JP2005090784A - Defrost adjusting device and controlling method, and heat pump type water heater - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To solve a problem in a freezing cycle device having two heat pump circuits in one freezing cycle device that the timings for starting the defrost in two heat pump circuits may come close depending upon an operating situation, and the performance can not be exercised when the defrosting operation is started. <P>SOLUTION: This freezing cycle device having two heat pump circuits in one freezing cycle device, comprises a defrost starting time difference determining part 17 for estimating the time when two evaporators start the defrost on the basis of an output temperature of each evaporator and outputting a signal to a main control part 8 in a case when the time difference becomes less than a set value. The main control part 8 gives the opposite commands (to increase operating frequency in compressor starting defrost earlier and to decrease operating frequency in compressor starting defrost later) to a first compressor control part 7 and a second compressor driving part 9 driving each compressor, on the basis of the signal, whereby the time difference in starting the defrost is enlarged and the possibility of simultaneous execution of defrost by two heat pump circuits can be reduced. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a defrosting control device, a control method, and a heat pump type hot water supply device, and more particularly to defrosting of a refrigeration cycle device having two heat pump circuits in one refrigeration cycle device.

  An explanation will be given by taking an air conditioner as an example of the prior art.

  Hereinafter, the conventional defrosting method will be described with reference to FIG. In the air conditioner, an outdoor heat exchanger provided in each of a plurality of outdoor units is connected to an indoor heat exchanger provided in one indoor unit, thereby forming a plurality of refrigerant circuits. There is something.

  Generally, when heating operation is continued, frost formation occurs in the outdoor heat exchanger. Since frost formation hinders heat exchange, defrosting operation is required to defrost the outdoor heat exchanger.

  However, if a plurality of outdoor units perform the defrosting operation at the same time, heating cannot be continued, so it is necessary to avoid the simultaneous defrosting operation.

Therefore, each of the first outdoor unit 100a and the second outdoor unit 100b is provided with a first defrost controller 101a and a second defrost controller 101b which are means for controlling defrosting, and a defrost signal is transmitted between these defrost control means. By giving and receiving, the 1st outdoor unit 100a and the 2nd outdoor unit 100b are not defrosted simultaneously (for example, refer patent document 1).
JP 2001-272083 A

  However, in the above-described conventional configuration, even if it is a situation where defrosting is necessary, when other outdoor units are performing defrosting, the current operation is forced and the ability cannot be sufficiently exhibited. A malfunction occurs.

  The present invention solves the conventional problem, relates to a refrigeration cycle apparatus having two heat pump circuits in one refrigeration cycle apparatus, estimates the time until the start of defrosting of each heat pump circuit, the difference is from the comparison value In the case of being short, the object is to provide a defrosting adjusting device and a control method for adjusting in advance the capacities of the respective heat pump circuits and preventing the defrosting operations from overlapping each other in advance.

According to a first aspect of the present invention, there is provided a first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, and a first fan for the first evaporator; A refrigeration cycle comprising two heat pump circuits, a second compressor, a second condenser, a second expansion valve, a second evaporator, and a second heat pump circuit comprising a second fan for the second evaporator In the apparatus, the first compressor control unit, the second compressor control unit, the first compressor control unit, and the first compressor that control the first compressor and the second compressor, respectively, according to a signal from a main control unit. (2) A main control unit that controls the compressor control unit and the entire control system, and estimates the time until the start of defrosting of each heat pump circuit, determines whether the difference is less than a set value, and determines the result as the main control unit And a defrosting start time difference determination unit that outputs to If the defrosting timings of two independent heat pump circuits are likely to overlap, increase the evaporator operating temperature by increasing the operating frequency of the compressor of the heat pump circuit that has the closest defrosting start timing. By lowering the capacity, the capacity is increased, and the start time of defrosting is further advanced. On the other hand, the capacity of the heat pump circuit is lowered by raising the evaporation temperature of the evaporator by lowering the operating frequency of the compressor, and the current temperature is lower Delay the start of defrosting.

  By providing this control means, it is possible to increase the time difference between the start of defrosting of both while keeping the capacity constant as a whole, and to prevent the defrosting operations of the two heat pump circuits from overlapping.

  According to a second aspect of the present invention, a first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, and a first fan for the first evaporator; A refrigeration cycle comprising two heat pump circuits, a second compressor, a second condenser, a second expansion valve, a second evaporator, and a second heat pump circuit comprising a second fan for the second evaporator In the apparatus, a first expansion valve control unit, a second expansion valve control unit, a first expansion valve control unit, and a first expansion control unit that control the first expansion valve and the second expansion valve, respectively, according to a signal from a main control unit. (2) A main control unit that controls the expansion valve control unit and the entire control system, and estimates the time until the start of defrosting of each heat pump circuit, determines whether the difference is less than a set value, and determines the result as the main control unit And a defrosting start time difference determination unit that outputs to If the defrosting timings of two independent heat pump circuits are likely to overlap, the evaporation of the evaporator can be reduced by reducing the opening degree of the expansion valve of the heat pump circuit that is closer to the defrosting start timing. Lowering the temperature further increases the capacity, and further accelerates the start of defrosting, while the heat pump circuit reduces the capacity by increasing the evaporation temperature of the evaporator by increasing the opening of the expansion valve. The defrost start time is delayed.

  By providing such control means, it is possible to increase the time difference between the start of defrosting of both while keeping the capacity constant as a whole, and to prevent the defrosting operations of the two heat pump circuits from overlapping. Have.

  According to a third aspect of the present invention, there is provided a first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, and a first fan for the first evaporator. A refrigeration cycle comprising two heat pump circuits, a second compressor, a second condenser, a second expansion valve, a second evaporator, and a second heat pump circuit comprising a second fan for the second evaporator In the apparatus, a first compressor control unit and a second compressor control unit that respectively control the first compressor and the second compressor by a signal from a main control unit, the first expansion valve, and the second expansion valve. A first expansion valve control unit, a second expansion valve control unit, a first compressor control unit, a second compressor control unit, a first expansion valve control unit, and a second expansion valve control for controlling the valves, respectively. Main control unit for controlling the control unit and the entire control system, and defrosting of each heat pump circuit A defrosting start time difference determining unit that estimates a time until start, determines whether the difference is equal to or less than a set value, and outputs the result to the main control unit. If the defrosting timing of the heat pump circuit is likely to overlap, the evaporator can be increased by increasing the operating frequency of the compressor of the heat pump circuit whose defrosting start time is closer or by reducing the opening of the expansion valve. By lowering the evaporation temperature, the capacity is increased, and the defrosting start time is further advanced. On the other hand, one of the heat pump circuits reduces the operating frequency of the compressor or increases the opening of the expansion valve. Raise the evaporation temperature to lower the capacity and delay the defrosting start time.

  By providing such control means, it is possible to increase the time difference between the start of defrosting of both while keeping the capacity constant as a whole, and to prevent the defrosting operations of the two heat pump circuits from overlapping. Have.

  According to a fourth aspect of the present invention, there is provided a first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, and a first fan for the first evaporator. A refrigeration cycle comprising two heat pump circuits, a second compressor, a second condenser, a second expansion valve, a second evaporator, and a second heat pump circuit comprising a second fan for the second evaporator In the apparatus, a first compressor control unit and a second compressor control unit for controlling the first compressor and the second compressor according to a signal from a main control unit, the first fan and the second fan, respectively. A first fan control unit, a second fan control unit, a first compressor control unit, a second compressor control unit, a first fan control unit, a second fan control unit, and an entire control system, which are respectively controlled. Main control unit to control the defrosting of each heat pump circuit A defrosting start time difference determining unit that estimates a time until start, determines whether the difference is equal to or less than a set value, and outputs the result to the main control unit. If the defrosting timing of the heat pump circuit is likely to overlap, evaporating the evaporator by increasing the operating frequency of the compressor of the heat pump circuit whose defrosting start time is closer, or decreasing the fan speed Lowering the temperature raises the capacity and further accelerates the start of defrosting. One heat pump circuit lowers the operating frequency of the compressor or raises the evaporation temperature of the evaporator by increasing the number of rotations of the fan. This lowers the capacity and delays the start of defrosting compared to the current situation.

  By providing such control means, it is possible to increase the time difference between the start of defrosting of both while keeping the capacity constant as a whole, and to prevent the defrosting operations of the two heat pump circuits from overlapping. Have.

  According to a fifth aspect of the present invention, there is provided a first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, and a first fan for the first evaporator. A refrigeration cycle comprising two heat pump circuits, a second compressor, a second condenser, a second expansion valve, a second evaporator, and a second heat pump circuit comprising a second fan for the second evaporator In the apparatus, a first expansion valve control unit and a second expansion valve control unit for controlling the first expansion valve and the second expansion valve, respectively, according to a signal from a main control unit, the first fan and the second fan A first fan control unit, a second fan control unit, a first expansion valve control unit, a second expansion valve control unit, a first fan control unit, a second fan control unit, and an entire control system, which are respectively controlled. Main control unit to control the defrosting of each heat pump circuit A defrosting start time difference determining unit that estimates a time until start, determines whether the difference is equal to or less than a set value, and outputs the result to the main control unit. When the defrosting timing of the heat pump circuit is likely to overlap, reduce the opening of the expansion valve of the heat pump circuit whose defrosting start time is closer, or reduce the fan speed to reduce the evaporator By lowering the evaporation temperature, the capacity is increased, and the defrosting start time is further advanced. On the other hand, the evaporation temperature of the evaporator can be increased by increasing the opening of the expansion valve or increasing the rotational speed of the fan. Raise the capacity to lower the capacity and delay the start of defrosting.

  By providing such control means, it is possible to increase the time difference between the start of defrosting of both while keeping the capacity constant as a whole, and to prevent the defrosting operations of the two heat pump circuits from overlapping. Have.

According to a sixth aspect of the present invention, there is provided a first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, and a first fan for the first evaporator. A refrigeration cycle comprising two heat pump circuits, a second compressor, a second condenser, a second expansion valve, a second evaporator, and a second heat pump circuit comprising a second fan for the second evaporator In the apparatus, a first compressor control unit and a second compressor control unit that respectively control the first compressor and the second compressor by a signal from a main control unit, the first expansion valve, and the second expansion valve. A first expansion valve control unit and a second expansion valve control unit for controlling the respective valves; a first fan control unit and a second fan control unit for controlling the first fan and the second fan; and the first compression unit. Machine controller, the second compressor controller, the first expansion valve controller, and the front Estimating the time until the start of defrosting of each heat pump circuit, the main control unit controlling the second expansion valve control unit, the first fan control unit, the second fan control unit and the entire control system, the difference is It is characterized by comprising a defrosting start time difference determining unit that determines whether or not a set value or less and outputs the result to the main control unit, and the timing of defrosting of two independent heat pump circuits is If they are likely to overlap, increase the operating frequency of the compressor of the heat pump circuit that is closer to the start of defrosting, reduce the opening of the expansion valve, or reduce the fan speed to reduce the evaporator Lowering the evaporating temperature increases the capacity and further accelerates the start of defrosting. One heat pump circuit lowers the operating frequency of the compressor, increases the opening of the expansion valve, or rotates the fan. Lower the more capable by increasing the evaporation temperature of the evaporator by increasing the number, delay the defrosting start time than the current.

  By providing such control means, it is possible to increase the time difference between the start of defrosting of both while keeping the capacity constant as a whole, and to prevent the defrosting operations of the two heat pump circuits from overlapping. Have.

  According to the seventh aspect of the present invention, the defrosting start time difference determining unit starts defrosting of the first heat pump circuit and the second heat pump circuit from the outlet temperatures of the first evaporator and the second evaporator. It is characterized in that the time until the time is estimated and the time difference is compared with a preset value, and a special additional cost, etc. is used because a detector or the like provided in a conventional heat pump circuit is used. Has the effect of not occurring.

  The invention according to claim 8 of the present invention is characterized in that the defrosting start time difference determination unit includes an external input unit that allows a comparison value with the estimated time to be input from the outside. The defrosting interval can be adjusted in the field according to the environment.

  According to a ninth aspect of the present invention, a first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, and a first fan for the first evaporator, A refrigeration cycle comprising two heat pump circuits, a second compressor, a second condenser, a second expansion valve, a second evaporator, and a second heat pump circuit comprising a second fan for the second evaporator In the apparatus, the first compressor control unit, the second compressor control unit, the first compressor control unit, and the first compressor that control the first compressor and the second compressor, respectively, according to a signal from a main control unit. (2) A main control unit that controls the compressor control unit and the entire control system, and estimates the time until the start of defrosting of each heat pump circuit, determines whether the difference is less than a set value, and determines the result as the main control unit The defrosting control device provided with the defrosting start time difference judgment part which outputs to In the control method, when the defrosting timings of two independent heat pump circuits are likely to overlap, the operation frequency of both compressors is controlled, and the defrosting of two independent heat pump circuits If it is likely to overlap, the capacity of the compressor of the heat pump circuit that is closer to the start of defrosting will be increased to lower the evaporation temperature of the evaporator, thereby increasing the capacity and further starting of defrosting. Advance the timing, one heat pump circuit lowers the capacity by raising the evaporation temperature of the evaporator by lowering the operating frequency of the compressor, and delays the defrosting start time than the current situation.

  By controlling in this way, it is possible to increase the time difference between the start of defrosting of both while keeping the capacity constant as a whole, and to prevent the defrosting operations of the two heat pump circuits from overlapping.

According to a tenth aspect of the present invention, there is provided a first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, and a first fan for the first evaporator; A refrigeration cycle comprising two heat pump circuits, a second compressor, a second condenser, a second expansion valve, a second evaporator, and a second heat pump circuit comprising a second fan for the second evaporator In the apparatus, a first expansion valve control unit, a second expansion valve control unit, a first expansion valve control unit, and a first expansion control unit that control the first expansion valve and the second expansion valve, respectively, according to a signal from a main control unit. (2) A main control unit that controls the expansion valve control unit and the entire control system, and estimates the time until the start of defrosting of each heat pump circuit, determines whether the difference is less than a set value, and determines the result as the main control unit Defrosting adjustment device provided with a defrosting start time difference determination unit that outputs to In this control method, when the defrosting timings of two independent heat pump circuits are likely to overlap, the opening degree of both expansion valves is controlled. If the frost implementation time is likely to overlap, the capacity of the expansion valve of the heat pump circuit circuit whose defrost start time is closer is reduced by lowering the evaporation temperature of the evaporator to further increase the capacity. The frost start time is advanced, and one heat pump circuit lowers the capacity by increasing the evaporation temperature of the evaporator by increasing the opening of the expansion valve, and delays the defrost start time from the current state.

  By controlling in this way, it is possible to increase the time difference between the start of defrosting of both while keeping the capacity constant as a whole, and to prevent the defrosting operations of the two heat pump circuits from overlapping.

  According to an eleventh aspect of the present invention, there is provided a first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, and a first fan for the first evaporator. A refrigeration cycle comprising two heat pump circuits, a second compressor, a second condenser, a second expansion valve, a second evaporator, and a second heat pump circuit comprising a second fan for the second evaporator In the apparatus, a first compressor control unit and a second compressor control unit that respectively control the first compressor and the second compressor by a signal from a main control unit, the first expansion valve, and the second expansion valve. A first expansion valve control unit, a second expansion valve control unit, a first compressor control unit, a second compressor control unit, a first expansion valve control unit, and a second expansion valve control unit that respectively control the valves; And the main control unit that controls the entire control system, and the defrosting of each heat pump circuit In the control method of the defrosting control device comprising the defrosting start time difference determining unit that estimates the time until the difference is less than a set value and outputs the result to the main control unit, two independent It is characterized by controlling the operating frequency of both compressors and the opening of the expansion valve when the timing of defrosting of the heat pump circuit is likely to overlap, and performing defrosting of two independent heat pump circuits If the timing seems to overlap, increase the operating frequency of the compressor of the heat pump circuit that is closer to the start of defrosting, or decrease the evaporation temperature of the evaporator by reducing the opening of the expansion valve. Increase the capacity, further advance the start of defrosting, one heat pump circuit to increase the evaporation temperature of the evaporator by lowering the operating frequency of the compressor or increasing the opening of the expansion valve Lower the more capable, than the current delay the defrost start time.

  By controlling in this way, it is possible to increase the time difference between the start of defrosting of both while keeping the capacity constant as a whole, and to prevent the defrosting operations of the two heat pump circuits from overlapping.

According to a twelfth aspect of the present invention, there is provided a first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, and a first fan for the first evaporator. A refrigeration cycle comprising two heat pump circuits, a second compressor, a second condenser, a second expansion valve, a second evaporator, and a second heat pump circuit comprising a second fan for the second evaporator In the apparatus, a first compressor control unit and a second compressor control unit for controlling the first compressor and the second compressor according to a signal from a main control unit, the first fan and the second fan, respectively. A first fan control unit, a second fan control unit, a first compressor control unit, a second compressor control unit, a first fan control unit, a second fan control unit, and an entire control system, which are respectively controlled. The main control unit that controls the In the control method of the defrosting control device comprising the defrosting start time difference determining unit that estimates the time until the start, determines whether the difference is equal to or less than a set value, and outputs the result to the main control unit, When the defrosting timings of the heat pump circuits are likely to overlap, the operation frequency of both compressors and the rotation speed of the fans are controlled, and the defrosting of two independent heat pump circuits is performed. If the timing is likely to overlap, increase the operating frequency of the compressor of the heat pump circuit that is closer to the start of defrosting, or lower the evaporation temperature of the evaporator by lowering the rotation speed of the fan to increase the capacity. One heat pump circuit can increase the evaporation temperature of the evaporator by lowering the operating frequency of the compressor or increasing the rotational speed of the fan. In lowering the more capable, than the current delay the defrost start time.

  By controlling in this way, it is possible to increase the time difference between the start of defrosting of both while keeping the capacity constant as a whole, and to prevent the defrosting operations of the two heat pump circuits from overlapping.

  According to a thirteenth aspect of the present invention, there is provided a first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, and a first fan for the first evaporator; A refrigeration cycle comprising two heat pump circuits, a second compressor, a second condenser, a second expansion valve, a second evaporator, and a second heat pump circuit comprising a second fan for the second evaporator In the apparatus, a first expansion valve control unit and a second expansion valve control unit for controlling the first expansion valve and the second expansion valve, respectively, according to a signal from a main control unit, the first fan and the second fan A first fan control unit, a second fan control unit, a first expansion valve control unit, a second expansion valve control unit, a first fan control unit, a second fan control unit, and an entire control system, which are respectively controlled. The main control unit that controls the In the control method of the defrosting control device comprising the defrosting start time difference determining unit that estimates the time until the start, determines whether the difference is equal to or less than a set value, and outputs the result to the main control unit, When the defrosting timing of the heat pump circuit is likely to overlap, the opening degree of both expansion valves and the rotation speed of the fan are controlled, and the defrosting of two independent heat pump circuits is performed. If the timing seems to overlap, reduce the evaporation temperature of the evaporator by lowering the opening of the expansion valve of the heat pump circuit that is closer to the start of defrosting, or lowering the rotation speed of the fan to increase the capacity. The heat pump circuit is more efficient by increasing the evaporation temperature of the evaporator by increasing the opening of the expansion valve or increasing the rotational speed of the fan. The lowering, delay the defrost start time than the present situation.

  By controlling in this way, it is possible to increase the time difference between the start of defrosting of both while keeping the capacity constant as a whole, and to prevent the defrosting operations of the two heat pump circuits from overlapping.

According to a fourteenth aspect of the present invention, there is provided a first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, and a first fan for the first evaporator. A refrigeration cycle comprising two heat pump circuits, a second compressor, a second condenser, a second expansion valve, a second evaporator, and a second heat pump circuit comprising a second fan for the second evaporator In the apparatus, a first compressor control unit and a second compressor control unit that respectively control the first compressor and the second compressor by a signal from a main control unit, the first expansion valve, and the second expansion valve. A first expansion valve control unit and a second expansion valve control unit for controlling the respective valves; a first fan control unit and a second fan control unit for controlling the first fan and the second fan; and the first compression unit. A machine control unit, the second compressor control unit, and the first expansion valve control unit, The second expansion valve control unit, the first fan control unit, the second fan control unit, and the main control unit that controls the entire control system, and the time until the defrosting start of each heat pump circuit is estimated and the difference In the control method of the defrosting control device comprising the defrosting start time difference determination unit that determines whether or not the value is equal to or less than a set value and outputs the result to the main control unit, the defrosting timing of two independent heat pump circuits Is characterized by controlling the operating frequency of both compressors, the opening of the expansion valve, and the rotational speed of the fan, and the timing of defrosting of the two independent heat pump circuits overlaps. If so, increase the operating frequency of the compressor of the heat pump circuit that is closer to the start of defrosting, or reduce the opening of the expansion valve,
Alternatively, by lowering the rotation speed of the fan to lower the evaporation temperature of the evaporator, the capacity is further increased, and the defrosting start timing is further advanced, while one heat pump circuit lowers the operating frequency of the compressor or expands By increasing the opening degree of the valve or increasing the rotation speed of the fan to raise the evaporation temperature of the evaporator, the capacity is further lowered, and the defrosting start timing is delayed from the current state.

  By controlling in this way, it is possible to increase the time difference between the start of defrosting of both while keeping the capacity constant as a whole, and to prevent the defrosting operations of the two heat pump circuits from overlapping.

  The invention according to claim 15 of the present invention is applied to a heat pump type hot water supply apparatus having a small hot water storage tank that performs hot water supply only by hot water generated by a heat pump, particularly during hot water supply, so that defrosting operation can be performed during hot water supply. By entering, it has the effect of minimizing the situation that affects the hot water supply temperature or amount.

  As described above, the invention according to claim 1 is provided with a control unit that detects a case where the defrosting timings of two independent heat pump circuits are likely to overlap and controls the frequency of the compressor. As a whole, the time difference between the start of both defrosting can be expanded while keeping the capacity constant, and the defrosting operations of two independent heat pump circuits can be prevented from overlapping.

  Further, the invention according to claim 2 is provided with a control means for detecting a case where defrosting timings of two independent heat pump circuits are likely to overlap and controlling the expansion valve. While keeping constant, the time difference of both defrosting start can be expanded, and it can prevent that the defrosting operation | movement of two independent heat pump circuits overlaps.

  In addition, with this configuration, the effect can be obtained even in a device having a constant compressor speed.

  Further, the invention according to claim 3 is provided with a control means for detecting a case where defrosting timings of two independent heat pump circuits are likely to overlap and controlling the compressor and the expansion valve. While the capacity is kept constant, the time difference between the start of both defrosting can be expanded, and the defrosting operations of two independent heat pump circuits can be prevented from overlapping.

  In addition, with this configuration, even if it is difficult to adjust the capacity with the compressor, the capacity adjustment with the expansion valve makes it possible to achieve the effect under a wider range of conditions than when adjusting the capacity with either one. Can be obtained.

  In addition, the invention according to claim 4 is provided with a control means for detecting a case where the defrosting timings of the two independent heat pump circuits are likely to overlap, and controlling the compressor and the fan, so that the capacity as a whole is improved. The time difference between the start of defrosting can be expanded while keeping the constant, so that the defrosting operations of two independent heat pump circuits can be prevented from overlapping.

  In addition, with this configuration, even when it is difficult to adjust the capacity with the compressor, the capacity is adjusted with a fan, so that the effect can be obtained under a wider range of conditions than when the capacity is adjusted with any one of them. be able to.

  Further, the invention according to claim 5 detects the case where the timings of defrosting of two independent heat pump circuits are likely to overlap, and by providing a control means for controlling the expansion valve and the fan, the capacity as a whole is improved. The time difference between the start of defrosting can be expanded while keeping the constant, so that the defrosting operations of two independent heat pump circuits can be prevented from overlapping.

  In addition, with this configuration, even when it is difficult to adjust the capacity with the fan, the capacity is adjusted with the expansion valve. be able to.

  Further, the invention according to claim 6 is provided with a control means for detecting a case where defrosting timings of two independent heat pump circuits are likely to overlap, and for controlling the compressor, the expansion valve, and the fan. As a result, it is possible to increase the time difference between the start of defrosting of both while keeping the capacity constant, and it is possible to prevent the defrosting operations of two independent heat pump circuits from overlapping.

  In addition, with this configuration, capacity adjustment can be performed by the compressor, the expansion valve, and the fan, and effects can be obtained under a wider range of conditions.

  In the invention according to claim 7 of the present invention, the defrosting start time difference determination unit performs defrosting of the first heat pump circuit and the second heat pump circuit from the outlet temperatures of the first evaporator and the second evaporator. Since the time until the start is estimated, a detector or the like provided in the conventional heat pump circuit is used, so that it can be realized without any special additional cost.

  In addition, the invention according to claim 8 of the present invention enables the input of the comparison value of the defrosting start time difference determination unit from the outside, so that an appropriate defrosting interval adjustment can be performed according to the installed environment. it can.

  According to the ninth aspect of the invention, the defrosting start time difference determination unit detects a case where the defrosting timings of two independent heat pump circuits are likely to overlap, and controls the operating frequency of the compressor according to the result. As a result, the time difference between the start of defrosting can be increased while keeping the capacity constant as a whole, and the defrosting operations of two independent heat pump circuits can be prevented from overlapping.

  Further, the invention according to claim 10 detects the case where the defrosting timings of two independent heat pump circuits are likely to overlap by the defrosting start time difference determination unit, and controls the opening degree of the expansion valve according to the result. As a result, the time difference between the start of defrosting can be increased while keeping the capacity constant as a whole, and the defrosting operations of two independent heat pump circuits can be prevented from overlapping. In addition, by performing this control, an effect can be obtained even in a device having a constant compressor speed.

  According to the eleventh aspect of the present invention, the defrosting start time difference determination unit detects a case where the defrosting timings of two independent heat pump circuits are likely to overlap, and the operation frequency of the compressor and the expansion valve are determined according to the result. Since the opening degree is controlled as a whole, the time difference between the start of defrosting can be increased while keeping the capacity constant as a whole, and the defrosting operations of the two heat pump circuits can be prevented from overlapping. In addition, by performing this control, even if it is difficult to adjust the capacity with the compressor, adjusting the capacity with the expansion valve, the effect can be achieved over a wider range of conditions than when adjusting the capacity with either one. Can be obtained.

  The invention according to claim 12 detects a case where the defrosting timings of two independent heat pump circuits are likely to overlap, and controls the operating frequency of the compressor and the rotational speed of the fan. While the capacity is kept constant, the time difference between the start of the defrosting of both can be expanded, and the defrosting operations of the two heat pump circuits can be prevented from overlapping. In addition, by performing this control, even when it is difficult to adjust the capacity with the compressor, the capacity is adjusted with a fan, so that the effect can be obtained under a wider range of conditions than when the capacity is adjusted with any one of them. be able to.

  Further, the invention according to claim 13 detects the case where the defrosting timings of two independent heat pump circuits are likely to overlap, and controls the opening degree of the expansion valve and the rotational speed of the fan. While the capacity is kept constant, the time difference between the start of both defrosting can be expanded, and the defrosting operations of two independent heat pump circuits can be prevented from overlapping. In addition, by performing this control, even when it is difficult to adjust the capacity with the fan, the capacity is adjusted with the expansion valve. be able to.

  The invention according to claim 14 detects a case where the timing of defrosting of two independent heat pump circuits is likely to overlap, and controls the operating frequency of the compressor, the opening degree of the expansion valve, and the rotational speed of the fan. As a result, the time difference between the start of defrosting can be increased while keeping the capacity constant as a whole, and the defrosting operations of two independent heat pump circuits can be prevented from overlapping. In addition, by performing this control, capacity adjustment by the compressor, expansion valve and fan can be performed, and the effect can be obtained under a wider range of conditions.

  Further, the invention according to claim 15 is a heat pump water heater equipped with a small hot water storage tank and constituted by two heat pump circuits and one hot water supply circuit, and when both heat pump circuits enter defrosting during hot water supply. If there is an overlap, it is detected that the defrosting timing of two independent refrigeration cycles is likely to overlap for the problem that hot water supply cannot be performed or the hot water supply capacity is greatly reduced, and a compressor or expansion valve or fan is detected. By providing a single and combined configuration of control means for controlling the defrosting operation, the time difference between the start of defrosting of both can be expanded while keeping the capacity constant as a whole, and the defrosting operation of two independent heat pump circuits Can be prevented from overlapping.

  Embodiments of the present invention will be described below with reference to the drawings. In addition, about the same structure as the past, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted.

(Embodiment 1)
FIG. 1 is a schematic diagram showing the configuration of a heat pump circuit and control elements according to Embodiment 1 of the present invention.

  FIG. 2 is a flowchart showing the processing contents of the defrosting start time difference determination unit 17.

  FIG. 3 is a flowchart showing the processing contents of the temperature difference expansion control, which is a partial function of the main control unit 8.

  The basic movement of the heat pump cycle will be described with reference to the first heat pump circuit 18 of FIG.

  The first heat pump circuit 18 includes a first compressor 1, a first condenser 2, a first expansion valve 3, and a first evaporator 4 that are sequentially arranged in a ring shape with a refrigerant tank. Said 1st compressor 1 is an inverter drive type compressor. The first compressor 1 compresses the refrigerant, and the first condenser 2 warms the target with the heat of the refrigerant discharged from the first compressor 1. The first expansion valve 3 depressurizes the refrigerant that has exchanged heat with the first condenser 2.

  The first evaporator 4 absorbs heat from the outside air into the refrigerant from the first expansion valve. Then, the refrigerant returns to the first compressor 1.

The above is the outline of the operation of the first heat pump circuit 18. The operation of the second heat pump circuit 19 is the same as that of the first heat pump circuit 18.

  When the cycle described above is repeated, frost accumulates in the first evaporator 4 or the second evaporator 13, and thus a defrosting operation is required. In an example of the start condition of the defrosting operation of the present embodiment, for the first heat pump circuit 18, the main control unit 8 detects the outlet temperature of the first evaporator 4 with the first temperature sensor 6, and this temperature is When the temperature falls below a preset temperature, it is determined that defrosting is necessary, and a defrosting operation is executed.

  When this defrosting start determination is performed without relation between the first heat pump circuit 18 and the second heat pump circuit 19, defrosting may occur at the same time and the desired capacity may not be obtained. Control for eliminating this problem will be described below. Below, an example of the processing content of the defrosting start time difference determination part 17 is demonstrated using the flowchart of FIG.

  Here, the defrosting start time difference determination part 17 is implemented by a certain set period (for example, every minute).

  First, in step 1, the outlet temperature (t10) of the first evaporator 4 is detected by the first temperature sensor 6, and the process proceeds to step 2. In step 2, the temperature change rate is calculated according to (Equation 1) from the currently detected outlet temperature (t10) and the previously detected outlet temperature (t11), and the process proceeds to step 3.

Δt1 = t10−t11 (1)
In step 3, the sign of the temperature gradient (Δt1) obtained in step 2 is determined. If the temperature gradient is positive, the process is terminated because the outlet temperature is increasing. On the other hand, when the temperature gradient (Δt1) is negative, the process proceeds to step 4 because the outlet temperature is decreasing. In step 4, the time (t1) to reach a preset determination value (Tset) from the temperature gradient (Δt1) obtained in step 2 and the current first evaporator 4 outlet temperature (t10) is expressed by (Expression 2). ) And go to Step 5.

t1 = (Tset−t10) / Δt1 (2)
In step 5, the current outlet temperature (t10) is stored in the previous outlet temperature (t11) of the first evaporator 4, and the process proceeds to step 6 in preparation for the next calculation. In Step 6, the outlet temperature (t20) of the second evaporator 13 is detected by the second temperature sensor 15, and the process proceeds to Step 7. In step 7, a temperature gradient is calculated according to (Equation 3) from the outlet temperature (t20) detected this time and the outlet temperature (t21) detected last time, and the process proceeds to step 8.

Δt2 = t20−t21 (3)
In step 8, the sign of the temperature gradient (Δt2) obtained in step 7 is determined. If the temperature gradient (Δt2) is positive, the process is terminated because the outlet temperature is increasing. On the other hand, when the temperature change rate (Δt2) is negative, the process proceeds to step 9 because the outlet temperature is decreasing. In step 9, the time (t2) to reach a preset judgment value (Tset) from the temperature gradient (Δt2) obtained in step 7 and the current outlet temperature (t20) of the second evaporator 14 is expressed by Calculate according to 4) and go to Step 10.

t2 = (Tset−t20) / Δt2 (4)
In step 10, the current outlet temperature (t20) of the second evaporator is stored in the previous outlet temperature (t21) of the second evaporator, and the process proceeds to step 11 in preparation for the next calculation. In step 11, the absolute value (Δt) of the difference between the time t1 until the start of defrosting of the first evaporator 4 obtained in step 4 and the time t2 until the start of defrosting of the second evaporator 13 obtained in step 9 is obtained. Go to step 12. In Step 12, the time difference (Tover) set in advance is compared with the defrosting start time difference (Δt) obtained in Step 11, and when the defrosting start time difference (Δt) is smaller than the set time difference (Tover), Step 13 is performed. If the defrosting start time difference (Δt) is greater than or equal to the set time difference (Tover), the process proceeds to step 14. In step 13, the main control unit 8 is requested to determine the evaporator identification information and the temperature difference expansion control that are near the start of defrosting, and the process is terminated. On the other hand, in step 14, the main control unit 8 is requested to stop the temperature difference expansion control, and the process is terminated.

  Next, the operation of the main control unit 8 when a request for either temperature difference expansion control or temperature difference expansion control stop is received from the defrosting start time difference determination unit 17 will be described with reference to the flowchart of FIG.

  The temperature difference expansion control in the main control unit 8 is performed at a certain set cycle (for example, every minute).

  In step 1, when the temperature difference expansion control is requested from the defrosting start time difference determination unit 17, the process proceeds to step 2, and when the temperature difference expansion control stop is requested, the process is terminated. In Step 2, when the start of defrosting of the first evaporator 4 is near according to the evaporator discrimination information from the defrosting start time difference determination unit 17, the process proceeds to Step 3, and when the start of defrosting of the second evaporator 13 is near Advances to step 7. In step 3, it is determined whether or not the operating frequency of the first compressor 1 can be increased. If it is possible, the process proceeds to step 4, and if it is not possible, the process is terminated. In step 4, it is determined whether or not the operating frequency of the second compressor 10 can be lowered. If it is possible, the process proceeds to step 5, and if it is not possible, the process is terminated. In step 5, the first compressor controller 7 is instructed to increase the operating frequency by a preset frequency, and the process proceeds to step 6. In step 6, the second compressor control unit 9 is instructed to lower the operating frequency by a preset frequency, and the process is terminated. On the other hand, in Step 7, it is determined whether or not the operating frequency of the second compressor 10 can be increased. If it is possible, the process proceeds to Step 8, and if it is not possible, the process is terminated. In Step 8, it is determined whether or not the operating frequency of the first compressor 1 can be lowered. If it is possible, the process proceeds to Step 9, and if it is not possible, the process is terminated. In step 9, the second compressor controller 9 is instructed to increase the operating frequency by a preset frequency, and the process proceeds to step 10. In step 10, the first compressor controller 7 is instructed to lower the operating frequency by a preset frequency, and the process is terminated.

  By issuing a frequency change command to the first compressor control unit 7 and the second compressor control unit 9 as described above, the evaporator with a near defrost start time increases the frosting speed by increasing the capacity, The defrosting start time becomes faster, while the ability of the evaporator with slow defrosting start time decreases, so that the speed of frost formation slows down and the defrosting start time becomes slower. The difference in the defrosting start time of the vessel will increase.

  According to the above embodiment, the time difference between the start of defrosting of both can be expanded while keeping the capacity constant as a whole, and as a result, both heat pumps may not have the ability of defrosting. Can be lowered.

(Embodiment 2)
FIG. 4 is a schematic diagram showing the configuration of a heat pump circuit and control elements according to Embodiment 2 of the present invention.

  FIG. 5 is a flowchart showing the processing contents of the temperature difference expansion control which is a partial function of the main control unit 40.

  Since the operation outline of the entire heat pump circuit and the processing contents of the defrosting start time difference determination unit 17 are the same as those described in the first embodiment, the description thereof will be omitted.

  However, the first expansion valve and the second expansion valve in the present embodiment are electric expansion valves and can be arbitrarily throttled.

  The operation of the main control unit 40 when receiving a request for either temperature difference expansion control or temperature difference expansion control stop from the defrosting start time difference determination unit 17 will be described with reference to the flowchart of FIG.

  The temperature difference expansion control in the main control unit 40 is performed at a certain set cycle (for example, every minute).

  In step 1, when temperature difference expansion control is requested from the defrosting start time difference determination unit 17, the process proceeds to step 2, and when stop of temperature difference expansion control is requested, the process ends. In Step 2, when the start of defrosting of the first evaporator 4 is near according to the evaporator discrimination information from the defrosting start time difference determination unit 17, the process proceeds to Step 3, and when the start of defrosting of the second evaporator 13 is near Advances to step 7. In step 3, it is determined whether or not the opening degree of the first expansion valve 3 can be reduced. If it is possible, the process proceeds to step 4, and if it is impossible, the process is terminated. In Step 4, it is determined whether or not the opening degree of the second expansion valve 12 can be increased. If it is possible, the process proceeds to Step 5, and if it is not possible, the process is terminated. In step 5, the first pressure expansion valve control unit 20 is instructed to decrease the expansion valve opening by a predetermined opening, and the process proceeds to step 6. In step 6, the second pressure expansion valve control unit 21 is instructed to increase the expansion valve opening by a predetermined opening, and the process is terminated. On the other hand, in step 7, it is determined whether or not the opening of the second expansion valve 12 can be reduced. If it is possible, the process proceeds to step 8, and if not, the process is terminated. In Step 8, it is determined whether or not the opening of the first expansion valve 3 can be increased. If it is possible, the process proceeds to Step 9, and if it is not possible, the process is terminated. In step 9, the second expansion valve control unit 21 is instructed to lower the expansion valve opening by a preset opening, and the process proceeds to step 10. In step 10, the first expansion valve control unit 20 is instructed to increase the expansion valve opening by a predetermined opening, and the process is terminated.

  As described above, by issuing an expansion valve opening degree change command to the first expansion valve control unit 20 and the second expansion valve control unit 21, the evaporator having a near defrosting start time increases the capacity, thereby increasing the frosting speed. The defrosting start time becomes faster, while the ability of the evaporator with the slower defrosting start time decreases, so that the speed of frosting slows down and the defrosting start time becomes slower. The difference between the defrosting start times of both evaporators will increase.

  According to the above embodiment, the time difference between the start of defrosting can be expanded while keeping the capacity constant as a whole, and as a result, both the heat pump circuits are in a state where the capacity is not defrosting. The possibility can be reduced, and in the case of the present embodiment, the present invention can be applied even when the compressor constituting the heat pump circuit is at a constant speed.

(Embodiment 3)
FIG. 6 is a schematic diagram showing the configuration of a heat pump circuit and control elements according to Embodiment 3 of the present invention.

  FIG. 7 is a flowchart showing the processing contents of the temperature difference expansion control, which is a partial function of the main control unit 41.

  Since the operation outline of the entire heat pump circuit and the processing contents of the defrosting start time difference determination unit 17 are the same as those described in the first embodiment, the description thereof will be omitted.

However, the first fan and the second fan in the present embodiment are of a type that can vary the rotational speed.

The operation of the main control unit 41 when receiving a request for either temperature difference expansion control or temperature difference expansion control stop from the defrosting start time difference determination unit 17 will be described with reference to the flowchart of FIG.
The temperature difference expansion control in the main control unit 41 is performed at a certain set cycle (for example, every minute).

  In step 1, when the temperature difference expansion control is requested from the defrosting start time difference determination unit 17, the process proceeds to step 2, and when the temperature difference expansion control stop is requested, the process is terminated.

  In Step 2, when the start of defrosting of the first evaporator 4 is near according to the evaporator discrimination information from the defrosting start time difference determination unit 17, the process proceeds to Step 3, and when the start of defrosting of the second evaporator 13 is near Advances to step 7.

  In step 3, it is determined whether or not the number of rotations of the first fan can be decreased. If it is possible, the process proceeds to step 4;

  In step 4, it is determined whether or not the rotation speed of the second fan can be increased. If it is possible, the process proceeds to step 5;

  In step 5, the first fan control unit 22 is instructed to decrease the fan rotational speed by a preset rotational speed, and the process proceeds to step 6.

  In step 6, the second fan control control unit 23 is instructed to increase the fan rotational speed by a preset rotational speed, and the process ends.

  On the other hand, in step 7, it is determined whether or not it is possible to reduce the rotation speed of the second fan. If it is possible, the process proceeds to step 8;

  In step 8, it is determined whether or not it is possible to increase the rotation speed of the first fan. If it is possible, the process proceeds to step 9;

  In step 9, the second fan control unit 23 is instructed to decrease the fan rotational speed by a preset rotational speed, and the process proceeds to step 10.

  In step 10, the first fan control unit 22 is instructed to increase the fan rotational speed by a preset rotational speed, and the process ends.

  As described above, by issuing a fan rotation speed change command to the first fan control unit 22 and the second fan control unit 23, the evaporator having a near defrosting start time increases in frosting speed due to an increase in capacity. The defrosting start time becomes faster, while the ability of the evaporator with slow defrosting start time decreases, so that the speed of frost formation slows down and the defrosting start time becomes slower. The difference in the defrosting start time of the vessel will increase.

  According to the above embodiment, the time difference between the start of defrosting can be expanded while keeping the capacity constant as a whole, and as a result, both the heat pump circuits are in a state where the capacity is not defrosting. The possibility can be lowered, and in the case of the present embodiment, the present invention can be applied even when the compressor constituting the heat pump circuit is at a constant speed and the expansion valve is fixed.

(Embodiment 4)
FIG. 8 is a schematic diagram showing the configuration of a heat pump circuit and control elements according to Embodiment 4 of the present invention.

  FIG. 9 is a flowchart showing the processing contents of the temperature difference expansion control, which is a partial function of the main control unit 42.

  Since the operation outline of the entire heat pump circuit and the processing contents of the defrosting start time difference determination unit 17 are the same as those described in the first embodiment, the description thereof will be omitted.

  However, the first compressor and the second compressor in the present embodiment are of a variable speed type. Further, the first expansion valve and the second expansion valve are electric expansion valves that can be set with arbitrary throttles.

The operation of the main control unit 42 when a request for either temperature difference expansion control or temperature difference expansion control stop is received from the defrosting start time difference determination unit 17 will be described with reference to the flowchart of FIG.
The temperature difference expansion control in the main control unit 42 is performed at a certain set cycle (for example, every minute).

  In step 1, when the temperature difference expansion control is requested from the defrosting start time difference determination unit 17, the process proceeds to step 2, and when the temperature difference expansion control stop is requested, the process is terminated.

  In Step 2, when the start of defrosting of the first evaporator 4 is near according to the evaporator discrimination information from the defrosting start time difference determination unit 17, the process proceeds to Step 3, and when the start of defrosting of the second evaporator 13 is near Advances to step 12.

  In step 3, it is determined whether or not the operating frequency of the first compressor 1 can be increased. If it is possible to increase the operating frequency, the process proceeds to step 4; otherwise, the process proceeds to step 5.

  In step 4, the first compressor controller 7 is instructed to increase the operating frequency by a preset frequency, and the process proceeds to step 7.

  On the other hand, in step 5, it is determined whether or not the opening of the expansion valve of the first expansion valve 3 can be reduced. If it is possible to reduce the opening degree of the expansion valve, the process proceeds to step 6; otherwise, the process is terminated.

  In step 6, the first expansion valve control unit 20 is instructed to decrease the expansion valve opening by a predetermined opening, and the process proceeds to step 7.

  In step 7, it is determined whether or not the operating frequency of the second compressor 10 can be lowered. If the operating frequency can be lowered, the process proceeds to step 8, and if not possible, the process proceeds to step 9.

  In step 8, the second compressor control unit 9 is instructed to lower the operating frequency by a preset frequency, and the process is terminated.

  On the other hand, in step 9, it is determined whether or not the opening of the second expansion valve can be increased. If it is possible to increase the opening of the expansion valve, the process proceeds to step 10, and if not, the process proceeds to step 11.

In step 10, the second expansion valve control unit 21 is instructed to increase the expansion valve opening by a preset opening, and the process is terminated.

  On the other hand, in step 11, the instruction to increase the operating frequency for the first compressor control unit 7 instructed in step 4 or the instruction to decrease the opening of the expansion valve to the first expansion valve control unit 20 instructed in step 6 is canceled. To finish.

  Next, the case where it is determined in step 2 that the start of defrosting of the second evaporator is near will be described.

  In step 12, it is determined whether the operating frequency of the second compressor 10 can be increased. If it is possible to increase the operating frequency, the process proceeds to step 13; otherwise, the process proceeds to step 14.

  In step 13, the second compressor control unit 9 is instructed to increase the operating frequency by a preset frequency, and the process proceeds to step 16.

  On the other hand, in step 14, it is determined whether or not the opening of the expansion valve of the second expansion valve 12 can be reduced. If it is possible to reduce the opening of the expansion valve, the process proceeds to step 15; otherwise, the process is terminated.

  In step 15, the second expansion valve control unit 21 is instructed to reduce the expansion valve opening by a predetermined opening, and the process proceeds to step 16.

  In step 16, it is determined whether or not the operating frequency of the first compressor 1 can be lowered. If it is possible to lower the operating frequency, the process proceeds to step 17; otherwise, the process proceeds to step 18.

  In step 17, the first compressor controller 7 is instructed to lower the operating frequency by a preset frequency, and the process is terminated.

  On the other hand, in step 18, it is determined whether or not the opening of the first expansion valve can be increased. If it is possible to increase the opening of the expansion valve, the process proceeds to step 19; otherwise, the process proceeds to step 20.

  In step 19, the first expansion valve control unit 20 is instructed to increase the expansion valve opening by a preset opening, and the process ends.

  On the other hand, in step 20, the instruction to increase the operating frequency for the second compressor control unit 9 instructed in step 13 or the instruction to decrease the opening of the expansion valve to the second tension valve control unit 21 instructed in step 15 is canceled. To finish.

  As described above, according to the output of the defrosting start time difference determination unit 17, the main control unit 42 causes the first compressor control unit 7, the second compressor control unit 9, the first expansion valve control unit 20, and the second expansion valve control unit 21. By issuing an operation change command to the evaporator, the evaporator with a short defrosting start time will increase the speed of frosting as the capacity increases, and the defrosting start time will become faster, while the evaporator with a slow defrosting start time will Since the speed of frosting slows down and the defrosting start time becomes slower, the difference between the defrosting start times of both evaporators increases.

According to the present embodiment, even when it is impossible to change the operating frequency of each compressor, the opening degree of each expansion valve can be controlled, so that the capacity remains constant as a whole. The time difference between the start of defrosting can be expanded, and as a result, the possibility that both heat pump circuits are defrosted and not capable of being in the capacity can be further reduced by manipulating two parameters.

(Embodiment 5)
FIG. 10 is a schematic diagram showing the configuration of a heat pump circuit and control elements according to Embodiment 5 of the present invention.

  FIG. 11 is a flowchart showing the processing contents of temperature difference expansion control, which is a partial function of the main control unit 43.

Since the operation outline of the entire heat pump circuit and the processing contents of the defrosting start time difference determination unit 17 are the same as those described in the first embodiment, the description thereof is omitted.
However, the first compressor and the second compressor, the first fan, and the second fan in the present embodiment are types capable of variable speed.

  The operation of the main control unit 43 when receiving a request for either temperature difference expansion control or temperature difference expansion control stop from the defrosting start time difference determination unit 17 will be described with reference to the flowchart of FIG. The temperature difference expansion control in the main control unit 43 is performed at a set cycle (for example, every minute).

  In step 1, when the temperature difference expansion control is requested from the defrosting start time difference determination unit 17, the process proceeds to step 2, and when the temperature difference expansion control stop is requested, the process is terminated.

  In Step 2, when the start of defrosting of the first evaporator 4 is near according to the evaporator discrimination information from the defrosting start time difference determination unit 17, the process proceeds to Step 3, and when the start of defrosting of the second evaporator 13 is near Advances to step 12.

  In step 3, it is determined whether or not the operating frequency of the first compressor 1 can be increased. If it is possible to increase the operating frequency, the process proceeds to step 4; otherwise, the process proceeds to step 5.

  In step 4, the first compressor controller 7 is instructed to increase the operating frequency by a preset frequency, and the process proceeds to step 7.

  On the other hand, in step 5, it is determined whether or not the rotational speed of the first fan 5 can be reduced. If the number of revolutions can be reduced, the process proceeds to step 6; otherwise, the process ends.

  In step 6, the first fan controller 22 is instructed to reduce the rotational speed by a preset rotational speed, and the process proceeds to step 7.

  In step 7, it is determined whether or not the operating frequency of the second compressor 10 can be lowered. If the operating frequency can be lowered, the process proceeds to step 8, and if not possible, the process proceeds to step 9.

  In step 8, the second compressor control unit 9 is instructed to lower the operating frequency by a preset frequency, and the process ends.

On the other hand, in step 9, it is determined whether or not the rotational speed of the second fan 14 can be increased. If it is possible to increase the number of revolutions, the process proceeds to step 10; otherwise, the process proceeds to step 11.

  In step 10, the second fan control unit 23 is instructed to increase the frequency by a preset frequency, and the process ends.

  On the other hand, in step 11, the instruction to increase the operating frequency for the first compressor control unit 7 instructed in step 4 or the instruction to decrease the rotational speed to the first fan control unit 22 instructed in step 6 is canceled and the process ends.

Next, the case where it is determined in step 2 that the start of defrosting of the second evaporator is near will be described.
In step 12, it is determined whether the operating frequency of the second compressor 10 can be increased. If it is possible to increase the operating frequency, the process proceeds to step 13; otherwise, the process proceeds to step 14.

In step 13, the second compressor control unit 9 is instructed to increase the operating frequency by a preset frequency, and the process proceeds to step 16.
On the other hand, in step 14, it is determined whether or not the rotational speed of the second fan 14 can be reduced. If the number of revolutions can be reduced, the process proceeds to step 15; otherwise, the process ends.

  In step 15, the second fan controller 23 is instructed to reduce the rotational speed by a preset rotational speed, and the process proceeds to step 16.

  In step 16, it is determined whether or not the operating frequency of the first compressor 1 can be lowered. If it is possible to lower the operating frequency, the process proceeds to step 17; otherwise, the process proceeds to step 18.

  In step 16, the first compressor controller 7 is instructed to lower the operating frequency by a preset frequency, and the process is terminated.

  On the other hand, in step 18, it is determined whether the rotation speed of the first fan 5 can be increased. If it is possible to increase the number of revolutions, the process proceeds to step 19; otherwise, the process proceeds to step 20.

  In step 19, the first fan control unit 22 is instructed to increase the rotational speed by a preset rotational speed, and the process ends.

  On the other hand, in step 20, the instruction to increase the operating frequency for the second compressor controller 9 instructed in step 13 or the instruction to decrease the rotational speed to the second fan controller 23 instructed in step 15 is canceled and the process ends.

  As described above, the main control unit 43 operates on the first compressor control unit 7, the second compressor control unit 9, the first fan control unit 22, and the second fan control unit 23 by the output of the defrosting start time difference determination unit 17. By issuing a change command, an evaporator with a near defrost start time will increase the speed of frost formation due to an increase in capacity, leading to a faster defrost start time, while the capacity of the evaporator with a slow defrost start time Since the frosting speed is slowed down and the defrosting start time becomes slower, the difference between the defrosting start times of the two evaporators increases.

According to the present embodiment, even when it is impossible to change the operating frequency of each compressor, the rotation speed of each fan can be controlled. The time difference at the start of defrosting can be expanded, and as a result, the possibility that both heat pump circuits will be defrosted, not having the capability, can be further reduced by operating two parameters.

(Embodiment 6)
FIG. 12 is a schematic diagram showing the configuration of a heat pump circuit and control elements according to Embodiment 6 of the present invention.

  FIG. 13 is a flowchart showing the processing content of temperature difference expansion control, which is a partial function of the main control unit 44.

Since the operation outline of the entire heat pump circuit and the processing contents of the defrosting start time difference determination unit 17 are the same as those described in the first embodiment, the description thereof is omitted.
However, the first expansion valve and the second expansion valve in the present embodiment are electric expansion valves that can be arbitrarily throttled. The first fan and the second fan can be driven at a variable speed.

  The operation of the main control unit 44 when a request for either temperature difference expansion control or temperature difference expansion control stop is received from the defrosting start time difference determination unit 17 will be described with reference to the flowchart of FIG. The temperature difference expansion control in the main control unit 44 is performed at a certain set cycle (for example, every minute).

  In step 1, when the temperature difference expansion control is requested from the defrosting start time difference determination unit 17, the process proceeds to step 2, and when the temperature difference expansion control stop is requested, the process is terminated.

  In Step 2, when the start of defrosting of the first evaporator 4 is near according to the evaporator discrimination information from the defrosting start time difference determination unit 17, the process proceeds to Step 3, and when the start of defrosting of the second evaporator 13 is near Advances to step 12.

  In step 3, it is determined whether or not the rotation speed of the first fan 5 can be reduced. If it is possible to reduce the number of revolutions, the process proceeds to step 4; otherwise, the process proceeds to step 5.

  In step 4, the first fan control unit 22 is instructed to decrease the rotational speed by a preset rotational speed, and the process proceeds to step 7.

  On the other hand, in step 5, it is determined whether or not the opening degree of the first expansion valve 3 can be reduced. If it is possible to reduce the expansion valve opening degree, the process proceeds to step 6; otherwise, the process is terminated.

  In step 6, the first expansion valve control unit 20 is instructed to decrease the expansion valve opening by a predetermined opening, and the process proceeds to step 7.

  In step 7, it is determined whether or not the rotation speed of the second fan 14 can be increased. If the number of revolutions can be increased, the process proceeds to step 8, and if not possible, the process proceeds to step 9.

  In step 8, the second fan control unit 23 is instructed to increase the rotational speed by a preset rotational speed, and the process is terminated.

On the other hand, in step 9, it is determined whether or not the opening degree of the second expansion valve 12 can be increased. If it is possible to increase the opening of the expansion valve, the process proceeds to step 10, and if not, the process proceeds to step 11.

  In step 10, the second expansion valve control unit 21 is instructed to increase the expansion valve opening by a preset opening, and the process is terminated.

  On the other hand, in step 11, the instruction to reduce the rotation speed for the first fan control unit 22 instructed in step 4 or the instruction to decrease the expansion valve opening degree instructed to the first expansion valve control unit 20 in step 6 is canceled. finish.

  Next, the case where it is determined in step 2 that the start of defrosting of the second evaporator is near will be described.

  In step 12, it is determined whether or not the rotation speed of the second fan 14 can be reduced. If the number of revolutions can be reduced, the process proceeds to step 13; otherwise, the process proceeds to step 14.

  In step 13, the second fan control unit 23 is instructed to decrease the rotational speed by a preset rotational speed, and the process proceeds to step 16.

  On the other hand, in step 14, it is determined whether or not the opening degree of the second expansion valve 12 can be reduced. If it is possible to reduce the opening of the expansion valve, the process proceeds to step 15; otherwise, the process is terminated.

  In step 15, the second expansion valve control unit 21 is instructed to reduce the expansion valve opening by a predetermined opening, and the process proceeds to step 16.

  In step 16, it is determined whether or not the rotation speed of the first fan 5 can be increased. If it is possible to increase the number of revolutions, the process proceeds to step 17; otherwise, the process proceeds to step 18.

  In step 17, the first fan control unit 22 is instructed to increase the rotational speed by a preset rotational speed, and the process ends.

  On the other hand, in step 18, it is determined whether or not the opening degree of the first expansion valve 3 can be increased. If it is possible to increase the opening of the expansion valve, the process proceeds to step 19; otherwise, the process proceeds to step 20.

  In step 19, the first expansion valve control unit 20 is instructed to increase the expansion valve opening by a preset opening, and the process ends.

  On the other hand, in step 20, the instruction to reduce the rotational speed to the second fan control unit 23 instructed in step 13 or the instruction to decrease the expansion valve opening degree to the second expansion valve control unit 21 instructed in step 15 is canceled. finish.

  As described above, the main control unit 44 operates on the first expansion valve control unit 20, the second expansion valve control unit 21, the first fan control unit 22, and the second fan control unit 23 by the output of the defrosting start time difference determination unit 17. By issuing a change command, an evaporator with a near defrost start time will increase the speed of frost formation as the capacity increases, and the defrost start time will become faster, while the capacity of the evaporator with a slow defrost start time will increase. Since the frosting speed is slowed down and the defrosting start time becomes slower, the difference between the defrosting start times of the two evaporators increases.

  According to this embodiment, even when each compressor is at a constant speed, the time difference between the start of defrosting of both of them is increased by controlling each fan and the expansion valve while keeping the capacity constant as a whole. As a result, it is possible to further reduce the possibility that both heat pump circuits will be in a defrosting state, ie, defrosting, by manipulating two parameters.

(Embodiment 7)
FIG. 14 is a schematic diagram showing the configuration of a heat pump circuit and control elements according to Embodiment 7 of the present invention.

  15 and 16 are flowcharts showing the processing contents of the temperature difference expansion control, which is a partial function of the main control unit 45.

  Since the operation outline of the entire heat pump circuit and the processing contents of the defrosting start time difference determination unit 17 are the same as those described in the first embodiment, the description thereof will be omitted.

  However, the first expansion valve and the second expansion valve in the present embodiment are electric expansion valves that can be arbitrarily throttled, and the first compressor, the second compressor, the first fan, and the second fan are variable speeds. It can be driven.

The operation of the main control unit 45 when receiving a request for either temperature difference expansion control or temperature difference expansion control stop from the defrosting start time difference determination unit 17 will be described with reference to the flowchart of FIG.
The temperature difference expansion control in the main control unit 45 is carried out at a certain set cycle (for example, every minute).

  In step 1, when the temperature difference expansion control is requested from the defrosting start time difference determination unit 17, the process proceeds to step 2, and when the temperature difference expansion control stop is requested, the process is terminated.

  In Step 2, when the start of defrosting of the first evaporator 4 is near according to the evaporator discrimination information from the defrosting start time difference determination unit 17, the process proceeds to Step 3, and when the start of defrosting of the second evaporator 13 is near Advances to step 16.

  In step 3, it is determined whether or not the operating frequency of the first compressor 1 can be increased. If it is possible to increase the operating frequency, the process proceeds to step 4; otherwise, the process proceeds to step 5.

  In step 4, the first compressor control unit 7 is instructed to increase the operating frequency by a preset frequency, and the process proceeds to step 9.

  On the other hand, in step 5, it is determined whether or not the rotational speed of the first fan 5 can be reduced. If it is possible to reduce the fan speed, the process proceeds to step 6; otherwise, the process proceeds to step 7.

  In step 6, the first fan control unit 22 is instructed to decrease the fan rotational speed by a preset rotational speed, and the process proceeds to step 9.

  On the other hand, in step 7, it is determined whether or not the opening degree of the first expansion valve 3 can be reduced. If it is possible to reduce the opening of the expansion valve, the process proceeds to step 8; otherwise, the process is terminated.

  In step 8, the first expansion valve control unit 20 is instructed to decrease the expansion valve opening by a preset opening, and the process proceeds to step 9.

  In step 9, it is determined whether or not the operating frequency of the second compressor 10 can be lowered. If the operating frequency can be lowered, the process proceeds to step 10, and if not possible, the process proceeds to step 11.

  In step 10, the second compressor control unit 9 is instructed to lower the operating frequency by a preset frequency, and the process ends.

  On the other hand, in step 11, it is determined whether the rotation speed of the second fan 14 can be increased. If it is possible to increase the number of fan rotations, the process proceeds to step 12; otherwise, the process proceeds to step 13.

  In step 12, the second fan control unit 23 is instructed to increase the fan rotational speed by a preset rotational speed, and the process ends.

  On the other hand, in step 13, it is determined whether or not the opening degree of the second expansion valve 12 can be increased. If it is possible to increase the opening of the expansion valve, the process proceeds to step 14; otherwise, the process proceeds to step 15.

  In step 14, the second expansion valve control unit 21 is instructed to increase the expansion valve opening by a preset opening, and the process is terminated.

  On the other hand, in step 15, an instruction to increase the operating frequency for the first compressor control unit 7 instructed in step 4, an instruction to decrease the fan speed to the first fan control unit 22 instructed in step 6, or step 8 The instruction | indication which makes the expansion valve opening degree with respect to the 1st expansion valve control part 20 instruct | indicated in (1) canceled is cancelled | finished.

Next, the case where it is determined in step 2 that the start of defrosting of the second evaporator 13 is near will be described.
In step 16, it is determined whether the operating frequency of the second compressor 10 can be increased. If it is possible to increase the operating frequency, the process proceeds to step 17; otherwise, the process proceeds to step 18.

  In step 17, the second compressor control unit 9 is instructed to increase the operating frequency by a preset frequency, and the process proceeds to step 22.

  On the other hand, in step 18, it is determined whether or not the rotational speed of the second fan 14 can be reduced. If it is possible to lower the fan speed, the process proceeds to step 19; otherwise, the process proceeds to step 20.

  In step 19, the second fan control unit 23 is instructed to decrease the fan rotational speed by a preset rotational speed, and the process proceeds to step 22.

  On the other hand, in step 20, it is determined whether or not the opening degree of the second expansion valve 12 can be reduced. If it is possible to reduce the expansion valve opening degree, the process proceeds to step 21; otherwise, the process is terminated.

  In step 21, the second expansion valve control unit 21 is instructed to reduce the expansion valve opening by a predetermined opening, and the process proceeds to step 22.

  In step 22, it is determined whether or not the operating frequency of the first compressor 1 can be lowered. If the operating frequency can be lowered, the process proceeds to step 23, and if not possible, the process proceeds to step 24.

  In step 23, the first compressor controller 7 is instructed to lower the operating frequency by a preset frequency, and the process is terminated.

  On the other hand, in step 24, it is determined whether or not the rotation speed of the first fan 5 can be increased. If it is possible to increase the number of fan rotations, the process proceeds to step 25; otherwise, the process proceeds to step 26.

  In step 25, the first fan control unit 22 is instructed to increase the fan rotational speed by a preset rotational speed, and the process ends.

  On the other hand, in step 26, it is determined whether or not the opening degree of the first expansion valve 3 can be increased. If it is possible to increase the opening degree of the expansion valve, the process proceeds to step 27, and if not, the process proceeds to step 28.

  In step 27, the first expansion valve control unit 20 is instructed to increase the expansion valve opening by a preset opening, and the process ends.

  On the other hand, in step 28, an instruction to increase the operating frequency for the second compressor control unit 9 instructed in step 17, or an instruction to decrease the fan speed to the second fan control unit 23 instructed in step 19, or step 21 The instruction | indication which makes the expansion valve opening small with respect to the 2nd expansion valve control part 21 instruct | indicated in (1) is canceled, and it complete | finishes.

  As described above, by the output of the defrosting start time difference determination unit 17, the main control unit 45 causes the first compressor control unit 7, the second compressor control unit 9, the first expansion valve control unit 20, and the second expansion valve control unit 21. By issuing an operation change command to one of the first fan control unit 22 and the second fan control unit 23, an evaporator with a near defrost start time increases the speed of frost formation due to an increase in capacity, and more The frost start time becomes faster, while the ability of the evaporator with slow defrost start time decreases, so the speed of frost formation slows down and the defrost start time becomes slower. The difference in defrosting start time will be enlarged.

  According to the present embodiment, by having three types of elements for operating the evaporation temperature of each evaporator, the possibility that the time difference between the start of defrosting of both can be further increased while keeping the capacity constant as a whole. As a result, it is possible to significantly reduce the possibility that both heat pump circuits will be in a state of no defrosting capability.

(Embodiment 8)
FIG. 17 is a schematic diagram showing the configuration of a heat pump circuit and control elements according to Embodiment 8 of the present invention.

  Since the operation outline of the entire heat pump circuit and the processing contents of the defrosting start time difference determination unit 17 are the same as those described in the first embodiment, the description thereof will be omitted.

  In the present embodiment, in the process of the defrosting start time difference determining unit 17 described with reference to FIG. 2 in the description of the first embodiment, the set time difference (Tover) used as the comparison value in Step 12 is externally set. The input unit 24 can be changed.

  According to the present embodiment, the setting time difference (Tover) can be input from the external input unit 24, so that it is possible to set according to each actual use situation.

  Specifically, the defrosting time varies depending on the environment in which the device is installed, and the set time difference (Tover) needs to be set longer than the actual defrosting time in the installed environment. Therefore, when installed in an environment where the defrosting time is long, the set time difference (Tover) is set long, and when installed in an environment where the defrosting time is short, the set time difference (Tober) is set short. Thus, it is possible to accurately adjust the defrosting time.

(Embodiment 9)
FIG. 18 shows an embodiment of a heat pump type hot water supply apparatus having a small hot water storage tank according to the ninth embodiment of the present invention, in which the water in the hot water storage tank is heated and hot water is stored in the tank. It is a circuit diagram in the case of supplying hot water directly without doing.

  As shown in FIG. 18, the heat pump hot water supply device 32 includes a heat pump unit 33, a hot water supply unit 34, and a faucet 30.

  The heat pump unit 33 includes two refrigeration cycle circuits. The first refrigeration cycle circuit 18 includes a first compressor 1, a first refrigerant-to-water heat exchanger 36, a first expansion valve 3, and a first evaporator 4 that are sequentially arranged in an annular manner by a refrigerant pipe. The second refrigeration cycle circuit 19 includes a second compressor 10, a second refrigerant-to-water heat exchanger 37, a second expansion valve 12, and a second evaporator 13 that are sequentially arranged in an annular manner by a refrigerant pipe.

  The first compressor 1 and the second compressor 10 compress the refrigerant, and the first refrigerant-to-water heat exchanger 36 and the second refrigerant-to-water heat exchanger 37 are discharged from the first compressor 1 and the second compressor 10. Water is heated by the heat of the refrigerant. The first expansion valve 3 and the second expansion valve 12 decompress the refrigerant heat-exchanged by the first refrigerant-to-water heat exchanger 36 and the second refrigerant-to-water heat exchanger 37.

  The hot water supply unit 34 has a hot water tank 25, a pump 27 that sends hot water to the second water heat exchanger 37 through the lower part of the hot water tank 25, hot water heated by the second water heat exchanger 37 and the first water heat exchanger 36. A hot water storage valve 26 that guides the hot water to the hot water storage tank, a mixing valve 28 that mixes hot water heated by the second water heat exchanger 37 and the first water heat exchanger 36 with hot water stored in the hot water storage tank 25, and a mixing valve 28 It comprises a regulating valve that mixes hot and cold water and tap water to adjust the hot water temperature and a hot water tank faucet 30.

  The hot water supply realization method in this Embodiment is demonstrated.

  In the present embodiment, since the hot water storage tank 25 is small, hot water necessary and sufficient is not stored like a hot water storage type hot water heater.

  In the initial stage of hot water supply, hot water supply is started at a desired hot water supply temperature using hot water stored in the hot water storage tank 25, but heating by the first heat pump circuit 18 and the second heat pump circuit 19 has sufficient capacity. Alternatively, even in a transient state until sufficient capacity is achieved, the hot water supply from the heat pump circuit is gradually increased, and finally, the method is switched to only the hot water supply by the heat pump.

  Since the hot water supply method described above is used, if both heat pump circuits start defrosting during hot water supply, there is a problem that hot water supply cannot be performed or the hot water supply capacity is greatly reduced.

  For this reason, by incorporating the functions described in the first to sixth embodiments into the heat pump unit 33, it is possible to greatly reduce the frequency of occurrence of the above-mentioned problems.

Schematic which showed the structure of the heat pump circuit and control element by Embodiment 1 of the defrost control apparatus by this invention. The flowchart which shows the processing content of the defrost start time difference determination part of the embodiment The flowchart which shows the processing content of the temperature difference expansion control which is a part of function of the main control part of the embodiment Schematic which showed the structure of the heat pump circuit and control element by Embodiment 2 of the defrost control apparatus by this invention. The flowchart which shows the processing content of the temperature difference expansion control which is a part of function of the main control part of the embodiment Schematic which showed the structure of the heat pump circuit and control element by Embodiment 3 of the defrost control apparatus by this invention. The flowchart which shows the processing content of the temperature difference expansion control which is a part of function of the main control part of the embodiment Schematic which showed the structure of the heat pump circuit and control element by Embodiment 4 of the defrost control apparatus by this invention. The flowchart which shows the processing content of the temperature difference expansion control which is a part of function of the main control part of the embodiment Schematic which showed the structure of the heat pump circuit and control element by Embodiment 5 of the defrost control apparatus by this invention. The flowchart which shows the processing content of the temperature difference expansion control which is a part of function of the main control part of the embodiment Schematic which showed the structure of the heat pump circuit and control element by Embodiment 6 of the defrost control apparatus by this invention. The flowchart which shows the processing content of the temperature difference expansion control which is a part of function of the main control part of the embodiment Schematic which showed the structure of the heat pump circuit and control element by Embodiment 7 of the defrost control apparatus by this invention. The flowchart which shows the processing content to step 15 of the temperature difference expansion control which is a part of function of the main control part of the embodiment. The flowchart which shows the processing content after step 16 of the temperature difference expansion control which is a part of function of the main control part of the same embodiment Schematic which showed the structure of the heat pump circuit and control element by Embodiment 8 of the defrost control apparatus by this invention. Schematic which showed the structure of the heat pump circuit and control element by Embodiment 9 of the defrost control apparatus by this invention. Schematic showing the configuration of a heat pump circuit in a conventional air conditioner

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 1st compressor 2 1st condenser 3 1st expansion valve 4 1st evaporator 5 1st fan 6 1st temperature sensor 7 1st compressor control part 8 main control part 9 2nd compressor control part 10 2nd Compressor 11 Second condenser 12 Second expansion valve 13 Second evaporator 14 Second fan 15 Second temperature sensor 17 Defrosting start time difference determination unit 18 First heat pump circuit 19 Second heat pump circuit 20 First expansion valve control unit 21 Second expansion valve control unit 22 First fan control unit 23 Second fan control unit 24 External input unit 40 Main control unit 41 Main control unit 42 Main control unit 43 Main control unit 44 Main control unit 45 Main control unit

Claims (15)

A first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, a first fan for the first evaporator, a second compressor, a second condenser, a second In a refrigeration cycle apparatus configured with two heat pump circuits including a second expansion pump, a second evaporator, and a second heat pump circuit including a second fan for the second evaporator, the first Controls a first compressor control unit, a second compressor control unit, a first compressor control unit, a second compressor control unit, and an entire control system that respectively control one compressor and the second compressor. And a defrosting start time difference determining unit for estimating a time until defrosting start of each heat pump circuit and determining whether the difference is equal to or less than a set value and outputting the result to the main control unit. A defrosting control device characterized by that. A first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, a first fan for the first evaporator, a second compressor, a second condenser, a second In a refrigeration cycle apparatus configured with two heat pump circuits including a second expansion pump, a second evaporator, and a second heat pump circuit including a second fan for the second evaporator, the first Controls the first expansion valve control unit, the second expansion valve control unit, the first expansion valve control unit, the second expansion valve control unit, and the entire control system for controlling the first expansion valve and the second expansion valve, respectively. And a defrosting start time difference determining unit for estimating a time until defrosting start of each heat pump circuit and determining whether the difference is equal to or less than a set value and outputting the result to the main control unit. A defrosting control device characterized by that. A first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, a first fan for the first evaporator, a second compressor, a second condenser, a second In a refrigeration cycle apparatus configured with two heat pump circuits including a second expansion pump, a second evaporator, and a second heat pump circuit including a second fan for the second evaporator, the first A first compressor control unit and a second compressor control unit for controlling the first compressor and the second compressor, respectively; a first expansion valve control unit for controlling the first expansion valve and the second expansion valve; A main control unit that controls the second expansion valve control unit, the first compressor control unit, the second compressor control unit, the first expansion valve control unit, the second expansion valve control unit, and the entire control system Estimate the time to start defrosting of each heat pump circuit and set the difference Defrosting adjusting device is characterized in that a defrosting start time difference determination unit that determines whether the value below and outputs the result to the main control unit. A first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, a first fan for the first evaporator, a second compressor, a second condenser, a second In a refrigeration cycle apparatus configured with two heat pump circuits including a second expansion pump, a second evaporator, and a second heat pump circuit including a second fan for the second evaporator, the first A first compressor control unit and a second compressor control unit for controlling the first compressor and the second compressor, respectively, a first fan control unit and a second fan for controlling the first fan and the second fan, respectively. A main control unit that controls the control unit, the first compressor control unit, the second compressor control unit, the first fan control unit, the second fan control unit, and the entire control system, and respective heat pump circuits The time until the start of defrosting is estimated and the difference is set. Defrosting adjusting device is characterized in that a defrosting start time difference determination unit that determines whether the value below and outputs the result to the main control unit. A first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, a first fan for the first evaporator, a second compressor, a second condenser, a second In a refrigeration cycle apparatus configured with two heat pump circuits including a second expansion pump, a second evaporator, and a second heat pump circuit including a second fan for the second evaporator, the first A first expansion valve control unit and a second expansion valve control unit for controlling the first expansion valve and the second expansion valve, respectively, a first fan control unit and a second fan for controlling the first fan and the second fan, respectively. A control unit;
The first expansion valve control unit, the second expansion valve control unit, the first fan control unit, the second fan control unit, and a main control unit that controls the entire control system, and defrosting start of each heat pump circuit A defrosting adjustment device comprising: a defrosting start time difference determining unit that estimates a time until a difference is determined to determine whether the difference is equal to or less than a set value and outputs the result to the main control unit. A first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, a first fan for the first evaporator, a second compressor, a second condenser, a second In a refrigeration cycle apparatus configured with two heat pump circuits including a second expansion pump, a second evaporator, and a second heat pump circuit including a second fan for the second evaporator, the first A first compressor control unit and a second compressor control unit for controlling the first compressor and the second compressor, respectively; a first expansion valve control unit for controlling the first expansion valve and the second expansion valve; A second expansion valve control unit, a first fan control unit and a second fan control unit for controlling the first fan and the second fan, respectively, the first compressor control unit and the second compressor control unit; The first expansion valve control unit, the second expansion valve control unit, and the first fan The main control unit that controls the control unit, the second fan control unit, and the entire control system, and the time until the start of defrosting of each heat pump circuit are estimated, and it is determined whether or not the difference is equal to or less than a set value. A defrosting adjustment apparatus comprising: a defrosting start time difference determination unit that outputs to the main control unit. The defrosting start time difference determination unit estimates the time until defrosting of the first heat pump circuit and the second heat pump circuit is started from the outlet temperatures of the first evaporator and the second evaporator, and the time difference is set in advance. The defrosting control device according to claim 1, wherein the defrosting control device is compared with a value that is present. The defrosting adjustment device according to claim 7, wherein the defrosting start time difference determination unit includes an external input unit that allows a comparison value with the estimated time difference to be input from the outside. A first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, a first fan for the first evaporator, a second compressor, a second condenser, a second In a refrigeration cycle apparatus configured with two heat pump circuits including a second expansion pump, a second evaporator, and a second heat pump circuit including a second fan for the second evaporator, the first Controls a first compressor control unit, a second compressor control unit, a first compressor control unit, a second compressor control unit, and an entire control system that respectively control one compressor and the second compressor. And a defrosting start time difference determining unit for estimating a time until defrosting start of each heat pump circuit and determining whether the difference is equal to or less than a set value and outputting the result to the main control unit. A control method for a defrosting control device, characterized by comprising: A first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, a first fan for the first evaporator, a second compressor, a second condenser, a second In a refrigeration cycle apparatus configured with two heat pump circuits including a second expansion pump, a second evaporator, and a second heat pump circuit including a second fan for the second evaporator, the first Controls the first expansion valve control unit, the second expansion valve control unit, the first expansion valve control unit, the second expansion valve control unit, and the entire control system for controlling the first expansion valve and the second expansion valve, respectively. And a defrosting start time difference determining unit for estimating a time until defrosting start of each heat pump circuit and determining whether the difference is equal to or less than a set value and outputting the result to the main control unit. A control method for a defrosting control device, characterized by comprising: A first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, a first fan for the first evaporator, a second compressor, a second condenser, a second In a refrigeration cycle apparatus configured with two heat pump circuits including a second expansion pump, a second evaporator, and a second heat pump circuit including a second fan for the second evaporator, the first A first compressor control unit and a second compressor control unit for controlling the first compressor and the second compressor, respectively; a first expansion valve control unit for controlling the first expansion valve and the second expansion valve; A main control unit that controls the second expansion valve control unit, the first compressor control unit, the second compressor control unit, the first expansion valve control unit, the second expansion valve control unit, and the entire control system Estimate the time to start defrosting of each heat pump circuit and set the difference The method of defrosting adjusting device, wherein a judgment result whether a value less than or equal to a defrost start time difference determination unit that outputs to the main control unit. A first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, a first fan for the first evaporator, a second compressor, a second condenser, a second In a refrigeration cycle apparatus configured with two heat pump circuits including a second expansion pump, a second evaporator, and a second heat pump circuit including a second fan for the second evaporator, the first A first compressor control unit and a second compressor control unit for controlling the first compressor and the second compressor, respectively, a first fan control unit and a second fan for controlling the first fan and the second fan, respectively. A main control unit that controls the control unit, the first compressor control unit, the second compressor control unit, the first fan control unit, the second fan control unit, and the entire control system, and respective heat pump circuits The time until the start of defrosting is estimated and the difference is set. The method of defrosting adjusting device, wherein a judgment result whether a value less than or equal to a defrost start time difference determination unit that outputs to the main control unit. A first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, a first fan for the first evaporator, a second compressor, a second condenser, a second In a refrigeration cycle apparatus configured with two heat pump circuits including a second expansion pump, a second evaporator, and a second heat pump circuit having a second fan for the second evaporator, the first A first expansion valve control unit and a second expansion valve control unit for controlling the first expansion valve and the second expansion valve, respectively, a first fan control unit and a second fan for controlling the first fan and the second fan, respectively. A main control unit that controls the control unit, the first expansion valve control unit, the second expansion valve control unit, the first fan control unit, the second fan control unit, and the entire control system, and respective heat pump circuits The time until the start of defrosting is estimated and the difference is set. The method of defrosting adjusting device, wherein a judgment result whether a value less than or equal to a defrost start time difference determination unit that outputs to the main control unit. A first heat pump circuit comprising a first compressor, a first condenser, a first expansion valve, a first evaporator, a first fan for the first evaporator, a second compressor, a second condenser, a second In a refrigeration cycle apparatus configured with two heat pump circuits including a second expansion pump, a second evaporator, and a second heat pump circuit including a second fan for the second evaporator, the first A first compressor control unit and a second compressor control unit for controlling the first compressor and the second compressor, respectively; a first expansion valve control unit for controlling the first expansion valve and the second expansion valve; A second expansion valve control unit, a first fan control unit and a second fan control unit for controlling the first fan and the second fan, respectively, the first compressor control unit and the second compressor control unit; The first expansion valve control unit, the second expansion valve control unit, and the first fan The main control unit that controls the control unit, the second fan control unit, and the entire control system, and the time until the start of defrosting of each refrigeration cycle circuit are estimated, and it is determined whether or not the difference is equal to or less than a set value. And a defrosting start time difference determining unit that outputs the defrosting time to the main control unit. The heat pump type hot water supply apparatus provided with the defrosting control apparatus as described in any one of Claims 1-6.

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