JP6095728B2 - Heat pump equipment - Google Patents

Description

  The present invention relates to a heat pump device that performs heating for heating and heating for hot water supply in parallel.

  In a conventional heat pump device (heat pump unit) that uses geothermal heat for heating and hot water supply (boiling hot water in a hot water storage tank) in parallel, the refrigerant discharged from the compressor is used for heating. It circulates through a plurality of distribution channels corresponding to heating and heating for hot water supply.

  An electromagnetic on-off valve is provided in each branch flow path and opens and closes in response to a heating instruction for heating or a heating instruction for hot water supply from a remote controller or the like by a user operation. Heating for hot water supply is usually performed and finished within a predetermined time of the night in order to operate a compressor, a circulation pump, etc. using inexpensive late-night power.

  In the conventional heat pump device, the refrigerant discharge flow rate of the compressor is further set to the difference between the set temperature and the detected temperature of the heat medium circulating between the heat pump device and the heating device in the heating space (= set temperature−detected temperature). Are controlled accordingly.

  Further, in the temperature and humidity adjusting device of Patent Document 1, the refrigerant discharged from the compressor is divided into two, a heating circuit and a refrigeration circuit, and each branch passage has an expansion valve (opening degree) at its upstream end. A kind of regulating valve) is provided. In the temperature / humidity adjusting device, when the opening degree of one of the expansion valves is changed, the refrigerant flow rate of the corresponding branch flow path is changed, and the ratio of the flow rate of the refrigerant divided into the heating circuit and the refrigeration circuit is also changed. Will do.

Japanese Patent No. 5634982

  In the conventional heat pump device, the electromagnetic on-off valve of each branch flow path simply opens and closes according to the execution and stop of heating for heating and heating for hot water supply, so in the parallel execution period of heating for heating and heating for hot water supply, The distribution ratio of the refrigerant flow rate between the branch channels is fixed.

  When heating for heating and heating for hot water supply are performed in parallel, the refrigerant flow rate corresponding to the heating demand for heating for heating changes according to changes in the set temperature for heating for heating or changes in the temperature of the heating medium. To do. Therefore, in the conventional heat pump apparatus in which the refrigerant discharge flow rate of the compressor is controlled in accordance with the heating heating requirement and the distribution rate of the refrigerant flow rate between the respective flow paths is fixed, the heating heat supply heating temperature is changed depending on the operation state. The refrigerant flow rate in the shunt channel may be insufficient. If the shortage period is prolonged, boiling of hot water in the hot water storage tank will be delayed and will not be completed during the midnight power period.

  In addition, there exists an upper limit in the circulating flow volume of hot water from the diameter of the piping which comprises the circulation path which circulates hot water between a hot water storage tank and a heat pump apparatus, and the performance of a circulation pump. Therefore, to prevent the refrigerant flow rate in the branch flow path for hot water supply from becoming insufficient during the boiling period of hot water, it is necessary to control the refrigerant discharge flow rate higher than the upper limit of the refrigerant flow rate in the flow path for hot water supply heating. The time for operating the compressor at the discharge flow rate including the minute increases. This increases wasteful power consumption.

  Therefore, as in Patent Document 1, an expansion valve is provided in each branch flow path, and the distribution ratio of the refrigerant flow rate between the respective flow paths is appropriately set in accordance with each heating request of heating for heating and heating for hot water supply at each time point. It is conceivable to control it.

  However, since the volume of the heating space and the capacity of the hot water storage tank vary depending on the situation where the heat pump device is installed, it is difficult to accurately grasp the heating required amount of the heating space and the hot water storage tank at each time point. Accordingly, it is also impossible to calculate the distribution ratio of the refrigerant flow rate in the branch flow path for heating for heating and hot water supply, which is determined according to the ratio of the required heating amount of the heating space or hot water storage tank. Since the opening control of the expansion valve must be performed according to the calculated distribution rate, the fact that the distribution rate cannot be calculated appropriately means that the refrigerant flow rate in each branch flow path is heated by the opening control of the expansion valve. It means that it cannot be controlled to the flow rate according to each heating requirement of heating for heating and heating for hot water supply.

  The object of the present invention is to supply refrigerant to the heating space and the hot water storage tank at an appropriate flow rate according to the required heating amount at each time point, even if the volume of the heating space and the capacity of the hot water storage tank vary depending on the installation situation. It is to provide a heat pump device that can.

The heat pump device of the present invention is
A refrigerant circulation path including a first branch flow path and a second branch flow path connected in parallel with each other, and having a refrigerant sealed therein;
A compressor that is provided in the middle of the refrigerant circulation path, compresses the refrigerant on the upstream side, and discharges the refrigerant on the downstream side;
A heat exchanger for heating that exchanges heat between a heat medium that circulates through a heating circulation path that passes through a heating device and a refrigerant that circulates through the first branch flow path;
A hot water supply heat exchanger for exchanging heat between hot water flowing through the hot water tank circulation path passing through the hot water storage tank and the refrigerant flowing through the second branch flow path;
A refrigerant heating unit for heating the refrigerant before being sucked into the compressor in the refrigerant circulation path;
An opening degree adjusting valve disposed in the first branch path or the second branch path and having an adjustable opening degree;
A temperature detector for the forward heat medium that detects the temperature of the forward heat medium that travels from the heating heat exchanger to the heating equipment in the heating circuit;
When the compressor is operated and heat exchange is performed by the heat exchanger for heating and the heat exchanger for hot water supply, the opening of the opening adjustment valve is set with respect to the current discharge flow rate of the compressor. The first process of changing the flow rate of the refrigerant in the second branch channel to an opening degree that can secure the set heating amount of the hot water in the hot water supply heat exchanger, the set temperature set for the outgoing heat medium, and the outgoing heat medium And alternately performing a second process of changing the refrigerant discharge flow rate of the compressor so that the absolute value of the difference from the current detected temperature detected by the forward-side heat medium temperature detector decreases, and During the execution of the first process, the discharge flow rate of the compressor is fixed to the discharge flow rate at the previous end of the second process, and during the second process, the opening degree of the opening adjustment valve is set to the first flow rate. With a processing control unit that fixes the opening at the end of the previous processing It is characterized in.

  According to the present invention, in the first process, the opening of the opening adjustment valve is set to the current discharge flow rate of the compressor while the discharge flow rate of the compressor is fixed to the discharge flow rate at the previous end of the second process. On the other hand, the refrigerant flow rate in the second branch passage is changed to an opening degree that can secure the set heating amount of hot water in the hot water supply heat exchanger. In the second process, while the opening of the opening adjustment valve is fixed at the opening at the previous end of the first process, the refrigerant discharge flow rate of the compressor is the set temperature of the forward heat medium and the forward heat medium. The absolute value of the difference from the current detected temperature detected by the industrial temperature detector is changed.

  That is, in the first process, the refrigerant flow rate in the second branch channel is changed so as to be optimized to a value corresponding to the required amount of heating for hot water supply without considering the refrigerant flow rate in the first branch channel. . On the other hand, by performing this first process, the refrigerant flow rate in the first branch channel deviates from an appropriate value corresponding to the required amount of heating for heating. This deviation is reflected in the difference between the set temperature of the outgoing heat medium and the current detected temperature for the outgoing heat medium heading to the heating device.

  In the second process, the refrigerant discharge flow rate of the compressor is changed so that the absolute value of the difference between the set temperature of the forward side heat medium and the current detected temperature is reduced for the forward side heat medium toward the heating device. . This change not only returns the refrigerant flow rate of the first branch flow path to an appropriate value according to the required amount of heating for heating, but also the first branch flow path and the second branch flow path under the current opening of the opening adjustment valve. The total excess and deficiency of the refrigerant flow is also alleviated. That is, the second process also has a function of appropriately correcting the excess or deficiency of the refrigerant flow rate in the entire heat pump apparatus. This means that the refrigerant flow rate in the second branch channel is closer to the current value corresponding to the required amount of heating for hot water supply than the refrigerant flow rate at the previous start of the first process.

  The first process subsequent to the second process is performed in response to the fact that the refrigerant flow rate in the second branch channel has approached the corresponding value of the current required amount of heating for hot water supply from that at the previous start of the first process. The Therefore, by the current execution of the first process, the refrigerant flow rate in the second branch channel is closer to the corresponding value of the current required amount of heating for hot water supply than during the previous execution of the first process.

  In this way, the first treatment and the second treatment are alternately performed repeatedly, and the refrigerant flow rates in the first branch passage and the second branch passage match the required heating heating amount and the required hot water heating amount, respectively. Converge to or close enough to

  As described above, according to the present invention, with respect to the simple first process that only optimizes the refrigerant flow rate in the second branch flow path, and the outgoing side heat medium that goes to the heating device, the set temperature of the outgoing side heat medium and the current A simple second process that simply changes the refrigerant discharge flow rate of the compressor so as to reduce the absolute value of the difference from the detected temperature is alternately repeated. Thus, even if the space of the heating space and the capacity of the hot water storage tank vary depending on the installation status of the heat pump device, the heating space and the hot water storage tank respond to the heating request amount at each time point after the predetermined time has elapsed. The refrigerant can be supplied at an appropriate flow rate.

In the heat pump device of the present invention,
The refrigerant heating unit is a heat collecting heat exchanger that exchanges heat between the refrigerant before being sucked into the compressor in the refrigerant circulation path and a predetermined heat collecting medium,
In the first process, the process control unit is configured to perform the second diversion with respect to the current discharge flow rate of the compressor as the temperature of the heat collecting medium on the heat collecting medium inlet side of the heat collecting heat exchanger increases. It is preferable to change the opening degree of the opening degree adjusting valve so that the ratio of the refrigerant flow rate in the passage becomes small.

  When the heat collecting medium passes through the heat collecting heat exchanger at a constant flow rate, the higher the temperature of the heat collecting medium at the heat collecting medium inlet side of the heat collecting heat exchanger, the heat collecting heat. The temperature of the refrigerant after heat exchange with the heat collecting medium in the exchanger rises, and the heat flow rate of the refrigerant discharged from the compressor increases. According to this configuration, the higher the temperature of the heat collecting medium on the heat collecting medium inlet side of the heat collecting heat exchanger, the smaller the ratio of the refrigerant flow rate in the second branch channel to the current discharge flow rate of the compressor. Thus, by changing the opening degree of the opening degree adjusting valve, it is possible to appropriately match the refrigerant flow rate of the second branch flow path with the flow rate required for heating for hot water supply in the first process.

  In the heat pump device of the present invention, in the first process, the process control unit is configured such that the higher the temperature of the hot water at the hot water inlet side of the hot water supply heat exchanger, the higher the temperature of the hot water at the discharge flow rate of the compressor. It is preferable to change the opening degree of the opening degree adjusting valve so that the ratio of the refrigerant flow rate in the passage becomes small.

  The higher the temperature of the hot water flowing into the hot water supply heat exchanger, the smaller the amount of heat exchange required to bring the hot water to the set temperature in the hot water supply heat exchanger. According to this configuration, the opening degree adjustment valve is configured such that the higher the temperature of the hot water on the hot water inlet side of the hot water supply heat exchanger, the smaller the ratio of the refrigerant flow rate in the second branch flow path to the current discharge flow rate of the compressor. By changing the opening degree, the refrigerant flow rate of the second branch channel can be appropriately adjusted to the flow rate required for hot water heating in the first process.

The heat pump device of the present invention is preferably
A third branch channel connected in parallel to both the first branch channel and the second branch channel;
A desiccant disposed across an air supply passage for guiding outdoor air to the indoor heating space and an exhaust passage for discharging the air in the indoor heating space to the outside;
A condenser that is disposed upstream of the desiccant in the air supply passage, and that heats the air before passing through the desiccant by the refrigerant in the third branch channel;
A first regulating valve disposed on the downstream side of the condenser in the third branch channel and having an adjustable opening;
A second regulating valve disposed on the upstream side of the condenser in the third branch channel and having an adjustable opening;
An evaporator disposed upstream of the desiccant in the exhaust passage and configured to cool the air before passing through the desiccant with a refrigerant in a third branch passage that has passed through the first adjustment valve;
The processing control unit
The refrigerant temperature on the refrigerant outlet side of the condenser is adjusted after the opening of the first adjustment valve is adjusted so that the refrigerant temperatures on the refrigerant inlet side and the refrigerant outlet side of the evaporator are within the first target temperature range. Performing a third process for adjusting the opening of the second adjustment valve so as to be within the second target temperature range;
The three processes of the first process, the second process and the third process are repeatedly performed in a predetermined order,
During the execution of the first process, the discharge flow rate of the compressor is fixed to the discharge flow rate at the previous end of the second process, and the opening degree of the first adjustment valve and the second adjustment valve is set to the third process. Fixed at the opening at the previous end of
During the execution of the second process, the opening of the opening adjustment valve is fixed to the opening at the previous end of the first process, and the opening of the first adjustment valve and the second adjustment valve is set to the first. 3 Fix the opening at the end of the previous process,
During the execution of the third process, the opening of the opening adjustment valve is fixed to the opening at the previous end of the first process, and the discharge flow rate of the compressor is the same as that at the previous end of the second process. Fix the discharge flow rate.

  According to this configuration, the first process, the second process, and the third process are repeatedly performed in a predetermined order. During the execution of each process, the opening of the opening adjustment valve, the discharge flow rate of the compressor, or the first adjustment valve and the second adjustment valve performed in the other two processes that have been stopped. The opening is fixed to a value at the previous end of the other two processes, and each process is performed.

  That is, in the first process and the third process, the refrigerant flow rates in the second branch flow path and the third branch flow path are the required amounts of heating for hot water supply and desiccant control without considering the refrigerant flow rate in the first branch flow path. To be optimized to a value according to On the other hand, by performing the first process and the third process, the refrigerant flow rate in the first branch flow path deviates from an appropriate value according to the required amount of heating for heating. This deviation is reflected in the difference between the set temperature of the outgoing heat medium and the current detected temperature for the outgoing heat medium heading to the heating device.

  In the second process, the refrigerant discharge flow rate of the compressor is changed so that the absolute value of the difference decreases. This change not only returns the refrigerant flow rate in the first branch flow path to an appropriate value corresponding to the required amount of heating for heating, but also reduces the current opening degree of the opening adjustment valve, the first adjustment valve, and the second adjustment valve. Thus, the excess and deficiency of the total refrigerant flow in the first branch path, the second branch path, and the third branch path is also alleviated. That is, the second process also has a function of appropriately correcting the excess or deficiency of the refrigerant flow rate in the entire heat pump apparatus. This is because the refrigerant flow rates in the second and third flow paths are higher than the refrigerant flow rates at the previous start of the first process and the third process, and the respective required amounts of heating for hot water supply and heating for desiccant control. It means that the corresponding value of was approached.

  In the first process and the third process following the second process, the coolant flow rates in the second branch path and the third branch path are higher than those at the previous start of the first process and the third process, and the current heating and desiccant control. It is implemented in response to the fact that it has approached the corresponding value of the required heating amount. Therefore, due to the current execution of the first process and the third process, the refrigerant flow rates in the second branch path and the third branch path are higher than those in the previous execution of the first process. Approaches the corresponding value of each requested quantity.

  Thus, the first process, the second process, and the third process are repeated in a predetermined order, and the refrigerant flow rates in the first branch path, the second branch path, and the third branch path are for heating for heating and hot water supply, respectively. It converges or approaches sufficiently to a value that matches the required amount of heating and heating for desiccant control.

  As described above, according to this configuration, in addition to the simple first process and the second process, the simple third process only for optimizing the refrigerant flow rate in the third branch flow path is added, and the execution is performed. It has only been repeated. Thus, even if the space of the heating space and the capacity of the hot water storage tank vary depending on the installation state of the heat pump device, after the predetermined time has elapsed, the heating request amount at each time point of the desiccant is determined together with the heating space and the hot water storage tank. The refrigerant can be supplied at an appropriate flow rate.

The block diagram of a geothermal heat pump system. The block diagram of a heat pump apparatus. The block diagram of a desiccant apparatus. The functional block diagram of a heat pump apparatus. The flowchart of the whole heating operation control. The flowchart of hot water supply distribution rate control. The flowchart of desiccant control. The flowchart of compressor control.

  FIG. 1 is a configuration diagram of a geothermal heat pump system 1. In FIG. 1 and FIG. 2 described later, Z1 to Z8 indicate that the same reference numerals are in the same location.

  The geothermal heat pump system 1 includes a heat pump device (heat pump unit) 2, an underground heat collecting unit 3, a desiccant device 4, a hot water storage tank unit 5, and a floor heating device 6. The heat pump device 2 and the hot water storage tank unit 5 are disposed outdoors or indoors in the house 10. The desiccant device 4 and the floor heating device 6 are disposed in the house 10.

  The underground heat collecting unit 3 employs a U-tube system including a forward-side heat collecting tube 8 and a return-side heat collecting tube 9. The forward-side heat collection pipe 8 and the return-side heat collection pipe 9 are vertically lowered to a predetermined depth in the underground 12 below the ground 11 and are connected to each other at the lowermost end. The forward-side heat collecting pipe 8 and the return-side heat collecting pipe 9 constitute a part of a heat collecting medium circulation path 85 through which a heat collecting medium (specifically, water containing antifreeze liquid) flows. The heat collecting medium is guided from the heat pump device 2 to the outgoing side heat collecting tube 8, folded back at the lowermost end of the outgoing side heat collecting tube 8, enters the return side heat collecting tube 9, passes through the return side heat collecting tube 9, and passes through the heat pump device 2. Return to.

  The hot water storage tank unit 5 includes a hot water storage tank 15 that stores hot water 16. The hot water storage tank 15 is connected to conduits 19 to 22. The conduits 19 and 20 constitute a part of a hot water storage circuit 89 serving as a hot water tank circulation path. The circulation pump P3 is disposed in the conduit 20. The hot water 16 in the hot water storage tank 15 circulates in the hot water storage circuit 89 by the operation of the circulation pump P3. The drive, stop, and rotation speed of the circulation pump P3 are controlled by the control board 97 (FIG. 2). Note that the rotational speed of the circulation pump P3 and the circulating flow rate of the hot water 16 in the hot water circulating circuit 89 are proportional to each other (circulating flow rate ∝ rotational speed).

  In FIG. 1, A1 shows the flow direction of the tap water (makeup water) supplied from the conduit 22 to the hot water storage tank 15, and A2 shows the hot water terminal 16 in the house 10 where the hot water 16 in the hot water storage tank 15 passes through the conduit 21. The direction of flow to Examples of the hot water outlet terminal in the house 10 include a hot water tap and shower of a bathtub in a bathroom, and a hot water tap of a kitchen.

  The bypass pipe 26 connects the conduit 21 and the conduit 22. The mixing device 27 is disposed at a connection point of the bypass pipe 26 to the conduit 21 and adjusts the mixing ratio between the tap water from the bypass pipe 26 and the hot water 16 from the hot water storage tank 15, and then the hot water outlet terminal. Lead towards.

  The floor heating device 6 is an example of a heating device that uses hot water as a heat medium, and is laid on the floor of a predetermined room in the house 10. In addition to the floor heating device 6, there are a panel heater, a fan coil unit, and the like in the hot water heating device used in the house 10.

  The conduits 29 and 30 are connected to the floor heating device 6, and the conduits 29 and 30 together with heat-dissipating hot water pipes embedded in the floor heating device 6 serve as heat as a heating circulation path via the floor heating device 6. A part of the medium circulation path 92 is formed. A circulation pump P2 (FIG. 2) is disposed in the heat medium circulation path 92, and a predetermined heat medium (specifically, water containing antifreeze liquid) circulates in the heat medium circulation path 92 by the operation of the circulation pump P2. The predetermined heat medium dissipates heat in the floor heating device 6 and warms the heating space when passing through the floor heating device 6.

  The desiccant device 4 is disposed near the wall in the house 10. A3 and A4 in FIG. 1 respectively show the flow of air supply from the outdoor to the indoor heating space and the flow of exhaust from the indoor heating space to the outdoor performed through the desiccant device 4.

  This heat pump device 2 is used for heating, cooling and hot water supply. The use in hot water supply can be performed simultaneously with the use for heating and the use for cooling. During the period in which the heat pump device 2 is operating for heating (hereinafter referred to as “heating operation period”), the heat medium heated by the heat pump device 2 circulates in the heat medium circulation path 92 and serves as a floor heating device as a terminal. 6 radiates heat. On the other hand, during the period in which the heat pump device 2 is operating for cooling (hereinafter referred to as “cooling operation period”), the heat medium cooled by the heat pump device 2 circulates in the heat medium circulation path 92, and the cooling terminal Endothermic is performed at (not shown). During a period in which the heat pump device 2 is operating for hot water supply (hereinafter referred to as “hot water supply operation period”), the hot water 16 in the hot water storage tank 15 circulates in the hot water storage circuit 89 and is heated by the heat pump device 2 at that time. After that, it returns to the hot water storage tank 15.

  The desiccant device 4 humidifies the air-conditioned space (heating space) during the heating operation period of the heat pump device 2, and dehumidifies the air-conditioned space (cooling space) during the cooling operation period of the heat pump device 2.

  The desiccant device 4 is connected to conduits 33 and 34. The conduits 33 and 34 constitute a part of the branch flow path 58 so that the refrigerant circulates. The detailed configuration of the desiccant device 4 will be described later with reference to FIG.

  FIG. 2 is a configuration diagram of the heat pump device 2. The compressor 50 is connected to the suction flow path 51 and the discharge flow path 52 on the suction side and the discharge side, respectively, and is rotationally driven by a three-phase induction motor 53 (FIG. 4) to compress the refrigerant in the suction flow path 51. It discharges to the discharge flow path 52. The refrigerant discharge flow rate from the compressor 50 is proportional to the drive rotation speed of the compressor 50 by the three-phase induction motor 53, and the drive rotation speed is supplied from the inverter (not shown) to the three-phase induction motor 53. Is controlled by the frequency F. Therefore, there is a proportional relationship between the refrigerant discharge flow rate from the compressor 50 and the frequency F (the refrigerant discharge flow rate ∝ frequency F from the compressor 50).

  The four-way switching valve 55 has ports 55a, 55b, 55c, and 55d. The discharge flow path 52 is connected to the port 55a, the combined flow path 57 is connected to the port 55b, the suction flow path 51 is connected to the port 55c, and the combined flow path 64 is connected to the port 55d.

  In the four-way switching valve 55, the rotational position of the valve body is switched by a control signal from the control board 97 (FIG. 4). The connection state between the ports of the four-way switching valve 55 shown in FIG. 2 and the flow direction indicated by “→” for the refrigerant indicate those during the heating operation period.

  At the rotational position of the valve body of the four-way switching valve 55 during the heating operation period of the heat pump device 2, the port 55a and the port 55b are connected, and the port 55c and the port 55d are connected. At the rotational position of the valve body of the four-way switching valve 55 during the cooling operation period of the heat pump device 2, the port 55a and the port 55d are in a connected state, the port 55b and the port 55c are in a connected state, and the refrigerant is in a heating operation period. Circulates in the opposite direction.

  The desuperheater 56 is disposed in the discharge flow path 52 and heats the hot water 16 in the hot water storage water circulation path 89 by using heat radiation when the refrigerant compressed by the compressor 50 changes from superheated steam to saturated steam. . The refrigerant in the combined flow path 57 is divided into the divided flow paths 58, 59, and 60 and merged again in the combined flow path 64.

  The suction flow path 51, the discharge flow path 52, the combined flow path 57, the branch flow paths 58, 59, 60, and the combined flow path 64 constitute a refrigerant circulation path in which a predetermined refrigerant is enclosed and circulated. The branch channels 58, 59, and 60 correspond to the third branch channel, the first branch channel, and the second branch channel of the present invention, respectively, and a part of the refrigerant circuit is formed as a plurality of branch channels connected in parallel to each other. Configure.

  In the branch flow path 58, an expansion valve Ex4 is disposed at the upstream end portion, and an expansion valve Ex5 is disposed at the downstream end portion. The expansion valve Ex such as the expansion valve Ex4 is an opening degree adjustment valve whose opening degree can be adjusted stepwise by a step motor (not shown). For example, 481 stages of 0 to 480 steps are set as the stage of opening. Full expansion of the expansion valve Ex corresponds to 0 step, and full expansion of the expansion valve Ex corresponds to 480 step.

  In the branch channel 59, an expansion valve Ex6, a heat exchanger 70, and an expansion valve Ex1 are arranged in order in the refrigerant flow direction. The electromagnetic on-off valve Mv1 is connected in parallel to the expansion valve Ex6. The electromagnetic open / close valve Mv such as the electromagnetic open / close valve Mv1 can be switched only between two positions of fully open (open position) and fully closed (closed position), and is opened at an intermediate position between fully open and fully closed like the expansion valve Ex. The degree cannot be set.

  In the heating operation period, the heat exchanger 70 in the branch channel 59 functions as a condenser. The heat medium in the heat medium circulation path 92 is circulated by the circulation pump P <b> 2 in the heat medium circulation path 92 and is heated by heat exchange with the refrigerant in the branch flow path 59 in the heat exchanger 70.

  The temperature sensors S3 and S4 are disposed on the outlet side and the inlet side of the heat medium with respect to the heat exchanger 70 in the heat medium circuit 92, respectively. The temperature sensor S such as the temperature sensor S3 is composed of a thermistor and detects the temperature of the heat medium or the like at the arrangement site.

  In the branch path 60, an electromagnetic on-off valve Mv2, a heat exchanger 74, and an expansion valve Ex2 are arranged in order in the refrigerant flow direction during the heating operation period.

  The heat exchanger 74 of the diversion channel 60 acts as a condenser during the heating operation period and the hot water supply operation period, and heats the hot water 16 that circulates in the stored hot water circulation path 89. 1, together with the conduits 19 and 20 of FIG. 1, constitute a circulation path of the hot water 16 that circulates between the hot water storage tank 15 and the desuperheater 56 and the heat exchanger 74 of the heat pump device 2.

  The hot water 16 in the hot water storage tank 15 is circulated through the hot water storage circuit 89 in the order of the conduit 20, the heat exchanger 74, the desuperheater 56, and the conduit 19 by the operation of the circulation pump P3 (FIG. 1). Return to tank 15. When the hot water 16 passes through the heat exchanger 74 and the desuperheater 56, it is heated by the refrigerant on the refrigerant circuit side.

  The temperature sensor S 5 detects the temperature of the hot water 16 on the return side from the hot water storage tank 15 in the hot water circulation path 89 of the hot water 16, and the temperature sensor S 6 is on the return side of the hot water 16 to the hot water storage tank 15 in the hot water circulation path 89. The temperature of the hot water 16 is detected.

  In the combined flow path 64, a heat exchanger 77 and an expansion valve Ex7 are disposed in order from the upstream side. The electromagnetic on-off valve Mv3 is connected in parallel to the expansion valve Ex7. During the heating operation period of the heat pump device 2, the electromagnetic on-off valve Mv3 is in the open position, and the heat exchanger 77 is used as an evaporator. The amount of refrigerant evaporated in the heat exchanger 77 is adjusted by adjusting the opening degree of the expansion valves Ex1 and Ex2.

  The downstream end of the branch flow path 58 is connected to the downstream side of the expansion valve Ex7 in the combined flow path 64, and the downstream ends of the flow paths 59 and 60 are connected to the upstream side of the heat exchanger 77 in the combined flow path 64.

  The circulation pump P <b> 1 is disposed on the outlet side of the heat collecting medium with respect to the heat exchanger 77 in the heat collecting medium circulation path 85, and circulates the heat collecting medium to the heat collecting medium circulation path 85. The temperature sensors S1 and S2 are arranged on the outlet side and the inlet side of the heat collecting medium with respect to the heat exchanger 77 in the heat collecting medium circulation path 85, respectively, and detect the temperature of the heat collecting medium at the arrangement site. To do.

  The control board 97 includes a microprocessor and other related elements necessary for executing the control program of the heat pump apparatus 2. The detailed configuration of the control board 97 will be described later with reference to FIG.

  FIG. 3 is a configuration diagram of the desiccant device 4. The desiccant device 4 includes an outdoor suction port 101 and an outdoor exhaust port 102 communicating with the outside of the house 10, and an indoor suction port 103 and an indoor space communicating with a predetermined room as an air-conditioned space (heating space or cooling space) in the house 10. And a discharge port 104.

  The supply passage 108 communicates the outdoor suction port 101 and the indoor discharge port 104. The exhaust passage 109 connects the outdoor exhaust port 102 and the indoor intake port 103. The blower fan 110 is disposed in the vicinity of the indoor discharge port 104 of the air supply passage 108, sucks outside air from the outdoor suction port 101, and supplies it to the room from the indoor discharge port 104. The blower fan 111 is disposed in the vicinity of the outdoor exhaust port 102 of the exhaust passage 109, sucks indoor air from the indoor suction port 103, and discharges the air from the outdoor exhaust port 102 to the outdoors.

  The desiccant device 4 includes a total heat exchanger 112. The total heat exchanger 112 performs heat exchange between the air at the upstream end portion of the air supply passage 108 and the air at the upstream end portion of the exhaust passage 109, and supplies air in the air supply passage 108 during the heating operation period. The air is heated by the exhaust air in the exhaust passage 109.

  The temperature / humidity sensor Na is disposed at the inlet of the total heat exchanger 112 in the supply passage 108, and the temperature / humidity sensor Nb is disposed at the inlet of the total heat exchanger 112 in the exhaust passage 109. The temperature / humidity sensor Nc is disposed at the outlet of the total heat exchanger 112 in the supply passage 108, and the temperature / humidity sensor Nd is disposed at the outlet of the total heat exchanger 112 in the exhaust passage 109.

  The temperature / humidity sensors Na to Nd detect the temperature and humidity of the air at each location. The dew point temperature of the supply air can be obtained from the air temperature Ta and humidity Ma of the temperature / humidity sensor Na or the air temperature Tc and humidity Mc of the temperature / humidity sensor Nc. The dew point temperature of the exhaust gas can be obtained from the air temperature Tb and humidity Mb of the temperature / humidity sensor Nb or the air temperature Td and humidity Md of the temperature / humidity sensor Nd.

  The desiccant 114 is formed in a circular plate shape, and is mounted on the desiccant device 4 so that the semicircular portions are located in the air supply passage 108 and the exhaust passage 109, respectively. The desiccant 114 is rotatable, and a semicircular portion located in the air supply passage 108 and a semicircular portion located in the exhaust passage 109 are alternately switched by rotation of 180 °. When the desiccant 114 is used for humidification, the amount of moisture adsorbed in the semicircular part located in the exhaust passage 109 becomes saturated, or the amount of adsorbed moisture in the semicircular part located in the air supply passage 108 falls below a predetermined threshold. When low, the desiccant 114 is rotated 180 °.

  The condensers 120 and 121 are disposed in the air supply passage 108 so as to sandwich the semicircular portion of the desiccant 114 from the downstream side and the upstream side, respectively, in the flow direction of the air supply. The evaporators 123 and 124 are disposed in the exhaust passage 109 so as to sandwich the semicircular portion of the desiccant 114 from the downstream side and the upstream side in the exhaust flow direction, respectively.

  In the heating operation period of the heat pump device 2, the refrigerant in the branch flow path 58 passes through the condensers 120 and 121, the expansion valve Ex3, and the evaporators 123 and 124 in this order. In the cooling operation period of the heat pump device 2, the flow direction of the refrigerant in the branch flow path 58 is reversed from that in the heating operation period, the condensers 120 and 121 function as an evaporator, and the evaporators 123 and 124 are condensers. Acts as

  The temperature sensors S7 and S8 are disposed at the inlet portion and the outlet portion of the branch flow path 58 from the condenser 121 disposed on the upstream side with respect to the desiccant 114 in the air supply passage 108, and the refrigerant temperatures at those portions. Is detected. The temperature sensors S9 and S10 are arranged at the inlet part and the outlet part of the diversion channel 58 from the evaporator 124 arranged upstream of the desiccant 114 in the exhaust passage 109, and the refrigerant temperatures at those parts are measured. To detect.

  FIG. 4 is a control block diagram of the heat pump device 2. The control board 97 is mounted with a microprocessor (not shown) that executes a program for causing the heat pump device 2 to perform heating operation control and cooling operation control.

  The control board 97 controls the expansion valves Ex1 to Ex7, the electromagnetic on-off valves Mv1 to Mv3, the circulation pumps P1 to P3, and the three-phase induction motor 53 based on inputs from the temperature sensors S1 to S10 and the temperature and humidity sensors Na to Nd. To do. Hereinafter, the temperatures detected by the temperature sensors S1 to S10 are represented by temperatures T1 to T10. The temperatures detected by the temperature and humidity sensors Na to Nd are represented by Ta to Td, and the humidity detected by the temperature and humidity sensors Na to Nd is represented by Ma to Md. Moreover, the opening degree of expansion valve Ex1-Ex7 is represented by O1-O7.

  The control board 97 is a functional part generated when a microprocessor (not shown) of the control board 97 executes a predetermined control program, and includes an on-board element control unit 131, a compressor control unit 132, and an expansion valve control unit. 133, an electromagnetic on-off valve control unit 134 and a pump control unit 135 are provided. The microprocessor receives an input signal via an input port or an A / D converter (not shown), and outputs an output signal via an output port or a D / A converter (not shown).

  The in-substrate element control unit 131 exchanges signals with the compressor control unit 132, the expansion valve control unit 133, the electromagnetic on / off valve control unit 134, and the pump control unit 135 as in-substrate elements, and these in-substrate elements Control the operation and stop of the. The in-substrate element control unit 131 further includes a process control unit 141.

  The compressor control unit 132 controls the rotational speed of the compressor 50 through frequency control of the three-phase induction motor 53. The expansion valve control unit 133 controls the opening degree of the expansion valves Ex1 to Ex7, and further includes a hot water supply distribution rate control unit 145 and a desiccant control unit 146. The electromagnetic on / off valve control unit 134 controls the opening / closing of the electromagnetic on / off valves Mv1 to Mv3. The pump control unit 135 controls the operation of the circulation pumps P1 to P3.

  The heat pump device 2 includes a remote controller (not shown) and an operation unit (not shown) arranged on the main body. The user operates the remote controller or the operation unit provided on the main body to give various instructions to the heat pump device 2. The user's instruction includes start and end of operation of the heat pump device 2, switching between heating operation and cooling operation, and the set temperature of the heat medium sent to the heating device (temperature sensor S3 in FIG. There are settings such as the set temperature of the part of the detector.

  Next, heating operation control performed by the microprocessor of the control board 97 during the heating operation period of the heat pump device 2 will be described with reference to the flowcharts of FIGS. The heating operation period of the heat pump device 2 and the period during which the microprocessor of the control board 97 performs the heating operation control are the same. FIG. 5 is a flowchart of the entire heating operation control. The heat exchanger 70 corresponds to the heating heat exchanger of the present invention, and the heat exchanger 77 corresponds to the heat collecting heat exchanger of the present invention.

  In this heating operation control, the electromagnetic on-off valve Mv2 is set to the open position, and the heat pump device 2 heats the hot water 16 in the hot water storage tank 15 together. That is, during the execution of the heating operation control, it is a heating operation period and a hot water supply operation period. When the hot water supply operation by the heat pump device 2 is stopped during the heating operation period, the electromagnetic on-off valve Mv2 is switched to the closed position.

  In this heating operation control, since the hot water supply operation is also performed, the electromagnetic on-off valve Mv2 is maintained at the open position, and the electromagnetic on-off valve Mv1 is maintained at the closed position, so that the opening degree adjustment of the expansion valve Ex6 is enabled. The Further, the expansion valve Ex5 is kept fully open in order to make the adjustment of the opening degree of the expansion valve Ex4 effective.

  The processing control unit 141 determines whether or not the execution condition of the heating operation control is satisfied in STEP1. Specifically, for example, the processing control unit 141 must instruct the heat pump device 2 to start the heating operation via the remote controller (not shown) and then instruct the end of the heating operation. If it is determined that the execution condition for the heating operation control is satisfied. Further, if the user has not yet instructed the start of the heating operation or has instructed the end of the heating operation, it is determined that the execution condition of the heating operation control is not satisfied. Note that the heating operation control period and the heating operation period of the heat pump device 2 are the same.

  In STEP2, the process control unit 141 causes the hot water supply distribution rate control unit 145 to perform hot water supply distribution rate control. The hot water supply distribution ratio Bc is defined as the ratio (= Qc / Q) of the diversion flow rate Qc of the diversion channel 60 to the total flow rate Q of the refrigerant discharged from the compressor 50. In STEP3, the process control unit 141 causes the desiccant control unit 146 to perform desiccant control. In STEP4, the process control unit 141 causes the compressor control unit 132 to perform compressor control. The process control unit 141 returns the process to STEP 1 after STEP 4 ends.

  That is, the process control unit 141 includes a first process as a hot water supply rate control by the hot water supply rate control unit 145 in STEP 2, a second process as a compressor control by the compressor control unit 132 in STEP 4, and a desiccant control unit in STEP 3. Three processes of the 3rd process as desiccant control by 146 are implemented repeatedly. Of these three processes, while one process is being performed, the other two processes are completely stopped, and the change value of the processing target of each process is fixed until the next restart of the process. The

  Specifically, the processing control unit 141 sets the opening degree of the expansion valves Ex3, Ex4 to the opening degree at the end of the previous execution of the desiccant control (STEP3) during the hot water supply distribution rate control (STEP2). The discharge flow rate of the compressor 50 is fixed to the discharge flow rate at the previous end of the compressor control (STEP 4). During the execution of the compressor control (STEP 4), the processing control unit 141 fixes the opening degree of the expansion valve Ex6 to the opening degree at the previous end of the hot water supply distribution rate control (STEP 2), and controls the expansion valves Ex3, Ex4. The opening is fixed to the opening at the previous end of the desiccant control (STEP 3). During the execution of the desiccant control (STEP 3), the processing control unit 141 fixes the opening of the expansion valve Ex6 to the opening at the previous end of the hot water supply distribution rate control (STEP 2), and the discharge flow rate of the compressor 50 is fixed. The discharge flow rate is fixed at the previous end of the compressor control (STEP 4).

  In the flowchart of FIG. 5, the next STEP is started immediately after the execution of each STEP, but it is preferable to provide an appropriate pause time between the STEPs. That is, in STEP 2 to 4, the opening degree O 6 of the expansion valve Ex 6, the opening degree O 4 of the expansion valve Ex 4, and the rotational speed of the compressor 50 are changed. It takes time until the refrigerant partial flow rate and refrigerant discharge flow rate, which are the basis for calculating the change value (opening O6 value, etc.) of the change target (expansion valve Ex6 opening degree O6, etc.) reach a steady value (until it reaches a steady value) Time varies depending on the situation). If the next STEP is performed before they become steady values, that is, values in a transient state, calculation of appropriate values in the next STEP is hindered. Therefore, it is preferable to set the time until the refrigerant partial flow rate and the refrigerant discharge flow rate, which change with the change of each STEP change target, to steady values, is the pause time between STEPs.

  FIG. 6 is a flowchart of hot water supply distribution rate control (STEP 2 in FIG. 5) performed by hot water supply distribution rate control unit 145. In STEP 201, the hot water supply distribution rate control unit 145 detects the return temperature of the heat collecting medium, that is, the temperature T2. In STEP 202, the hot water supply distribution rate control unit 145 acquires the control frequency of the compressor 50. The control frequency of the compressor 50 is specifically the frequency F of the drive current of the three-phase induction motor 53 that rotationally drives the compressor 50. The frequency F of the driving current of the three-phase induction motor 53 is determined by the compressor control unit 132, and the hot water supply distribution rate control unit 145 determines the control frequency of the compressor 50 from the compressor control unit 132 via the processing control unit 141. Get. The rotational speed of the compressor 50, that is, the refrigerant discharge flow rate of the compressor 50 is proportional to the control frequency of the compressor 50.

  In STEP 203, the hot water supply distribution rate control unit 145 detects the temperature T5 as the return temperature of the hot water 16.

  In STEP 204, the hot water supply distribution rate control unit 145 calculates a control value of the opening degree O6 of the expansion valve for heating distribution channel, that is, the expansion valve Ex6 of the distribution channel 59. The control value is calculated by substituting T2, F, and T5 detected or acquired in STEP 201 to 203 into the following (Equation 1), for example.

  Control value of opening degree O6 = c1, temperature T2 + c2, frequency F + c3, temperature T5 + intercept Da + correction value Db (Expression 1).

  In (Expression 1), the unit of the control value on the left side is a step value that the expansion valve control unit 133 instructs to a step motor (not shown) that adjusts the opening degree of the expansion valve Ex6. In the right side of Equation 1, the units of the temperatures T2 and T5 are ° C., and the unit of the frequency F is c / s (cycle / second). Therefore, c1, c2, and c3 are units in addition to numerical values as coefficient values. Contains a conversion operator for converting from ° C or c / s to step.

  In (Equation 1), there is no term relating to the opening degree O4 of the expansion valve Ex4 in the desiccant control of FIG. 7 described later, but this term can be added as appropriate. Even if the term does not exist, the heat flow rate of the refrigerant in the flow paths 58, 59, and 60 can be matched with the required heat amount of the heating destination by the existence of the term of c2 and frequency F on the right side. The reason will be described later.

  The total flow rate Q of the refrigerant discharged from the compressor 50 is uniquely determined by the frequency F described above. The total heat flow W of the refrigerant discharged from the compressor 50 in the heat exchanger 77 is determined from the flow rate Q and the temperature T2. In addition, if the heat quantity per unit volume of the refrigerant discharged from the compressor 50 is h, there is a relationship of W = h · Q.

  On the other hand, wh (corresponding to the set heating amount of the present invention) as a heat flow rate for completing the boiling of the hot water 16 in the hot water storage tank 15 is preset in the time zone of midnight power. For example, wh = {capacity of hot water storage tank 15 × (boiling temperature−tap water temperature)} / providing time of late-night power (in a general example, 8 hours from 11:00 pm to 7 am on the next day). When wh is displayed in watts per unit time (1 second), the midnight power time is expressed in seconds.

  Let Qa, Qb, and Qc be the flow rates of the refrigerant divided into the diversion channels 58, 59, and 60, respectively. Q = Qa + Qb + Qc. As described above, the hot water supply distribution ratio Bc as a ratio of the diversion flow rate Qc of the diversion flow path 60 to the total flow rate Q of the refrigerant discharged from the compressor 50 is represented by Bc = Qc / Q. The heat flow rate of the refrigerant in terms of the amount of heat to the diversion channels 58, 59, 60 is h · Qa, h · Qb, h · Qc. Since the total heat flow rate of the refrigerant discharged from the compressor 50 in terms of heat quantity is h · Q, the distribution ratio of hot water supply in the branch flow path 60 in terms of heat quantity is h · Qc / h · Q = · Qc / Q = Bc. Become. That is, the hot water supply distribution rate Bc of the flow rate as the volume flow rate and the hot water supply distribution rate h · Qc / h · Q of the heat flow rate are the same.

  (Equation 1) is calculated so that the control value of the opening degree O6 at which the heat flow rate of the refrigerant diverted from the combined flow path 57 to the diversion flow path 60 is secured with respect to T2, F, and T5 is calculated. , C2, c3, Da, Db are set.

  c1, c2, c3, Da, and Db are determined by, for example, a designer of the heat pump apparatus 2 performing a predetermined test at the time of manufacturing design. Specifically, first, predetermined reference values T2r, Fr, and T5r are determined for T2, F, and T5.

  For example, the reference value Fr of the frequency F is a frequency Fz corresponding to the lower limit Qz of the discharge flow rate Q of the compressor 50. The lower limit Qz of the discharge flow rate Q of the compressor 50 is set to the discharge flow rate Q of the compressor 50 in which the refrigerant flow rate of the hot water supply diversion channel 60 can ensure the heating required heat flow rate wh of the hot water supply heating. That is, when the expansion valves Ex4 and Ex6 are both fully closed, and the entire amount of refrigerant discharged from the compressor 50 is supplied to the branch flow path 60, the flow rate Q that can secure the required heat flow rate wh is set as Qz. The

  The reference value T2r is, for example, a lower limit temperature T2z of a temperature range assumed for the temperature T2 of the heat collecting medium during the heating operation period of the heat pump device 2 (the heat collecting medium temperature at the position of the temperature sensor S2). The reference value T5r is, for example, a start temperature assumed for a return temperature T5 of the hot water 16 (temperature of the hot water 16 at the position of the temperature sensor S5) during the boiling period of the hot water 16 in the hot water storage tank 15 (period of the midnight power time period). T5z as the lowest temperature for hot water 16).

  For example, how to obtain c1 is as follows. By fixing F = Fr and T5 = T5r, a plurality of combinations (T2, O6) when Qc is the lowest flow rate that can secure wh is obtained by experiment, the horizontal axis (x axis) is T2, the vertical axis ( Plot (T2, O6) on a coordinate plane with y-axis) as O6, and obtain c1 by regression analysis.

  The method for obtaining c2 is, for example, as follows. By fixing T2 = T2r and T5 = T5r, a plurality of combinations (F, O6) when Qc becomes the minimum flow rate that can secure wh is obtained by experiment, the horizontal axis (x axis) is F, and the vertical axis ( Plot (F, O6) on a coordinate plane with y-axis) as O6, and obtain c2 by regression analysis.

  For example, how to obtain c3 is as follows. By fixing T2 = T2r and F = Fr, a plurality of combinations (T5, O6) when Qc is the lowest flow rate that can secure wh is obtained by experiment, the horizontal axis (x axis) is T5, and the vertical axis ( Plot (T5, O6) on a coordinate plane with y-axis) as O6, and obtain c3 by regression analysis.

  The method for obtaining the intercept Da is, for example, as follows. T2 = T2z, F = Fz, and T5 = T5z, and O6 when Qc has a flow rate that can secure wh is defined as an intercept Da in (Expression 1). In (Equation 1), the control value of the opening degree O6 when the flow rate can secure wh is calculated only by the single terms of c1, temperature T2, c2, frequency F, and c3, temperature T5. There is a margin when combined. The intercept Da is set so as to cancel out this margin.

  The method for obtaining the correction value Db is, for example, as follows. The correction value Db is, for example, a correction value related to the setting value To (the setting value of the temperature T3 at the part of the temperature sensor S3 of the heat medium circulation path 92) of the forward temperature of the heating medium for heating. For example, when the correction value Db is set to T2 = T2z, F = Fz, T5 = T5z, and Da determined as described above is added (Expression 1), the predetermined flow rate is set to a minimum flow rate at which Qc can secure wh. It is set as the control value of the opening degree O6 when securing the flow rate to which the surplus ΔQ is added. And, as the set value To becomes higher, ΔQ decreases (however, with the condition of Q ≧ Qz), that is, the surplus flow rate is gradually directed toward the heating for heating, in other words, The correction value Db is set as a function of the set value To so that the additional amount of the refrigerant flow rate gradually increases toward the diversion channel 59.

  For example, c1 = 2.00, c2 = 4.00, c3 = 3.48, and Da = −201.65.

  The control value of the opening degree O6 calculated by (Equation 1) is not the expansion valve provided in the hot water supply diversion channel 60 but the expansion valve Ex6 provided in the heating diversion channel 59. It has become. Therefore, the increase / decrease in the control value of the opening degree O6 calculated by (Equation 1) is inversely related to the increase / decrease in the refrigerant flow rate Qc and the hot water supply distribution ratio Bc in the hot water supply diversion channel 60.

  In (Formula 1), as the temperature of the heat collecting medium on the heat collecting medium inlet side of the heat exchanger 77 as the heat collecting heat exchanger 77 is higher, the opening degree O6 is set to an opening degree that decreases the hot water supply distribution ratio Bc. Will be changed. Further, as the temperature of the hot water 16 on the hot water inlet side of the heat exchanger 74 serving as a heat exchanger for hot water supply is higher, the opening degree O6 is changed to an opening degree that decreases the hot water supply distribution ratio Bc.

  In the right side of (Expression 1), only the second term c2 and frequency F are left, the other terms are deleted, and the control value of the opening degree O6 is calculated as a control value that secures wh. be able to. Further, on the right side of (Expression 1), only the two terms of c1 and temperature T2 of the first term and c2 and frequency F of the second term are left, and other terms are deleted, and the control of the opening degree O6 is performed. A value can also be calculated. Further, on the right side of (Expression 1), at least one of the intercept Da and the correction value Db may be omitted.

  In STEP 205, the hot water supply distribution rate control unit 145 changes the opening degree O6 of the expansion valve Ex6 as the expansion valve for the heating distribution passage to the control value calculated in STEP 204.

  In this way, the heat flow rate by the refrigerant diverted to the diversion channel 60 is ensured to be wh or more, and the hot water supply distribution rate control unit 145 changes the opening degree O6 of the expansion valve Ex6.

  FIG. 7 is a flowchart of the desiccant control (STEP 3 in FIG. 5) performed by the desiccant control unit 146. The desiccant device 4 humidifies the air in the heating space during the heating operation period of the heat pump device 2 so that the air does not dry due to an increase in room temperature.

  The heat pump device 2 is necessary to prevent the refrigerant flow rate in the branch channel 58 from becoming excessive or insufficient with respect to the operation of humidification (humidification during the heating operation period) and dehumidification (dehumidification during the cooling operation period) by the desiccant device 4. While performing humidification or dehumidification, the energy consumption required for driving the compressor 50 is suppressed. In the desiccant control, the expansion valves Ex3 and Ex4 correspond to the first adjustment valve and the second adjustment valve of the present invention, respectively.

  In STEP 301, the desiccant control unit 146 acquires the dew point temperature Be of the air in the exhaust passage 109. The dew point temperature Be can be calculated from the temperature Tb and humidity Mb of the exhaust air detected by the temperature / humidity sensor Nb or the temperature Td and humidity Md of the exhaust air detected by the temperature / humidity sensor Nd.

  In STEP 302, the desiccant controller 146 sets the first target temperature range based on the dew point temperature Be. The first target temperature range is, for example, a temperature range that is greater than Be and less than or equal to Be + βe (Be <first target temperature range ≦ Be + βe). However, βe is a positive predetermined value. The moisture adsorption efficiency of the desiccant 114 increases as the temperature of the air passing through the desiccant 114 decreases. On the other hand, if the evaporator 124 is cooled too much, dew condensation occurs on the surface of the evaporator 124. The first target temperature range is set as a refrigerant temperature range of the evaporator 124 in which condensation on the surface of the evaporator 124 does not occur while increasing the moisture adsorption efficiency of the desiccant 114 as much as possible.

  In STEP 303, the refrigerant temperature (T9) on the refrigerant inlet side and the refrigerant temperature (T10) on the refrigerant outlet side of the evaporator 124 as the upstream evaporator of the exhaust passage 109 are detected.

  In STEP 304, the desiccant control unit 146 determines whether or not the temperatures T9 and T10 are both within the first target temperature range. The reason why it is determined whether or not both of the temperatures T9 and T10 are within the first target temperature range is not always the outlet side temperature T10> the inlet side temperature T9. Depending on the situation, the outlet side temperature T10 <the inlet side temperature. This is because it is sometimes T9. The desiccant control unit 146 advances the process to STEP 305 when the determination result is NO (NO). When the determination result is positive, the desiccant control unit 146 advances the processing to STEP 306.

  In STEP 305, the desiccant control unit 146 changes the opening degree O3 of the expansion valve Ex3 as the evaporation amount adjusting expansion valve by Δe or −Δe. However, Δe> 0. Specifically, when both the temperature T9 and the temperature T10 exceed the upper limit of the first target temperature range, the opening degree O3 of the expansion valve Ex3 is decreased by Δe (increase the evaporation amount), The cooling power of the evaporator 124 is increased. When at least one of the temperature T9 and the temperature T10 is below the lower limit of the first target temperature range, the opening degree O3 of the expansion valve Ex3 is increased by Δe (decreasing the evaporation amount), and the evaporator 124 Reduce cooling power.

  The desiccant control unit 146 returns the processing to STEP 303 after STEP 305 ends.

  In STEP 306, the desiccant control unit 146 acquires the dew point temperature Bi of the air in the supply passage 108. The dew point temperature Bi can be calculated from the temperature Ta and humidity Ma of the supply air detected by the temperature / humidity sensor Na or the temperature Tc and humidity Mc of the supply air detected by the temperature / humidity sensor Nc. The dew point temperature Bi can also be a value calculated from the temperature Tb and humidity Mb of the exhaust air in the heating space detected by the temperature / humidity sensor Nb in which the exhaust passage 109 is disposed. The reason why the dew point temperature Bi is calculated from the exhaust air sucked into the exhaust passage 109 from the heating space instead of the dew point temperature Bi of the air in the supply passage 108 is to control humidification according to the actual humidity of the heating space. It is.

  In STEP 307, the desiccant controller 146 sets the second target temperature range based on the dew point temperature Bi. For example, the second target temperature range is set as a range of a temperature section that is higher than the temperature section by a predetermined amount in association with the temperature section to which Bi belongs. The regeneration efficiency (moisture desorption efficiency) of the desiccant 114 increases as the temperature of the air passing through the desiccant 114 increases. However, when the regeneration saturation state is reached, the efficiency does not increase so much even if the air temperature is increased further. Only the air heating is wasted. By setting a second target temperature range that is not high or low in association with the temperature category to which Bi belongs, the regeneration efficiency of the desiccant 114 is increased, while wasteful air heating is suppressed, and wasteful energy consumption is reduced. Can be suppressed.

  In STEP 308, the refrigerant temperature (T8) on the refrigerant outlet side of the condenser 121 as the upstream condenser of the air supply passage 108 is detected.

  In STEP 309, the desiccant control unit 146 determines whether or not the temperature T8 is within the second target temperature range. When the determination result is negative, the desiccant control unit 146 proceeds with the process to STEP 310.

  In STEP 310, the desiccant controller 146 changes the opening degree O4 of the expansion valve Ex4 as the diversion adjusting expansion valve by Δi or −Δi. However, Δi> 0. Δi = Δe or Δi ≠ Δe.

  Specifically, when the temperature T8 exceeds the upper limit of the second target temperature range, the opening degree O4 of the expansion valve Ex4 is decreased by Δi, and the heating power of the condenser 121 is decreased. When the temperature T8 is below the lower limit of the second target temperature range, the opening degree O4 of the expansion valve Ex4 is increased by Δi, and the heating power of the condenser 121 is increased.

  The desiccant control unit 146 returns the processing to STEP 308 after STEP 310 ends.

  On the other hand, if the determination in STEP 309 is positive, the desiccant control unit 146 ends the desiccant control.

  Thus, when the desiccant control by the desiccant control unit 146 is finished, the flow rate of the refrigerant diverted to the diversion channel 58 is to increase the moisture adsorption efficiency in the desiccant 114 in a range in which no condensation occurs in the evaporator 124 in the exhaust passage 109. At the same time, the air supply passage 108 has a flow rate that suppresses wasteful energy consumption due to excessive air heating and increases the regeneration efficiency of the desiccant 114.

  FIG. 8 is a flowchart of compressor control performed by the compressor control unit 132. In STEP 401, the compressor control unit 132 obtains a setting value To of the heating-side heating medium temperature setting value (setting value of temperature at the temperature sensor S3 portion of the heat medium circulation path 92). The set value To is to be manually designated in advance by the user via the remote controller of the heat pump device 2 or the like. Therefore, since the set value To designated by the user is stored in the memory, the compressor control unit 132 can read and obtain the set value To from the memory.

  In STEP 402, the compressor control unit 132 detects the forward temperature (temperature T3) of the heating medium for heating.

  In STEP 403, the compressor control unit 132 determines the difference D (= To−T3) between the set value To and the detected value (temperature T3) of the forward temperature of the heating medium for heating (the temperature at the site of the temperature sensor S3). Is calculated.

  In STEP 404, the compressor control unit 132 determines whether or not the difference D> predetermined value α (where α> 0). If the determination is positive, the process proceeds to STEP 405, and the determination is negative. If so, the process proceeds to STEP 406.

  D> α indicates that the heat flow rate of the refrigerant in the branch channel 59 is insufficient. D <−α indicates that the heat flow rate of the refrigerant in the branch channel 59 is excessive.

  In STEP 405, the compressor control unit 132 increases the control frequency F of the compressor 50 (= the control frequency F of the three-phase induction motor 53) by ΔF. As a result, the rotational speed of the compressor 50 increases by a considerable amount ΔF, and the heat flow rate of the refrigerant in the branch flow path 59 increases by a predetermined amount. Then, the compressor control part 132 returns a process to STEP402.

  In STEP 406, the compressor control unit 132 determines whether or not D <−α. If the determination is positive, the process proceeds to STEP 407.

  In STEP 407, the compressor control unit 132 decreases the control frequency F of the compressor 50 (= control frequency F of the three-phase induction motor 53) by ΔF. As a result, the rotational speed of the compressor 50 is reduced by a considerable amount ΔF, and the heat flow rate of the refrigerant in the branch flow path 59 is reduced by a predetermined amount. Then, the compressor control part 132 returns a process to STEP402.

  On the other hand, if the determination in STEP 406 is negative, the compressor control unit 132 ends the compressor control. Thus, the flow rate of the refrigerant in the branch flow path 59 becomes a flow rate that secures the heat flow rate required by the floor heating device 6 as the heating device, and the compressor control (STEP 4) is terminated.

  Thereafter, as shown in FIG. 5, through STEP 1, STEP 2 to 4 are repeated one by one.

  In other words, in the hot water supply distribution rate control (STEP 2) and the desiccant control (STEP 3), the refrigerant flow rates in the diversion channel 60 and the diversion channel 58 are adjusted to the hot water supply heating and the desiccant control heating without considering the refrigerant flow rate in the diversion channel 59. It is changed so as to be optimized to a value according to the requested amount. On the other hand, by performing the hot water supply distribution rate control and the desiccant control, the refrigerant flow rate in the diversion channel 59 deviates from an appropriate value according to the required amount of heating for heating. This deviation is reflected in the difference between the set temperature To of the going-side heat medium and the current detected temperature T3 for the going-side heat medium that goes to the floor heating device 6 as the heating device.

  In the compressor control (STEP 4), the refrigerant discharge flow rate of the compressor 50 is changed so that the absolute value (| D |) of the difference D (= To−T3) decreases. This change not only returns the refrigerant flow rate of the diversion channel 59 to an appropriate value according to the required amount of heating for heating, but also the expansion valve Ex6 as the opening adjustment valve, the expansion valve Ex3 as the first adjustment valve, and the second adjustment valve. As a regulating valve, the total excess / deficiency of the refrigerant flow rate of the branch flow paths 58, 59, 60 is reduced under the current opening of the expansion valve Ex4. That is, the change of the refrigerant discharge flow rate of the compressor 50 by the compressor control (STEP 4) appropriately corrects the excess or deficiency of the refrigerant flow rate in the entire branch flow paths 58, 59, 60. This means that the refrigerant flow rates in the diversion channels 58 and 60 are closer to the corresponding values of the current required amount of heating for hot water supply and heating for desiccant control than the refrigerant flow rate at the previous start of hot water supply distribution rate control and desiccant control. Means that

  In the hot water distribution rate control (STEP 2) and the desiccant control (STEP 3) following the compressor control (STEP 4), the coolant flow rate in the branch channels 60 and 58 is higher than that at the previous start of the hot water distribution rate control and the desiccant control. It will be implemented in response to having approached the corresponding value of the required amount of heating for desiccant and heating for desiccant control. Therefore, by the current execution of the hot water supply distribution rate control and the desiccant control, the refrigerant flow rates in the diversion channel 60 and the diversion channel 58 are higher than those in the previous execution of the hot water supply distribution rate control. It approaches the corresponding value of the required amount.

  Thus, while the hot water distribution rate control (STEP 2), the desiccant control (STEP 3), and the compressor control (STEP 4) are repeatedly performed in a predetermined order, the refrigerant flow rates in the distribution channel 59, the distribution channel 60, and the distribution channel 58 are repeated. Are converged to or sufficiently close to the values corresponding to the respective required amounts of heating for heating, heating for hot water supply and heating for desiccant control.

  As described above, this heating operation control (FIG. 5) is merely a simple hot water supply distribution rate control (STEP 2) that optimizes the refrigerant flow rate Qc of the distribution channel 60 and only optimizes the refrigerant flow rate Qa of the distribution channel 58. The simple desiccant control (STEP 3) of the compressor and the compressor so as to reduce the absolute value | D | of the difference D between the set temperature of the forward heat medium and the current detected temperature for the forward heat medium toward the heating device The simple compressor control (STEP 4) that only changes the refrigerant discharge flow rate Q of 50 is repeated. As a result, even if the volume of the heating space and the capacity of the hot water storage tank vary depending on the installation state of the heat pump device 2, the heating request amount at each time point of the desiccant together with the heating space and the hot water storage tank after an appropriate time has elapsed. The refrigerant can be supplied at an appropriate flow rate according to the condition.

  In (Equation 1), there is no term related to the opening degree O4 of the expansion valve Ex4. However, the change of the refrigerant discharge flow rate based on the difference D in the compressor control (STEP 4) also includes a function of correcting the excess or deficiency of the refrigerant flow rate in the entire branch flow paths 58, 59, 60. Therefore, even if there is no term related to the opening degree O4 of the expansion valve Ex4 in (Equation 1), the opening degree O4 of the expansion valve Ex4 is the control value of the opening degree O6 calculated from (Equation 1). Reflected.

  That is, the change in the opening degree O4 of the expansion valve Ex4 by the desiccant control in FIG. 7 (STEP 3 in FIG. 5) is reflected in the value of the difference D through the change in the refrigerant flow rate in the branch flow path 59. In the compressor control performed thereafter, the refrigerant discharge flow rate is changed based on the difference D, and further, the control value of the opening degree O6 according to (Equation 1) is calculated in response to the change in the refrigerant discharge flow rate. The Therefore, the control value of the opening degree O6 calculated by (Equation 1) incorporates the change in the opening degree O4 of the expansion valve Ex4 by the desiccant control of FIG. 7 (STEP 3 of FIG. 5).

  However, (Equation 1) may include a term related to the opening degree O4 of the expansion valve Ex4. In that case, the control value of the opening degree O6 calculated by (Equation 1) becomes a value close to the convergence value, and the time during which the values to be processed in STEPs 2 to 4 are converged is advanced.

  Although the embodiment of the present invention has been described, the present invention is not limited to this embodiment, and can be implemented with various modifications.

  For example, the geothermal heat pump system 1 equipped with the heat pump device 2 of the embodiment includes the desiccant device 4, but the heat pump device of the present invention is also applied to the geothermal heat pump system 1 that does not include the desiccant device 4. Can do. In the geothermal heat pump system 1 that does not include the desiccant device 4, the processing of STEP 3 in FIG. 5 is omitted.

  In addition, although wh as a heat flow rate for securing boiling of the hot water 16 in the hot water storage tank 15 is set by wh = {capacity of the hot water storage tank 15 × (boiling temperature−tap water temperature)} / providing time of late-night power. , Wh has an upper limit determined by the diameter of the hot water circulation circuit 89 and the like. In the calculation of the control value of the opening degree O6 according to (Equation 1), the heat flow rate of the refrigerant in the branch flow path 60 corresponding to the calculated control value may exceed the upper limit of wh. In this case, the heat flow rate of the refrigerant in the branch flow path 60 is wasted. Therefore, it is preferable to set a limit corresponding to the upper limit of wh in the control value of the opening degree O6 according to (Equation 1) and limit the control value within the limit.

  In the embodiment, the refrigerant before being sucked into the compressor 50 in the refrigerant circulation path is heated by the heat exchanger 77 (heat collecting heat exchanger). However, in the present invention, an electric heater or a burner may be employed instead of the heat exchanger 77 as a refrigerant heating unit that heats the refrigerant before being sucked into the compressor in the refrigerant circuit.

  The heating power of the refrigerant heating unit for the refrigerant (when the refrigerant heating unit is the heat exchanger 77, the heating power is related not only to the temperature of the heat collecting medium but also to the circulation flow rate of the heat collecting medium), the compressor 50 It is preferable to control so as to increase or decrease in accordance with the increase or decrease of the refrigerant discharge flow rate. However, the heating power of the refrigerant heating unit can be set slightly larger, and the control of the heating power with respect to the increase or decrease of the refrigerant discharge flow rate of the compressor 50 can be omitted. This is because when the heating power is sufficient, the amount of the refrigerant that is heated in the refrigerant heating unit per certain time depends on the increase or decrease in the refrigerant discharge flow rate of the compressor 50 even if the heating power is constant. This is because it increases or decreases. In the embodiment, the rotation speed of the circulation pump P1 is kept constant regardless of the increase or decrease of the refrigerant discharge flow rate of the compressor 50, and the heat exchanger 77 performs heating according to the increase or decrease of the refrigerant discharge flow rate of the compressor 50. Side control is omitted.

  The heat pump device 2 of the embodiment uses a ground heat collection medium as the heat collection medium. However, the heat collection medium utilized by the heat pump device of the present invention may utilize heat of outdoor air, for example, other than underground heat.

  In the desiccant device 4, a condenser 120 and an evaporator 123 are also disposed downstream of the desiccant 114 in the air supply passage 108 and the exhaust passage 109. Although the condenser 120 and the evaporator 123 are related to the control of the supply air temperature supplied to the heating space during the heating operation control period, the supply air temperature and the exhaust gas temperature for controlling the moisture desorption amount and the moisture adsorption amount in the desiccant 114. It is not involved in the temperature control. Therefore, in the desiccant device 4 that does not control the supply air temperature, the condenser 120 and the evaporator 123 can be omitted.

Ex3 ... expansion valve (first adjustment valve), Ex4 ... expansion valve (second adjustment valve), Ex6 ... expansion valve (opening adjustment valve), S2, S3, S5 ... temperature sensors, DESCRIPTION OF SYMBOLS 2 ... Heat pump apparatus, 15 ... Hot water storage tank, 16 ... Hot water, 50 ... Compressor, 51 ... Intake flow path (circulation path), 52 ... Discharge flow path (circulation path) 57... Combined flow path (circulation path), 58... Split flow path (third split flow path), 59... Split flow path (first split flow path), 60. 64 ... Combined flow path (circulation path), 70 ... Heat exchanger (heat exchanger for heating), 74 ... Heat exchanger (heat exchanger for hot water supply), 77 ... Heat exchanger ( Refrigerant heating unit or heat exchanger for heat collection), 114 ... desiccant, 121 ... condenser, 124 ... evaporator, 141 ... processing control unit.

Claims (4)

A refrigerant circulation path including a first branch flow path and a second branch flow path connected in parallel with each other, and having a refrigerant sealed therein;
A compressor that is provided in the middle of the refrigerant circulation path, compresses the refrigerant on the upstream side, and discharges the refrigerant on the downstream side;
A heat exchanger for heating that exchanges heat between a heat medium that circulates through a heating circulation path that passes through a heating device and a refrigerant that circulates through the first branch flow path;
A hot water supply heat exchanger for exchanging heat between hot water flowing through the hot water tank circulation path passing through the hot water storage tank and the refrigerant flowing through the second branch flow path;
A refrigerant heating unit for heating the refrigerant before being sucked into the compressor in the refrigerant circulation path;
An opening degree adjusting valve disposed in the first branch path or the second branch path and having an adjustable opening degree;
A temperature detector for the forward heat medium that detects the temperature of the forward heat medium that travels from the heating heat exchanger to the heating equipment in the heating circuit;
When the compressor is operated and heat exchange is performed by the heat exchanger for heating and the heat exchanger for hot water supply, the opening of the opening adjustment valve is set with respect to the current discharge flow rate of the compressor. The first process of changing the flow rate of the refrigerant in the second branch channel to an opening degree that can secure the set heating amount of the hot water in the hot water supply heat exchanger, the set temperature set for the outgoing heat medium, and the outgoing heat medium And alternately performing a second process of changing the refrigerant discharge flow rate of the compressor so that the absolute value of the difference from the current detected temperature detected by the forward-side heat medium temperature detector decreases, and During the execution of the first process, the discharge flow rate of the compressor is fixed to the discharge flow rate at the previous end of the second process, and during the second process, the opening degree of the opening adjustment valve is set to the first flow rate. With a processing control unit that fixes the opening at the end of the previous processing Heat pump apparatus characterized by. In the heat pump device according to claim 1,
The refrigerant heating unit is a heat collecting heat exchanger that exchanges heat between the refrigerant before being sucked into the compressor in the refrigerant circulation path and a predetermined heat collecting medium,
In the first process, the process control unit is configured to perform the second diversion with respect to the current discharge flow rate of the compressor as the temperature of the heat collecting medium on the heat collecting medium inlet side of the heat collecting heat exchanger increases. A heat pump device, wherein the opening degree of the opening degree adjusting valve is changed so that the ratio of the refrigerant flow rate in the passage is reduced. In the heat pump device according to claim 1 or 2,
In the first process, as the temperature of the hot water on the hot water inlet side of the hot water supply heat exchanger is higher, the processing control unit has a ratio of the refrigerant flow rate of the second branch flow path to the current discharge flow rate of the compressor. A heat pump device, wherein the opening of the opening adjustment valve is changed so as to be small. In the heat pump device according to any one of claims 1 to 3,
A third branch channel connected in parallel to both the first branch channel and the second branch channel;
A desiccant disposed across an air supply passage for guiding outdoor air to the indoor heating space and an exhaust passage for discharging the air in the indoor heating space to the outside;
A condenser that is disposed upstream of the desiccant in the air supply passage, and that heats the air before passing through the desiccant by the refrigerant in the third branch channel;
A first regulating valve disposed on the downstream side of the condenser in the third branch channel and having an adjustable opening;
A second regulating valve disposed on the upstream side of the condenser in the third branch channel and having an adjustable opening;
An evaporator disposed upstream of the desiccant in the exhaust passage and configured to cool the air before passing through the desiccant with a refrigerant in a third branch passage that has passed through the first adjustment valve;
The processing control unit
The refrigerant temperature on the refrigerant outlet side of the condenser is adjusted after the opening of the first adjustment valve is adjusted so that the refrigerant temperatures on the refrigerant inlet side and the refrigerant outlet side of the evaporator are within the first target temperature range. Performing a third process for adjusting the opening of the second adjustment valve so as to be within the second target temperature range;
The three processes of the first process, the second process and the third process are repeatedly performed in a predetermined order,
During the execution of the first process, the discharge flow rate of the compressor is fixed to the discharge flow rate at the previous end of the second process, and the opening degree of the first adjustment valve and the second adjustment valve is set to the third process. Fixed at the opening at the previous end of
During the execution of the second process, the opening of the opening adjustment valve is fixed to the opening at the previous end of the first process, and the opening of the first adjustment valve and the second adjustment valve is set to the first. 3 Fix the opening at the end of the previous process,
During the execution of the third process, the opening of the opening adjustment valve is fixed to the opening at the previous end of the first process, and the discharge flow rate of the compressor is the same as that at the previous end of the second process. A heat pump device characterized by being fixed at a discharge flow rate.