JP6964482B2 - Heat pump type temperature control system - Google Patents

Description

The present invention relates to a heat pump type temperature control system in which an indoor terminal performs an air conditioning operation by a load-side circulating fluid having a heat pump device as a heat source.

Conventionally, in this type of system, as described in Patent Document 1, the refrigerant from the heat pump device and the load-side circulating fluid that has been heat-exchanged by the load-side heat exchanger are guided to the indoor terminal to perform heating or cooling. There was something.

In this prior art, the operation of the heat pump device is controlled by so-called return temperature control. That is, the heat pump device is controlled so that the return temperature of the load-side circulating fluid flowing from the indoor terminal into the load-side heat exchanger becomes a target return temperature corresponding to the temperature level set by the remote controller. In this return temperature control, the forward temperature changes according to the load, and when the load is low, the forward temperature can be set to a low temperature during heating and a high forward temperature during cooling, thus improving the efficiency of the heat pump device. It has the feature of being able to plan.

Japanese Unexamined Patent Publication No. 2015-129616

On the other hand, as a control method of the heat pump device different from the return temperature control, there is a so-called forward temperature control. In this case, the heat pump device is controlled so that the forward temperature of the load-side circulating fluid flowing out from the load-side heat exchanger to the indoor terminal becomes the target forward temperature corresponding to the temperature level set by the remote controller. .. This forward temperature control has a feature that it is easy to maintain the output of the indoor terminal because the supply temperature to the indoor terminal becomes constant.

Here, there are various types of indoor terminals, but depending on the type of indoor terminal, during operation (heating operation or cooling operation), due to its characteristics, the forward temperature control and the return temperature control can be performed. Of these, one of them may be particularly preferable.

For example, when a fan coil, which is a type of forced convection terminal, performs cooling operation, the indoor air is circulated by the fan, so that the humidity in the room is dehumidified to some extent evenly (that is, latent heat treatment) when the load is high at the beginning of operation. After that, the operation becomes stable and low load operation. Therefore, even if the return temperature control is performed with the main purpose of improving efficiency, it is unlikely that comfort will be impaired by high humidity during the low load operation.

On the other hand, for example, when a cold / hot water panel, which is a kind of radiant terminal, performs a cooling operation, a high load operation is performed at the initial stage of operation, but when the panel itself cools to some extent, the temperature in the room drops completely. Shift to low load operation without it. In this case, if the return control is performed, the temperature of the cold water supplied to the panel will gradually increase at the timing when the panel itself has cooled to some extent (even if the temperature in the room has not yet decreased). As a result, the indoor temperature is less likely to decrease, and as a result, the indoor humidity does not decrease completely during the low load operation, resulting in an unpleasant situation. Therefore, when the cold / hot water panel performs the cooling operation, it is preferable to control the forward temperature in order to surely lower the humidity in the room.

For example, an underfloor radiator, which is a type of natural convection terminal, has a function of heating the floor of the living room directly above by heating the underfloor and a function of sending warm air under the floor to the living room by natural convection to heat the room. Do both. At this time, since the heating of the living room is indirectly performed through the heating of the underfloor space, it is desirable to maintain the underfloor temperature as high as possible in order to keep the living room comfortable.
If the return temperature control is performed during the heating operation of the underfloor radiator, the temperature of the hot water will drop at the timing when the underfloor space warms up (even if the living room has not warmed up yet), and as a result, the living room will warm up. It becomes difficult. On the other hand, if the forward temperature control is performed, the underfloor radiator stably exerts an output, so that the living room warms up quickly. Therefore, when the underfloor radiator performs the heating operation, it is preferable to control the forward temperature in order to ensure the comfort of the living room space.

In the above-mentioned prior art, the point of applying a particularly preferable one of the return temperature control and the forward temperature control according to the type of the indoor terminal as described above is not particularly considered, and there is room for improvement. ..

In order to solve the above problems, in claim 1 of the present invention, load-side heat exchange for heat exchange between a refrigerant supplied from a heat pump device including a compressor, an expansion valve, and a heat pump heat exchanger and a load-side circulating liquid. A device, at least one operating means capable of setting the temperature level of the load-side circulating fluid supplied to at least one indoor terminal, and operating the at least one indoor terminal, and the load. The load side heat exchanger according to the forward temperature determining means for determining the outgoing temperature of the load side circulating fluid flowing out from the side heat exchanger to the indoor terminal and the temperature level set by the setting operation means. The target going temperature setting means for setting the target going temperature of the load-side circulating fluid supplied from the indoor terminal to the indoor terminal, and the return temperature of the load-side circulating fluid flowing from the indoor terminal into the load-side heat exchanger. A target return for setting a target return temperature of the load-side circulating fluid returning from the indoor terminal to the load-side heat exchanger according to the return temperature determining means to be determined and the temperature level set by the setting operation means. In a heat pump type temperature control system having a temperature setting means, a terminal determination means for determining the type of the indoor terminal to be operated based on the operation request of the indoor terminal and the load-side circulating fluid are used as the indoor terminal. In the operation of circulating in the machine, the forward temperature determined by the forward temperature determining means becomes the target forward temperature set by the target forward temperature setting means based on the determination result of the terminal determination means. The forward temperature control that controls the heat pump device, or the return temperature that controls the heat pump device so that the return temperature determined by the return temperature determining means becomes the target return temperature set by the target return temperature setting means. control, have a, a switching control means for performing switching the said terminal determination means, based on the operation request of the plurality of the indoor terminal, a plurality of the operation of at least certain types of the indoor terminal When the indoor terminal is determined and the switching control means determines that the specific type of indoor terminal is operated by the terminal determination means, the operation of the specific type of indoor terminal and the specific type are performed. In the first case where both the operation of the indoor terminal of the other type is performed, and the operation of the specific type of indoor terminal is performed and the indoor terminal of the type other than the specific type is not operated. In any of the second cases, the switching corresponding to the specific type of indoor terminal is executed. To do .

Further, in order to solve the above problem, in claim 2 of the present invention, the load side for heat exchange between the refrigerant supplied from the heat pump device including the compressor, the expansion valve and the heat pump heat exchanger and the load side circulating fluid. A heat exchanger and at least one operating means capable of operating the at least one indoor terminal, including a setting operating means capable of setting the temperature level of the load-side circulating fluid supplied to at least one indoor terminal. The load side heat is determined according to the forward temperature determining means for determining the forward temperature of the load side circulating fluid flowing out from the load side heat exchanger to the indoor terminal and the temperature level set by the setting operation means. A target outgoing temperature setting means for setting a target outgoing temperature of the load-side circulating fluid supplied from the exchanger to the indoor terminal, and a return of the load-side circulating fluid flowing into the load-side heat exchanger from the indoor terminal. The target return temperature of the load-side circulating fluid returning from the indoor terminal to the load-side heat exchanger is set according to the return temperature-determining means for determining the temperature and the temperature level set by the setting operation means. In a heat pump type temperature control system having a target return temperature setting means, the terminal determination means for determining the type of the indoor terminal to be operated based on the operation request of the indoor terminal and the load-side circulating fluid are described. During the operation of circulating in the indoor terminal, the forward temperature determined by the forward temperature determining means becomes the target forward temperature set by the target forward temperature setting means based on the determination result of the terminal determination means. Control the heat pump device so that the return temperature determined by the return temperature determining means becomes the target return temperature set by the target return temperature setting means. It has a switching control means for switching and executing the return temperature control, and the terminal determining means is at least specific among the plurality of indoor terminals to be operated based on the operation requests of the plurality of indoor terminals. When the type of indoor terminal is determined and the switching control means determines that the specific type of indoor terminal is operated by the terminal determination means, the type of indoor terminal other than the specific type is used. Cooling that executes the switching corresponding to the specific type of indoor terminal regardless of whether or not it is operated and circulates the load-side circulating fluid cooled by the load-side heat exchanger to the indoor terminal. During operation, the switching control means is a room of the specific type by the terminal determination means. When it is determined that the cold / hot water panel as the inner terminal is operated, the forward temperature control is executed, and in other cases, the return temperature control is executed.

Further, in order to solve the above problems, in claim 3 of the present invention, the load side for heat exchange between the refrigerant supplied from the heat pump device including the compressor, the expansion valve and the heat pump heat exchanger and the load side circulating fluid. A heat exchanger and at least one operating means capable of operating the at least one indoor terminal, including a setting operating means capable of setting the temperature level of the load-side circulating fluid supplied to at least one indoor terminal. The load side heat is determined according to the forward temperature determining means for determining the forward temperature of the load side circulating fluid flowing out from the load side heat exchanger to the indoor terminal and the temperature level set by the setting operation means. A target outgoing temperature setting means for setting a target outgoing temperature of the load-side circulating fluid supplied from the exchanger to the indoor terminal, and a return of the load-side circulating fluid flowing into the load-side heat exchanger from the indoor terminal. The target return temperature of the load-side circulating fluid returning from the indoor terminal to the load-side heat exchanger is set according to the return temperature-determining means for determining the temperature and the temperature level set by the setting operation means. In a heat pump type temperature control system having a target return temperature setting means, the terminal determination means for determining the type of the indoor terminal to be operated based on the operation request of the indoor terminal and the load-side circulating fluid are described. During the operation of circulating in the indoor terminal, the forward temperature determined by the forward temperature determining means becomes the target forward temperature set by the target forward temperature setting means based on the determination result of the terminal determination means. Control the heat pump device so that the return temperature determined by the return temperature determining means becomes the target return temperature set by the target return temperature setting means. It has a switching control means for switching and executing the return temperature control, and the terminal determining means is at least specific among the plurality of indoor terminals to be operated based on the operation requests of the plurality of indoor terminals. When the type of indoor terminal is determined and the switching control means determines that the specific type of indoor terminal is operated by the terminal determination means, the type of indoor terminal other than the specific type is used. A heating operation that executes the switching corresponding to the specific type of indoor terminal regardless of whether or not it is operated, and circulates the load-side circulating fluid absorbed by the load-side heat exchanger to the indoor terminal. At times, the switching control means is a room of the specific type by the terminal determination means. When it is determined that the underfloor radiator as a terminal is operated, the forward temperature control is executed, and in other cases, the return temperature control is executed.

Further, in order to solve the above problems, in claim 4 of the present invention, the load side for heat exchange between the refrigerant supplied from the heat pump device including the compressor, the expansion valve and the heat pump heat exchanger and the load side circulating fluid. A heat exchanger and at least one operating means capable of operating the at least one indoor terminal, including a setting operating means capable of setting the temperature level of the load-side circulating fluid supplied to at least one indoor terminal. The load-side heat is determined according to the forward temperature determining means for determining the forward temperature of the load-side circulating fluid flowing out from the load-side heat exchanger to the indoor terminal and the temperature level set by the setting operation means. The target outgoing temperature setting means for setting the target outgoing temperature of the load-side circulating fluid supplied from the exchanger to the indoor terminal, and the return of the load-side circulating fluid flowing into the load-side heat exchanger from the indoor terminal. The target return temperature of the load-side circulating fluid returning from the indoor terminal to the load-side heat exchanger is set according to the return temperature determining means for determining the temperature and the temperature level set by the setting operation means. In a heat pump type temperature control system having a target return temperature setting means, the terminal determination means for determining the type of the indoor terminal to be operated based on the operation request of the indoor terminal and the load-side circulating fluid are described. During the operation of circulating in the indoor terminal, the forward temperature determined by the forward temperature determining means becomes the target forward temperature set by the target forward temperature setting means based on the determination result of the terminal determination means. Control the heat pump device so that the return temperature determined by the return temperature determining means becomes the target return temperature set by the target return temperature setting means. The target return temperature setting means has a switching control means for switching and executing the return temperature control, and the target return temperature setting means has a predetermined numerical value in a numerical value corresponding to the temperature level set by the setting operation means during the cooling operation. Is set as the target return temperature, and during the heating operation, a subtraction value obtained by subtracting a predetermined value from the value corresponding to the temperature level set by the setting operation means is set as the target return temperature. To do.

Further, in claim 5 , the switching control means controls the compressor so that the forward temperature becomes the target forward temperature based on the determination result of the terminal determination means, or the return temperature is the same. It includes a compressor control means for controlling the number of revolutions of the compressor so as to reach a target return temperature.

According to claim 1 of the present invention, the refrigerant from the heat pump device and the load-side circulating fluid that has been heat-exchanged by the load-side heat exchanger are guided to at least one indoor terminal, and the indoor terminal is supplied therewith. The indoor air-conditioning operation (for example, heating operation or cooling operation) is performed using the load-side circulating fluid as a heat source. At least one operating means is provided to operate the at least one indoor terminal. The at least one operating means includes a setting operating means. This setting operation means is configured to be able to set the temperature level of the load-side circulating fluid in order to perform the air conditioning operation (heating operation or cooling operation). Then, the operation of the heat pump device is controlled based on the temperature level set by the setting operation means during the operation of circulating the load-side circulating liquid to the indoor terminal. Specifically, the control at this time includes an forward temperature control and a return temperature control.

In the forward temperature control, the target forward temperature of the load-side circulating fluid supplied from the load-side heat exchanger to the indoor terminal is set according to the temperature level (set by the target forward temperature setting means). Then, the heat pump device is controlled so that the forward temperature (determined by the forward temperature determining means) of the load-side circulating fluid flowing out from the load-side heat exchanger to the indoor terminal becomes the target forward temperature. This forward temperature control has a feature that it is easy to maintain the output of the indoor terminal because the supply temperature to the indoor terminal becomes constant.

In the return temperature control, the target return temperature of the load-side circulating fluid returning from the indoor terminal to the load-side heat exchanger is set according to the temperature level (set by the target return temperature setting means). Then, the heat pump device is controlled so that the return temperature (determined by the return temperature determining means) of the load-side circulating liquid flowing into the load-side heat exchanger from the indoor terminal becomes the target return temperature. In this return temperature control, the forward temperature changes according to the load, and when the load is low, the forward temperature can be set to a low temperature during heating and the forward temperature can be set to a high temperature during cooling. Therefore, the efficiency of the heat pump device should be improved. Can be done.

Here, there are various types of indoor terminals, but depending on the type of indoor terminal, during operation (heating operation or cooling operation), due to its characteristics, the forward temperature control and the return temperature control can be performed. Of these, one of them may be particularly preferable.

For example, when a fan coil, which is a type of forced convection terminal, performs cooling operation, the indoor air is circulated by the fan, so that the humidity in the room is dehumidified to some extent evenly (that is, latent heat treatment) when the load is high at the beginning of operation. After that, the operation becomes stable and low load operation. Therefore, even if the return temperature control is performed with the main purpose of improving efficiency, it is unlikely that comfort will be impaired by high humidity during the low load operation.

On the other hand, for example, when a cold / hot water panel, which is a kind of radiant terminal, performs a cooling operation, a high load operation is performed at the initial stage of operation, but when the panel itself cools to some extent, the temperature in the room drops completely. Shift to low load operation without it. In this case, if the return control is performed, the temperature of the cold water supplied to the panel will gradually increase at the timing when the panel itself has cooled to some extent (even if the temperature in the room has not yet decreased). As a result, the indoor temperature is less likely to decrease, and as a result, the indoor humidity does not decrease completely during the low load operation, resulting in an unpleasant situation. Therefore, when the cold / hot water panel performs the cooling operation, it is preferable to control the forward temperature in order to surely lower the humidity in the room.

For example, an underfloor radiator, which is a type of natural convection terminal, has a function of heating the floor of the living room directly above by heating the underfloor and a function of sending warm air under the floor to the living room by natural convection to heat the room. Do both. At this time, since the heating of the living room is indirectly performed through the heating of the underfloor space, it is desirable to maintain the underfloor temperature as high as possible in order to keep the living room comfortable.

If the return temperature control is performed during the heating operation of the underfloor radiator, the temperature of the hot water will drop at the timing when the underfloor space warms up (even if the living room has not warmed up yet), and as a result, the living room will warm up. It becomes difficult. On the other hand, if the forward temperature control is performed, the underfloor radiator stably exerts an output, so that the living room warms up quickly. Therefore, when the underfloor radiator performs the heating operation, it is preferable to control the forward temperature in order to ensure the comfort of the living room space.

Therefore, according to claim 1, a terminal determination means and a switching control means are provided. The terminal determination means determines the type of the indoor terminal to be operated based on the operation request of the indoor terminal. Then, the switching control means selectively switches and executes either the forward temperature control or the return temperature control based on the determination result of the terminal determination means. As a result, the forward temperature control and the return temperature control of the forward temperature control and the return temperature control are performed according to whether the heating operation or the cooling operation is performed for each type of the indoor terminal in accordance with the characteristics of the indoor terminal as described above. Of these, the optimum control can be executed.

Further, as described above, for example, when the cold / hot water panel performs the cooling operation or the underfloor radiator performs the heating operation, the forward temperature control is particularly preferable. According to claim 1 , when a plurality of indoor terminals are connected to the load side heat exchanger and a specific type of indoor terminal such as the cold / hot water panel or the underfloor radiator is operated, other than that. Priority is given to the indoor terminal of the above, and the control corresponding to the specific type of indoor terminal (in this example, the forward temperature control) is executed. As a result, the optimum control for the specific type of indoor terminal can be reliably executed.

Further , according to claim 2 , the humidity in the room can be surely lowered by controlling the forward temperature during the cooling operation of the cold / hot water panel.

Further , according to claim 3 , the living room can be quickly warmed up and the comfort of the living room space can be ensured by controlling the temperature during the heating operation of the underfloor radiator.

Further , according to claim 4 , the target return temperature can be set by a simple method from the temperature level in the setting operation means both during the cooling and heating operations. As a result, the setting operation means can be configured to set the temperature level at which the user goes to the indoor terminal (rather than the return temperature from the indoor terminal, which is difficult for the user to imagine).

Further , according to claim 5 , for each type of indoor terminal, the rotation speed of the compressor is set so as to be the rotation speed corresponding to the forward temperature control or the rotation speed corresponding to the return temperature control. It can be controlled and the optimum control for the indoor terminal can be executed.

The figure which shows the whole schematic structure of the structural example of the heat pump type temperature control system of one Embodiment of this invention. The figure which shows the whole schematic structure of another configuration example of the heat pump type temperature control system of one Embodiment of this invention. Diagram showing the external structure of the main remote controller A diagram schematically showing the refrigeration cycle during heating / cooling operation of the outdoor unit. Functional configuration diagram showing the main functions of the outdoor unit control unit The figure which shows the recommended control mode by type of the indoor terminal in a list. Flow chart showing the control procedure executed by the compressor control unit and the expansion valve control unit during heating FIG. 5 is a flowchart showing the detailed procedure of step S100 in FIG. 7 (a). Flow chart showing the control procedure executed by the compressor control unit and the expansion valve control unit during cooling. FIG. 5 is a flowchart showing the detailed procedure of step S100A of FIG. 8A. A sequence diagram showing an example of heating operation behavior in the configuration example shown in FIG. A sequence diagram showing an example of cooling operation behavior in the configuration example shown in FIG. The figure which shows the whole schematic structure of the heat pump type temperature control system of one Embodiment of this invention yet another configuration example. The figure which shows the whole schematic structure of the heat pump type temperature control system of one Embodiment of this invention yet another configuration example.

Next, an embodiment of the present invention will be described with reference to FIGS. 1 to 14.

<Configuration of an example of temperature control system>
FIG. 1 shows an overall schematic configuration of a configuration example of the heat pump type temperature control system of the present embodiment. In FIG. 1, the heat pump type temperature control system 100 is connected to an outdoor unit 1 as a heat pump heat source machine installed outdoors via a cold / hot water convection pipe 2 and a cold / hot water return pipe 3 to the outdoor unit 1. Two indoor terminals (in this example, an underfloor radiator 41 which is a natural convection terminal and also has a heat dissipation function by radiation) and a panel radiator 42 which is a radiation terminal. One) and.

The underfloor radiator 41 uses the hot water heated by the outdoor unit 1 to dissipate heat to the air in the room (however, the underfloor room; details will be described later) to heat the room.

The panel radiator 42 uses the hot water heated by the outdoor unit 1 to dissipate heat to the indoor air and heat the room.

At this time, the underfloor radiator 41 is arranged in the underfloor room of the upper and lower two-layer structure composed of the living room and the underfloor room located below the living room, and the panel radiator 42 is arranged in the living room. Then, one outgoing header 91 is provided in the middle of the cold / hot water outgoing pipe 2 extending from the outdoor unit 1, and the portion of the cold / hot water outgoing pipe 2 upstream of the outgoing header 91 is one common outgoing pipe. It is configured as 2A, and cold / hot water (corresponding to the load-side circulating fluid) is supplied from the outdoor unit 1. The portion 2B downstream of the outgoing header 91 of the cold / hot water outgoing pipe 2 is a plurality of (two in this example) outgoing pipes, that is, the outgoing pipe 2B1 to the underfloor radiator 41 and the panel radiator 42. It is connected to the outgoing header 91 in a form of branching to the outgoing pipe 2B2 to.

Similarly, one return header 92 is provided in the middle of the cold / hot water return pipe 3 extending to the outdoor unit 1, and a plurality of cold / hot water return pipes 3 upstream of the return header 92 (3B) ( In this example, it is divided into two) return pipes, that is, a return pipe 3B1 from the underfloor radiator 41 and a return pipe 3B2 from the panel radiator 42. The portion of the cold / hot water return pipe 3 downstream of the return header 92 is configured as one common return pipe 3A (that is, the branched return pipes 3B1 and 3B2 are gathered on the upstream side of the common return pipe 3A. The cold / hot water introduced through the return pipes 3B1 and 3B2 (which is connected to the return header 92) is returned to the outdoor unit 1.

A plurality of the outgoing pipes 2B1 to the underfloor radiator 41 and the outgoing pipes 2B2 to the panel radiator 42 can be opened and closed by a drive signal from the thermal valve controller CV (two in this example). Thermal valves V1 and V2 are provided respectively. In this example, in the living room, the heating / cooling operation of the indoor terminal (in this example, the underfloor radiator 41 and the panel radiator 42) (however, in the case of only the underfloor radiator 41 and the panel radiator 42, only heating is performed. The same) The main remote control device RM as a setting operation means for performing the operation, the terminal remote control device RA for performing the heating / cooling operation (however, only heating in this case) of the underfloor radiator 41, and the panel radiator. A terminal remote control device RB for performing the heating / cooling operation (however, in this case, only heating) of 42 is provided. The main remote control device RM, the terminal remote control device RA, and the terminal remote control device RB correspond to the operation means described in each claim.

A function equivalent to that of the main remote controller RM may be added to each of the terminal remote controller RA and RB, and the main remote controller RM may be omitted. In that case, the remote control devices RA and RB for each terminal are provided with the functions of the main remote control device RM described below. In this case, the terminal remote controller devices RA and RB correspond to the setting operation means, respectively.

The main remote controller RM outputs a control signal SS1 in response to a user operation. This control signal SS1 is input to an outdoor unit control unit (described later) that controls the outdoor unit 1, thereby controlling the flow rate, temperature, and the like of cold and hot water supplied to the common outbound pipe 2A. Further, in response to this, the control signal SS2 is output from the outdoor unit control unit to the thermal valve controller CV, and the thermal valve V1 is generated by the control signals S1 and S2 output from the thermal valve controller CV accordingly. , V2 opening and closing operation can be controlled. Further, the control signal Sa output in response to the operation in the remote controller device RA for the terminal is input to the thermal valve controller CV, and the control signal S1 output from the thermal valve controller CV in response to this is input to the thermal valve controller CV. The opening / closing operation of the thermal valve V1 can be controlled. Further, the control signal Sb output in response to the operation in the remote controller device RB for the terminal is input to the thermal valve controller CV, and the control signal S2 output from the thermal valve controller CV accordingly. The opening / closing operation of the thermal valve V2 can be controlled.

On the other hand, the return pipes 3B1 from the underfloor radiator 41 and the return pipes 3B2 from the panel radiator 42 are provided with return temperature sensors 54 and 55, respectively. These return temperature sensors 54 and 55 detect the temperature (return temperature) of hot water or cold water in the corresponding return pipes 3B1 and 3B2, respectively, and output a detection signal indicating the detection result to the thermal valve controller CV.

The thermal valve controller CV corresponds to the operation of the main remote controller device RM and the terminal remote controller devices RA and RB, and based on the return temperature detected by the return temperature sensors 54 and 55, the thermal valve V1 , V2 open / close control is performed (details will be described later). As a result, the user can control the operating state of the underfloor radiator 41 and the panel radiator 42 by appropriately operating the remote controller devices RM, RA, and RB.

<Another configuration of the temperature control system>
On the other hand, FIG. 2 shows an overall schematic configuration of another configuration example of the heat pump type temperature control system of the present embodiment. The same parts as those in FIG. 1 are designated by the same reference numerals, and the description thereof will be omitted or simplified as appropriate. In FIG. 2, in the heat pump type temperature control system 100, the outdoor unit 1 is replaced with the underfloor radiator 41 and the panel radiator 42 in FIG. 1 as the indoor terminal, which is a radiant terminal (provided that it is a radiation terminal). The cold / hot water panel 51 (which also has a heat dissipation function by natural convection) and the fan coil unit 52, which is a forced convection type terminal, are connected via the cold / hot water outflow pipe 2 and the cold / hot water return pipe 3.

The cold / hot water panel 51 dissipates heat or absorbs heat from the air in the room by using the hot water heated by the outdoor unit 1 or the cooled cold water, and heats or cools the room.

The fan coil unit 52 contains a heat exchanger (not shown), a blower fan (not shown), a thermal valve V3, an indoor temperature sensor (not shown) for detecting the indoor temperature, and a fan coil unit. It includes a water temperature sensor (not shown) that detects the temperature of hot water or cold water flowing through the 52, a terminal control unit 29, and the like. The terminal control unit 29 receives a signal from the indoor temperature sensor inside the fan coil unit 52 and a signal from the terminal remote controller RC (described later), and controls the drive of the blower fan and the thermal valve V3. As a result, the fan coil unit 52 allows the hot water or cooled cold water heated by the outdoor unit 1 to pass through the heat exchanger inside, and drives the blower fan to exchange heat with the indoor air. , Heat or cool the room.

The cold / hot water panel 51 is arranged in the A room of the A room and the B room, and the fan coil unit 52 is arranged in the B room. Then, of the downstream side portion 2B of the cold / hot water outflow pipe 2, the outbound pipe 2B1 extends to the cold / hot water panel 51, and the outbound pipe 2B2 extends to the fan coil unit 52. Correspondingly, the upstream side portion 3B of the cold / hot water return pipe 3 is composed of a return pipe 3B1 from the cold / hot water panel 51 and a return pipe 3B2 from the fan coil unit 52.

Then, in this example, the main remote controller RM and the cold / hot water panel 51 for performing the heating / cooling operation of the indoor terminal (in this example, the cold / hot water panel 51 and the fan coil unit 52) in the room A. The terminal remote controller device RA for performing the heating / cooling operation of the above is provided. Further, in this example, a wireless terminal remote control device RC for remotely controlling the fan coil unit 52 is provided in the room B.

Similarly to the above, the main remote control device RM may be omitted by adding a function equivalent to that of the main remote control device RM to the terminal remote control device RA. In this case, the terminal remote control device RA is the setting operation means. Corresponds to.

Similar to FIG. 1, the thermal valve controller CV corresponds to the operation of the main remote controller device RM and the terminal remote controller device RA, and is based on the return temperature detected by the return temperature sensors 54 and 55. It controls the opening and closing of the thermal valve V1. As a result, the user can control the operating state of the cold / hot water panel 51 and the fan coil unit 52 by appropriately operating the remote controller devices RM and RA.

The terminal remote control device RC has a heating switch 24 as a heating instruction means for causing the fan coil unit 52 to perform a heating operation for heating the room, and for causing the fan coil unit 52 to perform a cooling operation for cooling the room. A cooling switch 25 as a cooling instruction means, a stop switch 26 for stopping the operation of the fan coil unit 52, an indoor temperature setting switch 27 for setting the indoor temperature, and a display unit 28 for displaying the indoor set temperature and the operating state. The terminal control unit 29 is communicably connected to the terminal control unit 29.

<Main remote control device>
Next, the details of the main remote controller device RM shown in FIGS. 1 and 2 will be described.

FIG. 3 shows the appearance of the main remote controller RM. The main remote controller RM includes a display unit 250, the outdoor unit 1, and the indoor terminal (two underfloor radiator 41 and panel radiator 42 in the example of FIG. 1, cold / hot water panel 51 in the example of FIG. 2). A "run / stop" button 253 for instructing the start / stop of operation, a "timer" button 254 for instructing the indoor terminal to operate with a timer, and an operation mode (cooling / heating) of the indoor terminal. , Normal mode, save mode, etc.), "Operation switching" button 255, "Back" button 257 to return the screen display to the previous screen, "Menu / Enter" button 258, and up and down. A cross key 259 in the left-right direction is provided. The "run / stop" button 253, the "timer" button 254, the "operation switching" button 255, the "back" button 257, and the "menu / decision" button 258 are simply referred to as appropriate below. It is referred to as "operation button 253, etc.", and further, these operation buttons 253, etc. and the cross key 259 are collectively referred to as "operation unit 259, etc.". Although not shown, the main remote controller RM has a built-in CPU, a memory as a storage means, and the like.

The display unit 250 can switch and display various screens under the control of the CPU. In the illustrated example, the display unit 250 has a setting screen 200 for making settings related to the entire temperature control system 100 shown in FIG. 1 or 2, including temperature setting of hot water / cold water, cooling / heating switching, and the like. Is displayed. The setting screen 200 is arranged in the center and has an operating state display area 200A indicating the operating state of the entire temperature control system 100, and cold / hot water arranged at the right end and supplied from the outdoor unit 1 to the entire temperature control system 100. It is provided with a temperature setting display area 200B for displaying the set temperature (corresponding to the numerical value of the temperature level. The user can set it by using the operation unit 259 or the like).

In the illustrated example, in the operation state display area 200A, "hot water heating operation in progress" indicating a state in which hot water is supplied from the outdoor unit 1 and the temperature control system 100 as a whole is being heated is displayed. There is. Further, in the temperature setting display area 200B, a set temperature "40 ° C." of hot water set in advance (variably) by the user for heating is displayed.

<Outdoor unit configuration>
Next, a schematic system configuration of the outdoor unit 1 is shown in FIG. 4 (a). In FIG. 4A, the outdoor unit 1 circulates a refrigerant circulation circuit 21 that circulates a synthetic compound gas such as HFC as a refrigerant to absorb and dissipate heat outdoors, and circulates, for example, an antifreeze liquid as the cold / hot water to circulate the indoor terminal. The machine (two of the underfloor radiator 41 and the panel radiator 42 in the example of FIG. 1, two of the cold / hot water panel 51 and the fan coil unit 52 in the example of FIG. 2) absorbs and dissipates heat (the cold / hot water outflow pipe 2). It is a heat pump type heat source machine that exchanges heat between the cold / hot water circulation circuit 22 (consisting of the cold / hot water return pipe 3) and the hot / cold water circulation circuit 22.

That is, the refrigerant circulation circuit 21 exchanges heat between the refrigerant and the outside air, the four-way valve 6 provided in the outdoor unit 1 for switching the circulation direction of the refrigerant, the compressor 7 for compressing the refrigerant, and the outside air. An outdoor heat exchanger 8 (corresponding to a heat pump heat exchanger), an expansion valve 9 for decompressing and expanding the refrigerant, and the cold / hot water circulating in the cold / hot water outflow pipe 2 and the cold / hot water return pipe 3 and the refrigerant. A water-refrigerant heat exchanger 11 (corresponding to a load-side heat exchanger) for heat exchange is connected by a refrigerant pipe 15. The heat pump device is composed of the four-way valve 6, the compressor 7, the outdoor heat exchanger 8, and the expansion valve 9 connected to each other by the refrigerant pipe 15. Further, an outdoor fan 10 for blowing air to the outdoor heat exchanger 8 is further provided.

The four-way valve 6 is a valve provided with four ports, and for each of the 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. (Constituent) Switch which of the two ports for the other refrigerant subpath 15b is connected. The two ports for the refrigerant sub-path 15b are connected to each other 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 the low-pressure gas state to bring it into the high-pressure gas state, and also functions as a pump that circulates the refrigerant in the entire refrigerant pipe 15 in the outdoor unit 1. A discharge temperature sensor 55 is provided in the refrigerant sub-path 15b on the discharge side of the compressor 7, detects the temperature of the refrigerant discharged from the compressor 7 (refrigerant discharge temperature), and represents the detection result. The signal is output to the outdoor unit control unit CU described later. Further, a refrigerant temperature sensor 57 is provided in the refrigerant main path 15a between the expansion valve 9 and the water-refrigerant heat exchanger 11, and flows between the expansion valve 9 and the water-refrigerant heat exchanger 11. The temperature of the refrigerant is detected, and a detection signal indicating the detection result is output to the outdoor unit control unit CU described later.

Further, the two ports for the refrigerant main path 15a of the four-way valve 6 are connected to each other by the refrigerant main path 15a arranged in a loop, and the outdoor heat exchanger 8 and the outdoor heat exchanger 8 are connected on the refrigerant main path 15a. The expansion valve 9 and the water-refrigerant heat exchanger 11 are provided in order (in the example shown in FIG. 4A, the refrigerant main path 15a is counterclockwise).

The outdoor heat exchanger 8 functions as an evaporator that absorbs the heat of the outside air into the refrigerant and evaporates it into a gas state when the temperature of the refrigerant in a liquid state passing through the inside thereof is lower than the temperature of the outside air outside the room. Further, when the temperature of the refrigerant in a gas state passing through the inside is higher than the temperature of the outside air outside the room, it functions as a condenser that dissipates the heat of the refrigerant and condenses it into a liquid state (FIG. 4 (b) described later). reference).

The outdoor fan 10 blows air to the outdoor heat exchanger 8 to improve the performance of the outdoor heat exchanger 8.

The expansion valve 9 functions to expand the refrigerant in a high-pressure liquid state under reduced pressure to bring it into a low-pressure liquid state.

The water-refrigerant heat exchanger 11 is connected to the refrigerant main path 15a as described above to allow the refrigerant to pass through the inside thereof, and is also connected to the cold / hot water outflow pipe 2 and the cold / hot water return pipe 3 to be inside the water-refrigerant heat exchanger 11. Let cold and hot water pass through. When the temperature of the gas-state refrigerant passing through the inside of the water-refrigerant heat exchanger 11 is higher than the temperature of cold / hot water, it functions as a condenser that dissipates the heat of the refrigerant to cold / hot water and condenses it into a liquid state. .. Further, when the temperature of the liquid refrigerant passing through the inside of the water-refrigerant heat exchanger 11 is lower than the temperature of the cold / hot water, it is used as an evaporator that absorbs the heat of the cold / hot water with respect to the refrigerant and evaporates it into a gas state. It works (see FIG. 4 (b) below).

On the other hand, the cold / hot water circulation circuit 22 includes the water-refrigerator heat exchanger 11 provided in the outdoor unit 1, a circulation pump 12 for applying circulation pressure to the cold / hot water, a systurn tank 13, and the indoor terminal unit ( In the example of FIG. 1, the underfloor radiator 41 and the panel radiator 42 are used, and in the example of FIG. 2, the cold / hot water panel 51 and the fan coil unit 52 are used. It is formed by connecting the pipe 2A) and the hot / cold water return pipe 3 (specifically, the common return pipe 3A).

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

The systan tank 13 separates air bubbles generated in cold / hot water due to cavitation or the like (air / water separation function), absorbs expanded cold / hot water in the cold / hot water circulation circuit 22, and replenishes cold / hot water.

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

The cold / hot water outflow pipe 2 (specifically, the common outbound pipe 2A) on the outlet side (outflow side) of the water-refrigerant heat exchanger 11 is provided with an outflow temperature sensor 56A as an outflow temperature determining means. The temperature (forward temperature) of hot water or cold water in the common outgoing pipe 2A is determined (detected in this example; the same applies hereinafter), and a detection signal indicating the detection result is output to the outdoor unit control unit CU described later. Further, the cold / hot water return pipe 3 (specifically, the common return pipe 3A) on the inlet side (inflow side) of the water-refrigerant heat exchanger 11 is provided with a return temperature sensor 56B as a return temperature determining means. The temperature (return temperature) of hot water or cold water in the common return pipe 3A is determined (detected in this example; the same applies hereinafter), and a detection signal indicating the detection result is output to the outdoor unit control unit CU described later.

The outdoor unit 1 is provided with an outdoor unit control unit CU (corresponding to a heat source control unit) that controls the outdoor unit 1. The outdoor unit control unit CU is mainly composed of a microcomputer equipped with a CPU, a ROM, a RAM, and the like. The outdoor unit control unit CU and the main remote controller RM are connected by a bidirectional communication line, and signals can be exchanged with each other (see FIG. 1). As a result, as shown in FIG. 1, the outdoor unit control unit CU controls the entire outdoor unit 1 based on the control signal SS1 from the main remote controller device RM (details will be described later), and the corresponding control. The signal SS2 is output to the thermal valve controller CV.

In the configuration example shown in FIG. 2, in particular, between the outdoor unit control unit CU and the terminal control unit 29 of the fan coil unit 52, for example, a signal from the terminal control unit 29 is transmitted in one direction. It is connected by a terminal control line (so-called E-con communication line) (see FIG. 2). For example, when the heating switch 24 (or the cooling switch 25) of the remote control device RC for a terminal is operated by a user and an instruction to start operation is given, the terminal control unit 29 receives the instruction signal. Then, in response to the received instruction signal, the terminal control unit 29 outputs a hot water request signal (or a cold water request signal related to the cooling operation) SC related to the heating operation to the outdoor unit control unit CU (FIG. 4). (A) and the imaginary line in FIG. 4 (b)). When the heating or cooling is stopped after the operation is started, an appropriate stop instruction operation by the user (for example, the heating switch 24 or the cooling switch 25 is pressed again, or a separately provided stop switch is pressed. , Etc.), the terminal control unit 29 outputs a stop request signal (not shown) for the heating operation (or cooling operation) to the outdoor unit control unit CU.

When the fan coil unit 52 is provided as described above in the configuration example shown in FIG. 2, the configuration is not limited to the configuration in which the fan coil unit 52 is operated by the terminal remote controller device RC. That is, the fan coil unit 52 itself may be provided with a switch or a display unit having the same function as the switch of the terminal remote control device RC, and the terminal remote control device RC may be omitted. In this case, when an instruction to start operation is given by the user operating a switch or the like of the fan coil unit 52, the terminal control unit 29 receives the instruction signal, and the hot water is sent to the outdoor unit control unit CU. The request signal (or the cold water request signal) SC is output. Similarly, when the user performs a stop instruction operation using the switch or the like of the fan coil unit 52, the terminal control unit 29 sends the outdoor unit control unit CU the stop request signal for heating operation (or cooling operation). Is output. The same applies to other forced convection terminals such as the hot water room heater described later.

In the refrigerant circulation circuit 21 having the above configuration, 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. do. FIG. 4A shows the circulation direction during the heating operation in the configuration examples shown in FIGS. 1 and 2, and the refrigerant discharged from the compressor 7 is the water-refrigerant heat exchanger 11, the expansion valve 9, and the expansion valve 9. The outdoor heat exchanger 8 is distributed in this order. As a result, the gas-state refrigerant sucked at low temperature and low pressure is compressed by the compressor 7 to become high temperature and high pressure gas, and then the cold temperature is generated in the water-refrigerant heat exchanger 11 (functioning as a condenser). It changes to a high-pressure liquid while releasing heat to the hot water from the water return pipe 3. The refrigerant that has become liquid in this way is depressurized by the expansion valve 9 to become a low-pressure liquid that easily evaporates. After that, the low-pressure liquid evaporates in the outdoor heat exchanger 8 (functioning as an evaporator) and changes into a gas to absorb heat from the outside air. Then, the refrigerant returns to the compressor 7 again as a low-temperature, low-pressure gas.

At this time, the hot water heated by the water-refrigerant heat exchanger 11 as described above is transferred from the cold / hot water going pipe 2 to the indoor terminal (in the example of FIG. 1, the underfloor radiator 41 and the panel radiator 42). In the example of FIG. 2, it is supplied to the cold / hot water panel 51 and the fan coil unit 52) to dissipate heat to the room air to heat the room, and then passes through the systurn tank 13 and again the circulation pump 12 Return to. By exchanging heat between the refrigerating cycle of the refrigerant circulation circuit 21 and the cold / hot water circulation circuit 22 as described above, a heating operation for raising the temperature of the indoor air is performed.

On the other hand, FIG. 4B shows the circulation direction during the cooling operation in the configuration example shown in FIG. 2, and the refrigerant discharged from the compressor 7 is the outdoor heat exchanger 8, the expansion valve 9, and the water-refrigerant heat. It is distributed in the order of the exchanger 11. As a result, the gas-state refrigerant sucked at low temperature and low pressure is compressed by the compressor 7 to become high temperature and high pressure gas, and then the outdoor fan 10 is used in the outdoor heat exchanger 8 (functioning as a condenser). By being cooled by the air blown, it changes to a high-pressure liquid while releasing heat to the outside air. The refrigerant that has become liquid in this way is depressurized by the expansion valve 9 to become a low-pressure liquid that easily evaporates. After that, the low-pressure liquid evaporates in the water-refrigerant heat exchanger 11 (functioning as an evaporator) and changes into a gas to absorb heat from the cold water from the cold / hot water return pipe 3. Then, the refrigerant returns to the compressor 7 again as a low-temperature, low-pressure gas.

At this time, the cold water cooled by the water-refrigerant heat exchanger 11 as described above is transferred from the cold / hot water outflow pipe 2 to the indoor terminal (the cold / hot water panel 51 and the fan coil unit 52 in the example of FIG. 2). ), The room is cooled by absorbing heat from the room air, and then passes through the system tank 13 and returns to the circulation pump 12 again. By exchanging heat between the refrigerating cycle of the refrigerant circulation circuit 21 and the cold / hot water circulation circuit 22 as described above, a cooling operation for lowering the temperature of the indoor air is performed.

<Outdoor unit control unit>
Next, the main functional configuration of the outdoor unit control unit CU will be described with reference to FIG.

As shown in FIG. 5, the outdoor unit control unit CU functionally includes a compressor control unit 61 as a compressor control means and an expansion valve control unit 62 as an expansion valve control means.

The compressor control unit 61 includes an forward temperature control unit 61A and a return temperature control unit 61B.

The forward temperature control unit 61A performs so-called forward temperature control in which the rotation speed of the compressor 7 is controlled according to the forward temperature of hot water or cold water detected by the forward temperature sensor 56A. In particular, in this example, the forward temperature control unit 61A sets the forward temperature detected by the forward temperature sensor 56A corresponding to, for example, an operation of the operation unit 259 in the main remote controller RM (details omitted). The rotation speed of the compressor 7 is controlled so as to reach a desired target temperature (target temperature). In this forward temperature control, since the supply temperature to the indoor terminal is constant, it is easy to maintain the output of the indoor terminal.

The return temperature control unit 61B performs so-called return temperature control that controls the rotation speed of the compressor 7 according to the return temperature of hot water or cold water detected by the return temperature sensor 56B. In particular, in this example, the return temperature control unit 61B sets the return temperature detected by the return temperature sensor 56B, for example, in response to an operation of the operation unit 259 or the like in the main remote controller RM (details will be described later). The rotation speed of the compressor 7 is controlled so as to reach a desired target temperature (target return temperature). In this return temperature control, the forward temperature changes according to the load, and when the load is low, the forward temperature can be set to a low temperature during heating and a high forward temperature during cooling. Therefore, the efficiency of the heat pump device is high. It can be improved.

The expansion valve control unit 62 controls the valve opening degree of the expansion valve 9 according to the refrigerant discharge temperature detected by the discharge temperature sensor 55. In particular, in this example, in the expansion valve control unit 62, the refrigerant discharge temperature detected by the discharge temperature sensor 55 is appropriately set (details are omitted) in response to, for example, the operation of the main remote controller device RM. The valve opening degree of the expansion valve 9 is controlled so as to reach the target discharge temperature.

Here, there are generally various types of indoor terminals such as the underfloor radiator 41, the panel radiator 42, the cold / hot water panel 51, and the fan coil unit 52. At this time, depending on the type of the indoor terminal, one of the above-mentioned forward temperature control and return temperature control may be particularly preferable during operation (heating operation or cooling operation) due to its characteristics. This will be described with reference to FIG.

FIG. 6 is a diagram showing a list of preferable ones of the forward temperature control and the return temperature control for each type of indoor terminal.

In FIG. 6, for example, when the fan coil unit 52 shown in FIG. 2, which is a kind of forced convection type terminal, performs a cooling operation, the blower fan circulates the indoor air, so that the operation is started at the initial stage. After dehumidifying the humidity in the room to some extent (that is, latent heat treatment) at the time of high load, stable low load operation is performed. Therefore, even if the return temperature control is performed with the main purpose of improving efficiency, it is unlikely that comfort will be impaired by high humidity during the low load operation (hence, return temperature control is preferable).

On the other hand, for example, when the cold / hot water panel 51 shown in FIG. 2, which is a kind of radiant terminal, performs a cooling operation, a high load operation is performed at the initial stage of the operation, but the panel itself becomes cold to some extent. Then, even if the temperature in the room has not dropped completely, the operation shifts to low load operation. In this case, if the return control is performed, the temperature of the cold water supplied to the panel will gradually increase at the timing when the panel itself has cooled to some extent (even if the temperature in the room has not yet decreased). As a result, the indoor temperature is less likely to decrease, and as a result, the indoor humidity does not decrease completely during the low load operation, resulting in an unpleasant situation. Therefore, when the cold / hot water panel 51 performs the cooling operation, it is preferable to control the forward temperature in order to surely lower the humidity in the room.

Further, for example, the underfloor radiator 41 shown in FIG. 1, which is a kind of natural convection terminal, has a function of heating the floor surface of the living room directly above by heating the underfloor room and naturally warms the underfloor room. It performs both the function of sending to the living room by convection and heating. At this time, since the heating of the living room is indirectly performed through the heating of the underfloor room space, it is desirable to maintain the temperature of the underfloor room as high as possible in order to keep the living room space comfortable.
If the return temperature control is performed during the heating operation of the underfloor radiator 41, the temperature of the hot water going down will gradually decrease at the timing when the underfloor room space warms up (even if the living room has not warmed up yet). Becomes hard to warm up. On the other hand, if the forward temperature control is performed, the underfloor radiator 41 stably exerts an output, so that the living room is quickly warmed up. Therefore, when the underfloor radiator 41 is operated (heating operation), it is preferable to control the forward temperature in order to ensure the comfort of the living room space.

On the other hand, the panel radiator 42 shown in FIG. 1, which is a kind of radiant terminal, only heats the nearest region by radiant heat transfer, and therefore, the main purpose is to improve efficiency. It is preferable to control the return temperature.

In addition, indoor terminals other than those described above, for example, as shown in FIG. 6, a panel convector which is a radiant terminal (however, it also has a heat dissipation function by natural convection) and a hot water room heater which is a forced convection terminal. Also, for the floor heating panel, which is a radiant terminal (however, it also has a heat dissipation function by conduction), and the snow melting terminal, which is a conduction terminal, the above-mentioned return is focused on improving efficiency during operation (that is, during heating operation). It is preferable to control the temperature. The same applies to the heating operation of the fan coil unit 52 and the heating operation of the cold / hot water panel 51.

In the present embodiment, in view of the above, depending on what kind of indoor terminal unit 1 is connected to the outdoor unit 1 via the cold / hot water outflow pipe 2 and the cold / hot water return pipe 3. The compressor control unit 61 of the outdoor unit control unit CU switches between the forward temperature control by the forward temperature control unit 61A and the return temperature control by the return temperature control unit 61B. Hereinafter, the details of the method will be described step by step using the flowcharts of FIGS. 7 to 10.

<Control during heating>
First, the control contents during the heating operation will be described with reference to the flowcharts of FIGS. 7 (a) and 7 (b).

<Control of compressor control unit>
First, the control procedure by the compressor control unit 61 during the heating operation is shown in the flowchart of FIG. 7A. In FIG. 7A, first, in step S5, the compressor control unit 61 initializes the flag F indicating the execution of the forward temperature control to 0. Then, the process proceeds to step S10.

In step S10, the compressor control unit 61 determines whether or not the outdoor unit 1 is in the operation start state. Specifically, the operation start state is defined as, for example, from the stopped state when an appropriate operation start operation of the outdoor unit 1 is performed by the user via the main remote controller device RM or the terminal remote controller devices RA, RB, RC. This is the case when the outdoor unit 1 is started, or when the operation of the outdoor unit 1 is restarted after the operation is stopped (details will be described later). The determination in step S10 is not satisfied (S10: NO) until the operation start state is reached, and the loop waits. When the operation start state is reached, the determination in step S10 is satisfied (S10: YES), and the process proceeds to step S15.

In step S15, the compressor control unit 61 determines whether or not the outdoor unit 1 is in the operation end state. That is, when the heating operation is performed under the control of the rotation speed as described later and the heating load becomes small, the return temperature detected by the return temperature sensors 54 and 55 will eventually change even if the outdoor unit 1 is not operated. May reach the target return temperature or higher. In this case, the outdoor unit 1 is stopped by the known control by the outdoor unit control unit CU and enters the standby state (that is, the operation of the outdoor unit 1 is temporarily terminated). In step S15, the compressor control unit 61 determines whether or not the outdoor unit 1 is in this standby state. When the operation end state (that is, the standby state) is reached, the determination in step S15 is satisfied (S15: YES), and this flow ends. On the other hand, while the operation end state (that is, the standby state) is not reached, the determination in step S15 is not satisfied (S15: NO), and the process proceeds to step S100.

In step S100, the target temperature during heating is set according to the set temperature of the hot water appropriately set by the operation of the operation unit 259 or the like on the main remote controller RM. Perform processing (details will be described later). When this step S100 is completed, the process proceeds to step S17.

In step S17, the compressor control unit 61 determines whether or not the flag F is 1 (in other words, whether or not the forward temperature control is switched to and the target forward temperature is calculated in step S100 described later). .. When the target going temperature is calculated with the flag F = 1 (details will be described later), the determination is satisfied (S17: YES), and the process proceeds to step S20.

In step S20, in the compressor control unit 61, the forward temperature detected by the forward temperature control unit 61A from the forward temperature sensor 56A at this time is lower than the target forward temperature set in the step S100. Judge whether or not. If the forward temperature is lower than the target forward temperature, the determination is satisfied (S20: YES), and the process proceeds to step S25. In step S25, the compressor control unit 61 increases the rotation speed of the compressor 7 by the forward temperature control unit 61A. After that, the process returns to step S15 and the same procedure is repeated.

In the determination in step S20, if the forward temperature is equal to or higher than the target forward temperature, the determination is not satisfied (S20: NO), and the process proceeds to step S30. In step S30, the compressor control unit 61 reduces the rotation speed of the compressor 7 by the forward temperature control unit 61A. After that, the process returns to step S15 and the same procedure is repeated.

As described above, by the processing of step S20, step S25, and step S30, the forward temperature control unit 61A controls the rotation speed of the compressor 7 so that the forward temperature matches the target forward temperature. Is done by.

On the other hand, if the target return temperature is calculated while the flag F remains 0 in step S17 (details will be described later), the determination is not satisfied (S17: NO), and the process proceeds to step S35.

In step S35, in the compressor control unit 61, the return temperature detected by the return temperature control unit 61B from the return temperature sensor 56b at this time is lower than the target return temperature set in step S100. Judge whether or not. If the return temperature is below the target return temperature, the determination is satisfied (S35: YES), and the process proceeds to step S40. In step S40, the compressor control unit 61 increases the rotation speed of the compressor 7 by the return temperature control unit 61B. After that, the process returns to step S15 and the same procedure is repeated.

In the determination in step S35, if the return temperature is equal to or higher than the target return temperature, the determination is not satisfied (S35: NO), and the process proceeds to step S45. In step S45, the compressor control unit 61 reduces the rotation speed of the compressor 7 by the return temperature control unit 61B. After that, the process returns to step S15 and the same procedure is repeated.

As described above, the return temperature control unit 61B controls the rotation speed of the compressor 7 so that the return temperature matches the target return temperature by the processes of steps S35, S40, and S45. Is done by.

Next, the detailed procedure of step S100 will be described with reference to FIG.

In FIG. 8, the compressor control unit 61 first determines in step S110 whether or not the flag F = 1. If F = 0 is not satisfied in step S130 described later and F = 0, the determination is not satisfied (S110: NO), and the process proceeds to step S115.

In step S115, the compressor control unit 61 determines whether or not there is an operation request for the underfloor radiator 41 (see the configuration example shown in FIG. 1). In this determination, for example, the outdoor unit control unit CU acquires the control signal Sa output from the terminal remote controller device RA or the control signal S2 from the thermal valve controller CV to the thermal valve V1 (however, FIG. 1). The illustration in (1) is omitted), and it is sufficient to use a known method such as based on the acquisition result. When the underfloor radiator 41 is provided as in the configuration example shown in FIG. 1 but the operation request is not yet provided, or when the underfloor radiator 41 is not provided in the first place as in the configuration example shown in FIG. The determination is not satisfied (S115: NO), and the process proceeds to step S155.

In step S155, the compressor control unit 61 has a set temperature of hot water (in this case, a temperature appropriately set by the operation of the operation unit 259 or the like on the main remote controller RM) by the return temperature control unit 61B. Based on (40 ° C. in the example shown in 3) and by a known appropriate method (eg, based on a predetermined rule that uniquely determines the target return temperature from the set temperature), the corresponding target. Calculate the return temperature.

As the predetermined rule, for example, as described in Japanese Patent Application Laid-Open No. 2017-133775, the temperature level numerical value itself supplied to the indoor terminal in the heating operation, which is set by the main remote controller RM. A subtraction value Ts-α obtained by subtracting a predetermined numerical value α from the set temperature Ts can be set as the target return temperature Tm. At this time, specifically, in the range of Ts of 30 ° C. to 60 ° C., an appropriate value in the range of 5 ° C. to 15 ° C. is applied to α. Which value to apply to α may be optionally selectable in the main remote controller RM, or α is fixedly set to an appropriate value in the range of 5 ° C. to 15 ° C. in advance. May be good.

The predetermined rule is not limited to the method in which the target return temperature Tm is a subtraction value obtained by subtracting a predetermined value from the value of the temperature value of hot water itself as described above. For example, when strong / medium / weak indicating the heating intensity is used as the temperature level that can be set in the heating operation, the temperature conversion values corresponding to the strong / medium / weak (for example, strong is 60, medium is 45, and so on. As for weakness, 30) may be stored in advance, and a subtraction value obtained by subtracting a predetermined value from the value (temperature conversion value) Ts may be set as the target return temperature Tm. Alternatively, as the temperature level that can be set in the heating operation, even when a temperature level having 9 levels of heating intensity is used by using a numerical value of, for example, 1 to 9 for expressing the heating intensity, 9 levels of heating are used. The temperature conversion value corresponding to the strength of the above may be stored in advance, and the subtraction value obtained by subtracting a predetermined value from the value (temperature conversion value) Ts may be set as the target return temperature Tm.

The return temperature control unit 61B of the compressor control unit 61 that executes this step S155 functions as the target return temperature setting means according to each claim. After calculating the target return temperature as described above, the process proceeds to step S17 of FIG. 7, and the above procedure is repeated thereafter. As a result, step S155 → step S17 → step S35 → step S40 or step S45 → step S15 → step S110 → step S115 → step S155 → ... The compressor speed is increased / decreased (that is, the return temperature is controlled).

On the other hand, in step S115, when the underfloor radiator 41 is provided as in the configuration example shown in FIG. 1 and there is an operation request thereof, the determination in step S115 is satisfied (S115: YES), and the step. Move to S130.

In step S130, the compressor control unit 61 sets the flag F to F = 1, which indicates switching to temperature control. Then, the process proceeds to step S135.

In step S135, the compressor control unit 61 is based on the set temperature of hot water by the forward temperature control unit 61A (the temperature appropriately set by the operation of the operation unit 259 or the like in the main remote controller RM described above). The corresponding target forward temperature is calculated by a known method (the target forward temperature can be uniquely determined with respect to the set temperature). The forward temperature control unit 61A of the compressor control unit 61 that executes this step S135 functions as the target forward temperature setting means according to each claim. When step S135 is completed, the process proceeds to step S17 of FIG. After that, through the steps S17 → step S20 → step S25 or step S30 → step S15 as described above, since F = 1, the determination in step S110 is satisfied, and the process proceeds to step S140.

In step S140, the compressor control unit 61 determines whether or not there is a stop request for the underfloor radiator 41 for which an operation request has been made and the heating operation has been started as described above. Regarding this determination as well, for example, the outdoor unit control unit CU acquires the control signal Sa output from the terminal remote controller device RA or the control signal S2 from the thermal valve controller CV to the thermal valve V1. (However, the illustration in FIG. 1 is omitted), and it is sufficient to use a known method such as based on the acquisition result. For example, as in the configuration example shown in FIG. 1, if the underfloor radiator 41 is provided and the operation is performed, but the operation stop request is not yet satisfied, the determination is not satisfied (S140: NO), and the process proceeds to step S135. After that, the same procedure as described above is repeated. As a result, step S135 → step S17 → step S20 → step S25 or step S30 → step S15 → step S110 → step S140 → step S135 → ... Is repeated until the stop request of the underfloor radiator 41 is made. Then, the compressor rotation speed is increased or decreased (that is, the forward temperature control) according to the magnitude of the target forward temperature and the forward temperature.

The compressor control unit 61 that executes the step S140 and the step S115 functions as the terminal determination means according to each claim.

In this way, when there is a request to stop the operation of the underfloor radiator 41 in a state where the underfloor radiator 41 is provided and the heating operation is performed as in the configuration example shown in FIG. 1, step S140 is performed. The determination is satisfied (S140: YES), and the process proceeds to step S150.

In step S150, the compressor control unit 61 returns the flag F to 0, which represents switching to the return temperature control, and then moves to step S155, and the same procedure is repeated thereafter.

As described above, the compressor control unit 61 is used until the underfloor radiator 41 (corresponding to a specific type of indoor terminal in this case) provided in the system issues an operation request and then a stop request. In addition to controlling the forward temperature, the return temperature is controlled in other cases. That is, when the underfloor radiator 41 is operated, the forward temperature control can be performed with priority over other indoor terminals.

The compression that executes the steps S150 and S130 of FIG. 8 and the steps S17, step S20, step S25, step S30, step S35, step S40, and step S45 of FIG. 7A. The machine control unit 61 functions as the switching control means according to each claim.

<Control by expansion valve control unit>
Next, the control procedure by the expansion valve control unit 62 during the heating operation is shown in the flowchart of FIG. 7B. In FIG. 7B, first, in step S60, the expansion valve control unit 62 determines whether or not the outdoor unit 1 is in the operation start state in the same manner as in step S10 of FIG. 7A. The determination in step S60 is not satisfied (S60: NO) until the operation start state is reached, and the loop waits. When the operation start state is reached, the determination in step S60 is satisfied (S60: YES), and the process proceeds to step S65.

In step S65, the expansion valve control unit 62 determines whether or not the outdoor unit 1 is in the operation end state in the same manner as in step S15 of FIG. 7A. If the operation is in the end state (that is, the standby state), the determination in step S65 is satisfied (S65: YES), and this flow is ended. On the other hand, while the operation is not completed (that is, the standby state), the determination in step S65 is not satisfied (S65: NO), and the process proceeds to step S70.

In step S70, the expansion valve control unit 62 determines whether or not the refrigerant discharge temperature detected by the discharge temperature sensor 55 at this point is lower than the target discharge temperature. If the refrigerant discharge temperature is lower than the target discharge temperature, the determination is satisfied (S70: YES), and the process proceeds to step S75.

In step S75, the expansion valve control unit 62 reduces the valve opening degree of the expansion valve 9. Then, the process returns to step S65 and the same procedure is repeated.

On the other hand, in the determination in step S70, if the refrigerant discharge temperature is equal to or higher than the target discharge temperature, the determination is not satisfied (S70: NO), and the process proceeds to step S80.

In step S80, the expansion valve control unit 62 increases the valve opening degree of the expansion valve 9. Then, the process returns to step S65 and the same procedure is repeated.

As described above, by the processing of steps S70, S75, and S80, the refrigerant discharge temperature control for controlling the valve opening degree of the expansion valve 9 so that the refrigerant discharge temperature matches the target discharge temperature is performed. ..

<Control during cooling>
Next, the control contents during the cooling operation will be described with reference to the flowcharts of FIGS. 9A and 9B.

<Control of compressor control unit>
First, the control procedure by the compressor control unit 61 during the cooling operation is shown in the flowchart of FIG. 9A. As shown in FIG. 9A, in this flow, first, step S100A is provided instead of step S100 for performing the heating target temperature setting process in the flow of FIG. 7A, and the main remote control device RM is used. A cooling target temperature setting process is performed in which the target temperature (the target going temperature or the target return temperature) is set according to the set temperature of the cold water appropriately set by the operation of the operation unit 259 or the like (details will be described later). ..

Further, in this flow, steps S20 and S35 in the flow of FIG. 7A are replaced with steps S20A and S35A in which the directions of the inequality signs are reversed, respectively. That is, in step S20A, the forward temperature control unit 61A of the compressor control unit 61 exceeds the target forward temperature set in step S100A by the forward temperature of cold water detected by the forward temperature sensor 56A at this time. Determine if it is. If the forward temperature is higher than the target forward temperature, the determination is satisfied (S20A: YES), and the process proceeds to step S25. If the forward temperature is equal to or lower than the target forward temperature, the determination is not satisfied (S20A: NO). , The process proceeds to step S30. Further, in step S35A, in the return temperature control unit 61B of the compressor control unit 61, the return temperature of the cold water detected from the return temperature sensor 56B at this time exceeds the target return temperature set in the step S100A. Determine if it is. If the return temperature is higher than the target return temperature, the determination is satisfied (S35A: YES), and the process proceeds to step S40. If the return temperature is equal to or lower than the target return temperature, the determination is not satisfied (S35A: NO). , The process proceeds to step S45.

The procedure other than the above is the same as that in FIG. 7A, and the description thereof will be omitted.

Next, the detailed procedure of the step S100A will be described with reference to FIG. The same parts as those in FIG. 8 are designated by the same reference numerals, and the description thereof will be omitted or simplified as appropriate.

In FIG. 10, the compressor control unit 61 first determines whether or not the flag F = 1 in the same step S110. If F = 0 and the determination is not satisfied (S110: NO), the process proceeds to step S115A newly provided in place of step S115 in FIG.

In step S115A, the compressor control unit 61 determines whether or not there is an operation request for the cold / hot water panel 51 (see the configuration example shown in FIG. 2). In this determination, the outdoor unit control unit CU acquires, for example, the control signal Sa output from the terminal remote controller device RA or the control signal S2 from the thermal valve controller CV to the thermal valve V1 (as described above). However, the illustration in FIG. 2 is omitted), and a known method such as based on the acquisition result may be used. When the cold / hot water panel 51 is provided as in the configuration example shown in FIG. 2 but the operation request is not yet provided, or when the cold / hot water panel 51 is not provided in the first place as in the configuration example shown in FIG. Is not satisfied (S115A: NO), and the process proceeds to step S155 similar to that in FIG.

In step S155, as in FIG. 8, the compressor control unit 61 is appropriately set by the return temperature control unit 61B by operating the cold water set temperature (in this case, the operation unit 259 or the like on the main remote controller RM). Based on the determined temperature), the corresponding target return temperature is calculated by a known appropriate method (for example, based on a predetermined rule that uniquely determines the target return temperature from the set temperature). ..

As the predetermined rule, for example, as described in Japanese Patent Application Laid-Open No. 2017-133775, the temperature level numerical value itself supplied to the indoor terminal in the cooling operation is set by the main remote controller RM. The added value Ts + β obtained by adding a predetermined number β to the set temperature Ts can be set as the target return temperature Tm. At this time, specifically, in the range of Ts of 6 ° C. to 20 ° C., an appropriate value in the range of 5 ° C. to 15 ° C. is applied to β. Which value to apply to β may be optionally selectable in the main remote controller RM, or β is fixedly set to an appropriate value in the range of 5 ° C. to 15 ° C. in advance. May be good.

The predetermined rule is not limited to the method in which the target return temperature Tm is an addition value obtained by adding a predetermined value to the value of the temperature value of cold water itself as described above. For example, when strong / medium / weak indicating the cooling strength is used as the temperature level that can be set in the cooling operation, the temperature conversion values corresponding to the strong / medium / weak (for example, strong is 7, medium is 13, The weakness may be a rule in which 20) is stored in advance and the added value obtained by adding a predetermined value to the value (temperature conversion value) Ts is set as the target return temperature Tm. Alternatively, as the temperature level that can be set in the cooling operation, even when a temperature level having 9 levels of cooling strength is used, for example, a numerical value of 1 to 9 is used to express the cooling strength, and 9 levels of cooling are used. The temperature conversion value corresponding to the strength of the above may be stored in advance, and the addition value obtained by adding a predetermined value to the value (temperature conversion value) Ts may be set as the target return temperature Tm.

Also in this case, the return temperature control unit 61B of the compressor control unit 61 that executes the step S155 functions as the target return temperature setting means according to each claim. After calculating the target return temperature as described above, the process proceeds to step S17 of FIG. 9, and the above procedure is repeated thereafter. As a result, step S155 → step S17 → step S35A → step S40 or step S45 → step S15 → step S110 → step S115A → step S155 → ... The compressor speed is increased / decreased (that is, the return temperature is controlled).

On the other hand, in step S115A, when the cold / hot water panel 51 is provided as in the configuration example shown in FIG. 2 and there is an operation request thereof, the determination in step S115A is satisfied (S115A: YES), and the above. The process proceeds to step S130, which is the same as in FIG.

In step S130, the compressor control unit 61 sets the flag F to F = 1, which indicates switching to temperature control, as described above. After that, the process proceeds to step S135, which is the same as in FIG.

In step S135, the compressor control unit 61 is similarly set by the forward temperature control unit 61A to set the temperature of cold water (the temperature appropriately set by the operation of the operation unit 259 or the like in the main remote controller RM described above). Based on the above, the corresponding target forward temperature is calculated by a known method (the target forward temperature can be uniquely determined with respect to the set temperature). Also in this case, the forward temperature control unit 61A of the compressor control unit 61 that executes step S135 functions as the target forward temperature setting means according to each claim. When step S135 is completed, the process proceeds to step S17 of FIG. After that, through steps S17 → step S20A → step S25 or step S30 → step S15 as described above, since F = 1, the determination of step S110 is satisfied, and a step newly provided in place of step S140 is satisfied. Move to S140A.

In step S140A, the compressor control unit 61 determines whether or not there is a stop request for the cold / hot water panel 51 for which an operation request has been made and the cooling operation has been started as described above. Regarding this determination as well, for example, the outdoor unit control unit CU acquires the control signal Sa output from the terminal remote controller device RA or the control signal S2 from the thermal valve controller CV to the thermal valve V1. (However, the illustration in FIG. 2 is omitted), and it is sufficient to use a known method such as based on the acquisition result. For example, as in the configuration example shown in FIG. 2, if the cold / hot water panel 51 is provided and the operation is performed, but the operation stop request is not yet satisfied, the determination is not satisfied (S140A: NO), and the process proceeds to step S135. After that, the same procedure as described above is repeated. As a result, steps S135 → step S17 → step S20A → step S25 or step S30 → step S15 → step S110 → step S140A → step S135 → ... Are repeated until the stop request for the cold / hot water panel 51 is made. Then, the compressor rotation speed is increased or decreased (that is, the forward temperature control) according to the magnitude of the target forward temperature and the forward temperature.

In this case, the compressor control unit 61 that executes the step S140A and the step S115A functions as the terminal determination means according to each claim.

In this way, when there is a request to stop the operation of the cold / hot water panel 51 in a state where the cold / hot water panel 51 is provided and the cooling operation is performed as in the configuration example shown in FIG. 2, step S140A is performed. The determination is satisfied (S140A: YES), and the process proceeds to step S150 similar to FIG.

In step S150, the compressor control unit 61 returns the flag F to 0, which represents switching to the return temperature control, and then proceeds to step S155, and repeats the same procedure thereafter.

As described above, the compressor control unit 61 issues a stop request after the cold / hot water panel 51 (corresponding to a specific type of indoor terminal in this case) provided in the system issues an operation request during the cooling operation. The forward temperature is controlled until it is emitted, and the return temperature is controlled otherwise. That is, when the cold / hot water panel 51 is operated, the forward temperature control can be performed with priority over other indoor terminals.

Compression for executing the steps S150 and S130 of FIG. 10 and the steps S17, S20A, S25, S30, S35A, S40, and S45 of FIG. 9A. The machine control unit 61 functions as the switching control means according to each claim.

<Control of expansion valve control unit>
Further, the control procedure by the expansion valve control unit 62 during the cooling operation is shown in the flowchart of FIG. 9B. As shown in FIG. 9B, since the contents of all the procedures are the same as the flow of FIG. 7B in this flow, the description thereof will be omitted.

<Example of heating operation behavior>
Next, an example of the heating operation behavior in the configuration example shown in FIG. 1 will be described with reference to FIG. In the figure, FIG. 11A shows the time course of the operating state of the underfloor radiator 41 (in the figure, the operating state is referred to as “ON” and the stopped state is referred to as “OFF”). 11 (b) shows the time course of the operating state of the panel radiator 42 (in the figure, the operating state is referred to as “ON” and the stopped state is referred to as “OFF”). Further, FIG. 11C shows the time lapse of whether the control mode of the heat pump device (abbreviated as “HP” in the figure; in detail, the compressor 7) is the forward temperature control or the return temperature control. The transition is shown, and FIG. 11D shows the transition over time of the increase / decrease in the heating load by the underfloor radiator 41 and the panel radiator 42. Further, FIG. 11E shows the hot water temperature in the cold / hot water going pipe 2 (detected by the hot water sensor 56A) and the hot water temperature in the cold / hot water return pipe 3 (detected by the return temperature sensor 56B). The target outgoing temperature at the time of controlling the forward temperature and the target return temperature at the time of controlling the return temperature (see steps S135 and S155 of FIG. 8) are shown with respect to time. FIG. 11 (f) shows the time course of the rotation speed of the compressor 7.

In FIG. 11, in this example, first, the underfloor radiator 41 is not operated and only the panel radiator 42 is operated (see times t1 to t4 in FIGS. 11 (a) and 11 (b)). Since the underfloor radiator 41 is not in operation, the return temperature is controlled as described above (see time t1 to t4 in FIG. 11C) so that the actual return hot water temperature becomes the target return temperature of about 40 ° C. The rotation speed of the compressor 7 is controlled (see time t1 to t4 in FIG. 11E). While the heating load is constant (see time t1 to t2 in FIG. 11 (d)), the rotation speed of the compressor 7 is constant at about 90 rps (see time t1 to t2 in FIG. 11 (f)). The temperature of the hot water is also constant at about 50 ° C. (see time t1 to t2 in FIG. 11 (e)).

Then, when the room temperature of the living room, which is the heat dissipation target of the panel radiator 42, rises with the passage of time and the heating load decreases (see time t2 to t3 in FIG. 11D), the return temperature control causes the above. The rotation speed of the compressor 7 gradually decreases (see time t2 to t3 in FIG. 11 (f)), and as a result, the actual hot water temperature also gradually decreases (see time t2 to t3 in FIG. 11 (e)). .. In this example, when the heating load decreases and becomes a constant value (see time t3 to t4 in FIG. 11 (d)), the rotation speed of the compressor 7 becomes constant at about 50 rps (see FIG. 11 (f)). (See time t3 to t4), the actual hot water temperature also becomes constant at about 47 ° C. (see time t3 to t4 in FIG. 11 (e)).

After that, when the underfloor radiator 41 is started to operate (see time t4 in FIG. 11 (a)), the return temperature control is switched to the forward temperature control as described above (time t4 in FIG. 11 (c)). (See), the rotation speed of the compressor 7 is controlled so that the actual hot water temperature becomes the target temperature of about 50 ° C. (see time t4 to t8 in FIG. 11 (e)). That is, at the time of switching to the forward temperature control, the actual hot water temperature is lower than the target forward temperature of about 50 ° C. Therefore, in order to raise the actual hot water temperature and also in response to an increase in the heating load due to the addition of the underfloor radiator 41 (see time t4 to t5 in FIG. 11D), the compressor 7 The number of revolutions rises sharply (see time t4 to t5 in FIG. 11 (f)). When the increased actual hot water temperature reaches the target temperature of about 50 ° C. (see time t5 in FIG. 11 (e)), the rotation speed of the compressor 7 also becomes constant (time t5 to t6 in FIG. 11 (f)). reference).

At this time, as described above, the actual hot water temperature becomes constant at about 50 ° C. (see time t5 to t6 in FIG. 11 (e)), while the actual return hot water temperature changes according to the heating load. Since the heating load continues to be high (see time t5 to t6 in FIG. 11D), in this example, the return hot water temperature does not rise and remains almost constant at about 40 ° C. (FIG. 11 (e), see times t4 to t6).

Then, when the room temperature of the underfloor chamber, which is the heat dissipation target of the underfloor radiator 41, rises and the heating load decreases with the passage of time (see time t6 to t7 in FIG. 11D), the going temperature control The actual hot water temperature is maintained at about 50 ° C., and the rotation speed of the compressor 7 gradually decreases (see time t6 to t7 in FIG. 11 (f)). At this time, the actual return hot water temperature, which changes according to the heating load, gradually rises as the heating load decreases (see time t6 to t7 in FIG. 11 (e)). In this example, when the heating load decreases and becomes a constant value (see the times t7 to t8 in FIG. 11 (d)), the rotation speed of the compressor 7 becomes constant at about 50 rps (see FIG. 11 (f)). (See time t7 to t8), the actual return hot water temperature also becomes constant at about 43 ° C. (see time t7 to t8 in FIG. 11 (e)).

After that, when the underfloor radiator 41 is stopped (see time t8 in FIG. 11A), the switching from the forward temperature control to the return temperature control is performed again as described above (time in FIG. 11C). (See t8), the rotation speed of the compressor 7 is controlled so that the actual return hot water temperature becomes the target return temperature of about 40 ° C. However, at this time, at the time of switching to the return temperature control, the actual return hot water temperature exceeds the target return temperature of about 40 ° C. (see time t8 in FIG. 11 (e)). Therefore, in order to lower the actual return hot water temperature, the rotation speed of the compressor 7 is once lowered to about 30 rps in this example (see the times t8 to t9 in FIG. 11 (f)). As a result, the actual hot water temperature drops sharply (see times t8 to t9 in FIG. 11E), and the actual hot water temperature that becomes more and more corresponding to the output of the panel radiator 42 being operated also drops sharply. 11 (e), time t8 to t9).

When the suddenly falling actual return hot water temperature falls below the target return temperature of about 40 ° C. (see time t9 in FIG. 11E), the rotation speed of the compressor 7 increases in order to raise the actual return hot water temperature again. Then, when the actual return hot water temperature reaches the target return temperature of about 40 ° C., the rotation speed of the compressor 7 becomes constant (see time t9 to t10 in FIG. 11 (f)). The actual hot water temperature, which becomes as described above, rises according to the behavior of the actual return hot water temperature, but in this example, when the actual return hot water temperature becomes constant at about 40 ° C, it is about 47 ° C. (See time t9 to t10 in FIG. 11 (e)).

After that, in this example, the heating load increases as the temperature of the outside air decreases (see time t10 to t11 in FIG. 11D), and the rotation speed of the compressor 7 gradually increases due to the return temperature control. (See time t10 to t11 in FIG. 11 (f)), and as a result, the actual hot water temperature gradually rises (see time t10 to t11 in FIG. 11 (e)). In this example, when the heating load rises and becomes a constant value (see time t11 and later in FIG. 11D), the rotation speed of the compressor 7 becomes constant at about 90 rps (time in FIG. 11F). (Refer to t11 and later), the actual hot water temperature also becomes constant at about 50 ° C. (see time t11 and later in FIG. 11 (e)).

<Example of cooling operation behavior>
Next, an example of the cooling operation behavior in the configuration example shown in FIG. 2 will be described with reference to FIG. In the figure, as in FIG. 11, FIG. 12A shows the operating state of the cold / hot water panel 51 (in the drawing, the operating state is referred to as “ON” and the stopped state is referred to as “OFF”). The time course is shown, and FIG. 12B shows the time course of the operating state of the fan coil unit 52 (in the figure, the operating state is referred to as “ON” and the stopped state is referred to as “OFF”). Is shown. Further, in FIG. 12 (c), similarly to FIG. 11 (c), whether the control mode of the heat pump device (abbreviated as “HP” in the figure; in detail, the compressor 7) is the forward temperature control or not. The time course of whether or not the return temperature is controlled is shown, and FIG. 12D shows the time course of increase / decrease in the cooling load by the cold / hot water panel 51 and the fan coil unit 52. Further, FIG. 12 (e) shows the same as in FIG. 11 (e), the going cold water temperature in the cold / hot water going pipe 2 (detected by the going temperature sensor 56A) and the returning cold water temperature in the cold / hot water return pipe 3. (Detected by the return temperature sensor 56B), the target return temperature during the forward temperature control and the target return temperature during the return temperature control (see steps S135 and S155 in FIG. 10), and their respective changes over time are shown. .. Then, FIG. 12 (f) shows the time course of the rotation speed of the compressor 7 as in FIG. 11 (f).

In FIG. 12, in this example, the cold / hot water panel 51 is not operated first, and only the fan coil unit 52 is operated (see times t21 to t24 in FIGS. 12 (a) and 12 (b)). Since the cold / hot water panel 51 is not in operation, the return temperature is controlled as described above (see time t21 to t24 in FIG. 12C) so that the actual return cold water temperature becomes the target return temperature of about 17 ° C. The rotation speed of the compressor 7 is controlled (see time t21 to t24 in FIG. 12 (e)). While the cooling load is constant (see time t21 to t22 in FIG. 12 (d)), the rotation speed of the compressor 7 is constant at about 90 rps (see time t21 to t22 in FIG. 12 (f)). The temperature of the cold water is also constant at about 7 ° C. (see time t21 to t22 in FIG. 12 (e)).

Then, as the room temperature of the chamber B, which is the heat dissipation target of the fan coil unit 52, decreases with the passage of time and the cooling load decreases (see the times t22 to t23 in FIG. 12D), the return temperature control As a result, the rotation speed of the compressor 7 gradually decreases (see time t22 to t23 in FIG. 12 (f)), and as a result, the actual cold water temperature gradually increases (time t22 to t23 in FIG. 12 (e)). reference). In this example, when the cooling load decreases and becomes a constant value (see time t23 to t24 in FIG. 12 (d)), the rotation speed of the compressor 7 becomes constant at about 50 rps (see FIG. 12 (f)). (See time t23 to t24), the actual cold water temperature also becomes constant at about 10 ° C. (see time t23 to t24 in FIG. 12 (e)).

After that, when the cold / hot water panel 51 starts operation (see time t24 in FIG. 12 (a)), switching from return temperature control to forward temperature control is performed as described above (time t24 in FIG. 12 (c)). (See), the rotation speed of the compressor 7 is controlled so that the actual cold water temperature becomes the target temperature of about 7 ° C. (see time t24 to t28 in FIG. 12 (e)). That is, at the time of switching to the forward temperature control, the actual cold water temperature exceeds the target forward temperature of about 7 ° C. Therefore, in order to lower the actual cold water temperature, and also in response to an increase in the cooling load due to the addition of the cold / hot water panel 51 (see time t24 to t25 in FIG. 12D), the compressor 7 The number of revolutions rises sharply (see time t24 to t25 in FIG. 12 (f)). When the lowered actual cold water temperature reaches the target temperature of about 7 ° C. (see time t25 in FIG. 12 (e)), the rotation speed of the compressor 7 also becomes constant (time t25 to t26 in FIG. 12 (f)). reference).

At this time, as described above, the actual cold water temperature is constant at about 7 ° C. (see time t25 to t26 in FIG. 12 (e)), while the actual return cold water temperature becomes higher depending on the cooling load. Since the state where the cooling load is high continues (see time t25 to t26 in FIG. 12D), in this example, the return chilled water temperature does not decrease and remains almost constant at about 17 ° C. (FIG. 12 (e) time t24-t26).

Then, as the room temperature of the room A, which is the heat absorption target of the cold / hot water panel 51, decreases with the passage of time and the cooling load decreases (see time t26 to t27 in FIG. 12D), the forward temperature control The actual cold water temperature is maintained at about 7 ° C., and the rotation speed of the compressor 7 gradually decreases (see time t26 to t27 in FIG. 12 (f)). At this time, the actual return chilled water temperature, which increases according to the cooling load, gradually decreases as the cooling load decreases (see time t26 to t27 in FIG. 12 (e)). In this example, when the cooling load decreases and becomes a constant value (see time t27 to t28 in FIG. 12 (d)), the rotation speed of the compressor 7 becomes constant at about 50 rps (see FIG. 12 (f)). (See time t27 to t28), the actual return chilled water temperature also becomes constant at about 14 ° C. (see time t27 to t28 in FIG. 12 (e)).

After that, when the cold / hot water panel 51 is stopped (see time t28 in FIG. 12 (a)), the switching from the forward temperature control to the return temperature control is performed again as described above (time in FIG. 12 (c)). (See t28), the rotation speed of the compressor 7 is controlled so that the actual return chilled water temperature becomes the target return temperature of about 17 ° C. However, at this time, when switching to the return temperature control, the actual return chilled water temperature is below the target return temperature of about 17 ° C. (see time t28 in FIG. 12 (e)). Therefore, in order to raise the actual return chilled water temperature, the rotation speed of the compressor 7 once drops to about 30 rps in this example (see time t28 to t29 in FIG. 12 (f)). As a result, the actual return chilled water temperature rises sharply (see time t28 to t29 in FIG. 12E), and the actual chilled water temperature that becomes more and more corresponding to the output of the operating fan coil unit 52 also rises sharply. See time t28-t29 in FIG. 12 (e)).

When the suddenly rising actual return chilled water temperature exceeds the target return temperature of about 17 ° C. (see time t29 in FIG. 12E), the rotation speed of the compressor 7 increases in order to lower the actual return chilled water temperature again. When the actual return chilled water temperature reaches the target return temperature of about 17 ° C., the rotation speed of the compressor 7 becomes constant (see time t29 to t30 in FIG. 12 (f)). The actual return chilled water temperature, which becomes as described above, decreases according to the behavior of the actual return chilled water temperature, but in this example, when the actual return chilled water temperature becomes constant at about 17 ° C, it is about 10 ° C. (See time t29 to t30 in FIG. 12 (e)).

After that, in this example, the cooling load increases as the temperature of the outside air rises (see times t30 to t31 in FIG. 12D), and the rotation speed of the compressor 7 gradually rises due to the return temperature control. (See time t30 to t31 in FIG. 12 (f)), and as a result, the actual cold water temperature gradually decreases (see time t30 to t31 in FIG. 12 (e)). In this example, when the cooling load rises and becomes a constant value (see time t31 or later in FIG. 12 (d)), the rotation speed of the compressor 7 becomes constant at about 90 rps (time in FIG. 12 (f)). (Refer to t31 and later), the actual cold water temperature also becomes constant at about 7 ° C. (see time t31 and later in FIG. 12 (e)).

<Effect of embodiment>
As described above, according to the temperature control system 100 of the present embodiment, the type of the indoor terminal to be operated is determined based on the operation request of the indoor terminal (steps S115 and S140 of FIG. 8). , Step S115A and step S140A in FIG. 10). Then, based on the determination result, either the forward temperature control by the forward temperature control unit 61A of the compressor control unit 61 or the return temperature control by the return temperature control unit 61B is selectively switched and executed (the above). (See steps S20 to S45 in FIG. 7, and steps S20A to S45 in FIG. 9). As a result, the forward temperature control is performed according to whether the heating operation or the cooling operation is performed for each type of the indoor terminal in accordance with the characteristics of the indoor terminal as described above (see FIG. 6). And the optimum control of the return temperature control can be executed.

Further, in the present embodiment, particularly when a plurality of indoor terminals are connected to the water-refrigerator heat exchanger 11 as shown in FIGS. 1 and 2, the underfloor radiator 41 and the cold / hot water panel 51 When such a specific type of indoor terminal is operated, control corresponding to the specific type of indoor terminal (in this example, going temperature control) is executed with priority over other indoor terminals. As a result, the optimum control for the specific type of indoor terminal can be reliably executed.

Further, in the present embodiment, in particular, in the configuration example shown in FIG. 2, when it is determined that the cold / hot water panel 51 is operated during cooling, the forward temperature control is executed, and in other cases, the above-mentioned Perform return temperature control. By controlling the forward temperature during the cooling operation of the cold / hot water panel 51 in this way, the supply temperature to the cold / hot water panel 51 becomes constant at the target forward temperature even if the cooling load changes, so that the indoor temperature is ensured. It is possible to lower the temperature and surely lower the humidity in the target room A.

Further, in the present embodiment, in particular, in the configuration example shown in FIG. 1, when it is determined that the underfloor radiator 41 is operated during heating, the forward temperature control is executed, and in other cases, the above-mentioned Perform return temperature control. By controlling the forward temperature during the heating operation of the underfloor radiator 41 in this way, the supply temperature to the underfloor radiator 41 becomes constant at the target forward temperature even if the heating load changes, so that the living room can be quickly moved. It can be warmed up to ensure the comfort of the space in the living room.

Further, in the present embodiment, in particular, when the return temperature is controlled by the return temperature control unit 61B, when the target return temperature is set, and when the heating operation is performed, a predetermined value is set from the set temperature Ts set by the main remote control device RM. The subtraction value Ts-α obtained by subtracting α is set to the target return temperature Tm, and during the cooling operation, the target is an additional value Ts + β obtained by adding a predetermined numerical value β to the set temperature Ts set by the main remote control device RM. Set the return temperature to Tm. As a result, the target return temperature Tm can be set by a simple method from the temperature setting in the main remote controller RM during both the cooling and heating operations. As a result, as described above, the main remote controller RM can be configured to set the temperature level at which the user goes to the indoor terminal instead of the return temperature from the indoor terminal, which is difficult for the user to imagine.

Further, in the present embodiment, in particular, the forward temperature control unit 61A or the return temperature control unit 61B of the compressor control unit 61 has a rotation speed corresponding to the forward temperature control or a rotation speed corresponding to the forward temperature control for each type of indoor terminal. The rotation speed of the compressor 7 is controlled so that the rotation speed corresponds to the return temperature control. As a result, the optimum control for the indoor terminal can be reliably executed.

The present invention is not limited to the above embodiment, and various modifications can be made without changing the gist of the invention.

For example, in the above embodiment, the temperature (forward temperature) of hot water or cold water in the common forward pipe 2A is detected by the forward temperature sensor 56A, and the detected value is used for control, but the forward temperature sensor 56A is omitted. (Or without using the detected value), the detected value of the discharge temperature sensor 55, the detected value of the return temperature sensor 56B, the detected value of the refrigerant temperature sensor 57, and the refrigerant state amount related to the refrigerant circulation amount. The forward temperature may be estimated (estimated) from the rotation speed of the compressor 7 and the valve opening degree of the expansion valve 9 as the refrigerant state amount related to the refrigerant circulation amount.

Also in the above modified example, the outdoor unit control unit CU functionally includes a compressor control unit 61 as a compressor control means and an expansion valve control unit 62 as an expansion valve control means. .. The compressor control unit 61 includes an forward temperature control unit 61A'(not shown) instead of the forward temperature control unit 61A in FIG. 5, and a return temperature control unit 61B similar to that in FIG.

The forward temperature control unit 61A'has the refrigerant discharge temperature detected by the discharge temperature sensor 55, the return temperature of hot or cold water detected by the return temperature sensor 56B, and the refrigerant detected by the refrigerant temperature sensor 57. In the common forward pipe 2A, based on the temperature, the rotation speed of the compressor 7 as the refrigerant state amount related to the refrigerant circulation amount, and the valve opening degree of the expansion valve 9 as the refrigerant state amount related to the refrigerant circulation amount. The forward temperature control is performed by determining (estimating) the forward temperature of hot water or cold water and controlling the rotation speed of the compressor 7 according to the determined forward temperature. In particular, in this example, the forward temperature control unit 61A'is a desired target in which the determined forward temperature is set (details omitted) in response to, for example, an operation of the operation unit 259 in the main remote controller RM. The rotation speed of the compressor 7 is controlled so as to reach the temperature (target temperature).

As described above, the forward temperature control unit 61A'determines (estimates) the forward temperature and controls the forward temperature according to the determined forward temperature. The temperature is not limited to the modification, but the temperature is estimated by another method, and the temperature control unit 61A'controls the temperature according to the estimated (determined) temperature. You may.

Further, also in the above-described modified example, the same effect as that of the above-described embodiment can be obtained. That is, the type of the indoor terminal to be operated is determined based on the operation request of the indoor terminal, and based on the determination result, the forward temperature control unit 61A'(based on the forward temperature determined from the return temperature). ) Either the forward temperature control or the return temperature control (based on the return temperature) by the return temperature control unit 61B is selectively switched and executed. Thereby, the optimum control can be executed for each type of the indoor terminal according to the characteristics of the indoor terminal as described above.

Further, for example, in the above embodiment, in the configuration example shown in FIG. 1, the case where the underfloor radiator 41 and the panel radiator 42 are provided in the temperature control system 100 as an indoor terminal is shown in FIG. In the configuration example, the case where the cold / hot water panel 51 and the fan coil unit 52 are provided in the temperature control system 100 has been described as an example, but the present invention is not limited to this.

That is, for example, as shown in FIG. 13, the above configuration can be applied even when only the underfloor radiator 41 is provided as the indoor terminal. In this case, since there is only one indoor terminal, the outgoing header 91 and the return header 92 shown in FIG. 1 are omitted, and the water is directly connected by one cold / hot water outgoing pipe 2 and one cold / hot water return pipe 3. -The refrigerant heat exchanger 11 and the underfloor radiator 41 are connected. Along with this, the thermal valves V1 and V2, the thermal valve controller CV, the remote controller devices RA and RB for terminals, and the like are also omitted. In this case, when the user performs the heating operation start operation via the main remote controller RM, the hot water from the outdoor unit 1 is supplied to the underfloor radiator 41 to dissipate heat to the underfloor room, and the main remote controller 1 is used. When the heating operation is stopped by the user via the RM, the supply of hot water to the underfloor radiator 41 is stopped, and the heat dissipation to the underfloor chamber is stopped. In the above flowchart, the determination in step S115 of FIG. 8 is read as a determination as to whether or not the heating operation start operation has been performed by the user via the main remote controller RM (underfloor radiator when heating is stopped). The determination in step S140 in FIG. 8 (because the stop is 41) can be read as a determination as to whether or not the heating operation stop operation has been performed by the user via the main remote controller device RM. Each procedure shown in 7 (b) can be applied as it is.

Further, for example, as shown in FIG. 14, the above configuration can be applied even when only the cold / hot water panel 51 is provided as the indoor terminal. In this case as well, since the number of indoor terminals is one, the outgoing header 91 and the return header 92 shown in FIG. 2 are omitted, and one cold / hot water outgoing pipe 2 and one cold / hot water return pipe 3 are omitted. Directly connects the water-refrigerant heat exchanger 11 and the cold / hot water panel 51. In this case, when the user performs a heating or cooling operation start operation via the main remote controller RM, hot water or cold water from the outdoor unit 1 is supplied to the cold / hot water panel 51 to dissipate heat or absorb heat to the living room. When the heating or cooling operation is stopped by the user via the main remote controller RM, the hot water or cold water supply to the cold / hot water panel 51 is stopped, and the heat dissipation or heat absorption to the living room is stopped.

Then, in the above-mentioned flowchart, since the determination in step S115 of FIG. 8 is not always satisfied during the heating operation (in other words, F = 0 remains without being set to F = 1 in the subsequent step S130). Therefore, step S115 → step S155 → step S17 in FIG. 7A → step S35 → step S40 or step S45 → step S15 → step S115 → ... The return temperature control is always executed. ..

On the other hand, during the cooling operation, the determination in step S115A of FIG. 10 is read as a determination as to whether or not the cooling operation start operation has been performed by the user via the main remote controller device RM (when cooling is stopped). The determination in step S140A in FIG. 10 (because the cold / hot water panel 51 is stopped) can be read as a determination as to whether or not the cooling operation stop operation has been performed by the user via the main remote controller device RM. ) And each procedure shown in FIG. 9 (b) can be applied as they are.

Further, at least one indoor terminal (for example, a panel controller, a hot water room heater, a floor heating panel, a snow melting terminal, etc. shown in FIG. 6), which does not include the underfloor radiator 41 and the cold / hot water panel 51 at all, and the like. The above configuration can also be applied to a temperature control system provided with).
In this case, since the determination in step S115 of FIG. 8 is not always satisfied during the heating operation (in other words, F = 0 remains without being set to F = 1 in the subsequent step S130). Similar to the above, step S115 → step S155 → step S17 in FIG. 7A → step S35 → step S40 or step S45 → step S15 → step S115 → ... The return temperature control is always executed. (The same applies even if the cold / hot water panel 51 and the fan coil unit 52 are included).
Further, even during the cooling operation, the determination in step S115A of FIG. 10 is not always satisfied (in other words, F = 0 remains without being set to F = 1 in the subsequent step S130). S115A → step S155 → step S17 in FIG. 9A → step S35A → step S40 or step S45 → step S15 → step S115A → ... The return temperature control is always executed (fan coil unit 52). The same applies even if is included).

The number of indoor terminals provided in the temperature control system 100 is not limited to one or two as described above, and may be three or more.

Further, in the above embodiment, the heat source machine has an outdoor fan 10 that blows outside air while passing the refrigerant through the outdoor heat exchanger 8 as the heat source side heat exchanger, and the outside air as the heat source and the refrigerant heat. The case where the outdoor unit 1 which is an air heat source type heat pump to be replaced is used has been described as an example, but the present invention is not limited to this. That is, the heat source machine may be configured such that water or antifreeze liquid is supplied to the heat source side heat exchanger and the liquid and the refrigerant exchange heat in the heat source side heat exchanger.
Further, a heat source side heat exchanger may be provided in the ground or in a relatively large-capacity water source, and the heat source side heat exchanger may be configured to exchange heat between the ground or the water source and the refrigerant. Further, a composite heat source type configuration may be provided in which a heat pump circuit using the heat of the underground or the water source and another heat pump circuit using air heat are provided.
Further, if the heat source side heat exchanger can exchange heat with the refrigerant, it includes other substances (for example, smoke generation, smoke exhaust, various high temperature gases, etc.) in place of the liquid, the outside air, and the water source. Gas, hot sand, dust, fluid solid containing various particles, etc.) can be passed through the heat source side heat exchanger, or heat from sunlight, reflected light, or other radiation can be supplied to the heat source side heat exchanger for use. good.

7 Compressor 8 Outdoor heat exchanger (heat pump heat exchanger)
9 Expansion valve 11 Water-refrigerant heat exchanger (load side heat exchanger)
41 Underfloor radiator (specific types of indoor terminals, indoor terminals)
42 Panel radiator (indoor terminal)
51 Cold / hot water panel (specific type of indoor terminal, indoor terminal)
52 Fan coil unit (indoor terminal)
56A Forward temperature sensor (forward temperature determination means)
56B Return temperature sensor (return temperature determination means)
61 Compressor control unit (compressor control means)
61A Forward temperature control unit 61A'Forward temperature control unit 61B Return temperature control unit CU Outdoor unit control unit RA, RB, RC Remote control device for terminals (operating means)
RM main remote controller (setting operation means, operation means)

Claims (5)

A load-side heat exchanger that exchanges heat between the refrigerant supplied from a heat pump device equipped with a compressor, expansion valve, and heat pump heat exchanger and the load-side circulating fluid.
A setting operating means capable of setting the temperature level of the load-side circulating fluid supplied to at least one indoor terminal, and at least one operating means capable of operating the at least one indoor terminal.
The forward temperature determining means for determining the forward temperature of the load-side circulating fluid flowing out from the load-side heat exchanger to the indoor terminal, and
A target outgoing temperature setting means for setting a target outgoing temperature of the load-side circulating fluid supplied from the load-side heat exchanger to the indoor terminal according to the temperature level set by the setting operating means, and a target outgoing temperature setting means.
A return temperature determining means for determining the return temperature of the load-side circulating fluid flowing into the load-side heat exchanger from the indoor terminal, and a return temperature determining means.
A target return temperature setting means for setting a target return temperature of the load-side circulating fluid returning from the indoor terminal to the load-side heat exchanger according to the temperature level set by the setting operation means.
In a heat pump type temperature control system with
A terminal determination means for determining the type of the indoor terminal to be operated based on the operation request of the indoor terminal, and
During the operation of circulating the load-side circulating liquid to the indoor terminal, the forward temperature determined by the forward temperature determining means is set by the target forward temperature setting means based on the determination result of the terminal determining means. The forward temperature control that controls the heat pump device so as to reach the target forward temperature, or the return temperature determined by the return temperature determining means becomes the target return temperature set by the target return temperature setting means. The switching control means for switching and executing the return temperature control for controlling the heat pump device, and
Have a,
The terminal determination means
Based on the operation request of the plurality of indoor terminals, at least a specific type of indoor terminal among the plurality of indoor terminals to be operated is determined.
The switching control means
When it is determined by the terminal determination means that the specific type of indoor terminal is operated,
In the first case where both the operation of the specific type of indoor terminal and the operation of the indoor terminal of a type other than the specific type are performed, and
In the second case, the specific type of indoor terminal is operated and the type of indoor terminal other than the specific type is not operated.
In any case, the heat pump type temperature control system is characterized in that the switching corresponding to the specific type of indoor terminal is executed. A load-side heat exchanger that exchanges heat between the refrigerant supplied from a heat pump device equipped with a compressor, expansion valve, and heat pump heat exchanger and the load-side circulating fluid.
A setting operating means capable of setting the temperature level of the load-side circulating fluid supplied to at least one indoor terminal, and at least one operating means capable of operating the at least one indoor terminal.
The forward temperature determining means for determining the forward temperature of the load-side circulating fluid flowing out from the load-side heat exchanger to the indoor terminal, and
A target outgoing temperature setting means for setting a target outgoing temperature of the load-side circulating fluid supplied from the load-side heat exchanger to the indoor terminal according to the temperature level set by the setting operating means, and a target outgoing temperature setting means.
A return temperature determining means for determining the return temperature of the load-side circulating fluid flowing into the load-side heat exchanger from the indoor terminal, and a return temperature determining means.
A target return temperature setting means for setting a target return temperature of the load-side circulating fluid returning from the indoor terminal to the load-side heat exchanger according to the temperature level set by the setting operation means.
In a heat pump type temperature control system with
A terminal determination means for determining the type of the indoor terminal to be operated based on the operation request of the indoor terminal, and
During the operation of circulating the load-side circulating liquid to the indoor terminal, the forward temperature determined by the forward temperature determining means is set by the target forward temperature setting means based on the determination result of the terminal determining means. The forward temperature control that controls the heat pump device so as to reach the target forward temperature, or the return temperature determined by the return temperature determining means becomes the target return temperature set by the target return temperature setting means. The switching control means for switching and executing the return temperature control for controlling the heat pump device, and
Have,
The terminal determination means
Based on the operation request of the plurality of indoor terminals, at least a specific type of indoor terminal among the plurality of indoor terminals to be operated is determined.
The switching control means
When the terminal determination means determines that the specific type of indoor terminal is operated, the specific type of indoor terminal is operated regardless of whether or not the specific type of indoor terminal is operated. Execute the above switching corresponding to the terminal,
During the cooling operation in which the load-side circulating liquid cooled by the load-side heat exchanger is circulated to the indoor terminal, the switching control means uses the terminal determination means to cool and hot water as the specific type of indoor terminal. the forward running temperature control, features and be Ruhi Toponpu formula temperature control system that is otherwise executing the return temperature control when the panel is determined to be operated. A load-side heat exchanger that exchanges heat between the refrigerant supplied from a heat pump device equipped with a compressor, expansion valve, and heat pump heat exchanger and the load-side circulating fluid.
A setting operating means capable of setting the temperature level of the load-side circulating fluid supplied to at least one indoor terminal, and at least one operating means capable of operating the at least one indoor terminal.
The forward temperature determining means for determining the forward temperature of the load-side circulating fluid flowing out from the load-side heat exchanger to the indoor terminal, and
A target outgoing temperature setting means for setting a target outgoing temperature of the load-side circulating fluid supplied from the load-side heat exchanger to the indoor terminal according to the temperature level set by the setting operating means, and a target outgoing temperature setting means.
A return temperature determining means for determining the return temperature of the load-side circulating fluid flowing into the load-side heat exchanger from the indoor terminal, and a return temperature determining means.
A target return temperature setting means for setting a target return temperature of the load-side circulating fluid returning from the indoor terminal to the load-side heat exchanger according to the temperature level set by the setting operation means.
In a heat pump type temperature control system with
A terminal determination means for determining the type of the indoor terminal to be operated based on the operation request of the indoor terminal, and
During the operation of circulating the load-side circulating liquid to the indoor terminal, the forward temperature determined by the forward temperature determining means is set by the target forward temperature setting means based on the determination result of the terminal determining means. The forward temperature control that controls the heat pump device so as to reach the target forward temperature, or the return temperature determined by the return temperature determining means becomes the target return temperature set by the target return temperature setting means. The switching control means for switching and executing the return temperature control for controlling the heat pump device, and
Have,
The terminal determination means
Based on the operation request of the plurality of indoor terminals, at least a specific type of indoor terminal among the plurality of indoor terminals to be operated is determined.
The switching control means
When the terminal determination means determines that the specific type of indoor terminal is operated, the specific type of indoor terminal is operated regardless of whether or not the specific type of indoor terminal is operated. Execute the above switching corresponding to the terminal,
During the heating operation in which the load-side circulating fluid absorbed by the load-side heat exchanger is circulated to the indoor terminal, the switching control means is an underfloor radiator as the specific type of indoor terminal by the terminal determination means. There the forward running temperature control, features and be Ruhi Toponpu formula temperature control system that is otherwise executing the return temperature control if it is determined to be operated. A load-side heat exchanger that exchanges heat between the refrigerant supplied from a heat pump device equipped with a compressor, expansion valve, and heat pump heat exchanger and the load-side circulating fluid.
A setting operating means capable of setting the temperature level of the load-side circulating fluid supplied to at least one indoor terminal, and at least one operating means capable of operating the at least one indoor terminal.
The forward temperature determining means for determining the forward temperature of the load-side circulating fluid flowing out from the load-side heat exchanger to the indoor terminal, and
A target outgoing temperature setting means for setting a target outgoing temperature of the load-side circulating fluid supplied from the load-side heat exchanger to the indoor terminal according to the temperature level set by the setting operating means, and a target outgoing temperature setting means.
A return temperature determining means for determining the return temperature of the load-side circulating fluid flowing into the load-side heat exchanger from the indoor terminal, and a return temperature determining means.
A target return temperature setting means for setting a target return temperature of the load-side circulating fluid returning from the indoor terminal to the load-side heat exchanger according to the temperature level set by the setting operation means.
In a heat pump type temperature control system with
A terminal determination means for determining the type of the indoor terminal to be operated based on the operation request of the indoor terminal, and
During the operation of circulating the load-side circulating liquid to the indoor terminal, the forward temperature determined by the forward temperature determining means is set by the target forward temperature setting means based on the determination result of the terminal determining means. The forward temperature control that controls the heat pump device so as to reach the target forward temperature, or the return temperature determined by the return temperature determining means becomes the target return temperature set by the target return temperature setting means. The switching control means for switching and executing the return temperature control for controlling the heat pump device, and
Have,
The target return temperature setting means is
During the cooling operation, the target return temperature is set by adding a predetermined value to the value corresponding to the temperature level set by the setting operation means.
In the heating operation, features and be Ruhi Toponpu formula temperature control system to set the value corresponding to the temperature level set by the setting operation means, a subtraction value obtained by subtracting the predetermined value to the target return temperature. The switching control means
Based on the determination result of the terminal determination means, the compressor is controlled so that the forward temperature becomes the target forward temperature, or the number of revolutions of the compressor so that the return temperature becomes the target return temperature. The heat pump type temperature control system according to any one of claims 1 to 4 , further comprising a compressor control means for controlling the temperature control system.

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