JP5989534B2 - Refrigeration system apparatus and air conditioner - Google Patents

Description

  The present invention relates to a refrigeration system apparatus including a receiver that adjusts the amount of refrigerant circulating in a refrigerant circuit and a flow rate adjusting apparatus, and an air conditioner including the same.

  As this type of air conditioner, Patent Document 1 discloses a refrigeration system device in which a compressor, a condenser, a high-pressure side throttle device, a receiver, a low-pressure side throttle device, and an evaporator are connected in series by a pipe. Yes. In this refrigeration system apparatus, the optimum amount of refrigerant flowing through the refrigerant circuit differs between the cooling operation and the heating operation. Therefore, in order to circulate the refrigerant with the optimum amount of refrigerant according to the operation state such as cooling or heating, the refrigerant By adjusting the opening area of the throttle device and changing the opening area of the throttle device, the refrigerant is stored in the receiver or returned from the receiver to the refrigerant circuit to adjust the amount of refrigerant circulating. ing.

  And in patent document 1, in order to detect the driving | running state of a freezing apparatus, the supercooling detection part which detects the supercooling characteristic value of a refrigerating cycle, and the superheat detection part which detects a superheating characteristic value are provided, and the control part Then, by adjusting the opening area of the expansion device on the high-pressure side and the low-pressure side so that the detection results of the supercooling detection unit and the superheat detection unit are close to the target value, the refrigeration cycle is always stable with good operating efficiency. An economical and highly reliable refrigeration system apparatus that maintains an operating state and a control method thereof are disclosed.

  Further, in Patent Document 1, after the operating state of the refrigeration system apparatus is changed, when the discharge temperature of the compressor becomes equal to or higher than a predetermined temperature or after a predetermined time elapses, the high pressure side and the low pressure are decreased in order to stabilize the refrigeration cycle. A method of controlling the opening area of the aperture device on the side is employed.

Japanese Patent No. 3334507

  By the way, in patent document 1, since the change of the installation environment of an outdoor unit and the rotation speed of a compressor is not considered, there existed a possibility that refrigerant | coolant amount variable control might become unstable. That is, generally, when the installation environment (for example, the outside air temperature) of the outdoor unit that houses the compressor and the outdoor heat exchanger changes, the refrigerant discharge temperature of the compressor also changes. For example, if the outside air temperature increases, the refrigerant discharge temperature of the compressor also increases. Moreover, if the rotation speed of a compressor changes, the refrigerant | coolant discharge temperature of a compressor will also change. For example, if the rotation speed of the compressor increases, the refrigerant discharge temperature from the compressor also increases.

  It is considered that the discharge temperature of the compressor changes due to such changes in the installation environment of the outdoor unit and the rotation speed of the compressor, and accordingly, the time required for stabilization of the refrigeration cycle also changes. However, in Patent Document 1, since the waiting time (predetermined time) before the opening control of the expansion device is made constant, if this predetermined time is set short, the change in the outside air temperature and the rotation speed of the compressor Along with the change, there is a possibility that the aperture area of the expansion device will be controlled in a state where the operation state is not yet stable. In general, when the standby time considering safety is determined uniformly, a long predetermined time is inevitably set. For this reason, there is a possibility that it becomes an extra standby time, and there is a problem that it is not possible to efficiently raise a good operation state.

  In view of the above, the present invention improves the operation efficiency by adjusting the amount of refrigerant according to the operation state, and in this case, even when a change in the installation environment of the outdoor unit or the operation state of the refrigeration cycle occurs, An object of the present invention is to provide a refrigeration system apparatus and an air conditioner that can perform stable control.

  In order to achieve the above object, in the present invention, a compressor, a condenser, a high pressure side flow rate adjustment device, a receiver, a low pressure side flow rate adjustment device, and an evaporator are sequentially connected by a pipe, and a refrigeration device The supercooling detection unit for detecting the supercooling characteristic value of the refrigeration apparatus, the overheating detection unit for detecting the superheating characteristic value of the refrigeration apparatus, and the detection results of the supercooling detection unit and the superheating detection unit are brought close to the target value. A control unit that adjusts the opening area of the high-pressure side flow rate adjustment device and the low-pressure side flow rate adjustment device, a discharge temperature detection unit that detects the discharge temperature of the compressor, and a rotation speed detection unit that detects the rotation speed of the compressor And an outside air temperature detecting unit for detecting the outside air temperature, and the control unit adjusts an opening area of the high pressure side flow rate adjusting device and / or the low pressure side flow rate adjusting device according to a change in the operating state of the refrigeration apparatus. When the compressor The adjustment of the opening area is waited until the time change of the temperature difference between the discharge temperature and the outside air temperature is within the predetermined value range, and the refrigeration apparatus is stable when the time change is within the predetermined value range. It is determined that the adjustment of the opening area of the flow rate adjusting device is started.

  According to the present invention, when the opening area of the high-pressure side and / or low-pressure side flow control device is controlled after the operating state of the refrigeration apparatus is changed, from an arbitrary expression composed of the discharge temperature, the rotation speed, and the outside air temperature. Since stability is determined using the obtained saturation curve, it is possible to provide a refrigeration system apparatus that is more reliable than conventional ones.

It is a block diagram of the refrigeration system apparatus at the time of air_conditionaing | cooling operation which is embodiment of this invention. It is a block diagram of the refrigeration system apparatus at the time of heating operation similarly. It is a control flowchart of the opening area of a flow regulating device. It is a flowchart of stabilization determination similarly. It is a Mollier chart of a refrigeration system apparatus. (A)-(c) is a reference graph when creating the formula for determination flows. (A) and (b) are reference graphs when creating a formula for determination flow following FIG.

  Hereinafter, an embodiment in which the present invention is applied to a refrigeration system apparatus for an air conditioner will be described with reference to the drawings. FIG. 1 is a configuration diagram of a refrigeration system apparatus during cooling operation, and FIG. 2 is a configuration diagram of the refrigeration system apparatus during heating operation.

  As shown in FIGS. 1 and 2, the refrigeration system apparatus for an air conditioner according to the present embodiment has one indoor unit 1 and one outdoor unit 2 connected by a refrigerant pipe 3. The compressor 4 includes a four-way valve 5 for switching the refrigerant flow path, the outdoor heat exchanger 6 and the expansion device 7, and the indoor unit 1 includes an indoor heat exchanger 8. Moreover, although not shown in figure, an indoor fan is arrange | positioned facing an indoor heat exchanger, and an outdoor fan is arrange | positioned facing an outdoor heat exchanger.

  In this refrigeration system apparatus, during cooling operation, the refrigerant discharged from the compressor 4 is compressed from the four-way valve 5 through the outdoor heat exchanger 6, the expansion device 7, and the indoor heat exchanger 8 as shown in FIG. The forward flow returns to the machine 4. In the heating operation, as shown in FIG. 2, the refrigerant discharged from the compressor 4 returns from the four-way valve 5 to the compressor 4 through the indoor heat exchanger 8, the expansion device 7, and the outdoor heat exchanger 6. The flow is in the opposite direction.

  Therefore, in the refrigeration system apparatus of this example, the outdoor heat exchanger 6 functions as a condenser and the indoor heat exchanger 8 functions as an evaporator during cooling operation. During the heating operation, the indoor heat exchanger 8 functions as a condenser, and the outdoor heat exchanger 6 functions as an evaporator. The refrigeration system apparatus during such cooling operation and heating operation is a reversible cycle refrigerant circuit, and the flow direction of the refrigerant is as shown by the arrows in FIGS. The refrigerant circuit 10 is configured by flowing in the order of the condenser, the expansion device 7, and the evaporator.

  In this example, as shown in FIGS. 1 and 2, a bypass path 12 with an on-off valve 11 is connected in parallel with the outdoor heat exchanger 6 to return a part of the refrigerant in the refrigerant circuit 10 to the compressor side. However, it may be a refrigerant circuit without these bypass passages with on-off valves.

In this example, the flow rate adjustment unit 13 that adjusts the flow rate of the refrigerant flowing through the refrigerant circuit 10 includes:
The refrigerant connected to the expansion device 7 in parallel is controlled so that the refrigerant flowing through the refrigerant circuit 10 has an optimum flow rate. The flow rate adjusting unit 13 includes a receiver 14 that accumulates the refrigerant using the pressure of the refrigerant flowing from the high pressure side before and after the expansion device 7 to the low pressure side, and the high pressure side branch portion of the expansion device 7 in the refrigerant circuit 10 and the receiver 14. The high-pressure side and the low-pressure side flow rate adjustment respectively interposed between the high-pressure side connecting pipe to be connected and the low-pressure side connecting pipe connecting the receiver 14 with the low-pressure side branch of the expansion device 7 in the refrigerant circuit 10. Devices 15 and 16.

  These flow rate adjusting devices 15 and 16 adjust the amount of refrigerant accumulated in the receiver 14 by adjusting the opening area thereof, and adjust the flow rate of the refrigerant flowing through the refrigerant circuit 10 to an optimum flow rate. Like the expansion valve and the throttle device 7, the flow rate adjustment devices 15 and 16 have a function of adjusting the amount of refrigerant entering the receiver 14 by changing the area of the opening through which the refrigerant passes.

  In this example, an example in which the flow rate adjusting unit 13 is connected in parallel with the expansion device 7 is shown, but this is not limiting, and only the flow rate adjusting unit including the receiver 14 and the high-pressure side and low-pressure side flow rate adjusting devices 15 and 16 is shown. And a refrigeration system device that does not include the expansion device 7 may be used.

  As in this example, in the refrigeration system apparatus in which the expansion device 7 and the flow rate adjustment unit 13 are connected in parallel, the expansion device 7 is normally activated at the initial opening area at the initial operation stage, thereby the refrigerant pressure of the refrigeration device. Etc., the control for adjusting the opening areas of the flow rate adjusting devices 15 and 16 of the flow rate adjusting unit 13 is performed. That is, when the throttle amount of the throttle device 7 is controlled by a preset value according to the outside air temperature or set temperature at the start-up, and then the rotation speed of the compressor is varied in accordance with the change in the outside air temperature or the room temperature For example, when the operating state of the refrigeration apparatus is varied, the opening area of the flow rate adjustment devices 15 and 16 is controlled and stored in the receiver 14 in order to finely adjust the refrigerant circulating in the refrigerant circuit 10 to the optimum refrigerant amount. Adjust the amount of refrigerant. That is, rough control is performed by the throttle device 7 and fine control is performed by the flow rate adjusting devices 15 and 16. Therefore, the expansion device 7 and the flow rate adjusting unit 13 are controlled according to each purpose.

  In this example, the necessity of changing the operation state as described above arises, and when it is necessary to finely adjust the opening area of the high-pressure side and / or low-pressure side flow rate adjustment device, the operation state of the refrigeration apparatus is After the stabilization, an attempt is made to adjust the opening area of the flow rate adjusting device.

  That is, the control unit 20 of this example waits for the adjustment operation of the opening areas of the flow rate adjusting devices 15 and 16 until the time change of the temperature difference between the discharge temperature of the compressor 4 and the outside air temperature is within a predetermined value range. Then, when the time change falls within a predetermined value range, it is determined that the refrigeration apparatus is stable, and the adjustment operation of the opening areas of the flow rate adjusting devices 15 and 16 is started.

  Hereinafter, a specific configuration will be exemplified. Since the refrigerant flows in a reversible cycle between the cooling operation and the heating operation, the high-pressure side and low-pressure side flow control devices 15 and 16 have different refrigerant flow directions during the cooling operation and the heating operation. Become. That is, in the flow rate adjustment unit 13, as shown in FIG. 1, the first flow rate adjustment device 15 interposed in the connecting pipe on the outdoor heat exchanger 6 side of the expansion device 7 and the indoor heat exchanger than the expansion device 7. The second flow rate adjustment device 16 interposed in the 8-side connecting pipe is provided. When there is a refrigerant flow from right to left, such as in the cooling operation cycle, the first flow rate adjustment device 15 is on the high pressure side. The second flow rate adjusting device 16 functions as a low pressure side flow rate adjusting device. Also, as shown in FIG. 2, when there is a refrigerant flow from left to right, such as in a heating operation cycle, the second flow rate adjustment device 16 functions as a high-pressure side flow rate adjustment device, and the first flow rate adjustment device Reference numeral 15 functions as a low-pressure flow rate adjusting device.

  The expansion device 7 adjusts the condensation and evaporation pressure of the refrigerant circuit 10, and a pressure difference is generated before and after the flow path. By utilizing this pressure difference, a part of the refrigerant in the refrigerant circuit 10 is condensed and stored in the receiver 14 of the flow rate adjusting unit 13, and the refrigerant in the receiver 14 is returned to the refrigerant circuit.

  In the refrigerant circuit 10 of the cooling operation cycle shown in FIG. 1, the high-temperature and high-pressure refrigerant discharged from the compressor 4 is heat-exchanged by the outdoor heat exchanger 6 functioning as a condenser, and then depressurized through the expansion device 7. Then, it enters into the indoor heat exchanger 8 that functions as an evaporator as a gas refrigerant, where heat is exchanged and returns to the compressor 4. In the refrigerant circuit 10 of the heating operation cycle shown in FIG. 2, the high-temperature and high-pressure refrigerant discharged from the compressor 4 is heat-exchanged by the indoor heat exchanger 8 functioning as a condenser, and then depressurized through the expansion device 7. Then, it enters into the outdoor heat exchanger 6 that functions as an evaporator as a gas refrigerant, where heat is exchanged and returns to the compressor 4.

  In such a cooling operation cycle and a heating operation cycle, in the flow rate adjustment unit 13, the high-pressure liquid refrigerant enters from the high-pressure side flow rate adjustment device, is decompressed, and is stored in the receiver 14 in a liquid refrigerant state. The degree of pressure reduction is affected by the opening degree (opening area) of the flow rate adjusting devices 15 and 16. On the other hand, the liquid refrigerant in the receiver 14 enters the low-pressure side flow rate adjusting device from the connection port, is reduced in pressure to become a mixed refrigerant of gas and liquid, and is returned to the refrigerant circuit 10.

  In the case of the refrigerant flow in the cooling operation cycle shown in FIG. 1, the first flow rate adjustment device 15 becomes a high-pressure side flow rate adjustment device, and the second flow rate adjustment device 16 becomes a low-pressure side flow rate adjustment device. In the case of the refrigerant flow in the heating operation cycle shown in FIG. 2, the second flow rate adjustment device 16 becomes a high-pressure side flow rate adjustment device, and the first flow rate adjustment device 15 becomes a low-pressure side flow rate adjustment device.

  FIG. 5 is a Mollier chart of the refrigeration system apparatus in the present embodiment. In the figure, AD and a-d are symbols assigned for explaining the characteristic state values of the respective refrigerants at the respective positions of the refrigeration cycle. In this refrigeration system apparatus, the refrigerant (in the state A) sucked into the compressor 4 is compressed in the compressor 4 (in the state B), and the condenser (the outdoor heat exchanger 6 in the cooling operation, the indoor heat exchange in the heating operation). The refrigerant 8 is condensed to become a liquid refrigerant (state C), and is squeezed by the expansion device 7 to reduce the pressure (state D), and the evaporator (the indoor heat exchanger in the cooling operation, the outdoor heat exchanger in the heating operation). ) And is again sucked into the compressor 4 (state A).

  At this time, if the throttle amount of the throttle device 7 or the opening areas of the flow rate adjusting devices 15 and 16 change, the condensation pressure and the evaporation pressure change, the degree of supercooling of the refrigerant on the outlet side of the condenser, and the suction side of the compressor 4 The degree of refrigerant superheat changes. Further, when the rotation speed of the compressor is varied in accordance with the change in the outside air temperature or the change in the room temperature, or the refrigerant discharge temperature of the compressor also fluctuates due to the change in the outside air temperature. When the rotational speed of the compressor is varied due to such a variation factor, or when the opening area of the throttle device or the flow rate adjusting device is changed as described above, the degree of refrigerant supercooling on the outlet side of the condenser and the suction of the compressor The refrigerant superheat degree on the side changes, and the Mollier chart shown in FIG. 5 changes.

  Therefore, in this example, the supercooling detection unit for detecting the supercooling characteristic value of the refrigeration apparatus, the overheating detection unit for detecting the superheating characteristic value of the refrigeration apparatus, and the detection results of the supercooling detection part and the superheating detection part A control unit 20 is provided that adjusts the opening areas of the high-pressure side flow rate adjustment device and the low-pressure side flow rate adjustment device so as to approach the target value and controls the refrigerant flow rate to an optimum value.

  The subcooling detection unit consists of a combination of a temperature detection sensor that detects the outlet side temperature of the condenser and a central temperature detection sensor that detects the temperature near the center of the condenser, and the temperature deviation detected from both temperature sensors. The value is the degree of supercooling. The reason for detecting the temperature near the center of the condenser is that the temperature near this is considered to correspond to the saturation temperature of the refrigerant corresponding to the refrigerant pressure in the condenser.

  The overheat detection unit is composed of a combination of a temperature sensor that detects the temperature on the inlet side of the evaporator and a temperature sensor that detects the temperature on the outlet side of the evaporator, and calculates the deviation value of the temperature detected from both temperature sensors. And

  Note that the outdoor heat exchanger 6 and the indoor heat exchanger 8 become condensers or evaporators depending on the direction in which the refrigerant flows. In FIGS. 1 and 2, the outdoor heat exchanger 6 and the indoor heat exchanger 8 Only the temperature sensors 22 to 27 are illustrated in the vicinity of the entrance and the center. Therefore, the temperature information from the temperature sensors 22 to 27 is collected according to the cooling operation cycle or the heating operation cycle, and the opening areas of the flow rate adjusting devices 15 and 16 are adjusted.

  The control unit 20 is composed of a general microcomputer, and the high-pressure side flow rate adjustment device and / or the low-pressure side flow rate adjusting device and / or the low-pressure side so as to bring the detection results of the supercooling detection unit and the superheat detection unit close to the target value stored in advance. The opening area of the flow rate adjusting device is adjusted to control the refrigerant flow rate to an optimum value.

  Further, the control unit 20 detects the discharge temperature of the compressor 4, a discharge temperature detection unit 30, a rotation number detection unit 31 that detects the rotation number of the compressor 4, and an external unit for detecting the installation environment of the outdoor unit. An outside air temperature detecting unit 32 that detects the air temperature is provided, and it is determined whether or not the refrigeration apparatus is stable based on the detected information. Although the discharge temperature detection unit 30 is originally installed in the refrigerant flow path on the discharge side of the compressor, in this example, as an alternative measure, it is installed on the outer surface side of the discharge pipe of the compressor 4, The discharge pipe surface temperature is detected. The compressor rotation speed detector 31 of this example detects the rotation speed by detecting the rotor position of the compressor motor. Further, the outside air temperature detection unit 32 detects the outside air temperature by a temperature sensor exposed to the outside from the outdoor unit.

  When the controller 20 adjusts the opening area of the high-pressure side flow rate adjustment device and / or the low-pressure side flow rate adjustment device according to the change in the operating state of the refrigeration apparatus, the discharge temperature of the compressor 4, the compressor 4 And adjusting the opening area of the flow rate adjusting devices 15 and 16 until the time change of the temperature difference between the discharge temperature of the compressor 4 and the outside air temperature is within a predetermined value range. It is made to stand by, and when the said time change becomes in the range of a predetermined value, it judges that the freezing apparatus was stabilized, and starts the adjustment operation of the opening area of the said flow control apparatus.

  Specifically, the control unit 20 sets and stores a functional expression of a temperature difference between the compressor discharge temperature and the outside air temperature, using the compressor rotation speed, the compressor discharge temperature, and the outside air temperature as parameters. The stability of the refrigeration apparatus is judged using this function formula.

  Adjustment of the opening areas of the flow rate adjusting devices 15 and 16 in the control unit 20 is performed as follows. First, the controller 20 calculates a deviation value between a target value of the refrigerant supercooling degree at the outlet of the condenser and a target value of the refrigerant superheated degree of the compressor 4 and a measured value or an estimated value thereof, and the obtained deviation value and Since the relational expression that correlates the change rate of the opening area of the high pressure side flow rate adjustment device and the low pressure side flow rate adjustment device is created and stored in advance from the theoretical and experimental results, each measured value and Based on the degree of subcooling and the degree of superheat from each target value, the change rate of the opening area of each flow rate adjustment device 4 is calculated, and the opening of the high pressure side flow rate adjustment device and low pressure side flow rate adjustment device is calculated from this calculation result. The area is controlled by the control unit. In this way, both the refrigerant supercooling degree at the outlet of the condenser and the suction refrigerant superheating degree of the compressor can be brought close to the target value corresponding to the preset operating state of the refrigeration apparatus.

  Next, the control for determining the stability of the refrigeration apparatus is performed as follows. FIG. 3 is an overall flowchart showing the flow of the entire process. When controlling the compressor intake refrigerant superheat degree and the condenser outlet refrigerant supercool degree indicating the state characteristic value of the refrigeration cycle, when the operation of the compressor 4 is started, it is set in advance from a test result or a calculation result. The diaphragm amount of the diaphragm device 7 is adjusted so as to be the initial activation opening area (S1).

  Next, when adjusting the opening area of the high pressure side flow rate adjustment device and / or the low pressure side flow rate adjustment device in accordance with the change in the operating state of the refrigeration device, a determination process of the stability of the refrigeration device is performed (S2). After the stability determination process, it is determined whether or not it is stable (S3). As a result, if it is determined that the refrigeration apparatus is stable, the opening areas of the flow control devices 15 and 16 are controlled, and according to the operating state of the refrigeration system. The refrigeration cycle state characteristic values, for example, the intake refrigerant superheat degree of the compressor and the refrigerant subcooling degree of the condenser outlet are tested in advance so as to obtain the best operating efficiency of the refrigeration system, or Calculate target values of the refrigerant superheat degree of the compressor and the refrigerant subcooling degree at the outlet of the condenser, which serve as a guide for the refrigerant state quantity of each part obtained from the calculation results, and adjust the flow rate on the high pressure side so that the target values are obtained. The opening area of the adjusting device and / or the flow adjusting device on the low pressure side is controlled (S4). This process is continued until the target values of the refrigerant superheat degree and the refrigerant supercool degree at the condenser outlet are reached (S5).

  Then, it is determined whether or not the operating state has changed (S6). If the operating state has changed, the process returns to step S2 to perform the stability determination process (S2). Thereafter, if it is determined that the refrigeration apparatus is stable. For example, the process of controlling the opening area of the flow rate adjusting devices 15 and 16 is repeated (S4 to S6).

  FIG. 4 is a flowchart of the stabilization determination process. As shown in FIG. 4, first, in the stability determination process, a temporal change in the discharge pipe surface temperature of the compressor is measured, and an approximate expression A2 is created from the function expression A1 and the measured value that are set and stored in advance. (S7), the outside air temperature and the rotation speed of the compressor are input to the approximate expression A2 (S8). Then, it is determined whether or not the time change of the temperature difference ΔT between the discharge temperature of the compressor 4 and the outside air temperature is within the range of the predetermined value δ (S9). This process is repeated, and when the time change of the temperature difference ΔT falls within the range of the predetermined value δ, it is determined that the refrigeration apparatus is stable (S10), the stabilization determination process is terminated, and the process proceeds to step S3 in FIG. After returning and judging that it is stable, the adjustment operation of the opening areas of the flow rate adjusting devices 15 and 16 is started.

  A specific procedure for creating the approximate expression A2 will be described with reference to FIGS. 6 (a) to 6 (c) and FIGS. 7 (a) and 7 (b). In step S11, when the outside air temperature Tout1 is changed, the discharge pipe surface temperature Td11, Td12 at the stable time when rotating at the rotation speed f1 and the rotation speed f2, and the time change of the discharge pipe surface temperature when rotating at the rotation speed f2. Measure. FIG. 6A is a graph in which the vertical axis represents the temperature difference ΔT between the discharge pipe surface temperature and the outside air temperature, and the horizontal axis represents time t. In the graph of FIG. 6 (a), the measured value (x mark) of [the discharge pipe surface temperature−the temperature difference of the outside air temperature] when the compressor is rotated at the rotation speed f2, and the compressor for reference. Actual value (● mark) of [Discharge pipe surface temperature-temperature difference between outside air temperature] when rotated at rotation speed f1 and [Stable discharge pipe surface temperature Td11-Tout] when rotated at rotation speed f1 Is represented by ΔT1, and [stable discharge pipe surface temperature Td12−Tout] when rotated at a rotational speed f2 is represented by ΔT2. Tout indicates an arbitrary outside temperature. The discharge pipe surface temperature is for detecting the discharge temperature of the refrigerant of the compressor, and is detected by a discharge temperature sensor. As is apparent from the plotted actual measurement values, the temperature difference function ΔT (t) converges to ΔT1 and ΔT2 with time.

Therefore, a function formula A1 shown in Formula 1 is created and stored in the storage unit of the control unit 20. The function formula A1 is a formula that takes into account the rate of change due to the rotational speed of the compressor.

  Stabilization determination processing is performed using this function equation A1. In step S12, Formula 2 is obtained by substituting f = f2 as the predetermined rotational speed shown in Formula 1. Formula 2 represents the upper limit value of the time change curve of the temperature difference ΔT between the discharge temperature of the compressor 4 and the outside air temperature created from Formula 1.

ΔT(t)：吐出管表面温度−Tout
f：任意の回転数
f1：回転数1
f2：回転数2
τ：パラメータ

ΔT (t): Discharge pipe surface temperature-Tout
f: Arbitrary rotation speed
f1: Number of revolutions 1
f2: Number of revolutions 2
τ: Parameter

  In step S13, the parameter τ is determined by the measurement result of step S11 and the least square method. FIG. 5B is a time variation curve of ΔT2 at the rotation speed f2. As is apparent from this figure, the slope of the saturation curve varies greatly depending on the value of the parameter τ. FIG. 6B illustrates three types of curves of τ = 1.5, τ = 3.5, and τ = 7.0. In FIG. 6B, a curve with the parameter τ = 3.5 is given as a curve that most closely approximates the plotted measurement values.

  Similarly, in step 14, Formula 1 to Formula 3 are created with the predetermined rotation speed f = f1 of Formula 1. The parameter τ is determined from the measurement result in step 11. Then, a curve that most closely approximates the measurement values plotted in FIG. FIG. 6C shows a saturation curve created by the rotation speed f2 and the rotation speed f1 by a dotted line. The curve with the rotational speed f2 represents the upper limit value, and the curve with the rotational speed f1 represents the lower limit value. Within the region sandwiched between the two curves, the saturation curve created by Equation 1 varies with the rotational speed f. Therefore, the function formula A1 of Formula 1 is called, and the time when the actually measured value that changes with time by substituting the rotational speed f converges to a predetermined temperature difference ΔT is found.

Equation 3 shows the terms whose values have been determined by the above procedures by underlining. Equation 3 shows that the curve changes depending on the unknown number (rotation number) f.

  In step S15 and subsequent steps, in ΔT (t) of Equation 3, an attempt is made to obtain a more accurate approximate expression A2 by correcting ΔT1 and ΔT2 in consideration of the influence of the outside air temperature on the discharge temperature of the compressor. Is. That is, in step S15, the change in time of the stable discharge pipe surface temperatures Td21 and Td22 when the outside air temperature is changed to Tout2 and rotated at the rotation speed f1 and the rotation speed f2 is measured. In step S16, the measurement result of the rotation speed f = f1 is substituted into Equation 4, and in Step S17, the measurement result of the rotation speed f = f2 is substituted into Equation 5. Equations 4 and 5 are equations that take into account the rate of change due to the outside air temperature.

In step S18, ΔT1 and ΔT2 of Equation 4 and Equation 5 are substituted into Equation 1 to create Equation 6. For ΔT2 and ΔT1 expressed in bold, Formula 1 is created using Formula 4 obtained in Step S16 and Formula 5 obtained in Step S17. FIG. 7A shows a saturation curve having a correction width according to Equation 4 and Equation 5 at this time. That is, the saturation curve also changes depending on the outside air temperature.

  And it is determined whether it is a stable state using Formula 6. Specifically, in Formula 1 in which an arbitrary number of revolutions f and an outside air temperature Tout are substituted, a stable state is established when the time change rate of ΔT (t) becomes smaller than the threshold δ (FIG. 7B). reference). The threshold δ may be, for example, ± 0.1 ° C./min. ± 0.1 ° C./min is merely an example, and is not limited to this.

  As is apparent from the above description of the embodiment, the present invention is a refrigeration system in which a compressor, a condenser, a high-pressure side flow rate adjustment device, a receiver, a low-pressure side flow rate adjustment device, and an evaporator are sequentially connected by piping. A supercooling detection unit for detecting the supercooling characteristic value of the refrigeration apparatus, an overheating detection unit for detecting the superheating characteristic value of the refrigeration apparatus, and the detection results of the supercooling detection unit and the overheating detection unit as target values A control unit that adjusts the opening area of the high-pressure side flow rate adjustment device and the low-pressure side flow rate adjustment device so as to approach, a discharge temperature detection unit that detects a discharge temperature of the compressor, and a rotation number of the compressor A rotation speed detection unit that detects the outside air temperature, and an outside air temperature detection unit that detects the outside air temperature. The control unit controls the high-pressure side flow rate adjustment device and / or the low-pressure side flow rate adjustment device according to a change in the operating state of the refrigeration apparatus. Adjust the opening area of When the time change of the temperature difference between the discharge temperature of the compressor and the outside air temperature is within the predetermined value range, the adjustment operation of the opening area is waited, and the time change is within the predetermined value range. Then, it is determined that the refrigeration apparatus is stable, and the adjustment operation of the opening area of the flow rate adjustment apparatus is started.

  According to the above configuration, when adjusting the opening area of the high pressure side flow rate adjustment device and / or the low pressure side flow rate adjustment device according to the change in the operating state of the refrigeration apparatus, the temperature difference between the discharge temperature of the compressor and the outside air temperature The adjustment of the opening area is waited until the time change is within a predetermined value range, and when the time change is within the predetermined value range, it is determined that the refrigeration apparatus is stable, and the opening area is adjusted. Since the adjustment operation is started, it is possible to provide a refrigeration system apparatus having higher reliability than the conventional one.

  Further, the control unit sets and stores a function equation of a temperature difference between the compressor discharge temperature and the outside air temperature, using the compressor rotation speed, the compressor discharge temperature and the outside air temperature as parameters, and stores the function equation. The structure which uses and judges the stability of a freezing apparatus can be employ | adopted.

  According to the above configuration, the stability of the refrigeration apparatus is determined based on whether or not the time change of the temperature difference between the discharge temperature of the compressor and the outside air temperature falls within a predetermined value based on a function expression stored in advance. As in the prior art, it is not necessary to take a stable waiting time more than necessary, and the responsiveness can be improved.

  Further, in the refrigeration apparatus according to the present invention, the supercooling is performed by changing the flow area from the high pressure side flow control device, the receiver and the low pressure side flow control device, and the opening area of the flow path from the condenser outlet to the evaporator inlet. You may employ | adopt the structure with which the diaphragm | throttle device which changes a degree was connected in parallel.

  The present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the claims, and the technical means disclosed in different embodiments can be appropriately combined. Such embodiments are also included in the technical scope of the present invention.

DESCRIPTION OF SYMBOLS 1 Indoor unit 2 Outdoor unit 3 Refrigerant piping 4 Compressor 5 Four-way valve 6 Outdoor heat exchanger 7 Throttle device 8 Indoor heat exchanger 10 Refrigerant circuit 11 On-off valve 13 Flow rate adjustment part 14 Receiver 15 1st flow rate adjustment device 16 2nd Flow rate adjusting device 20 Control unit 22 to 27 Temperature sensor 30 Discharge temperature detection unit 31 Rotational speed detection unit 32 Outside air temperature detection unit

Claims (3)

Compressor, condenser, high-pressure side flow control device, receiver, low-pressure side flow control device, and evaporator are connected by piping in sequence, and supercooling detection that detects the supercooling characteristic value of the refrigeration device An overheat detection unit that detects an overheat characteristic value of the refrigeration apparatus, and the high pressure side flow rate adjustment device and the low pressure side flow rate adjustment device so that the detection results of the overcooling detection unit and the overheat detection unit are brought close to target values. And a controller for adjusting the opening area of
A discharge temperature detection unit for detecting the discharge temperature of the compressor, a rotation number detection unit for detecting the rotation number of the compressor, and an outside air temperature detection unit for detecting the outside air temperature;
In the control unit, when adjusting the opening area of the high pressure side flow rate adjustment device and / or the low pressure side flow rate adjustment device according to a change in the operating state of the refrigeration apparatus, the temperature difference between the discharge temperature of the compressor and the outside air temperature is adjusted. The adjustment of the opening area is waited until the time change falls within a predetermined value range, and when the time change falls within the predetermined value range, the refrigeration apparatus is determined to be stable, and the flow rate adjustment device The refrigeration system apparatus characterized by starting the adjustment operation of the opening area of the refrigeration system. The control unit sets and stores a function equation of a temperature difference between the compressor discharge temperature and the outside air temperature using the compressor rotation speed, the compressor discharge temperature and the outside air temperature as parameters, and uses this function equation. The refrigeration system apparatus according to claim 1, wherein stability of the refrigeration apparatus is determined. In the refrigeration apparatus, a flow rate adjustment unit including a high-pressure side flow rate adjustment device, a receiver, and a low-pressure side flow rate adjustment device, and a throttle that changes the degree of supercooling by changing the opening area of the flow path from the condenser outlet to the evaporator inlet. The refrigeration system apparatus according to claim 1 or 2, wherein the apparatus is connected in parallel.

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