JP6346122B2 - Hot water heating system - Google Patents

Description

  The present invention relates to a hot water heating system capable of performing heating using hot water exchanged with a heat pump device.

  Conventionally, in this type of system, there has been a system in which a plurality of heat exchange terminals (heat radiating terminals) are connected to a water heat exchanger of an outdoor unit (see, for example, Patent Document 1). In this system, during the heating operation, hot water generated in the water heat exchanger by the refrigerant from the heat pump device is supplied to each heat radiating terminal via the introduction pipe.

JP2013-217522A

  Here, in recent years, R32 refrigerant is being used in heat pump devices instead of R22 and R410A refrigerants that have been widely used in heat pump devices. It is known that this R32 refrigerant has a higher refrigeration capacity per unit volume than the conventionally used R22 and R410A refrigerants, and can reduce the filling amount in the refrigerant pipes than the R410A refrigerant. Therefore, when the pressure is reduced on the upstream side of the evaporator (air heat exchanger), it is necessary to set the pressure reduction rate larger than the pressure reduction rate in the conventional heat pump device for the R410A refrigerant.

  With such a decrease in the filling amount and an increase in the decompression rate in the R32 refrigerant (compared to the R410A refrigerant), the heat pump device for the R32 refrigerant heats the frost attached to the condenser in the defrosting operation. How quickly it melts), and the longer the time of defrosting, the longer the time during which the heating operation at the heat exchange terminal is interrupted, and the lowering of the room temperature impairs indoor comfort was there.

  In order to solve the above problem, in claim 1 of the present invention, a heat pump device including a compressor for R32 refrigerant, an expansion valve, an air heat exchanger, and water supplied from the heat pump device with R32 refrigerant supplied. An outdoor unit having a water heat exchanger that generates hot water by heat exchange with the outdoor unit, and indoor water using the hot water generated by the water heat exchanger of the outdoor unit and supplied via an introduction pipe Heating is performed by heat radiation, and the heat exchange terminal that recirculates the hot water after heat radiation to the water heat exchanger of the outdoor unit through a discharge pipe by a circulation pump, and the operation state of the heat exchange terminal In the hot water heating system for R32 refrigerant having a remote control device controlled in a control mode and an outdoor control unit for controlling the compressor, the expansion valve and the like according to a command from the remote control device, the air heat exchanger A heat exchange sensor that detects the temperature and an outside air temperature sensor that detects the temperature of the outside air are provided, and a temperature difference c between the heat exchange temperature a detected by the heat exchange sensor and the outside air temperature b detected by the outside air temperature sensor is When the temperature difference is equal to or greater than the first predetermined temperature difference c1, the defrosting operation is started, the decirculation operation is continued at the first predetermined rotation speed d1 and the compressor at the first predetermined frequency e1, and then the defrosting operation is performed. When the heat exchange temperature a after the first predetermined time t1 has elapsed from the start of operation is equal to or lower than the first predetermined temperature a1, the rotational speed of the circulation pump is set to a second predetermined rotational speed d2 that is greater than the first predetermined rotational speed d1. It has a defrost control means to change.

  Moreover, in Claim 2, the said heat exchanger temperature a at the time of 1st predetermined time t1 progressing from the said defrost operation start is below 1st predetermined temperature a1, and the rotation speed of the said circulation pump is set rather than 1st predetermined rotation speed d1. After changing to a large second predetermined rotational speed d2, the defrosting operation is continued, and the heat exchange temperature a when the second predetermined time t2 greater than the first predetermined time t1 has elapsed from the start of the defrosting operation is the first predetermined temperature. When the temperature is equal to or lower than a1, the compressor has defrosting control means for changing the compressor to a second predetermined frequency e2 that is higher than the first predetermined frequency e1.

  According to a third aspect of the present invention, the defrosting operation is terminated when the heat exchange temperature a continues at the second predetermined temperature a2 higher than the first predetermined temperature a1 for the third predetermined time t3 during the defrosting operation. It has a defrost control means which restarts heating operation.

  In claim 1 of the present invention, in order to eliminate the above-described adverse effects resulting from the use of the R32 refrigerant, the progress of defrosting after the first predetermined time from the start of the defrosting operation is detected by the heat exchange temperature, When the progress of defrosting is poor, increasing the rotation speed of the circulation pump to improve the evaporation capacity of the water heat exchanger will improve the condensation capacity of the air heat exchanger and improve the defrosting performance. The defrosting operation can be completed in a short time, and as a result, the comfort of the heating operation is improved.

  According to claim 2, when the progress of defrosting after the second predetermined time from the start of the defrosting operation is detected by the heat exchange temperature, and the progress of defrosting is poor, the frequency of the compressor is further reduced. Is raised, the condensation capability of the air heat exchanger is improved, and the defrosting performance is further improved. As a result, it is possible to moderate the deterioration in the comfort of the heating operation by ending the long defrosting operation time as soon as possible and restarting the heating operation.

  Moreover, according to claim 3, the end of the defrosting is judged by the rise in the heat exchange temperature during the defrosting operation, and the heating operation is restarted promptly, so that the decrease in the comfort of the heating operation is moderated. Can do.

The figure which shows the whole schematic structure of the hot-water cooling / heating system of one Embodiment of this invention. Schematic representation of the refrigeration cycle during defrosting and heating operations of the outdoor unit Explanatory drawing of switching conditions for the defrosting operation Explanatory drawing of operation of each part by switching of the defrosting operation Flow chart showing the control procedure

  Hereinafter, an embodiment of the present invention will be described with reference to FIGS.

  The whole schematic structure of the hot water heating system of this embodiment is shown in FIG. In FIG. 1, this hot water heating system 100 includes an outdoor unit 1 that is installed outdoors, and a plurality of heat units that are installed indoors by being connected to the outdoor unit 1 via a hot water forward pipe 2 and a hot water return pipe 3. And an exchange terminal (in this example, a heating panel 51, a heating panel 52, and a floor heating panel 53).

  In this example, the heating panel 51 is arranged in the A room among the three-room structure consisting of the A room, the B room, and the C room, the heating panel 52 is arranged in the B room, and the floor heating. The panel 53 is disposed in the C chamber. At this time, one forward header 91 is provided in the middle of the warm water outgoing pipe 2 extending from the outdoor unit 1, and the upstream side portion of the warm water outgoing pipe 2 from the forward header 91 is one common outgoing pipe 2A. The hot water from the outdoor unit 1 is supplied. The downstream portion of the warm water forward pipe 2 from the forward header 91 includes an outgoing pipe 2B1 to the heating panel 51, an outgoing pipe 2B2 to the heating panel 52, and an outgoing pipe 2B3 to the floor heating panel 53. And is divided. The common forward pipe 2A and the forward pipe 2B1 correspond to the introduction pipe line to the heating panel 51, and the common forward pipe 2A and the forward pipe 2B2 correspond to the introduction pipe line to the heating panel 52, The common forward pipe 2 </ b> A and the forward pipe 2 </ b> B <b> 3 correspond to introduction pipes to the floor heating panel 53. Similarly, one return header 92 is provided in the middle of the hot water return pipe 3 extending to the outdoor unit 1, and a portion of the hot water return pipe 3 upstream from the return header 92 is connected to the heating panel 51. Return pipe 3B1, a return pipe 3B2 from the heating panel 52, and a return pipe 3B3 from the floor heating panel 53. A portion of the hot water return pipe 3 downstream from the return header 92 is configured as one common return pipe 3A, and the hot water introduced through the return pipes 3B1, 3B2, and 3B3 is returned to the outdoor unit 1. . The common return pipe 3A and the return pipe 3B1 correspond to the lead-out pipe line from the heating panel 51, and the common return pipe 3A and the return pipe 3B2 correspond to the lead-out pipe line from the heating panel 52, The common return pipe 3 </ b> A and the return pipe 3 </ b> B <b> 3 correspond to a lead-out pipe line from the floor heating panel 53.

  The forward pipe 2B1 to the heating panel 51, the forward pipe 2B2 to the heating panel 52, and the forward pipe 2B3 to the floor heating panel 53 are each forward pipe by a drive signal from a thermal valve controller CV. Thermally operated valves V1, V2, V3 that can be opened and closed are respectively provided. In this example, the room A is provided with a main remote controller RM for performing a heat radiation (heating) operation of the heating panel 51 and a heat radiation (heating) operation of the heating panel 52 and the floor heating panel 53. The room B is provided with a terminal remote controller RA for performing a heat radiation (heating) operation of the heating panel 52, and the room C is provided with a heat radiation (heating) operation of the floor heating panel 53. A terminal remote control device RB is provided for performing the above.

  A control signal SS1 output in response to an operation on the main remote controller RM is input to an outdoor unit controller (described later) that controls the outdoor unit 1, and is thereby supplied to the common forward pipe 2A. The flow rate and temperature of the heated water are controlled, and the control signal SS2 is output from the outdoor unit controller to the thermal valve controller CV in response to this, and the thermal valve controller CV outputs the control signal accordingly. The opening / closing operations of the thermal valves V1, V2, V3 are controlled by the control signals S1, S2, S3. Accordingly, by appropriately operating the main remote controller RM, the operation states of the heating panel 51, the heating panel 52, and the floor heating panel 53 can be collectively controlled (hereinafter, as appropriate) The control mode is referred to as “collective control”). Further, the control signal Sa output in response to the operation on the terminal remote controller RA is input to the thermal valve controller CV, and in response to the control signal S2 output from the thermal valve controller CV. The opening / closing operation of the thermal valve V2 is controlled. Accordingly, the operating state of the heating panel 52 can be individually controlled by appropriately operating the terminal remote controller RA (hereinafter, such a control mode is referred to as “individual control” as appropriate). Further, the control signal Sb output in response to the operation on the terminal remote control device RB is input to the thermal valve controller CV, and in response to the control signal S3 output from the thermal valve controller CV. The opening / closing operation of the thermal valve V3 is controlled. Thereby, the operating state of the floor heating panel 53 can be individually controlled by appropriately operating the terminal remote control device RB.

  Next, the schematic system configuration of the outdoor unit 1 is shown in FIG. 2 (a) during the defrosting operation and (b) during the heating operation. In FIG. 2A, an outdoor unit 1 includes a refrigerant circulation circuit 21 that circulates an R32 refrigerant that has been used in recent years and absorbs and releases heat outside the room, instead of the R410A refrigerant that has been widely used in air conditioners. For example, the antifreeze is circulated as hot water to radiate heat at the plurality of heat exchange terminals (the heating panel 51, the heating panel 52, and the floor heating panel 53 in the above example) (the hot water outlet pipe 2 and Heat exchange with the warm water circulation circuit 22 (consisting of the warm water return pipe 3) is performed.

  That is, the refrigerant circulation circuit 21 performs heat exchange between the refrigerant and the outside air, which is provided in the outdoor unit 1 and switches the four-way valve 6 that switches the circulation direction of the refrigerant, the compressor 7 that compresses the refrigerant, and the like. Heat exchange between the refrigerant and the hot water circulating through the outdoor heat exchanger 8 (corresponding to an air heat exchanger), an expansion valve 9 for decompressing and expanding the refrigerant, the hot water outlet pipe 2 and the hot water return pipe 3 is performed. A water / refrigerant heat exchanger 11 (corresponding to a water heat exchanger) to be performed is connected by a refrigerant pipe 15. The four-way valve 6, the compressor 7, the outdoor heat exchanger 8, and the expansion valve 9 that are connected to each other through the refrigerant pipe 15 constitute a heat pump device. Further, an outdoor fan 10 for blowing air to the outdoor heat exchanger 8 is further provided. And the heat exchange sensor 8a which detects the temperature of the substantially intermediate | middle part surface of the said outdoor heat exchanger 8, and the temperature (outside temperature t) of the air inhaled by the outdoor fan 10 provided in the windward side of the said outdoor fan 10 Is provided with an outside air temperature sensor 10a.

  The four-way valve 6 is a valve having four ports. For each of two ports for the refrigerant main path 15a (which constitutes a part of the refrigerant pipe 15), a part of the refrigerant pipe 15 is provided. Configure) Switch which of the two ports for the other refrigerant sub-path 15b is connected. The two ports for the refrigerant sub-path 15b are connected by a refrigerant sub-path 15b arranged in a loop, and the compressor 7 is provided on the refrigerant sub-path 15b.

  The compressor 7 pressurizes the refrigerant in a low-pressure gas state to be in a high-pressure gas state, and also functions as a pump for circulating the refrigerant in the entire refrigerant pipe 15 in the outdoor unit 1. Then, the compression capacity is changed by continuously and variably controlling the rotational speed between 20 and 105 Hz by a known inverter device (not shown).

  The two ports for the refrigerant main path 15a of the four-way valve 6 are connected by the refrigerant main path 15a arranged in a loop shape, and the outdoor heat exchanger 8, The expansion valve 9 and the water-refrigerant exchanger 11 are provided in this order (in the example shown in FIG. 2A, in the order of the counterclockwise refrigerant main path 15a).

  In the heating operation of FIG. 2 (b), the outdoor heat exchanger 8 is in a gas state in which the temperature of the refrigerant in the liquid state passing through the interior thereof is lower than the outdoor outdoor temperature, and the heat of the outdoor air is absorbed by the refrigerant. Functions as an evaporator to evaporate. The heat absorbed from the outside air by the outdoor heat exchanger 8 is carried to the water-refrigerant exchanger 11 by the refrigerant circuit, and the room is heated through the hot water circulation circuit 22. When the outside air temperature b falls below about 5 ° C., the outdoor heat exchanger 8 decreases to below freezing point, and the moisture contained in the passing outside air freezes, so that frost formation starts on the surface of the outdoor heat exchanger 8. Is generated more as the outside air temperature b is lower, and gradually increases along the duration of the heating operation. As frost develops, heat exchange is inhibited and the temperature of the refrigerant passing through the outdoor heat exchanger 8 further decreases. Therefore, the defrosting operation is required periodically at an appropriate timing (in this embodiment, the temperature difference between the outside air temperature b and the heat exchange temperature a is 8 deg or more).

  Fig. 2 (a) During the defrosting operation, the high-temperature and high-pressure gas pressurized by the compressor 7 is sent to the outdoor heat exchanger 8 and heated to remove frost attached to the outdoor heat exchanger 8 and to perform outdoor heat exchange. In this case, normal heat exchange is performed in the vessel 8 and functions as a condenser that radiates the heat of the refrigerant and condenses it into a liquid state.

  The outdoor fan 10 improves the performance of the outdoor heat exchanger 8 by sending air to the outdoor heat exchanger 8. The outside air temperature sensor 10a is arranged on the windward side of the outdoor fan 10 and in the vicinity of the outdoor air inlet, and detects the outside air temperature.

  The expansion valve 9 functions to decompress and expand the refrigerant in a high-pressure liquid state to a low-pressure liquid state.

  As described above, the water-refrigerant heat exchanger 11 is connected to the refrigerant main path 15a and allows the refrigerant to pass through it, and is also connected to the cold / hot water return pipe 2 and the cold / hot water return pipe 3 so as to have the inside thereof. Allow warm water to pass through. When the temperature of the liquid state R32 refrigerant passing through the inside of the water-refrigerant heat exchanger 11 is lower than the temperature of the hot water, it functions as an evaporator that absorbs the heat of the cold / hot water and evaporates it into a gas state. Moreover, when the temperature of the gaseous refrigerant passing through the inside of the water-refrigerant heat exchanger 11 is higher than the temperature of the cold / hot water, the condenser radiates the heat to the cold / hot water and condenses it into a liquid state. Function.

  On the other hand, the hot water circulation circuit 22 includes the water-refrigerant heat exchanger 11, a circulation pump 12 that applies a circulation pressure to the hot water, a cistern tank 13, and the plurality of heat exchange terminals provided in the outdoor unit 1. (In the above example, the heating panel 51, the heating panel 52, and the floor heating panel 53) are connected by the hot water outlet pipe 2 and the hot water return pipe 3.

  The water-refrigerant heat exchanger 11 is connected to the hot water return pipe 2 and the hot water return pipe 3, and the cistern tank 13 and the circulation pump 12 are provided on the hot water return pipe 3.

  The cistern tank 13 separates bubbles generated in the hot water by cavitation or the like (air / water separation function), absorbs the hot / warm water in the hot water circulation circuit 22 and supplies cold / hot water.

  The circulation pump 12 functions to circulate hot water throughout the hot water forward pipe 2 and the hot water return pipe 3.

  At this time, the outdoor unit 1 includes an outdoor unit control unit CU as a defrosting control unit that controls the outdoor unit 1. The outdoor unit control unit is mainly composed of a microcomputer including a CPU, a ROM, a RAM, and the like. Based on the control signal SS1 from the main remote controller RM, the frequency of the compressor 7 and the circulation pump 12 The overall control of the outdoor unit 1 such as the number of rotations is performed, and the corresponding control signal SS2 is output to the thermal valve controller CV.

  In the refrigerant circulation circuit 21 configured as described above, the compressor 7 circulates the refrigerant in one direction on the refrigerant sub-path 15b, and controls the circulation direction of the refrigerant on the refrigerant main path 15a by switching the four-way valve 6. To do. FIG. 2A shows the circulation direction during the defrosting operation, and the high-temperature refrigerant discharged from the compressor 7 flows in the order of the outdoor heat exchanger 8, the expansion valve 9, and the water-refrigerant heat exchanger 11. To do. Thereby, after the refrigerant in the gas state sucked at low temperature and low pressure is compressed by the compressor 7 to become high temperature and high pressure gas, it adheres to the surface in the outdoor heat exchanger 8 (functioning as a condenser). Melt the frost. At this time, the air blown by the outdoor fan 10 is controlled to rotate according to the outside air temperature, and changes to a high-pressure liquid while releasing heat to the outside air (frost attached to the outdoor heat exchanger 8). The refrigerant that has become liquid in this manner is decompressed by the expansion valve 9 to become a low-pressure liquid that is easily evaporated. Thereafter, the low-pressure liquid evaporates in the water-refrigerant heat exchanger 11 (functions as an evaporator) and changes into gas, thereby absorbing heat from the cold water from the hot water return pipe 3. Here, if the rotational speed of the circulation pump 12 is increased, the flow rate of the cold water from the hot water return pipe 3 increases and the amount of heat absorption also increases, so that the temperature of the refrigerant passing through the water-refrigerant heat exchanger 11 also increases. Also, the defrosting ability is improved. The refrigerant then returns to the compressor 7 again as a low-temperature and low-pressure gas. Further, if the operating frequency of the compressor 7 is increased, the output is improved and the refrigerant circulation amount is also increased, so that the defrosting ability is improved.

  On the other hand, FIG. 2B shows the circulation direction during the heating operation, and the refrigerant discharged from the compressor 7 flows in the order of the water-refrigerant heat exchanger 11, the expansion valve 9, and the outdoor heat exchanger 8. Thereby, after the refrigerant in the gas state sucked at low temperature and low pressure is compressed by the compressor 7 to become high temperature and high pressure gas, the hot water is supplied in the water-refrigerant heat exchanger 11 (functioning as a condenser). It changes into a high-pressure liquid while releasing heat into the warm water from the return pipe 3. The refrigerant that has become liquid in this manner is decompressed by the expansion valve 9 to become a low-pressure liquid that is easily evaporated. Thereafter, the low-pressure liquid evaporates in the outdoor heat exchanger 8 (functions as an evaporator) and changes into gas, thereby absorbing heat from the outside air. The refrigerant then returns to the compressor 7 again as a low-temperature and low-pressure gas.

  At this time, the hot water heated by the water-refrigerant heat exchanger 11 as described above is supplied from the hot water outlet pipe 2 to the plurality of heat exchange terminals (in the above example, the heating panel 51, the heating panel 52, the floor heating panel). 53), the heat is radiated to the room air to heat the room, and then passes through the cistern tank 13 and returns to the circulation pump 12 again. The circulation pump 12 operates at a rotational speed of about 4,200 rps during normal operation. However, during construction, when the number and capacity of heat exchange terminals are small and the flow resistance is small, the contractor sets the rotational speed during normal operation. Sometimes it is set low. By performing heat exchange between the refrigeration cycle of the refrigerant circuit 21 and the hot water circuit 22 as described above, a heating operation for raising the temperature of the indoor air is performed.

  Next, the main remote controller RM can display the operation state and various setting states of the plurality of heat exchange terminals (in the example shown in FIG. 1, the heating panel 51, the heating panel 52, and the floor heating panel 53). Display unit (not shown), a “power” button (not shown) for turning on / off the main remote control device RM itself, and “operation” for instructing the start of operation of the heat exchange terminal A number of operation buttons such as a button (not shown) and a “timer” button (not shown) for instructing the heat exchange terminal to operate by a timer are provided. Although not shown, the remote controller RM incorporates a CPU as a calculation unit, a memory as a storage unit, and the like for performing various displays.

  Each condition from the start of the defrosting operation to the end of the defrosting and the operation of each component corresponding to each condition will be described with reference to FIGS.

  In the heating operation, the four-way valve 6 is located on the heating side, the R32 refrigerant circulates in the refrigerant circulation circuit 21 in the direction shown in FIG. 2 (b), and during normal heating, depending on the load of the heat exchange terminal, The compressor 7 is continuously variably controlled in the range of 20 Hz to 105 Hz, the outdoor fan 10 is variably controlled in the range of 600 rpm to 800 rpm according to the load, and the expansion valve 9 is also opened according to the load. The circulation pump 12 of the hot water circulation circuit 22 whose (pressure reduction degree) is variably controlled continues to rotate at a constant speed of about 4,200 rpm. In the state where frost is not generated in the outdoor heat exchanger 8, the outdoor heat exchange temperature a is substantially equal to the outside air temperature c. (S1)

  When the outside air temperature b drops below about 5 ° C., frost begins to adhere to the surface of the outdoor heat exchanger 8. When the outside air temperature b falls below freezing point, frost develops rapidly and covers the outdoor heat exchanger 8. Whether the temperature difference c between c and the outdoor heat exchanger temperature a exceeds 8 deg (corresponding to the first predetermined temperature difference c1) is determined (s2). If Yes is greater than 8 deg, the process proceeds to s3. 4 "Defrosting 1" is started, and if it is No or less than 8 deg, return to s1 and continue the heating operation. When the defrosting operation is started in s3, the four-way valve 6 is switched to the cooling side, the outdoor fan 10 is stopped so as not to prevent the defrosting, and the compressor 7 is set to an intermediate frequency of 70 Hz (to the first predetermined frequency e1). Correspondingly, the circulation pump 12 is controlled to be switched to a low speed of 2,000 rpm (corresponding to the first predetermined rotation speed d1) so as not to lower the temperature of the hot water circulation circuit 22 as much as possible, and the defrosting operation is continued.

  Next, the defrost termination condition is determined at s4. If the frost of the outdoor heat exchanger 8 melts and the heat exchange temperature a exceeds 8 ° C. (corresponding to the second predetermined temperature a2) for 60 seconds (corresponding to the third predetermined time t3), the process proceeds to Yes in s11. The defrosting operation ends. If the heat exchange temperature a is 8 ° C. or lower in s4, the process proceeds to s5 in No, and the determination of “condition 1” in FIG. 3 is performed. Determining whether the progress of defrosting is poor, the heat exchange temperature a is lower than 1 ° C. (corresponding to the first predetermined temperature a1), and 7 minutes (corresponding to the first predetermined time t1) have elapsed since the start of defrosting If No, the operation returns to s3 and continues the operation of "defrosting 1". If Yes, the operation proceeds to s6 and switches to the operation of "defrosting 2" in FIG. The defrosting capability is improved and the defrosting time is shortened by increasing the rotation speed to 1,000,000 rpm (second predetermined rotation speed).

  Next, in s7, the defrost termination condition is determined as in s4. If the defrosting termination condition is satisfied, the process proceeds to s11 in Yes to end the defrosting operation, and if No, the process proceeds to s8 and the determination of “condition 2” in FIG. 3 is performed. Determining whether the progress of defrosting is poor, the heat exchange temperature a is lower than 1 ° C. (corresponding to the first predetermined temperature a1), and 10 minutes (corresponding to the second predetermined time t2) have elapsed since the start of defrosting. If No, the operation returns to s6 and continues the operation of "defrosting 2". If Yes, the operation proceeds to s9 to switch to the operation of "defrosting 3" in FIG. By raising the frequency to 80 Hz (corresponding to the second predetermined frequency e2), the defrosting capability is further improved and the defrosting time is shortened, and both the compressor 7 and the circulation pump 12 have a high output and a high rotation speed. The defrosting operation is immediately finished and the heating is restarted to restart the heating, thereby quickly returning the room temperature lowered by the defrosting operation.

  Next, in s10, the defrost termination condition is determined as in s4. If the defrosting termination condition is satisfied, the process proceeds to s11 in Yes to end the defrosting operation. If No, the process returns to s9 and the operation of "defrosting 3" is continued until the defrosting termination condition is satisfied. If it progresses to s11 and a defrost operation is complete | finished, it will return to a normal heating operation in s1.

  As described above, in the hot water heating system of the present embodiment, in order to eliminate the adverse effects resulting from the use of the R32 refrigerant, the defrosting progress after the first predetermined time t1 from the start of the defrosting operation is determined as the heat exchange temperature. When the progress of defrosting is poor, the condensing capacity of the air heat exchanger 8 is improved by increasing the rotation speed of the circulation pump 12 and improving the evaporation capacity of the water heat exchanger 11, By improving the defrosting performance, the defrosting operation can be completed in a short time, and as a result, the comfort of the heating operation is improved.

  Further, the progress of defrosting after the second predetermined time t2 from the start of the defrosting operation is detected by the heat exchange temperature a, and if the progress of defrosting is poor, the frequency of the compressor 7 is further increased. Thus, the condensation capacity is improved, the defrosting performance is further improved, and the long defrosting operation time is finished as soon as possible. And the fall of the comfort of heating operation can be moderated by restarting heating operation at an early stage. Moreover, the fall of the comfort of heating operation can be moderated by detecting the completion | finish by detecting the raise of the heat exchanger temperature a at the time of a defrost operation, and restarting heating operation rapidly.

1 Outdoor unit 6 Four-way valve 7 Compressor 8 Outdoor heat exchanger (air heat exchanger)
8a Heat exchange sensor 9 Expansion valve 10 Outdoor fan 10a Outside air temperature sensor 11 Water-refrigerant heat exchanger (water heat exchanger)
12 Circulating pump 2 Hot water outlet pipe 3 Hot water return pipe 51 Heating panel (heating terminal, heat exchange terminal)
52 Heating panel (heating terminal, heat exchange terminal)
53 Floor heating panel (floor heating terminal, heat exchange terminal)
CU outdoor unit control unit (defrost control means)
RM Main remote control device (remote control device)

Claims (3)

A heat pump device including a compressor for R32 refrigerant, an expansion valve, an air heat exchanger, and a water heat exchanger that receives the supply of the R32 refrigerant from the heat pump device and generates hot water by heat exchange with water. Outdoor unit,
Heating is performed by radiating heat to indoor air using the hot water generated by the water heat exchanger of the outdoor unit and supplied via an inlet pipe, and the hot water after the heat radiating is supplied to the outdoor via a lead-out pipe. A heat exchange terminal that recirculates to the water heat exchanger of the machine with a circulation pump;
A hot water heating system for R32 refrigerant having a remote control device that controls the operating state of the heat exchange terminal in a predetermined control mode, and an outdoor control unit that controls the compressor, the expansion valve, and the like according to a command from the remote control device In
A heat exchange sensor for detecting the temperature of the air heat exchanger and an outside air temperature sensor for detecting the temperature of the outside air are provided,
When the temperature difference c between the heat exchange temperature a detected by the heat exchange sensor and the outside air temperature b detected by the outside air temperature sensor is equal to or greater than a first predetermined temperature difference c1,
The defrosting operation is started, the circulation pump is operated at the first predetermined rotational speed d1, and the compressor is continuously operated at the first predetermined frequency e1.
When the heat exchange temperature a when the first predetermined time t1 has elapsed from the start of the defrosting operation is equal to or lower than the first predetermined temperature a1.
A hot water heating system comprising defrosting control means for changing the rotation speed of the circulation pump to a second predetermined rotation speed d2 larger than the first predetermined rotation speed d1. When the first predetermined time t1 has elapsed from the start of the defrosting operation, the heat exchange temperature a is equal to or lower than the first predetermined temperature a1, and the rotation speed of the circulating pump is greater than the first predetermined rotation speed d1. After changing to, continue the defrosting operation,
When the heat exchange temperature a is equal to or lower than the first predetermined temperature a1 when the second predetermined time t2 larger than the first predetermined time t1 has elapsed since the start of the defrosting operation,
The hot water heating system according to claim 1, further comprising a defrosting control unit that changes the compressor to a second predetermined frequency e2 that is higher than the first predetermined frequency e1. During the defrosting operation, the defrosting operation is terminated and the heating operation is resumed when the heat exchange temperature a continues at a second predetermined temperature a2 higher than the first predetermined temperature a1 for a third predetermined time t3. 3. The hot water heating system according to claim 1, further comprising a control unit.

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