protective device occurs due to an excessive rise in the temperature of the discharged refrigerant caused by becoming.

The present invention has been made to solve the above-described problems, and avoids an excessive discharge refrigerant temperature state caused by an excessively high degree of intake refrigerant heating of the compressor, and performs normal air conditioning operation. An object of the present invention is to provide an air conditioner that can be performed.

As means for solving the above problems, an air conditioner according to the present invention includes a compressor, a condenser, a pressure reducing device, and an evaporator, which are sequentially connected to each other by piping, and an air conditioner provided with a refrigerant circuit for circulating the refrigerant. An internal heat exchanger that is installed in a suction pipe connected to the suction side of the compressor and exchanges heat between the refrigerant flowing through the suction pipe and the refrigerant between the condenser and the pressure reducing device. A bypass pipe connected to the suction pipe arranged on the inlet side of the internal heat exchanger and the other connected to the suction pipe arranged on the outlet side of the internal heat exchanger; The first flow rate adjustment valve installed in the compressor, the discharge refrigerant temperature detection means for detecting the discharge refrigerant temperature of the compressor, and the first flow rate adjustment based on the discharge refrigerant temperature detected by the discharge refrigerant temperature detection means Control valve opening A control unit that includes a.

The air conditioner according to the present invention controls the first flow rate adjustment valve of the bypass pipe based on the discharge refrigerant temperature of the compressor detected by the discharge refrigerant temperature detection means, thereby controlling the internal heat exchanger. Since the amount of exchange heat can be adjusted, even when R32 is used as the refrigerant circulating in the refrigerant circuit, it is possible to reliably avoid an excessive discharge refrigerant temperature state, and normal air-conditioning operation can be realized.

It is a refrigerant circuit block diagram of the air conditioning apparatus which concerns on Embodiment 1 of this invention. It is a control block diagram of the air conditioning apparatus which concerns on Embodiment 1 of this invention. FIG. 5 is a Ph diagram illustrating a state transition of a refrigerant in the air-conditioning apparatus according to Embodiment 1 of the present invention. It is a flowchart which shows the flow of control operation | movement of the flow regulating valve of the air conditioning apparatus which concerns on Embodiment 1 of this invention. It is a refrigerant circuit block diagram of the air conditioning apparatus which concerns on Embodiment 2 of this invention. It is a flowchart which shows the flow of control operation | movement of the flow regulating valve of the air conditioning apparatus which concerns on Embodiment 2 of this invention.

Embodiment 1. FIG.
"Equipment configuration"
Next, an embodiment of an air conditioner according to the present invention will be described with reference to the drawings.
FIG. 1 is a refrigerant circuit configuration diagram of an air-conditioning apparatus according to Embodiment 1 of the present invention. FIG. 2 is a control block diagram of the air-conditioning apparatus according to Embodiment 1 of the present invention.
As shown in FIG. 1, the air conditioner connects a compressor 1, a four-way valve 2, an outdoor heat exchanger 3, a first pressure reducing device 5 a, a second pressure reducing device 5 b, and an indoor heat exchanger 7 in order by refrigerant piping. It is used for indoor air conditioning by performing a vapor compression refrigeration cycle operation. This air conditioner includes an outdoor unit A that is installed outdoors and an indoor unit B that is installed on the indoor ceiling by being embedded or suspended, or by being wall-mounted on an indoor wall surface. The outdoor unit A and the indoor unit B are connected in parallel via the liquid connection pipe 6 and the gas connection pipe 9.
In addition, in the air conditioning apparatus of Embodiment 1 shown in FIG. 1, although it is the structure which used the indoor unit B as one unit, it is not limited to this, The structure which used multiple units may be sufficient. Further, when both the outdoor unit A and the indoor unit B are configured by a plurality of units, the respective capacities may differ from large to small, or all may have the same capacity.

Examples of the refrigerant used in the air conditioner include HFC refrigerants such as R410A, R407C, R404A, and R32, HFO refrigerants such as R1234yf / ze, HCFC refrigerants such as R22 and R134a, or carbon dioxide (CO ₂ ) and hydrocarbons. There are natural refrigerants such as helium, propane, etc., but the first embodiment will be described on the assumption that R32 refrigerant is used.

<Outdoor unit A>
The outdoor unit A constitutes an outdoor refrigerant circuit that is a part of the refrigerant circuit, and includes a compressor 1, a four-way valve 2, an outdoor heat exchanger 3, a first pressure reducing device 5a, a receiver 11, and a second pressure reducing device. 5b and the outdoor air blower 4. The switching of the four-way valve 2 and the operation of the outdoor heat exchanger 3 are controlled by a control unit 30 installed in the air conditioner.

The compressor 1 compresses the sucked refrigerant and discharges it in a high-temperature and high-pressure state. The refrigerant discharge side is connected to the four-way valve 2 and the refrigerant suction side is connected to the receiver 11. For example, the compressor 1 has a configuration in which the operating capacity (frequency) can be varied. For example, a positive displacement compressor driven by a motor (not shown) controlled by an inverter is used. .
In the embodiment shown in FIG. 1, the number of the compressors 1 is one. However, the present invention is not limited to this, and two or more compressors are connected in parallel or in series according to the number of indoor units B connected. It may be a configuration.

The four-way valve 2 has a function of switching the refrigerant flow path. During the cooling operation, the four-way valve 2 connects the discharge side of the compressor 1 and the gas side of the outdoor heat exchanger 3 as shown by a broken line in FIG. The refrigerant flow path is switched so as to connect the side. As shown by the solid line in FIG. 1, the four-way valve 2 connects the discharge side of the compressor 1 and the gas connection pipe 9 side as well as the gas of the suction side of the compressor 1 and the outdoor heat exchanger 3 during heating operation. The refrigerant flow path is switched so as to connect the side.
In addition, although Embodiment 1 shows the case where the refrigerant circuit which can switch between cooling operation and heating operation by installing the four-way valve 2 is shown, only the cooling operation or only the heating operation without installing the four-way valve 2 is shown. It is good also as composition which performs.

The outdoor heat exchanger 3 functions as a condenser during the cooling operation, and exchanges heat between the refrigerant discharged from the compressor 1 and the air. In addition, the outdoor heat exchanger 3 functions as an evaporator during heating operation, and performs heat exchange between the refrigerant flowing out of the first decompression device 5a and the air. One of the outdoor heat exchangers 3 is connected to the four-way valve 2 and the other is connected to the first pressure reducing device 5a.
The outdoor heat exchanger 3 is, for example, a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins.

The outdoor blower 4 has a function of sucking outdoor air into the outdoor unit A and discharging the air heat-exchanged with the refrigerant by the outdoor heat exchanger 3 to the outside.
The outdoor air blower 4 is a fan capable of changing the flow rate of air supplied to the outdoor heat exchanger 3, and is composed of, for example, a propeller fan driven by a DC motor (not shown). .

The first decompression device 5a and the second decompression device 5b are arranged on the liquid side of the outdoor unit A and have a function of adjusting the flow rate of the refrigerant flowing in the refrigerant circuit. One of the first decompression devices 5 a is connected to the outdoor heat exchanger 3 and the other is connected to the receiver 11. One of the second decompression devices 5 b is connected to the indoor heat exchanger 7 via the liquid connection pipe 6, and the other is connected to the receiver 11.

The receiver 11 is a refrigerant container that stores liquid refrigerant, and stores liquid refrigerant that has become surplus during operation and also has a gas-liquid separation function. The receiver 11 is installed on a refrigerant pipe between the first decompression device 5a and the second decompression device 5b.
A part of a suction pipe 15 that connects the four-way valve 2 and the suction side of the compressor 1 is disposed inside the receiver 11, and the refrigerant flowing through the suction pipe 15, the first decompression device 5 a, and the second decompression An internal heat exchanger 14 for exchanging heat with the refrigerant between the devices 5b is installed.

The suction pipe 15 is provided with a bypass pipe 12 having a function of partially bypassing the refrigerant circulating through the suction pipe 15.
One of the bypass pipes 12 is connected to the suction pipe 15 on the side connecting the four-way valve 2 and the internal heat exchanger 14, and the other is connected to the suction pipe 15 on the side connecting the internal heat exchanger 14 and the compressor 1. It is connected. The bypass pipe 12 is provided with a first flow rate adjustment valve 13 a that adjusts the flow rate of the refrigerant flowing through the bypass pipe 12. The opening degree of the first flow rate adjustment valve 13 a is controlled by the control unit 30. Although an electronic expansion valve is suitable as the first flow rate adjustment valve 13a, other types of flow rate adjustment valves may be used as long as the same opening degree adjustment is possible.

In the outdoor unit A, various temperature sensors are installed.
First, the compressor 1 is provided with a discharge temperature sensor 201 and a shell temperature sensor 208 as discharge refrigerant temperature detection means for detecting the discharge refrigerant temperature Td.
Next, the outdoor heat exchanger 3 is provided with a gas side temperature sensor 202 for detecting the refrigerant temperature in the gas-liquid two-phase state. The refrigerant temperature in the gas-liquid two-phase state is a refrigerant temperature corresponding to the condensation temperature Tc during the cooling operation and a refrigerant temperature corresponding to the evaporation temperature Te during the heating operation.
Next, a liquid side temperature sensor 204 that detects the temperature of the refrigerant in the liquid state or the gas-liquid two-phase state is installed on the liquid side of the outdoor heat exchanger 3.
Finally, an outdoor temperature sensor 203 that detects the temperature of the outdoor air flowing into the outdoor unit A, that is, the outdoor air temperature Ta, is installed on the outdoor air inlet side of the outdoor unit A.
The discharge temperature sensor 201, the gas side temperature sensor 202, the outdoor temperature sensor 203, the liquid side temperature sensor 204, and the shell temperature sensor 208 are all configured by a thermistor as an example.

<Indoor unit B>
The indoor unit B constitutes an indoor refrigerant circuit that is a part of the refrigerant circuit, and includes an indoor heat exchanger 7 and an indoor air blower 8. Operation | movement of the indoor air blower 8 is controlled by the control part 30 installed in the air conditioning apparatus.

The indoor heat exchanger 7 functions as an evaporator during the cooling operation, and performs heat exchange between the refrigerant flowing out of the second decompression device 5b and the air. Moreover, the indoor heat exchanger 7 functions as a condenser during heating operation, and performs heat exchange between the refrigerant discharged from the compressor 1 and the air. One of the indoor heat exchangers 7 is connected to the four-way valve 2 via a gas connection pipe 9, and the other is connected to the second decompression device 5 b via a liquid connection pipe 6.
The indoor heat exchanger 7 is, for example, a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins.

The indoor air blower 8 has a function of sucking indoor air into the indoor unit B and supplying the air heat-exchanged with the refrigerant by the indoor heat exchanger 7 into the room.
The indoor blower 8 is a fan capable of changing the flow rate of air supplied to the indoor heat exchanger 7, and is, for example, a centrifugal fan or a multiblade driven by a DC motor (not shown). Consists of fans and the like.

Various temperature sensors are installed in the indoor unit B.
First, a liquid side temperature sensor 205 that detects the temperature of the refrigerant in the liquid state or the gas-liquid two-phase state is installed on the liquid side of the indoor heat exchanger 7. The refrigerant temperature in the liquid state or the gas-liquid two-phase state is a refrigerant temperature corresponding to the supercooled liquid temperature Tco during the heating operation and a refrigerant temperature corresponding to the evaporation temperature Te during the cooling operation.
Next, an indoor temperature sensor 206 for detecting the temperature of the indoor air flowing into the indoor unit B is installed on the indoor air inlet side of the indoor unit B.
Finally, a gas-side temperature sensor 207 that detects the temperature of the gas-liquid two-phase refrigerant is installed in the indoor heat exchanger 7. Here, the refrigerant temperature in the gas-liquid two-phase state is a refrigerant temperature corresponding to the condensation temperature Tc during the heating operation, and a refrigerant temperature corresponding to the evaporation temperature Te during the cooling operation.
Note that the liquid side temperature sensor 205, the gas side temperature sensor 207, and the room temperature sensor 206 are all composed of a thermistor as an example.

<Control unit>
Next, the control part 30 of Embodiment 1 is demonstrated based on FIG.
The control unit 30 performs measurement control of the air conditioner, and includes the compressor 1, the four-way valve 2, the indoor blower 8, the outdoor blower 4, the first decompressor 5a, the second decompressor 5b, and the first flow rate. The operation of the regulating valve 13a is controlled. The control unit 30 has sensors connected to the input side and actuators connected to the output side.

The control unit 30 is built in, for example, the outdoor unit A, and includes a measurement unit 30a, a calculation unit 30b, a drive unit 30c, and a determination unit 30e configured by, for example, a microcomputer, and a storage unit 30d configured by, for example, a semiconductor memory. And.

The measurement unit 30a receives the operation state quantity detected by the pressure sensor and the temperature sensors 201 to 208, and measures the pressure and temperature. The operation state quantity measured by the measurement unit 30a is input to the calculation unit 30b.

The calculation unit 30b calculates, for example, a refrigerant physical property value (saturation pressure, saturation temperature, enthalpy, etc.) based on the operation state quantity measured by the measurement unit 30a using a formula given in advance. Moreover, the calculating part 30b performs a calculation process based on the driving | running state amount measured by the measurement part 30a.

The drive part 30c is based on the calculation result of the calculating part 30b, the compressor 1, the four-way valve 2, the outdoor air blower 4, the 1st pressure reduction device 5a, the 2nd pressure reduction device 5b, the indoor air blower 8, and the 1st flow regulating valve 13a. Etc. are driven or stopped.

The storage unit 30d stores a result obtained by the calculation unit 30b, a predetermined constant, a function expression for calculating a physical property value (saturation pressure, saturation temperature, dryness, etc.), a function table (table), and the like. . These stored contents in the storage unit 30d can be referred to and rewritten as necessary. The storage unit 30d further stores a control program, and the control unit 30 controls the air conditioner according to the program in the storage unit 30d.

The determination unit 30e performs processing such as large / small comparison and determination based on the result obtained by the calculation unit 30b.

In addition, although it was set as the structure which incorporates the control part 30 in an air conditioning apparatus in Embodiment 1, this invention is not limited to this. Although illustration is omitted in detail, the outdoor control unit A is provided in the outdoor unit A, and the sub-control unit having a part of the control unit function is provided in the indoor unit B. Between the main control unit and the sub-control unit, It can also be implemented with a configuration in which cooperative processing is performed by performing data communication, a configuration in which a control unit having all functions is installed in the indoor unit B, or a configuration in which a control unit is separately provided outside these units.

<Basic operation of air conditioner>
Next, the operation | movement at the time of air_conditionaing | cooling operation and heating operation of the air conditioning apparatus which consists of the said structure is demonstrated based on FIG.1 and FIG.3. FIG. 3 is a Ph diagram showing the refrigerant state transition of the air-conditioning apparatus according to Embodiment 1 of the present invention.

First, the operation of the air conditioner during cooling operation will be described. During the cooling operation, the four-way valve 2 is in the state indicated by the broken line in FIG. 1, that is, the discharge side of the compressor 1 is connected to the outdoor heat exchanger 3, and the suction side of the compressor 1 is connected to the indoor heat exchanger 7. It is in a state.

The high-temperature and high-pressure gas refrigerant discharged from the compressor 1 reaches the outdoor heat exchanger 3 that is a condenser via the four-way valve 2, and is condensed and liquefied by the blowing action of the outdoor blower 4. Become. The condensed and liquefied high-temperature and low-pressure refrigerant is decompressed by the first decompression device 5 a to become a medium-pressure two-phase refrigerant, further decompressed by the second decompression device 5 b via the receiver 11, and evaporated via the liquid connection pipe 6. It is sent to the indoor heat exchanger 7 which is a vessel. The decompressed two-phase refrigerant evaporates in the indoor heat exchanger 7 by the blowing action of the indoor blower 8 and becomes a low-pressure gas refrigerant. The low-pressure gas refrigerant is compressed again after exchanging heat with the medium-pressure two-phase refrigerant between the first decompression device 5a and the second decompression device 5b via the four-way valve 2 in the internal heat exchanger 14. Inhaled into machine 1.

In the operation of the air conditioner during the cooling operation, in the internal heat exchanger 14, as shown in FIG. 3, the high-temperature medium-pressure two-phase refrigerant decompressed by the first decompression device 5a is converted into the four-way valve 2 and the compressor. 1 is cooled to the saturated liquid refrigerant by the low-temperature low-pressure refrigerant circulating between the suction sides (change from point D to point E). At the same time, the low-pressure gas refrigerant discharged from the indoor heat exchanger 7 is superheated and flows into the compressor 1 as a low-pressure superheated gas refrigerant (change from point G to point A). Due to the heat exchange action in the internal heat exchanger 14, the enthalpy of the refrigerant flowing into the indoor heat exchanger 7 is reduced, and the enthalpy difference at the entrance and exit of the indoor heat exchanger 7 is increased. Therefore, the refrigerant circulation amount necessary for obtaining the predetermined capacity is reduced and the pressure loss is reduced, so that the COP of the refrigeration cycle can be improved. At the same time, since the low-pressure refrigerant flowing into the compressor 1 is in an overheated gas state, a liquid back state due to an excessive inflow of liquid refrigerant into the compressor 1 can be avoided.

Here, in the first pressure reducing device 5a, the flow rate of the refrigerant flowing through the outdoor heat exchanger 3 with the opening degree adjusted by the control unit 30 so that the refrigerant subcooling degree at the outlet of the outdoor heat exchanger 3 becomes a target value. Is controlled. Therefore, the liquid refrigerant condensed in the outdoor heat exchanger 3 has a target degree of supercooling. The refrigerant supercooling degree at the outlet of the outdoor heat exchanger 3 is a value obtained by subtracting the detection value (corresponding to the refrigerant condensation temperature Tc) from the detection value by the gas side temperature sensor 202 from the detection value by the liquid side temperature sensor 204.

Further, the opening of the second decompression device 5b is adjusted by the control unit 30 so that the discharge refrigerant temperature Td of the compressor 1 becomes a target value, and the flow rate of the refrigerant circulating in the indoor heat exchanger 7 is controlled. Yes. That is, the indoor heat exchanger 7 is supplied with a refrigerant having a flow rate corresponding to the operation load required in the air-conditioned space in which the indoor unit B is installed. Note that the discharge refrigerant temperature Td of the compressor 1 is detected by the discharge temperature sensor 201 or the shell temperature sensor 208.

Next, the operation during the heating operation will be described with reference to FIGS. 1 and 3.
In the heating operation, the four-way valve 2 is shown by a solid line in FIG. 1, that is, the discharge side of the compressor 1 is connected to the indoor heat exchanger 7 and the suction side of the compressor 1 is connected to the outdoor heat exchanger 3. It has become.

The high-temperature and high-pressure gas refrigerant discharged from the compressor 1 reaches the indoor heat exchanger 7 as a condenser via the four-way valve 2 and the gas connection pipe 9, and the refrigerant is condensed and liquefied by the blowing action of the indoor blower 8. High pressure and low temperature. The condensed and liquefied high-temperature and low-pressure refrigerant is decompressed by the second decompression device 5b via the liquid connection pipe 6 and becomes a medium-pressure two-phase refrigerant, further decompressed by the first decompression device 5a via the receiver 11, It is sent to the outdoor heat exchanger 3 which is an evaporator. The decompressed two-phase refrigerant evaporates in the outdoor heat exchanger 3 by the blowing action of the outdoor blower 4 and becomes a low-pressure gas refrigerant. The low-pressure gas refrigerant exchanges heat with the medium-pressure two-phase refrigerant between the first decompression device 5a and the second decompression device 5b through the four-way valve 2 and then the compressor again. Inhaled into 1.

In the operation of the air conditioner during the heating operation, in the internal heat exchanger 14, the high-temperature medium-pressure two-phase refrigerant decompressed by the second decompression device 5b circulates between the four-way valve 2 and the compressor 1 suction side. The refrigerant is cooled down to the saturated liquid refrigerant by the low-temperature, low-pressure refrigerant (change from point D to point E). At the same time, the low-pressure gas refrigerant discharged from the outdoor heat exchanger 3 is superheated and flows into the compressor 1 as a low-pressure superheated gas refrigerant (change from point G to point A). Due to the heat exchange action in the internal heat exchanger 14, the enthalpy of the refrigerant flowing into the indoor heat exchanger 7 is reduced, and the enthalpy difference at the entrance and exit of the indoor heat exchanger 7 is increased. Therefore, the refrigerant circulation amount necessary for obtaining the predetermined capacity is reduced and the pressure loss is reduced, so that the COP of the refrigeration cycle can be improved. At the same time, since the low-pressure refrigerant flowing into the compressor 1 is in an overheated gas state, a liquid back state due to an excessive inflow of liquid refrigerant into the compressor 1 can be avoided.

Here, in the second decompression device 5b, the flow rate of the refrigerant flowing through the indoor heat exchanger 7 with the opening degree adjusted by the control unit 30 so that the degree of refrigerant supercooling at the outlet of the indoor heat exchanger 7 becomes a target value. Is controlled. Therefore, the liquid refrigerant condensed in the indoor heat exchanger 7 has a target degree of supercooling. The refrigerant supercooling degree at the outlet of the indoor heat exchanger 7 is a value obtained by subtracting a detection value (corresponding to the refrigerant condensation temperature Tc) from the detection value of the liquid side temperature sensor 205 from the detection value of the gas side temperature sensor 207.

Further, the opening of the first decompression device 5a is adjusted by the control unit 30 so that the discharge refrigerant temperature Td of the compressor 1 becomes a target value, and the flow rate of the refrigerant circulating in the outdoor heat exchanger 3 is controlled. Yes. Therefore, the discharge gas refrigerant discharged from the compressor 1 is in a target temperature state. Thus, the refrigerant | coolant of the flow volume according to the driving | running load requested | required in the air-conditioning space in which the indoor unit B was installed flows into the indoor heat exchanger 7. FIG. Note that the discharge refrigerant temperature Td of the compressor 1 is detected by the discharge temperature sensor 201 or the shell temperature sensor 208.

In the first embodiment, the detection value of the temperature sensor installed in each heat exchanger is used as the refrigerant condensation temperature Tc. However, a pressure sensor is installed on the discharge side of the compressor 1 to detect the refrigerant discharge pressure. The detected value of the discharge pressure may be converted into the saturation temperature and used as the refrigerant condensing temperature Tc.

<< Control Method of First Flow Control Valve >>
Operation | movement of the 1st flow regulating valve 13a in the air conditioning apparatus of Embodiment 1 is demonstrated based on FIG. FIG. 4 is a flowchart showing a flow of control operation of the flow rate adjustment valve of the air-conditioning apparatus according to Embodiment 1 of the present invention.

(Step S11)
After starting the control flow, the control unit 30 detects the discharge refrigerant temperature Td of the compressor 1 with the measurement unit 30a. As the discharge refrigerant temperature Td, a detection value of the discharge temperature sensor 201 or the shell temperature sensor 208 is used.

(Step S12)
The control unit 30 compares the detected discharge refrigerant temperature Td detected by the determination unit 30e with the discharge refrigerant temperature excessive temperature determination value Tdo stored in the storage unit 30d in advance, and the discharge refrigerant temperature of the compressor 1 It is determined whether Td is in an excessive state. Specifically, it is determined whether or not the discharged refrigerant temperature Td is higher than the discharged refrigerant temperature excessive state determination value Tdo. The discharge refrigerant temperature excessive state determination value Tdo is determined by the product specifications of the compressor 1, and is set to 120 degrees, for example, which is the operation guarantee range upper limit value of the discharge refrigerant temperature Td of the compressor 1.
If it is determined that the discharged refrigerant temperature Td is higher than the discharged refrigerant temperature excessive state determination value Tdo, the control unit 30 proceeds to step S13, and if not, the control unit 30 proceeds to step S14.

(Step S13)
When it is determined in step S12 that the discharged refrigerant temperature Td is higher than the discharged refrigerant temperature excessive state determination value Tdo, the control unit 30 fully opens the first flow rate adjustment valve 13a in the drive unit 30c, and the process proceeds to step S15. .

(Step S14)
When it is determined in step S12 that the discharged refrigerant temperature Td is not higher than the discharged refrigerant temperature excessive state determination value Tdo, the control unit 30 fully closes the first flow rate adjustment valve 13a in the drive unit 30c and performs the control flow. finish.

(Step S15)
After fully opening the first flow rate adjustment valve 13a in step S13, the control unit 30 obtains the intake refrigerant superheat degree SHs as the intake refrigerant state of the compressor 1 based on the refrigerant evaporation temperature Te in the calculation unit 30b. The intake refrigerant superheat degree SHs is calculated by subtracting the refrigerant evaporation temperature Te from the intake refrigerant temperature Ts.

Here, the evaporating temperature Te of the refrigerant is detected by a gas side temperature sensor 207 installed in the indoor heat exchanger 7 during the cooling operation, and a detection value of the gas side temperature sensor 202 installed in the outdoor heat exchanger 3 during the heating operation. It is.
The suction refrigerant temperature Ts is a suction refrigerant pressure Ps (equivalent to the compressor suction pressure) obtained by converting the refrigerant evaporation temperature Te into a saturation pressure, and a high pressure Pd (equivalent to a compressor discharge pressure) obtained by converting the refrigerant condensation temperature Tc into a saturation pressure. ) And the discharge refrigerant temperature Td, the compression process of the compressor 1 can be calculated from the following equation 1 assuming that the polytropic index n is a polytropic change.

Here, Ts and Td are temperature [K], Ps and Pd are pressure [MPa], and n is a polytropic index [-]. The polytropic index may be a constant value (for example, n = 1.2), but by defining it as a function of Ps and Pd, the intake refrigerant temperature Ts can be estimated more accurately.

Note that the high-pressure pressure Pd and the suction refrigerant pressure Ps of the refrigerant are calculated by the refrigerant condensing temperature Tc and the evaporation temperature Te, but pressure sensors are installed on the suction side and the discharge side of the compressor 1. And may be detected directly. Further, a temperature sensor may be installed on the suction side of the compressor 1 to directly detect the suction refrigerant temperature Ts.

(Step S16)
Based on the intake refrigerant superheat degree SHs detected in step S15, the control unit 30 determines whether the intake refrigerant of the compressor 1 is in the liquid back state by the determination unit 30e. If it is an overheated gas state (intake refrigerant superheat degree SHs> 0), it is determined that it is not in the liquid back state, and the control flow is ended as it is. If it is not an overheated gas state (intake refrigerant superheat degree SHs> 0), it is determined that the liquid is in a back-up state, and the process proceeds to step S17.

(Step S17)
If it determines with it being a liquid back state in step S16, the control part 30 will adjust the opening degree of the 1st flow regulating valve 13a in the direction which closes with the drive part 30c, and will return to step S15 again after opening degree adjustment.
Here, for example, when an electronic expansion valve is used, the opening adjustment of the first flow rate adjustment valve 13a is adjusted by a method of decreasing the opening degree by a certain amount (for example, 20 pulses) according to the specification of the valve and the opening characteristic. .

In the first embodiment, the method of adjusting the opening degree of the first flow rate adjustment valve 13a based on the suction refrigerant superheat degree SHs of the compressor 1 has been described, but based on the suction refrigerant dryness instead of the suction refrigerant superheat degree SHs. Thus, a method of adjusting the opening of the first flow rate adjusting valve 13a may be used. In this case, since the refrigerant dryness X = 1 is a saturated gas state and X> 1 is an overheated gas state, the opening of the first flow rate adjusting valve 13a may be adjusted so that X ≧ 1. The intake refrigerant dryness can be stored in advance as physical property information of the refrigerant, and can be obtained using the intake refrigerant temperature Ts and the intake refrigerant pressure Ps.

<Effect>
The air conditioner according to the first embodiment controls the first flow rate adjustment valve 13a of the bypass pipe 12 based on the discharge refrigerant temperature Td of the compressor 1 detected by the discharge refrigerant temperature detection unit, so that the internal heat exchanger 14 Since the amount of exchange heat can be adjusted, even when R32 is used as the refrigerant circulating in the refrigerant circuit, an excessive discharge refrigerant temperature state can be avoided, and normal air conditioning operation can be realized.

Further, the air conditioner according to the first embodiment controls the opening degree of the first flow rate adjustment valve 13a based on the suction refrigerant state on the suction side of the compressor 1, so that the liquid refrigerant is present on the suction side of the compressor 1. An excessively flowing liquid back state can be avoided, and a compressor failure due to seizure of the sliding portion of the compressor 1 can be avoided, and high reliability can be realized.

Embodiment 2. FIG.
"Equipment configuration"
FIG. 5 is a refrigerant circuit configuration diagram of an air-conditioning apparatus according to Embodiment 2 of the present invention. In the second embodiment, differences from the first embodiment will be mainly described, and the same portions are denoted by the same reference numerals and the description thereof will be omitted.
In the air conditioner of Embodiment 2, as shown in FIG. 5, the bypass pipe 12 is provided with a first flow rate adjusting valve 13a for adjusting the flow rate of the bypass pipe 12, and the four-way valve 2 and the internal heat. Among the suction pipes 15 connecting the exchanger 14, a second flow rate adjustment valve 13 b that adjusts the flow rate flowing through the suction pipe 15 is provided between the connection point of the suction pipe 15 and the bypass pipe 12 and the internal heat exchanger 14. is set up. The first flow rate adjustment valve 13 a and the second flow rate adjustment valve 13 b are controlled to be opened and closed by the control unit 30.

<< Control Method of First Flow Rate Adjustment Valve and Second Flow Rate Adjustment Valve >>
Next, operations of the first flow rate adjustment valve 13a and the second flow rate adjustment valve 13b in the air conditioner of Embodiment 2 will be described with reference to FIG. FIG. 6 is a flowchart showing the flow of the control operation of the flow rate adjustment valve of the air-conditioning apparatus according to Embodiment 2 of the present invention.

(Step S21)
After starting the control flow, the control unit 30 detects the discharge refrigerant temperature Td of the compressor 1 with the measurement unit 30a. As the discharge refrigerant temperature Td, a detection value of the discharge temperature sensor 201 or the shell temperature sensor 208 is used.

(Step S22)
The control unit 30 compares the detected discharge refrigerant temperature Td detected by the determination unit 30e with the discharge refrigerant temperature excessive temperature determination value Tdo stored in the storage unit 30d in advance, and the discharge refrigerant temperature of the compressor 1 It is determined whether Td is in an excessive state. Specifically, it is determined whether or not the discharged refrigerant temperature Td is higher than the discharged refrigerant temperature excessive state determination value Tdo. The discharge refrigerant temperature excessive state determination value Tdo is determined by the product specifications of the compressor 1, and is set to 120 degrees, for example, which is the operation guarantee range upper limit value of the discharge refrigerant temperature Td of the compressor 1.
If it is determined that the discharged refrigerant temperature Td is higher than the discharged refrigerant temperature excessive state determination value Tdo, the control unit 30 proceeds to step S23, and if not, the control unit 30 proceeds to step S24.

(Step S23)
When it is determined in step S22 that the discharged refrigerant temperature Td is higher than the discharged refrigerant temperature excessive state determination value Tdo, the control unit 30 fully opens the first flow rate adjustment valve 13a in the drive unit 30c and adjusts the second flow rate. The valve 13b is fully closed, and the process proceeds to step S25.

(Step S24)
When it is determined in step S22 that the discharged refrigerant temperature Td is not higher than the discharged refrigerant temperature excessive state determination value Tdo, the control unit 30 fully closes the first flow rate adjustment valve 13a in the drive unit 30c and sets the second flow rate. The control valve 13b is fully opened to end the control flow.

(Step S25)
In step S23, the control unit 30 fully opens the first flow rate adjustment valve 13a and fully closes the second flow rate adjustment valve 13b, and then in the calculation unit 30b, based on the refrigerant evaporation temperature Te, the intake refrigerant state of the compressor 1 As a result, the suction refrigerant superheat degree SHs is obtained. The intake refrigerant superheat degree SHs is calculated by subtracting the refrigerant evaporation temperature Te from the intake refrigerant temperature Ts.

(Step S26)
Based on the intake refrigerant superheat degree SHs detected in step S25, the control unit 30 determines whether the intake refrigerant of the compressor 1 is in the liquid back state by the determination unit 30e. If it is an overheated gas state (intake refrigerant superheat degree SHs> 0), it is determined that it is not in the liquid back state, and the control flow is ended as it is. If it is not an overheated gas state (intake refrigerant superheat degree SHs> 0), it is determined that the liquid is in a back-up state, and the process proceeds to step S27.

(Step S27)
When determining that the liquid is in the liquid back state in step S26, the control unit 30 adjusts the opening of the first flow rate adjustment valve 13a in the closing direction by the drive unit 30c and opens the opening of the second flow rate adjustment valve 13b. After adjusting in the direction, the process returns to step S25 again.
Here, the opening adjustment of the first flow rate adjusting valve 13a and the second flow rate adjusting valve 13b is, for example, when an electronic expansion valve is used, according to the valve specifications and the opening characteristics, a constant opening (for example, 20 pulses). Make adjustments by decreasing the size gradually.

In the second embodiment, the method of adjusting the opening of the first flow rate adjustment valve 13a and the second flow rate adjustment valve 13b based on the intake refrigerant superheat degree SHs of the compressor 1 has been described, but instead of the intake refrigerant superheat degree SHs. Alternatively, the opening of the first flow rate adjustment valve 13a and the second flow rate adjustment valve 13b may be adjusted based on the dryness of the suction refrigerant. In this case, the dryness of the refrigerant X = 1 is a saturated gas state, and X> 1 is a superheated gas state, so the opening degree of the first flow rate adjustment valve 13a and the second flow rate adjustment valve 13b is adjusted so that X ≧ 1. Good. The intake refrigerant dryness can be stored in advance as physical property information of the refrigerant, and can be obtained using the intake refrigerant temperature Ts and the intake refrigerant pressure Ps.

<Effect>
The air conditioner according to the second embodiment includes a first flow rate adjustment valve 13a of the bypass pipe 12 and a second flow rate adjustment valve 13b of the suction pipe 15 based on the discharge refrigerant temperature Td of the compressor 1 detected by the discharge refrigerant temperature detection means. Since the amount of heat exchanged in the internal heat exchanger 14 can be adjusted by controlling the refrigerant, it is possible to avoid an excessive discharge refrigerant temperature state even when R32 is used as the refrigerant circulating in the refrigerant circuit. And normal air-conditioning operation can be realized.

Further, the air conditioner according to the second embodiment controls the opening of the first flow rate adjustment valve 13a and the second flow rate adjustment valve 13b based on the suction refrigerant state on the suction side of the compressor 1, thereby A liquid back state in which the liquid refrigerant excessively flows into the suction side of the compressor can be avoided, and a compressor failure due to seizure of the sliding portion of the compressor 1 can be avoided, and high reliability can be realized.

<Modification of air conditioner>
Although the present invention has been described above based on the embodiment, the present invention is not limited to the configuration of the above-described embodiment. For example, the contents of the refrigerant flow path configuration (piping connection), the configuration of the refrigerant circuit elements such as the compressor, the heat exchanger, and the decompression device are not limited to the contents described in each embodiment. Modifications can be made as appropriate within the scope of the technology of the invention. In short, it should be noted that the scope of the present invention also includes the scope of various changes, applications, and uses made by those skilled in the art as needed.

1 compressor, 2 way valve, 3 outdoor heat exchanger, 4 outdoor blower, 5a first decompressor, 5b second decompressor, 6 liquid connection piping, 7 indoor heat exchanger, 8 indoor blower, 9 gas connection Pipe, 11 receiver, 12 bypass pipe, 13a 1st flow rate adjustment valve, 13b 2nd flow rate adjustment valve, 14 internal heat exchanger, 15 intake pipe, 30 control unit, 30a measurement unit, 30b calculation unit, 30c drive unit, 30d Storage unit, 30e determination unit, 201 discharge temperature sensor, 202 gas side temperature sensor, 203 outdoor temperature sensor, 204 liquid side temperature sensor, 205 liquid side temperature sensor, 206 indoor temperature sensor, 207 gas side temperature sensor, 208 shell temperature sensor , A outdoor unit, B indoor unit.

Claims

A compressor, a condenser, a decompression device, and an evaporator are sequentially connected by a pipe, and an air conditioner including a refrigerant circuit for circulating a refrigerant,
An internal heat exchanger that is installed in a suction pipe connected to the suction side of the compressor and exchanges heat between the refrigerant flowing through the suction pipe and the refrigerant between the condenser and the decompression device;
One bypass pipe connected to the suction pipe disposed on the inlet side of the internal heat exchanger, and the other connected to the suction pipe disposed on the outlet side of the internal heat exchanger;
A first flow control valve installed in the bypass pipe;
A discharge refrigerant temperature detecting means for detecting a discharge refrigerant temperature of the compressor;
An air conditioner comprising: a control unit that controls an opening degree of the first flow rate adjustment valve based on a discharge refrigerant temperature detected by the discharge refrigerant temperature detection unit.
The decompressor includes a first decompressor and a second decompressor,
A receiver is installed on the refrigerant pipe between the first decompressor and the second decompressor;
The air according to claim 1, wherein the internal heat exchanger exchanges heat between the refrigerant flowing through the suction pipe and the refrigerant between the first decompression device and the second decompression device inside the receiver. Harmony device.
The control unit determines whether or not the discharged refrigerant temperature detected by the discharged refrigerant temperature detecting means is in an excessive state,
When it is determined that the discharged refrigerant temperature is in an excessively high state, control is performed to fully open the opening of the first flow rate adjustment valve,
The air conditioning apparatus according to claim 1 or 2, wherein when the discharge refrigerant temperature is determined not to be in an excessively rising state, control is performed to fully close the opening of the first flow rate adjustment valve.
An intake refrigerant state detection means for detecting an intake refrigerant heating degree or an intake refrigerant dryness of the compressor;
The control unit determines whether or not the liquid is back based on the suction refrigerant heating degree or the suction refrigerant dryness detected by the suction refrigerant state detection means, and when the liquid back state is determined, The air conditioner according to any one of claims 1 to 3, wherein control is performed in a direction in which the opening of the flow rate adjustment valve is closed.
Among the suction pipes arranged on the inlet side of the internal heat exchanger, a second flow rate adjustment valve installed between the connection point of the suction pipe and the bypass pipe and the internal heat exchanger,
The said control part controls the opening degree of a said 1st flow regulating valve and a said 2nd flow regulating valve based on the discharged refrigerant temperature detected by the said discharged refrigerant temperature detection means. Air conditioner.
The control unit determines whether or not the discharged refrigerant temperature detected by the discharged refrigerant temperature detecting means is in an excessive state,
When it is determined that the discharge refrigerant temperature is in an excessively high state, the opening of the first flow rate adjustment valve is fully opened and the opening of the second flow rate adjustment valve is fully closed,
When it is determined that the discharged refrigerant temperature is not in an excessively rising state, control is performed to fully close the opening of the first flow rate adjustment valve and fully open the opening of the second flow rate adjustment valve. 5. The air conditioner according to 5.
An intake refrigerant state detection means for detecting an intake refrigerant heating degree or an intake refrigerant dryness of the compressor;
The control unit determines whether or not the liquid is back based on the suction refrigerant heating degree or the suction refrigerant dryness detected by the suction refrigerant state detection means, and when the liquid back state is determined, The air conditioner according to claim 5 or 6, wherein control is performed in a direction in which the opening degree of the flow rate adjustment valve is closed and control is performed in a direction in which the opening degree of the second flow rate adjustment valve is opened.
The air conditioner according to any one of claims 1 to 7, wherein the refrigerant circulating in the refrigerant circuit is R32.