JP6381712B2 - Refrigeration cycle equipment - Google Patents

Description

  The present invention relates to a refrigeration cycle apparatus.

  The conventional refrigeration cycle apparatus determines whether or not R32 refrigerant is used as the refrigerant. When it is determined that R32 refrigerant is used, the difference between the temperature on the suction side of the compressor and the temperature of the evaporator is determined. A certain superheat SH is detected, and it is determined whether or not the superheat SH is within the range of 0.85 to 0.75. If the superheat SH is not within the range, the rotation speed of the compressor or the expansion valve The opening degree is controlled and operation control is performed so that the refrigerant temperature on the discharge side of the compressor falls within a predetermined range (see, for example, Patent Document 1).

Japanese Patent Laid-Open No. 2001-194015 (page 5-7, FIG. 1-3)

  The conventional refrigeration cycle device lowers the discharge temperature of the compressor to ensure reliability such as lubrication and wear of the compressor, but at the cost of the ability to lower the operating efficiency COP and control the compressor and the expansion valve. However, there is a problem that the compressor hunting operation may be caused due to the temperature rise characteristic of the R32 refrigerant.

  The present invention has been made to solve the above-described problems, and controls the temperature of the refrigerant discharged from the compressor without causing a hunting operation, thereby preventing an abnormal stop due to performance degradation or protection device operation. It aims at obtaining the refrigerating-cycle apparatus which can be suppressed.

A refrigeration cycle apparatus according to the present invention includes a compressor, a four-way valve, an outdoor heat exchanger, a receiver having an expansion valve on the upstream side and the downstream side of the refrigerant flow, and a refrigerant circuit in which an indoor heat exchanger is sequentially connected by a refrigerant pipe. , A temperature sensor for detecting the temperature of the case constituting the outer shell of the compressor, and an upper limit in which a predicted case temperature according to the speed of temperature rise per hour from the temperature of the case detected by the temperature sensor is preset And a control device for controlling the opening degree of the expansion valve located on the upstream side of the refrigerant flow with respect to the receiver so as not to exceed the value.

  In the present invention, the degree of opening of the expansion valve located upstream of the refrigerant flow with respect to the receiver is set so that the temperature does not exceed a preset upper limit value from the change in the temperature of the case detected by the temperature sensor. I try to control it. With this configuration, it is not necessary to lower the operating frequency of the compressor for suppressing the temperature rise of the refrigerant discharged from the compressor, and therefore, it is possible to suppress the performance degradation due to the reduction in the operating frequency of the compressor. Accordingly, the compressor does not cause a hunting operation, and an abnormal stop due to the operation of the protective device can be prevented.

1 is a refrigerant circuit diagram showing a schematic configuration of an air conditioner as Embodiment 1 of a refrigeration cycle apparatus according to the present invention. The refrigerant circuit figure which shows schematic structure of the air conditioner as Embodiment 2 of the refrigeration cycle apparatus which concerns on this invention.

Embodiment 1 FIG.
FIG. 1 is a refrigerant circuit diagram showing a schematic configuration of an air conditioner as Embodiment 1 of a refrigeration cycle apparatus according to the present invention.
In the first embodiment, for example, a low GWP R32 refrigerant is used in an air conditioner that can use an R410A refrigerant.
As shown in FIG. 1, this air conditioner includes a compressor 1, a four-way valve 2, an outdoor heat exchanger 3, a second expansion valve 4b, a receiver 6, a first expansion valve 4a, and indoor heat. A refrigerant circuit configured by connecting an exchanger 5 and a first internal heat exchanger 7 installed in the receiver 6 in order by refrigerant pipes (hereinafter referred to as “gas pipe 8, liquid pipe 9”), and control Device 31. The compressor 1 incorporates a motor whose rotational speed is controlled by an inverter.

  The compressor 1 is a high-pressure type that takes in a refrigerant directly into a compression chamber and compresses it. The four-way valve 2 is a four-way switching valve that switches the flow of the refrigerant based on the control from the control device 31. The four-way valve 2 switches the flow path so that the refrigerant discharged from the compressor 1 flows to the outdoor heat exchanger 3 during the cooling operation, and the refrigerant discharged from the compressor 1 flows to the indoor heat exchanger 5 during the heating operation. Switch the flow path to. The outdoor heat exchanger 3 operates as a condenser during the cooling operation, and operates as an evaporator during the heating operation.

  The opening degree of the first expansion valve 4a and the second expansion valve 4b is controlled according to control from the control device 31, and the pressure of the liquid refrigerant is reduced. The receiver 6 is a tank that stores surplus refrigerant that circulates in the refrigerant circuit. The indoor heat exchanger 5 operates as an evaporator during the cooling operation, and operates as a condenser during the heating operation. The first internal heat exchanger 7 is configured such that a part of a gas pipe 8 that connects the four-way valve 2 and the suction portion of the compressor 1 is installed in the receiver 6, and a low-temperature inflow through the four-way valve 2. The gas refrigerant exchanges heat with the high-temperature liquid refrigerant stored in the receiver 6.

  A plurality of temperature sensors 21 to 29 are installed on the refrigerant circuit of the air conditioner. The temperature sensor 21 is installed in the discharge side piping of the compressor 1, the temperature sensor 22 is installed in a case constituting the outer shell of the compressor 1, and the temperature sensor 23 is provided between the four-way valve 2 and the outdoor heat exchanger 3. Installed in the gas pipe 8, the temperature sensor 24 is installed on the refrigerant flow path in the middle of the outdoor heat exchanger 3.

  Furthermore, the temperature sensor 25 is installed in the liquid pipe 9 between the outdoor heat exchanger 3 and the second expansion valve 4b, and the temperature sensor 26 is installed in the liquid pipe 9 between the receiver 6 and the first expansion valve 4a. The temperature sensor 29 is installed in the suction side piping of the compressor 1. Further, the temperature sensor 27 is installed in the liquid pipe 9 between the indoor heat exchanger 5 and the first expansion valve 4 a, and the temperature sensor 28 is installed on the refrigerant flow path in the middle part of the indoor heat exchanger 5. By detecting the temperature of the refrigerant that is a gas-liquid two-phase refrigerant at each intermediate portion of the outdoor heat exchanger 3 and the indoor heat exchanger 5 by the temperature sensors 24 and 28, the high and low pressure refrigerant saturation temperature is detected. Can do.

  The control device 31 operates the compressor 1, the outdoor heat exchanger 3 and the indoors based on the refrigerant temperature of each part detected by the plurality of temperature sensors 21 to 29, the operation of the air conditioner (cooling or heating), and the like. The air volume of each blower (not shown) of the heat exchanger 5 and the opening degree of the first and second expansion valves 4a and 4b are controlled.

  This control device 31 samples the temperature of the refrigerant discharged from the compressor 1 detected by the temperature sensor 21 at regular intervals during the operation of the air conditioner so that the sampled temperature of the discharged refrigerant becomes the target discharge temperature. The opening degree of the first expansion valve 4a or the second expansion valve 4b is controlled. The opening of the second expansion valve 4b is controlled during the cooling operation, and the opening of the first expansion valve 4a is controlled during the heating operation. The target discharge temperature is a temperature value obtained based on the temperature difference between the refrigerant saturation temperature of the outdoor heat exchanger 3 detected by the temperature sensor 24 and the refrigerant saturation temperature of the indoor heat exchanger 5 detected by the temperature sensor 28. is there.

  Further, the control device 31 samples the case temperature (shell temperature) of the compressor 1 detected by the temperature sensor 22 at regular intervals, and the temperature exceeds a preset upper limit value from the change in the sampled case temperature. Is predicted, the opening degree of the first expansion valve 4a or the second expansion valve 4b is controlled. Note that the case temperature may be sampled at substantially the same timing as the temperature of the refrigerant discharged from the compressor 1, or at a different timing and the sampling interval of the case temperature may be shorter than the temperature of the refrigerant discharged. .

  Since the temperature gradient of the case temperature is larger than the temperature of the discharged refrigerant, the control described above should be performed when it is predicted that the case temperature will reach the upper limit value from the change in the case temperature per certain time. Yes. This control has a characteristic that the R32 refrigerant has a characteristic that the temperature rises faster than the R410A refrigerant (for example, 15 to 30 K). Therefore, the protection device protects each component on the refrigerant circuit from the high temperature by the temperature rise. The operating temperature value is not reached. That is, the upper limit value is set lower than the operating temperature value of the protective device, and the protective device is prevented from operating due to the temperature rise of the R32 refrigerant.

In the air conditioner of Embodiment 1 configured as described above, the operation during cooling operation will be described.
High-temperature and high-pressure gas refrigerant is discharged from the compressor 1. This high-temperature and high-pressure gas refrigerant enters the outdoor heat exchanger 3 through the four-way valve 2. The gas refrigerant is heat-exchanged with the outside air by the outdoor heat exchanger 3 to become a liquid refrigerant, and is reduced in pressure by passing through the second expansion valve 4b to become a high-temperature two-phase refrigerant having a dryness within 0.1. This high-temperature two-phase refrigerant enters the receiver 6, is cooled to a saturated liquid state by the low-temperature and low-pressure gas refrigerant flowing in the first internal heat exchanger 7 in the receiver 6, and exits the receiver 6.

  Since the enthalpy at the entrance of the indoor heat exchanger 5 is reduced by the cooling here, the difference in enthalpy at the entrance and exit of the indoor heat exchanger 5 called the so-called refrigeration effect is increased. That is, the saturated liquid refrigerant that has flowed out of the receiver 6 becomes a low-temperature and low-pressure two-phase refrigerant having a dryness of 0.2 to 0.3 by the first expansion valve 4 a and enters the indoor heat exchanger 5. This low-temperature and low-pressure two-phase refrigerant is heat-exchanged with indoor air by the indoor heat exchanger 5 and evaporates to become a low-temperature and low-pressure two-phase refrigerant having a dryness of 0.9 to 1.0, via the four-way valve 2. It passes through the first internal heat exchanger 7 in the receiver 6. At this time, the low-temperature and low-pressure two-phase refrigerant of high dryness that has entered the first internal heat exchanger 7 is heat-exchanged with the high-temperature and high-pressure two-phase refrigerant flowing in the receiver 6 to become a low-pressure superheated gas refrigerant. 1 is inhaled. During this cooling operation, excess refrigerant generated during circulation of the refrigerant circuit is stored in the receiver 6 as saturated liquid refrigerant.

  As described above, since the excess refrigerant generated during the circulation of the refrigerant is stored in the receiver 6 in which the first internal heat exchanger 7 is installed, the accumulator can be eliminated, the pressure loss is reduced, and the refrigeration cycle COP can be improved. In addition, since the high-temperature and high-pressure two-phase refrigerant in the receiver 6 and the low-pressure and low-temperature two-phase refrigerant flowing through the first internal heat exchanger 7 are heat-exchanged, for example, at the time of cooling, the inlet of the indoor heat exchanger 5 that is an evaporator The enthalpy is reduced, and the difference in enthalpy at the evaporator side called the refrigeration effect is increased. Thereby, the refrigerant circulation amount necessary for obtaining a predetermined capacity is reduced, the pressure loss can be further reduced, and the COP of the refrigeration cycle can be further improved.

  Moreover, the dryness of the refrigerant | coolant suck | inhaled to the compressor 1 can be improved by heat-exchanging the liquid refrigerant | coolant with high temperature which exists in the receiver 6, and the low temperature refrigerant | coolant which flows through the 1st internal heat exchanger 7. it can. And the fall of the density | concentration of the refrigerating machine oil in the compressor 1 by this liquid refrigerant returning can be suppressed, and the reliability of the compressor 1 can be hold | maintained.

  In any of the cooling operation and the heating operation, the degree of dryness of the refrigerant sucked in the compressor 1 can be adjusted by controlling the flow rate of the liquid refrigerant from the receiver 6.

Next, the control operation during the cooling operation of the air conditioner will be described.
First, the control device 31 sets the capacity of the compressor 1 and the opening degrees of the first and second expansion valves 4a and 4b to initial values, and when a predetermined time has elapsed, the room temperature becomes the set temperature. In addition, the capacity of the compressor 1 is controlled.

  The control device 31 reads the saturation temperature of the high-pressure refrigerant detected by the temperature sensor 24 and reads the outlet temperature of the outdoor heat exchanger 3 detected by the temperature sensor 25. Then, the control device 31 sets a preset target value of the refrigerant supercooling degree SC at the outlet of the outdoor heat exchanger 3 obtained by the temperature difference between the saturation temperature of the read high-pressure refrigerant and the outlet temperature of the outdoor heat exchanger 3. The opening degree of the second expansion valve 4b is controlled so as to be (for example, 10 ° C.).

  Further, the control device 31 reads the intake temperature of the compressor 1 detected by the temperature sensor 29 and reads the saturation temperature of the low-pressure refrigerant detected by the temperature sensor 28. Then, the control device 31 sets a target value (for example, 10 ° C.) in which the refrigerant superheat degree SH of the compressor 1 obtained by the temperature difference between the read intake temperature of the compressor 1 and the saturation temperature of the low-pressure refrigerant is set in advance. The opening of the first expansion valve 4a is controlled so that

  The control device 31 samples the temperature of the refrigerant discharged from the compressor 1 detected by the temperature sensor 21 at regular intervals, and opens the second expansion valve 4b so that the temperature of the discharged refrigerant becomes the target discharge temperature. Control the degree. Further, the control device 31 samples the case temperature of the compressor 1 detected by the temperature sensor 22 every predetermined time, and predicts that the temperature exceeds the preset upper limit value from the change in the case temperature. Sometimes, the opening degree of the second expansion valve 4b is controlled so that the case temperature is equal to or lower than the upper limit value. In the heating operation, the opening degree of the first expansion valve 4a is controlled when the case temperature is equal to or lower than the upper limit value.

  Thus, the opening degree of the first expansion valve 4a or the second expansion valve 4b is controlled so that the case temperature of the compressor 1 is equal to or lower than the upper limit value lower than the operating temperature value of the protection device. With this configuration, it is not necessary to lower the operating frequency of the compressor 1 for suppressing the rise in the temperature of the refrigerant discharged from the compressor 1, and therefore, it is possible to suppress a decrease in performance due to a decrease in the operating frequency of the compressor. Accordingly, the compressor does not cause a hunting operation, and an abnormal stop due to the operation of the protective device can be prevented.

Embodiment 2. FIG.
FIG. 2 is a refrigerant circuit diagram showing a schematic configuration of an air conditioner as Embodiment 2 of the refrigeration cycle apparatus according to the present invention. In addition, the same code | symbol is attached | subjected to the part similar to Embodiment 1 demonstrated in FIG.
The air conditioner according to the second embodiment is configured by adding the second internal heat exchanger 10 and the injection circuit 11 to the air conditioner of the first embodiment, and uses low GWP R32 as a refrigerant. . The compressor 1 has a built-in motor whose rotational speed is controlled by an inverter, as in the first embodiment.

  The second internal heat exchanger 10 is provided between the second expansion valve 4 b and the receiver 6. The injection circuit 11 branches from the liquid pipe 9 between the receiver 6 and the second internal heat exchanger 10 and is connected to the compression chamber of the compressor 1 via the third expansion valve 4 c and the second internal heat exchanger 10. Has been configured. The third expansion valve 4c is a pressure reducing device for injection.

  The control device 31 in the second embodiment samples the discharge temperature of the compressor 1 detected by the temperature sensor 21 at regular intervals, and the opening degree of the third expansion valve 4c so that the discharge temperature becomes the target discharge temperature. To control. In this case, the opening degree of the third expansion valve 4c is controlled in any of the cooling operation and the heating operation.

  The control device 31 samples the case temperature of the compressor 1 detected by the temperature sensor 22 every predetermined time, and predicts that the temperature exceeds a preset upper limit value from the change in the case temperature. The opening degree of the first expansion valve 4a or the second expansion valve 4b is controlled so that the case temperature becomes equal to or lower than the upper limit value.

In the air conditioner of Embodiment 2 configured as described above, the operation during heating operation will be described.
High-temperature and high-pressure gas refrigerant is discharged from the compressor 1. This high-temperature and high-pressure gas refrigerant flows into the gas pipe 8 through the four-way valve 2 and enters the indoor heat exchanger 5. The high-temperature and high-pressure gas refrigerant is condensed and liquefied while dissipating heat in the indoor heat exchanger 5 and becomes a high-pressure and low-temperature liquid refrigerant. At this time, the room is heated by applying heat radiated from the refrigerant to a load-side medium such as air or water on the load side. The low-temperature and high-pressure liquid refrigerant exiting the indoor heat exchanger 5 flows into the liquid pipe 9 and is slightly depressurized by the first expansion valve 4a, and then flows into the receiver 6, where the first internal heat exchanger in the receiver 6 7, the low-temperature gas refrigerant sucked into the compressor 1 is heated and cooled.

  A part of the liquid refrigerant exiting the receiver 6 flows into the injection circuit 11 and is reduced to an intermediate pressure by the third expansion valve 4c to become a low-temperature two-phase refrigerant, and the remaining liquid refrigerant is second internal heat. Enter the exchanger 10. The high-pressure liquid refrigerant passing through the second internal heat exchanger 10 is further cooled by exchanging heat with the two-phase refrigerant passing through the third expansion valve 4 c of the injection circuit 11.

  Thereafter, the liquid refrigerant that has passed through the second internal heat exchanger 10 is depressurized to a low pressure by the second expansion valve 4b to become a two-phase refrigerant. The two-phase refrigerant flows into the outdoor heat exchanger 3 to absorb heat and becomes a low-temperature and low-pressure gas refrigerant. The gas refrigerant passes through the four-way valve 2, is heat-exchanged with the high-pressure liquid refrigerant in the first internal heat exchanger 7, is heated, and is sucked into the compressor 1.

  On the other hand, the two-phase refrigerant, which has been decompressed by the third expansion valve 4 c of the injection circuit 11 and becomes a low temperature, is heated by exchanging heat with the high-pressure liquid refrigerant in the second internal heat exchanger 10, and is injected into the compressor 1. The Inside the compressor 1, the sucked gas refrigerant is compressed and heated to an intermediate pressure and then merged with the injected refrigerant. After the temperature is lowered, the refrigerant is compressed to a high pressure and discharged as a high-temperature and high-pressure gas refrigerant. Is done.

  The heat exchange in the receiver 6 is mainly performed by exchanging the gas refrigerant out of the gas-liquid two-phase refrigerant into contact with the suction pipe to be condensed and liquefied. Therefore, the smaller the amount of liquid refrigerant staying in the receiver 6, the more the area where the gas refrigerant and the suction pipe are in contact with each other, and the amount of heat exchange increases. Conversely, if the amount of the liquid refrigerant staying in the receiver 6 is large, the area where the gas refrigerant and the suction pipe are in contact with each other decreases, and the heat exchange amount decreases.

  The configuration of the refrigerant circuit in this air conditioner is a so-called gas injection circuit that injects the gas refrigerant into the compressor 1 out of the refrigerant that has been discharged from the indoor heat exchanger 5 serving as a condenser and then has been reduced to an intermediate pressure. ing. By performing gas injection, the flow rate of refrigerant discharged from the compressor 1 increases, and the flow rate of refrigerant discharged from the compressor 1 = the flow rate of refrigerant sucked by the compressor 1 + the flow rate of refrigerant injected. Therefore, since the refrigerant | coolant flow volume which flows into the indoor heat exchanger 5 used as a condenser increases, in the case of heating operation, a heating capability increases.

  As described above, the injection circuit suppresses a decrease in refrigerant circulation due to a low pressure drop during heating and low temperature, and the second internal heat exchanger 10 increases the dryness of the injection refrigerant, thereby suppressing an increase in power of the compressor. Can do. Therefore, efficient operation is possible while suppressing a decrease in capacity at the time of heating and low temperature.

Next, the control operation during the heating operation of the air conditioner will be described.
First, the control device 31 sets the capacity of the compressor 1 and the opening degrees of the first and second expansion valves 4a and 4b to initial values, and when a predetermined time has elapsed, the room temperature becomes the set temperature. In addition, the capacity of the compressor 1 is controlled.

  The control device 31 reads the saturation temperature of the high-pressure refrigerant detected by the temperature sensor 28 and reads the outlet temperature of the indoor heat exchanger 5 detected by the temperature sensor 27. Then, the control device 31 sets a target value in which the refrigerant subcooling degree SC at the outlet of the indoor heat exchanger 5 obtained by the temperature difference between the read saturation temperature of the high-pressure refrigerant and the outlet temperature of the indoor heat exchanger 5 is set in advance. The opening degree of the first expansion valve 4a is controlled so as to be (for example, 10 ° C.).

  Next, the control device 31 reads the intake temperature of the compressor 1 detected by the temperature sensor 29 and reads the saturation temperature of the low-pressure refrigerant detected by the temperature sensor 24. Then, the control device 31 sets a target value (for example, 10 ° C.) in which the refrigerant superheat degree SH of the compressor 1 obtained by the temperature difference between the read intake temperature of the compressor 1 and the saturation temperature of the low-pressure refrigerant is set in advance. The opening of the second expansion valve 4b is controlled so that

  The control device 31 samples the discharge temperature of the compressor 1 detected by the temperature sensor 21 at regular intervals, and controls the opening of the third expansion valve 4c so that the discharge temperature becomes the target discharge temperature. . Further, the control device 31 samples the case temperature of the compressor 1 detected by the temperature sensor 22 every predetermined time, and predicts that the temperature exceeds the preset upper limit value from the change in the case temperature. Sometimes, the opening degree of the first expansion valve 4a is controlled so that the case temperature becomes the upper limit value or less. In the cooling operation, the opening degree of the second expansion valve 4b is controlled when it is predicted from the change in the case temperature that the temperature exceeds a preset upper limit value.

  Thus, the opening degree of the first expansion valve 4a or the second expansion valve 4b is controlled so that the case temperature of the compressor 1 is equal to or lower than the upper limit value lower than the operating temperature value of the protection device. With this configuration, it is not necessary to lower the operating frequency of the compressor 1 for suppressing the rise in the temperature of the refrigerant discharged from the compressor 1, and therefore, it is possible to suppress a decrease in performance due to a decrease in the operating frequency of the compressor. Accordingly, the compressor does not cause a hunting operation, and an abnormal stop due to the operation of the protective device can be prevented.

  DESCRIPTION OF SYMBOLS 1 Compressor, 2 Four way valve, 3 Outdoor heat exchanger, 4a 1st expansion valve, 4b 2nd expansion valve, 4c 3rd expansion valve, 5 Indoor heat exchanger, 6 Receiver, 7 1st internal heat exchanger, 8 Gas pipe, 9 liquid pipe, 10 second internal heat exchanger, 11 injection circuit, 21, 22, 23, 24, 25, 26, 27, 28, 29 temperature sensor, 31 control device.

Claims (5)

A refrigerant circuit in which a compressor, a four-way valve, an outdoor heat exchanger, a receiver having an expansion valve on the upstream side and the downstream side of the refrigerant flow, and an indoor heat exchanger are sequentially connected by a refrigerant pipe;
A temperature sensor for detecting the temperature of the case constituting the outer shell of the compressor;
An upstream side of the refrigerant flow with respect to the receiver so that a predicted case temperature according to the speed of the temperature rise per hour from the temperature of the case detected by the temperature sensor does not exceed a preset upper limit value. And a control device for controlling the opening degree of the expansion valve located in the refrigeration cycle device.   The refrigeration cycle apparatus according to claim 1, wherein a first internal heat exchanger that connects the four-way valve and the compressor is installed inside the receiver. A second internal heat exchanger provided on a refrigerant pipe between the outdoor heat exchanger and the receiver;
An injection circuit that branches off from a refrigerant pipe between the receiver and the second internal heat exchanger and is connected to the compressor via the second internal heat exchanger; The refrigeration cycle apparatus according to claim 2. A discharge temperature sensor for detecting the temperature of the discharge pipe of the compressor;
The control device controls an opening degree of the expansion valve located on the upstream side of the refrigerant flow with respect to the receiver so that a discharge refrigerant temperature detected by the discharge temperature sensor becomes a preset target discharge temperature. The refrigeration cycle apparatus according to any one of claims 1 to 3 , wherein: The refrigeration cycle apparatus according to any one of claims 1 to 4 , wherein R32 is used as a refrigerant circulating in the refrigerant circuit.

Images