JP6978363B2 - Heat pump heat source machine - Google Patents

Description

The present invention relates to a heat pump heat source machine having a heat pump device including a compressor and an expansion valve.

Conventionally, in this type of heat pump heat source machine, as described in Patent Document 1, in the heat pump device provided in the heat pump heat source machine, the rotation speed of the compressor is changed to the temperature fluctuation of hot water or cold water (load fluctuation of heating or cooling). In addition to controlling according to the above, the opening degree of the expansion valve is controlled according to the refrigerant discharge temperature of the refrigerant discharged from the compressor.

JP-A-2017-150791

In this conventional one, since the expansion valve opening degree is controlled according to the refrigerant discharge temperature of the refrigerant discharged from the compressor as described above, when the rotation speed of the compressor fluctuates greatly, the valve is valved. The opening could not follow quickly and the refrigerant discharge temperature changed significantly, which could lead to instability of the load side output.

In order to solve the above problems, in claim 1 of the present invention, a heat pump device in which a compressor, an expansion valve, and a heat source side heat exchanger are connected by a refrigerant pipe, and a refrigerant is supplied from the heat pump device via the refrigerant pipe. A water-refrigerator heat exchanger that receives and exchanges heat with water to generate hot or cold water, a compressor control means that controls the number of revolutions of the compressor, and an expansion valve control means that controls the opening degree of the expansion valve. the heat pump heat source machine having the expansion valve control means based on the rotation speed of the change amount of the compressor by the compressor control unit, increases the amount rotation speed of the compressor under the control of the compressor control unit The opening degree of the expansion valve is changed to the open side accordingly, and the opening degree of the expansion valve is changed to the closed side according to the amount of decrease in the rotation speed of the compressor under the control of the compressor control means. As described above, when the opening degree of the expansion valve is controlled and the opening degree of the expansion valve is changed to the closed side according to the amount of decrease in the rotation speed of the compressor by the control of the compressor control means. In the first range where the amount of decrease in the number of revolutions is small, the expansion valve control means adjusts the fluctuation range of the amount of decrease in the opening degree so as to have a first change pattern with respect to the fluctuation range of the amount of decrease in the number of revolutions. In the second range in which the amount of decrease in the number of revolutions is larger than the first range, the fluctuation range of the amount of decrease in the opening degree is larger than that in the first change pattern with respect to the fluctuation range of the amount of decrease in the number of revolutions. The fluctuation range of the amount of decrease in the opening degree is reduced so that the second change pattern becomes smaller .

Further, in claim 2 , in the first range, the expansion valve control means reduces the opening degree of the expansion valve proportionally to the fluctuation range of the decrease amount of the rotation speed by using the first coefficient. In the second range, the amount of decrease in the opening degree of the expansion valve is proportional to the fluctuation range of the amount of decrease in the number of revolutions by using a second coefficient smaller than the first coefficient. It reduces the fluctuation range.

According to claim 1 of the present invention, the heat pump device and the water-refrigerant heat exchanger are connected by a refrigerant pipe.

For example, when hot water is generated by the water-refrigerant heat exchanger, the refrigerant discharged from the compressor of the heat pump device flows in the order of the water-refrigerant heat exchanger, the expansion valve, and the heat source side heat exchanger. As a result, the gas-state refrigerant sucked at low temperature and low pressure is compressed by the compressor to become high temperature and high pressure gas, and then hot water is used in the water-refrigerant heat exchanger (in this case, functioning as a condenser). It changes to a high-pressure liquid while releasing heat. The refrigerant that has become liquid in this way is decompressed by the expansion valve to become a low-pressure liquid that easily evaporates, and then evaporates in the heat source side heat exchanger (in this case, functions as an evaporator) and changes to gas. As a result, it absorbs heat and returns to the compressor again as a low-temperature, low-pressure gas.

Further, for example, when cold water is generated by the water-refrigerant heat exchanger, the refrigerant discharged from the compressor of the heat pump device flows in the order of the heat source side heat exchanger, the expansion valve, and the water-refrigerant heat exchanger. As a result, the gas-state refrigerant sucked at low temperature and low pressure is compressed by the compressor to become high temperature and high pressure gas, and then heat is applied to the heat source side heat exchanger (in this case, functioning as a condenser). It changes to a high-pressure liquid while being released. The refrigerant that has become liquid in this way is decompressed by the expansion valve to become a low-pressure liquid that easily evaporates, and then evaporates in the water-refrigerant heat exchanger (in this case, functions as an evaporator) and changes to gas. By doing so, heat is absorbed from the cold water, and the gas returns to the compressor again as a low-temperature, low-pressure gas.

In the above configuration, in order to stably generate cold water or hot water, it is necessary to keep the temperature of the refrigerant discharged from the compressor of the heat pump device constant. Therefore, according to claim 1, a compressor control means and an expansion valve control means are provided.

That is, when the temperature of hot water or cold water from the water-refrigerant heat exchanger fluctuates (the load of heating or cooling fluctuates), the number of revolutions of the compressor is fluctuated by the control by the compressor control means.
Further, the opening degree of the expansion valve is controlled by the expansion valve control means. At this time, when the expansion valve control means controls the opening degree of the expansion valve according to the refrigerant discharge temperature of the refrigerant discharged from the compressor, for example, the rotation speed of the compressor greatly fluctuates. If this happens, the valve opening cannot follow quickly, and the refrigerant discharge temperature changes significantly, which may lead to destabilization of the load side output.

Therefore, according to claim 1, the expansion valve control means controls the opening degree of the expansion valve based on the amount of change in the rotation speed of the compressor by the compressor control means (so-called feedforward control).
As a result, even when the rotation speed of the compressor fluctuates greatly, the opening degree of the expansion valve changes rapidly correspondingly, so that the change in the refrigerant discharge temperature can be suppressed to a small value.
It is possible to stabilize the output on the load side. )be able to.

Further , according to claim 1 , the opening degree of the expansion valve is further opened when the rotation speed of the compressor is increased, and the opening degree of the expansion valve is further closed when the rotation speed of the compressor is decreased. Changes can be reliably suppressed.

When the opening degree of the expansion valve is changed to the closed side according to the decrease in the rotation speed of the compressor, the temperature of the evaporator suddenly drops due to the evaporation of the refrigerant. As a result, when the hot water is generated, frost may occur due to a decrease in the temperature of the heat source side heat exchanger, and when the cold water is generated, the cold water inside the pipe on the cold / hot water side may freeze due to the temperature decrease of the water-refrigerant heat exchanger. There is.

Therefore , according to claim 1 , the expansion valve control means has a first range in which the amount of decrease in the rotation speed of the compressor is relatively small, and a second range in which the amount of decrease in the rotation speed of the compressor is relatively large. , And the mode of expansion valve control is switched. That is, in the second range, the expansion valve has a change pattern (second change pattern) in which the fluctuation range of the amount of decrease is smaller than that in the first range (that is, it decreases more slowly than in the first range). Change the amount of decrease in the opening of. As a result, the above-mentioned frost formation in the heat source side heat exchanger and the freezing in the water-refrigerant heat exchanger are prevented while stabilizing the load side output by suppressing the change in the refrigerant discharge temperature. can do.

Further , according to claim 2, when the opening degree of the expansion valve is smoothly changed to the closed side by proportional control with respect to the decrease in the number of revolutions of the compressor and finely followed, the heat exchanger on the heat source side is used. It is possible to prevent the frost formation and the freezing in the water-refrigerant heat exchanger.

The figure which shows the whole schematic structure of the structural example of the heat pump type temperature control system provided with the outdoor unit of 1st 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 A flowchart showing a control procedure executed by the compressor control unit during heating and a control procedure executed by the compressor control unit during cooling. Flow chart showing the control procedure executed by the normal control unit of the expansion valve control unit during heating and cooling. The figure which shows an example of the relationship between the change amount of a compressor rotation speed and the change amount of an expansion valve opening degree. Graph diagram conceptually showing an example of the relationship between the amount of change in compressor rotation speed and the amount of change in expansion valve opening. A flowchart showing a control procedure executed by the feedforward control unit of the expansion valve control unit during heating and cooling. Sequence diagram showing an example of heating operation behavior Sequence diagram showing an example of cooling operation behavior The figure which shows an example of the relationship between the change amount of the compressor rotation speed and the change amount of the expansion valve opening degree in the outdoor unit of the 2nd Embodiment of this invention. Graph diagram conceptually showing an example of the relationship between the amount of change in the number of revolutions of the compressor and the amount of change in the opening of the expansion valve. The figure which shows the time-dependent behavior such as the expansion valve opening when the rotation speed deviation of a compressor is -10 [rps]. The figure which shows the time-dependent behavior such as the expansion valve opening when the rotation speed deviation of a compressor is -15 [rps]. The figure which shows the time-dependent behavior such as the expansion valve opening when the rotation speed deviation of a compressor is -20 [rps]. Sequence diagram showing an example of heating operation behavior Sequence diagram showing an example of cooling operation behavior

Next, an embodiment of the present invention will be described with reference to FIGS. 1 to 18.

<First Embodiment>
The first embodiment of the present invention will be described with reference to FIGS. 1 to 11.

<Configuration of an example of temperature control system>
FIG. 1 shows an overall schematic configuration of a configuration example of a heat pump type temperature control system including the heat pump heat source machine 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 to the outdoor unit 1 via a hot / cold water outflow pipe 2 and a cold / hot water return pipe 3. It has at least one indoor terminal (in this example, a cold / hot water panel 51 and a fan coil unit 52) installed indoors.

The cold / hot water panel 51 dissipates heat or absorbs heat from the indoor air 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 has a heat exchanger (not shown) and a blower fan (not shown) inside the fan coil unit 52.
(Not shown), thermal valve V3, indoor temperature sensor (not shown), water temperature sensor (not shown) that detects the temperature of hot or cold water flowing in the fan coil unit 52,
And a terminal control unit 29 and the like are provided. 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 control device 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 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 to heat or cool the room. conduct.

The cold / hot water panel 51 is arranged in the A room among the A room and the B room provided in the living room, and the fan coil unit 52 is arranged in the B 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 from the outgoing header 91 is one common outgoing pipe. It is configured as 2A, and cold / hot water from the outdoor unit 1 is supplied. 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 hot / cold water panel 51 and the fan coil unit. Outbound pipe to 52 2B
It is connected to the outgoing header 91 in a form of branching to 2.

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, two) return pipes, that is, the return pipe 3B1 from the hot / cold water panel 51,
It is divided into a return pipe 3B2 from the fan coil unit 52. The portion of the cold / hot water return pipe 3 on the downstream side 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.

The outgoing pipe 2B1 to the cold / hot water panel 51 is provided with a thermal valve V1 capable of opening and closing the outgoing pipe 2B1 by a drive signal from the thermal valve controller CV.

Then, in this example, the main remote controller RM and the cold / hot water panel 51 for performing the heating / cooling operation operation of the indoor terminal (in this example, the cold / hot water panel 51 and the fan coil unit 52) in the room A are provided. A remote control device RA for terminals for performing air-conditioning operation 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.

In addition, the function equivalent to that of the main remote control device RM may be added to the terminal remote control device RA, and the main remote control device RM may be omitted.

The main remote controller RM outputs the control signal SS1 in response to the user's operation.
This control signal SS1 is input to an outdoor unit control unit (described later) that controls the outdoor unit 1 and is input to the outdoor unit control unit (described later).
As a result, the flow rate, temperature, etc. of the cold / hot water supplied to the common going pipe 2A are controlled, and in response to this, the control signal SS2 is output from the outdoor unit control unit to the thermal valve controller CV. In response to this, the opening / closing operation of the thermal valve V1 can be controlled by the control signal S1 output from the thermal valve controller CV. Further, the control signal Sa output corresponding 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 the input to the thermal valve controller CV. The thermal valve V1
The opening and closing operation of is controllable.

On the other hand, the return pipe 3B1 from the cold / hot water panel 51 is provided with a return temperature sensor 54. The return temperature sensor 54 detects the temperature (return temperature) of hot water or cold water in the corresponding return pipe 3B1, and outputs a detection signal indicating the detection result to the thermal valve controller CV.
Output to.

The thermal valve controller CV controls the opening / closing of the thermal valve V1 based on the return temperature detected by the return temperature sensor 54 while supporting the operation of the main remote controller device RM and the terminal remote controller device RA. conduct. As a result, the user can use the remote control devices RM and RA.
The operating state of the cold / hot water panel 51 and the fan coil unit 52 can be controlled by appropriately operating the above.

The remote control device RC for terminals includes 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 the fan coil unit 52.
A cooling switch 25 as a cooling instruction means for causing a cooling operation to cool the room, and
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 are provided with respect to the terminal control unit 29. It is connected so that it can communicate.

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

FIG. 2 shows the appearance of the main remote controller RM. The main remote controller RM is instructed to start / stop the operation of the display unit 250, the outdoor unit 1, and the indoor terminal (cold / hot water panel 51 among the cold / hot water panel 51 and the fan coil unit 52). Start / Stop "
A button 253, a "timer" button 254 for instructing the indoor terminal to operate by a timer, and an instruction to switch the operation mode (cooling / heating, normal mode / save mode, etc.) of the indoor terminal. It is equipped with a "operation switching" button 255, a "back" button 257 for returning the screen display to the previous screen, a "menu / decision" button 258, and a cross key 259 in the up / down / left / right directions. .. The "run / stop" button 253, the "timer" button 254, the "operation switching" button 255, the "return" 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 C.
It has a built-in PU and a memory as a storage means.

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, an operating state display area 200A showing 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. Temperature setting display area 200 for displaying the set temperature (corresponding to the numerical value of the temperature level, which can be set by the user using the operation unit 259 or the like)
It is equipped with B.

In the illustrated example, "during hot water heating operation" indicating a state in which hot water is supplied from the outdoor unit 1 to the operation state display area 200A and the heating operation is performed as a whole of the temperature control system 100.
Is displayed. Further, in the temperature setting display area 200B, the 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. 3 (a). In FIG. 3A, 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 an antifreeze liquid or the like as the cold / hot water to circulate the indoor terminal. Heat exchange between the hot / cold water circulation circuit 22 (consisting of the hot / cold water outgoing pipe 2 and the cold / hot water return pipe 3) that absorbs and dissipates heat in the machine (cold / hot water panel 51 and fan coil unit 52). It is a heat pump type heat source machine.

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. The heat of the heat source side heat exchanger 8 which is a heat pump heat exchanger, the expansion valve 9 which decompresses and expands the refrigerant, and the hot and cold water circulating in the hot and cold water forward pipe 2 and the cold and hot water return pipe 3 and the refrigerant. The water-refrigerant heat exchanger 11 to be exchanged is connected by a refrigerant pipe 15. The heat pump device is composed of the four-way valve 6, the compressor 7, the heat source side 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 heat source side 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 a low-pressure gas state to a high-pressure gas state, and also functions as a pump for circulating the refrigerant in the entire refrigerant pipe 15 in the outdoor unit 1. A discharge temperature sensor 55 is provided in the refrigerant sub-path 15b on the discharge side of the compressor 7. 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.

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 heat source side heat exchanger 8 is 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. 3A, in the order of the refrigerant main path 15a counterclockwise).

The heat source side 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. 3 described later).
b) See).

The outdoor fan 10 blows air to the heat source side heat exchanger 8 to improve the performance of the heat source side 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 hot / cold water forward pipe 2 and the hot / cold 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 the cold / hot water, it functions as a condenser that dissipates the heat to the cold / hot water and condenses it into the 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, 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 Figure 3 (b) below).

On the other hand, the cold / hot water circulation circuit 22 includes the water-hydrogen heat exchanger 11 provided in the outdoor unit 1, a circulation pump 12 for applying a circulating pressure to the cold / hot water, a systurn tank 13, and the indoor terminal unit (the indoor terminal unit (2). The cold / hot water panel 51 and the fan coil unit 52) are combined with the cold / hot water outbound pipe 2 (specifically, the common outbound pipe 2A) and the cold / hot water return pipe 3 (specifically, the common return pipe 3).
It is formed by connecting at A).

The water-refrigerant heat exchanger 11 is connected to the hot / cold water going 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 (separation of air bubbles).
Air-water separation function), absorption of expanded cold / hot water in the cold / hot water circulation circuit 22, and replenishment of cold / hot water.

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

In this example, 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 has a return temperature sensor 56B as a return temperature determining means. Is provided, the temperature of hot water or cold water in the common return pipe 3A (hereinafter, appropriately referred to as “actual return temperature”) is detected, 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 that controls the outdoor unit 1. The outdoor unit control unit CU is mainly composed of a microcomputer equipped with a CPU, ROM, 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. 1, in particular, a signal from the terminal control unit 29 is transmitted in one direction between the outdoor unit control unit CU and the terminal control unit 29 of the fan coil unit 52, for example. It is connected by a terminal control line (so-called E-con communication line) (see FIG. 1). For example, the heating switch 24 (or the cooling switch 25) of the remote control device RC for the terminal.
Is operated by the 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 sets the outdoor unit control unit CU.
On the other hand, the hot water request signal related to the heating operation (or the cold water request signal related to the cooling operation) S.
Output C (see the imaginary line in FIGS. 3 (a) and 3 (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. 1, the configuration is not limited to the configuration in which the fan coil unit 52 is operated by the terminal remote control 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 remote control device RC for the terminal, and the remote control device RC for the terminal may be omitted. In this case, when the operation start instruction is given by the user operating the switch or the like of the fan coil unit 52, the terminal control unit 29 receives the instruction signal and receives the instruction signal.
The hot water request signal (or the cold water request signal) SC is output to the outdoor unit control unit CU.
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 tells the outdoor unit control unit CU the stop request signal for heating operation (or cooling operation). Is output.

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 the refrigerant main path 15a is switched by switching the four-way valve 6.
Controls the circulation direction of the upper refrigerant. FIG. 3A shows the circulation direction during the heating operation in the configuration example shown in FIG. 1, and the refrigerant discharged from the compressor 7 is the water-refrigerant heat exchanger 11, the expansion valve 9, and the heat on the heat source side. It is distributed in the order of the exchanger 8. 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, which is in a state where it is easy to evaporate. After that, the low-pressure liquid evaporates in the heat source side heat exchanger 8 (functions as an evaporator) and changes into a gas, thereby absorbing 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 supplied from the cold / hot water going pipe 2 to the indoor terminal (two of the cold / hot water panel 51 and the fan coil unit 52). It dissipates heat to the room air to heat the room, and then passes through the systurn 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 hot / cold 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. 3B shows the circulation direction during the cooling operation in the configuration example shown in FIG. 1, and the refrigerant discharged from the compressor 7 is the heat source side heat exchanger 8, the expansion valve 9, and the water-refrigerant. It is distributed in the order of the heat 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 is used in the heat source side heat exchanger 8 (functioning as a condenser). By being cooled by the blast of 10, 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, which is in a state where it is easy to evaporate. After that, the low-pressure liquid evaporates in the water-refrigerant heat exchanger 11 (functions as an evaporator) and changes into a gas, thereby absorbing heat from the cold water from the hot / cold 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 supplied from the cold / hot water going pipe 2 to the indoor terminal (two of the cold / hot water panel 51 and the fan coil unit 52). It absorbs heat from the room air to cool the room, and then passes through the systurn 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.

In the outdoor unit 1 having the circuit configurations shown in FIGS. 3A and 3B, the temperature of the refrigerant discharged from the compressor 7 is kept constant in order to stably generate cold water or hot water. There is a need. Therefore, as shown in FIG. 4, 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.

<Compressor control unit>
As shown in FIG. 4, the compressor control unit 61 includes a return temperature control unit 61B. The return temperature control unit 61B performs so-called return temperature control that controls the rotation speed of the compressor 7 according to the actual return temperature of hot water or cold water detected by the return temperature sensor 56B.

<Control of compressor control unit during heating operation>
First, the control procedure by the return temperature control unit 61B during the heating operation is shown in the flowchart of FIG. 5A. In FIG. 5A, first, 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 started from the stopped state by, for example, an appropriate operation start operation of the outdoor unit 1 is performed by the user via the main remote control device RM or the terminal remote control devices RA and RC. Or, when the operation of the outdoor unit 1 is restarted after the operation is stopped (details will be described later).
Is. The determination in step S10 is not satisfied until the operation start state is reached (S10: NO).
When the loop waits and the operation start state is reached, the determination in step S10 is satisfied (S10: YES).
), Move 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 sensor 54 is the same without operating the outdoor unit 1. It may reach above the target return temperature. 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, step S is not in the operation end state (that is, the standby state).
The determination of 15 is not satisfied (S15: 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 in 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.

After calculating the target return temperature as described above, the process proceeds to step S35. Step S
In 35, in the compressor control unit 61, the actual 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 the step S155. Determine if it is. 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, during the heating operation of the cold / hot water panel 51, steps S35 and S40
By the process of step S45, the return temperature control unit 61B controls the return temperature to control the rotation speed of the compressor 7 so that the return temperature matches the target return temperature.

<Control of compressor control unit during cooling operation>
Next, the control procedure by the compressor control unit 61 during the cooling operation is shown in the flowchart of FIG. 5 (b). As shown in FIG. 5B, in this flow, step S35 in the flow of FIG. 5A is replaced with step S35A in which the direction of the inequality sign is reversed. That is, in step S35A, in the return temperature control unit 61B of the compressor control unit 61, the actual return temperature of the cold water detected from the return temperature sensor 56B at this point is the step S1.
It is determined whether or not the target return temperature set in 55 is exceeded. If the return temperature is higher than the target return temperature, the determination is satisfied (S35A: YES) and the step S40.
If the forward temperature is equal to or lower than the target forward temperature, the determination is not satisfied (S35A).
: NO), the process proceeds to step S45.

Procedures other than the above are the same as those in FIG. 5A, and the description thereof will be omitted.

As described above, during the cooling operation of the cold / hot water panel 51, steps S35A and S4
0, By the process of step S45, the return temperature control unit 61B controls the return temperature to control the rotation speed of the compressor 7 so that the return temperature matches the target return temperature.

<Control of expansion valve opening with respect to compressor rotation speed>
For example, when the temperature of hot water or cold water from the water-refrigerant heat exchanger 11 fluctuates (the load of heating or cooling fluctuates), it is shown in FIGS. 5 (a) and 5 (b) by the return temperature control unit 61B. The rotation speed of the compressor 7 fluctuates depending on the control. Here, for example, the expansion valve control unit 62 sets the opening degree of the expansion valve 9 according to the refrigerant discharge temperature of the refrigerant discharged from the compressor 7, which is usually performed in this type of heat pump device. When the control is performed, for example, when the rotation speed of the compressor 7 fluctuates greatly, the valve opening degree of the expansion valve 9 cannot follow quickly, and the refrigerant discharge temperature changes significantly, so that the load side It may lead to output instability.

Therefore, in the present embodiment, the expansion valve control unit 62 is set in a normal situation by the normal control unit 62A.
In a situation where the amount of change in the rotation speed of the compressor 7 is small), in addition to performing normal control for controlling the opening degree of the expansion valve so that the refrigerant discharge temperature reaches the target temperature, the feedforward control unit 62B (
When a peculiar situation (a situation in which the amount of change in the rotation speed of the compressor 7 becomes large) occurs due to the expansion valve control means), the compressor control unit 61 controls the rotation speed of the compressor 7. The opening degree of the expansion valve 9 is controlled (so-called feedforward control). At this time, in particular, in the present embodiment, the feedforward control unit 62B controls to change the opening degree of the expansion valve 9 proportionally to the amount of change in the rotation speed of the compressor 7 by using a predetermined coefficient. ..

<The normal control by the normal control unit>
As shown in FIG. 4, the normal control unit 62A of the expansion valve control unit 62 inputs the detection result of the discharge temperature sensor 55 (in FIGS. 3A and 3B to prevent complications). (Not shown), the expansion valve 9 so that the detected refrigerant discharge temperature becomes an appropriate target discharge temperature that is appropriately set (details omitted) in response to the operation of the main remote controller RM, for example. Control the valve opening. The control contents of the normal control unit 62A will be described step by step using the flowchart of FIG.

<Control content>
The control content of the expansion valve 9 during the heating operation by the normal control unit 62A will be described with reference to the flowchart of FIG. In FIG. 6, first, in step S160, the normal control unit 62A determines whether or not the outdoor unit 1 is in the operation start state. Specifically, the operation start state is
For example, when the outdoor unit 1 is started from a stopped state by an appropriate operation start operation of the outdoor unit 1 by the user via the main remote control device RM or the terminal remote control devices RA, RC, or restarted after the operation is stopped. Then, when the operation of the outdoor unit 1 is restarted, this is the case. The determination in step S160 is not satisfied (S160: NO) until the operation start state is reached, and the loop standby is performed. When the operation start state is reached, the determination in step S160 is satisfied (S160: YES).
The process proceeds to step S165.

In step S165, the normal control unit 62A 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 actual return temperature detected by the return temperature sensor 56B returns to the target without operating the outdoor unit 1. It may reach above the temperature (details below). in this case,
The outdoor unit 1 is stopped by the known control by the outdoor unit control unit CU and enters a standby state (that is, the operation of the outdoor unit 1 is temporarily terminated). When the operation end state (that is, the standby state) is reached, the determination in step S165 is satisfied (S165: YES), and this flow ends. On the other hand, step S1 is not in the operation end state (that is, the standby state).
The determination of 65 is not satisfied (S165: NO), and the process proceeds to step S170.

In step S170, the normal control unit 62A 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 (S170: YES), and the process proceeds to step S175.

In step S175, the normal control unit 62A reduces the valve opening degree of the expansion valve 9. After that, the process returns to step S165 and the same procedure is repeated.

On the other hand, in the determination in step S170, if the refrigerant discharge temperature is equal to or higher than the target discharge temperature, the determination is not satisfied (S170: NO), and the process proceeds to step S180.

In step S180, the normal control unit 62A increases the valve opening degree of the expansion valve 9. After that, the process returns to step S165 and the same procedure is repeated.

As described above, by the processing of step S170, step S175, and step S180, the normal 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 can be obtained. Will be done.

As for the control content of the expansion valve 9 during the cooling operation, the same control as in the flowchart of FIG. 6 is sufficient, and thus the description thereof will be omitted.

<The feedforward control by the expansion valve control unit>
FIG. 7 shows an example of the relationship between the amount of change in the rotation speed of the compressor 7 and the amount of change in the opening degree of the expansion valve 9 in the feedforward control executed by the expansion valve control unit 62. In FIG. 7, in this example, the amount of change in the rotation speed is one cycle from the current rotation speed instruction value of the compressor 7 at a certain control timing and the control timing, for example, when the control content is periodically updated. It is represented by a deviation obtained by subtracting the rotation speed indicated value of the previous compressor 7 at the previous control timing (hereinafter, appropriately referred to as “rotation speed deviation”). Then, in response to the rotation speed deviation when the rotation speed of the compressor 7 changes in this way, the expansion valve control unit 62 receives the expansion valve 9
An example of the current opening change amount indicated value to be executed is shown. However, in this example, the opening degree of the expansion valve 9 and the opening change amount indicated value are the number of pulses which is the drive control amount of the stepping motor of the actuator that opens and closes the expansion valve 9 and its deviation (hereinafter, appropriately, the number of pulses). deviation)
It is expressed as a substitute. In the present embodiment, a positive value of the pulse number deviation corresponds to a positive value of the opening change amount indicated value of the expansion valve 9, and a negative value of the pulse number deviation corresponds to the expansion valve by a known method. It is associated with a negative value of the opening degree change amount indicated value of 9.

As shown in FIG. 7, in the present embodiment, when the rotation speed indicated value of the compressor 7 (hereinafter, appropriately simply referred to as “the rotation speed of the compressor 7”) increases by a value of 30 [rps] or more, The opening degree of the expansion valve 9 is controlled so as to increase by a magnitude corresponding to 120 [pulses] of the stepping motor (hereinafter, as appropriate, simply "controlled so that the opening degree increases by 120 pulses" and the like will be described. ). When the rotation speed of the compressor 7 increases by 20 [rps] or more and less than 30 [rps],
The opening degree of the expansion valve 9 is controlled to increase by 80 [pulse]. Similarly, when the rotation speed of the compressor 7 is increased by 15 [rps] or more and less than 20 [rps], the opening degree of the expansion valve 9 is 60.
[Pulse] is controlled to increase, and the rotation speed of the compressor 7 is 10 [rps] or more and 15 [rp].
When it increases by less than s], the opening degree of the expansion valve 9 is controlled to increase by 40 [pulse].

Further, when the rotation speed of the compressor 7 increases by less than 10 [rps], the rotation speed is maintained at the same value, or the rotation speed decreases by less than 10 [rps], the expansion valve 9 is opened. The degree is controlled so that there is almost no increase or decrease.

Further, when the rotation speed of the compressor 7 decreases by 10 [rps] or more and less than 15 [rps], the opening degree of the expansion valve 9 is controlled to decrease by 40 [pulses], and the rotation speed of the compressor 7 is reduced. Is 15
When it decreases by more than [rps] and less than 20 [rps], the opening degree of the expansion valve 9 is controlled to decrease by 60 [pulse]. Similarly, the rotation speed of the compressor 7 is 20 [rps] or more and 30 [r].
When it decreases by less than [ps], the opening degree of the expansion valve 9 is controlled to decrease by 80 [pulse], and when the rotation speed of the compressor 7 decreases by more than 30 [rps], the expansion valve The opening degree of 9 is controlled to decrease by 120 [pulse].

As described above, the opening degree of the expansion valve 9 is controlled to the opening side according to the increase amount of the rotation speed of the compressor 7, and to the closing side according to the decrease amount of the rotation speed of the compressor 7. Be controlled.

FIG. 8 is a graph conceptually showing the behavior of the expansion valve 9 when the expansion valve control unit 62 executes the control content of FIG. 7. That is, as described with reference to FIG. 7, the opening degree of the expansion valve is actually controlled so as to change stepwise, but by providing a certain number of such steps, almost the same behavior as the graph of FIG. 8 is realized. can do. In the graph of FIG. 8, the horizontal axis represents the amount of change in the rotation speed of the compressor 7 [rps], and the vertical axis represents the amount of change in the opening degree [pulse] of the expansion valve 9. As shown in the figure, in this case, the amount of change in the opening degree of the expansion valve 9 (however, expressed by substituting [pulse]) has a coefficient k1 (k1≈4 in this example) with respect to the amount of change in the rotation speed of the compressor 7. It will be controlled proportionally so that the change pattern is multiplied by.

<Control by feedforward control unit>
FIG. 9 shows the control procedure by the feedforward control unit 62B of the expansion valve control unit 62 described above.
It is shown in the flowchart of. The same control content is used during both the heating operation and the cooling operation. Figure 9
First, in step S60, the feedforward control unit 62B has the feedforward control unit 62B in FIG. 5A.
In the same manner as in step S10 of the above, it is determined whether or not the outdoor unit 1 is in the operation start state. 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 feedforward control unit 62B determines whether or not the outdoor unit 1 is in the operation end state in the same manner as in step S15 of FIG. 5A. When the operation is completed (that is, the standby state), the determination in step S65 is satisfied (S65).
: YES), end this flow. 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 S68.

In step S68, the feedforward control unit 62B determines at this point whether or not the current rotation speed of the compressor 7 has increased or decreased by a predetermined range (less than ± 10 [rps] in the above example) from the previous rotation speed. .. If the current rotation speed of the compressor 7 has increased or decreased or has not increased or decreased by ± 10 [rps], the determination is satisfied (S68: YES), and step S6.
Move on to 9.

In step S69, the feedforward control unit 62B adjusts the valve opening degree of the expansion valve 9.
It does not increase or decrease, it maintains (that is, it does nothing in terms of control). After that, the process returns to step S65 and the same procedure is repeated.

On the other hand, if the rotation speed of the compressor 7 is increased or decreased this time in step S68, the determination is satisfied (S69: YES), and the process proceeds to step S70. In step S70, the feedforward control unit 62B determines at this point whether or not the current rotation speed of the compressor 7 is lower than the previous rotation speed. When the rotation speed of the compressor 7 is reduced this time, the determination is satisfied (S70).
: YES), move to step S75.

In step S75, the feedforward control unit 62B adjusts the valve opening degree of the expansion valve 9.
According to FIG. 7, the amount is reduced by the amount corresponding to the decrease in the rotation speed of the compressor 7 this time (see also FIG. 8). After that, the process returns to step S65 and the same procedure is repeated.

On the other hand, in the determination in step S70, if the current rotation speed of the compressor 7 increases from the previous rotation speed, the determination is not satisfied (S70: NO), and the process proceeds to step S80.

In step S80, the feedforward control unit 62B adjusts the valve opening degree of the expansion valve 9.
According to FIG. 7 above, the amount is increased by an amount corresponding to the increase in the rotation speed of the compressor 7. Then, the process returns to step S65 and the same procedure is repeated (see also FIG. 8).

As described above, by the processing of step S70, step S75, and step S80, the opening degree of the expansion valve 9 is controlled according to the control of the rotation speed of the compressor 7 by the compressor control unit 61.

By controlling the expansion valve 9 by the expansion valve control unit 62 as described above, even if the rotation speed of the compressor 7 fluctuates greatly as described above, the opening degree of the expansion valve 9 changes rapidly correspondingly. Therefore, the change in the refrigerant discharge temperature can be suppressed to a small value, and the load side output can be stabilized.

<Example of heating operation behavior>
Next, an example of the conceptual behavior of the heat pump type temperature control system 100 during the heating operation when the control is performed by the compressor control unit 61 and the expansion valve control unit 62 as described above will be described with reference to FIG.

In the figure, FIG. 10A shows the time course of the actual return temperature (denoted as “actual water temperature”) in the cold / hot water return pipe 3 (note that the return temperature sensor 56B in the present embodiment).
Actually detected by). FIG. 10B shows the time course of the refrigerant discharge temperature discharged from the compressor 7. FIG. 10C shows the time course of the temperature of the refrigerant flowing into the heat source side heat exchanger 8 (indicated as “refrigerant temperature (evaporation)” in the figure). FIG. 10D shows the time course of the rotation speed of the compressor 7 under the control of the compressor control unit 61. FIG. 10
(E) shows the time course of the opening degree of the expansion valve 9 under the control of the expansion valve control unit 62.
FIG. 10 (f) shows the time course (along with the target output) of the actual output during the heating operation by the cold / hot water panel 51 and the fan coil unit 52.

In FIG. 10, the return temperature is controlled as described above, and the rotation speed of the compressor 7 is controlled so that the actual return temperature becomes the target return temperature (40 [° C.] in this example).

Here, for example, the heating load is reduced due to the heating of the rooms A and B by a heat source of another system (not shown), and the heating output (target output) that must be performed by the heat pump type temperature control system 100 is increased. It becomes smaller (see time t1 to t2 in FIG. 10 (f)), and as a result, the actual return hot water temperature gradually rises and begins to move away from the target return temperature of 40 ° C. (see time t1 to t2 in FIG. 10 (a)). ). Therefore, by the return temperature control of the compressor control unit 61, the rotation speed of the compressor 7 is controlled to decrease from 90 [rps] to 75 [rps] (time t2 in FIG. 10D). reference). Then, in response to this decrease in the number of revolutions by 15 [rps], the opening degree of the expansion valve 9 is controlled to decrease at once from 300 [pulse] to 240 [pulse] by the control of the expansion valve control unit 62. (See time t2 in FIG. 10 (e)). As a result, the refrigerant discharge temperature is kept substantially constant (see time t1 to t2 in FIG. 10B).

However, in this example, since the actual return temperature continues to rise even after the time t2 (see time t2 to t3 in FIG. 10A), the return temperature control of the compressor control unit 61 is performed. , The rotation speed of the compressor 7 is controlled to further decrease from 75 [rps] to 55 [rps] (see time t3 in FIG. 10D), and corresponds to this decrease in rotation speed by 20 [rps]. Then, the opening degree of the expansion valve 9 is controlled to decrease from 240 [pulse] to 160 [pulse] at once by the control of the expansion valve control unit 62 (see time t3 in FIG. 10E).
.. As a result, the refrigerant discharge temperature is continuously kept substantially constant (see time t2 to t3 in FIG. 10B).

Due to such control, the actual return temperature starts to decrease after the time t3 has passed, but in this example, when the time t4 is reached thereafter, the target return temperature is below 40 [° C.].
Due to the return temperature control of the compressor control unit 61, the rotation speed of the compressor 7 is again 55 [rps].
] To 70 [rps] (see time t4 in FIG. 10 (d)). Along with this, in response to the increase in the rotation speed by 15 [rps], the opening degree of the expansion valve 9 is controlled to increase again from the 160 [pulse] to the 220 [pulse] by the control of the expansion valve control unit 62. (See time t4 in FIG. 10 (e)). As a result, the refrigerant discharge temperature is continuously kept substantially constant (see time t3 to t4 in FIG. 10B). Then, the actual return temperature reaches the target return temperature (40 [° C.] in this example) at the subsequent time t41, and then stabilizes.

<Example of cooling operation behavior>
Next, an example of the conceptual behavior of the heat pump type temperature control system 100 during the cooling operation when the control is performed by the compressor control unit 61 and the expansion valve control unit 62 as described above will be described with reference to FIG.

In the illustration, FIG. 11 (a) shows the time course of the actual return temperature (denoted as “actual water temperature”) as in FIG. 10 (a), and FIG. 11 (b) is the above-mentioned FIG. 10 (b). Similarly, the transition of the refrigerant discharge temperature over time is shown, and FIG. 11 (c) shows the temperature of the refrigerant flowing into the water-refrigerant heat exchanger 11.
In the figure, it is expressed as "refrigerant temperature (evaporation)") over time. Further, FIG. 11 (d) shows the time course of the rotation speed of the compressor 7 in the same manner as in FIG. 10 (d), and FIG. 11 (e) shows the time course.
Similar to FIG. 10 (e), the time course of the opening degree of the expansion valve 9 is shown. And FIG. 11
(F) shows the time course (along with the target output) of the actual output during the cooling operation by the cold / hot water panel 51 and the fan coil unit 52.

In FIG. 11, the return temperature is controlled as described above, and the rotation speed of the compressor 7 is controlled so that the actual return temperature becomes the target return temperature (10 ° C. in this example).

Here, the cooling load is reduced as in FIG. 10, and the heat pump type temperature control system 10
The cooling output (target output) that must be performed at 0 becomes smaller (time t1 to t in FIG. 11 (f)).
2), and as a result, the actual return hot water temperature gradually decreases and begins to move away from the target return temperature of 10 ° C. (see time t1 to t2 in FIG. 11A). Therefore, due to the return temperature control of the compressor control unit 61, the rotation speed of the compressor 7 is changed from 90 [rps] to 75 [rps].
(See time t2 in FIG. 11 (d)). And this 15 [rps]
In response to the decrease in the number of revolutions per minute, the opening degree of the expansion valve 9 is controlled to decrease from 300 [pulse] to 240 [pulse] at once by the control of the expansion valve control unit 62 as in FIG.
(See time t2 in FIG. 11 (e)), and as a result, the refrigerant discharge temperature is kept substantially constant (see time t1 to t2 in FIG. 11 (b)).

After that, even after the time t2, the actual return temperature continues to decrease (FIG. 11).
(See time t2 to t3 in (a)), the rotation speed of the compressor 7 is controlled to further decrease from 75 [rps] to 55 [rps] by the return temperature control as in FIG. 10 (FIG. 11).
(See time t3 in (d)), the opening degree of the expansion valve 9 is 240 [] under the control of the expansion valve control unit 62.
It is controlled to further decrease from [pulse] to 160 [pulse] (see time t3 in FIG. 11 (e)). As a result, the refrigerant discharge temperature is continuously kept substantially constant (FIG. 11 (b).
) Times t2 to t3).

After the time t3 has passed, the actual return temperature starts to rise, but in this example, the time t4 is thereafter.
When the temperature reached 10 [° C.], the target return temperature exceeded 10 [° C.]. Therefore, due to the return temperature control, the rotation speed of the compressor 7 again increased from 55 [rps] to 70 [rps] as in FIG.
(See time t4 in FIG. 11 (d)). Along with this, the opening degree of the expansion valve 9 is controlled to increase again from the 160 [pulse] to the 220 [pulse] by the control of the expansion valve control unit 62 (see time t4 in FIG. 11E), and this result. The refrigerant discharge temperature is subsequently kept substantially constant (see time t3 to t4 in FIG. 11B). Then, the actual return temperature reaches the target return temperature (10 [° C.] in this example) at the subsequent time t41, and then stabilizes.

<Effect of the first embodiment>
In the outdoor unit 1 of the present embodiment, in order to stably generate cold water or hot water, the compressor 7
Since it is necessary to keep the temperature of the refrigerant discharged from the compressor constant, the compressor control unit 61 and the expansion valve control unit 62 are provided. The temperature of hot water or cold water from the water-refrigerant heat exchanger 11 fluctuates (
When the load of heating or cooling fluctuates), the compressor 7 is controlled by the compressor control unit 61.
The number of revolutions of is fluctuated. Then, the feedforward control unit 62B of the expansion valve control unit 62 controls the opening degree of the expansion valve 9 based on the amount of change in the rotation speed of the compressor 7 by the compressor control unit 61 (so-called feedforward control). As a result, even if the rotation speed of the compressor 7 fluctuates greatly, the opening degree of the expansion valve 9 changes rapidly correspondingly.
The change in the refrigerant discharge temperature can be suppressed to a small extent, and the output on the load side can be stabilized.

Further, in the present embodiment, in particular, the feedforward control unit 62B of the expansion valve control unit 62
As shown in FIGS. 7 and 8, the opening degree of the expansion valve 9 is changed to the open side according to the amount of increase in the rotation speed of the compressor 7 under the control of the compressor control unit 61. The opening degree of the expansion valve 9 is changed to the closed side according to the amount of decrease in the rotation speed of the compressor 7 under the control of the compressor control unit 61. In this way, when the rotation speed of the compressor 7 increases, the opening degree of the expansion valve 9 is further opened, and when the rotation speed of the compressor 7 decreases, the opening degree of the expansion valve 9 is further closed, thereby changing the refrigerant discharge temperature. Can be reliably suppressed.

Further, in the present embodiment, in particular, the feedforward control unit 62B of the expansion valve control unit 62
Is a predetermined coefficient (first) with respect to the amount of change in the rotation speed of the compressor 7, as shown in FIG.
The opening degree of the expansion valve 9 is proportionally changed (= proportional control) using the coefficient k1). In this way, by smoothly changing the opening degree of the expansion valve 9 with respect to the amount of change in the rotation speed of the compressor 7 by proportional control, the opening degree of the expansion valve 9 is adjusted with respect to the fluctuation of the rotation speed of the compressor 7. It can be made to follow finely, and the change in the refrigerant discharge temperature can be suppressed more reliably.

<Second Embodiment>
Next, the second embodiment of the present invention will be described with reference to FIGS. 12 to 18. In this embodiment, the relationship between the amount of change in the rotation speed of the compressor 7 and the amount of change in the opening degree of the expansion valve 9 described with reference to FIG. 7 in the first embodiment is related to the region on the minus side of the rotation speed deviation. It is an embodiment when it is changed in a part of.

FIG. 12 is a diagram corresponding to FIG. 7 of the first embodiment, and similarly, the rotation of the compressor 7 in the control executed by the feedforward control unit 62B of the expansion valve control unit 62 of the present embodiment. This is an example of the relationship between the amount of change in the number and the amount of change in the opening degree of the expansion valve 9. In the table shown in FIG. 12, the difference from FIG. 7 is that when the rotation speed of the compressor 7 decreases by 20 [rps] or more and less than 30 [rps], the opening degree of the expansion valve 9 decreases by 65 [pulses]. (In FIG. 7 above, it is controlled to decrease by 80 [pulse]), and when the rotation speed of the compressor 7 decreases by more than 30 [rps], the opening degree of the expansion valve 9 decreases by 75 [pulse] ( In FIG. 7, the point is controlled so as to decrease by 120 [pulse]). In the rotation speed classification other than the above, the values are the same as those in FIG. 7.

FIG. 13 shows the feedforward control unit 62B with the control contents of FIG. 12 as in FIG.
Is a graph conceptually showing the behavior of the expansion valve 9 when It is expressed by taking the amount of change [pulse]. As shown in the figure, in this case, in the first range in which the amount of decrease in the rotation speed of the compressor 7 is small (in this example, the range in which the amount decreases by 0 [rps] or more and 15 [rps] or less), the amount of decrease in the rotation speed is said. Coefficient k1 similar to that of the first embodiment (k1 ≈ 4 in this example. 1st
A change pattern (corresponding to a coefficient) in which the fluctuation range of the opening reduction amount of the expansion valve 9 is relatively large (corresponding to a coefficient).
The opening degree of the expansion valve 9 is changed so as to correspond to the first change pattern). And the compressor 7
In the second range (in this example, the range in which the decrease amount of the rotation speed exceeds 15 [rps]) larger than the first range, the change pattern different from the first change pattern (in this example,).
As the second coefficient, a change pattern obtained by multiplying a coefficient k2, which is about 1 smaller than k1, that is, a change pattern in which the fluctuation range of the opening reduction amount of the expansion valve 9 is relatively small. The opening degree of the expansion valve 9 is changed so as to correspond to the second change pattern). Also in this case, as in the first embodiment,
The opening degree of the expansion valve 9 is controlled to the opening side according to the increase amount of the rotation speed of the compressor 7, and is controlled to the closing side according to the decrease amount of the rotation speed of the compressor 7. There is no change.

<Significance of expansion valve opening control of the present embodiment>
In the first embodiment, as described above, the change pattern using the first coefficient k1 which is the same as the case where the rotation speed increases even when the rotation speed decreases with respect to the change amount of the rotation speed of the compressor 7. The opening degree of the compressor 7 is changed proportionally with.

Therefore, for example, during the heating operation shown in FIG. 10, the temperature of the refrigerant flowing into the heat source side heat exchanger 8 (indicated as “refrigerant temperature (evaporation)” in the figure) becomes − after time t4.
A low temperature of about 5 [° C.] to -10 [° C.] continues, and section A after the time t4 (2 in FIG. 10).
(Refer to the dotted line), frost formation may occur and defrosting operation may be required. Further, in the section B of the time t3 to t41 (see the two-dot chain line in FIG. 10), the water-refrigerant heat exchanger 11 also cannot absorb enough heat as described above. Sufficient heat exchange is not possible, and as a result, the heating output (denoted as "actual output" in the figure) is reduced (see FIG. 10 (f)).

Similarly, during the cooling operation shown in FIG. 11, the temperature of the refrigerant flowing into the water-refrigerant heat exchanger 11 reaches at least -10 [° C.] during the section C of the time t3 to t4. ° C] The following conditions continue, and as a result, the cold water inside the piping on the cold / hot water side of the water-refrigerant heat exchanger 11 may freeze.

In the present embodiment, in order to improve the above, as described above, in the first range where the amount of decrease in the rotation speed of the compressor 7 is small, the amount of decrease in the rotation speed varies as in the first embodiment. The rotation speed of the compressor 7 while changing the opening degree of the expansion valve 9 in a change pattern in which the fluctuation width of the opening degree decrease amount is relatively large using the coefficient k1 (k1≈4 in this example) with respect to the width. In the second range where the amount of decrease in the amount of rotation is large, the coefficient k2 (k1 ≈ 1 in this example) with respect to the fluctuation range of the amount of decrease in the number of rotations.
The opening degree of the expansion valve 9 is changed in a slightly loose change pattern in which the fluctuation range of the opening degree decrease amount is relatively small.

14, 15, and 16 show a specific example of controlling the opening degree of the expansion valve 9 in the present embodiment in comparison with the control of the opening degree of the expansion valve in the first embodiment during the heating operation. It is a figure which shows.

For example, in FIG. 14, the current rotation speed of the compressor 7 at a certain control timing and the rotation speed of the compressor 7 at the previous control timing one cycle before are subtracted from the control timing, and the rotation speed deviation is -10 [rps. ] (In other words, the compressor rotation speed is 1)
When it decreases by 0 [rps], the same applies hereinafter), the feedforward control unit 62B.
Behavior over time of the opening degree of the expansion valve 9 under the control of the above, the refrigerant discharge temperature coming out of the compressor 7, and the temperature of the refrigerant flowing into the heat source side heat exchanger 8 (indicated as "refrigerant temperature (evaporation)" in the figure). It is a figure showing. The behavior of the present embodiment is shown by a solid line, and the behavior of the first embodiment is shown by a broken line (the same applies to FIGS. 15 and 16 described later).

In FIG. 14, in this case, the control behavior in the second embodiment and the control behavior in the first embodiment are the same. That is, for example, when the heating load is reduced as described above and the rotation speed of the compressor 7 is controlled to decrease from 90 [rps] to 80 [rps] at time T1 by the return temperature control, this is followed. Correspondingly, the opening degree of the expansion valve 9 is from 200 [pulse] to 1.
It is controlled to decrease to 60 [pulse]. As a result, the target discharge temperature slightly decreases from 90 [° C.] at time T2, but then starts to increase, and then 90 [° C.] at time T3.
℃], and is maintained stable thereafter.

Further, for example, FIG. 15 shows a case where the rotation speed deviation becomes −15 [rps] due to, for example, a further significant reduction in the heating load. In FIG. 15, also in this case, the control behavior in the second embodiment and the control behavior in the first embodiment are the same. That is, similarly to FIG. 14, the rotation speed of the compressor 7 is 90 [rps] to 75 [rps] at time T1.
Correspondingly, the opening degree of the expansion valve 9 decreases from 200 [pulse] to 140 [pulse]. Similar to FIG. 14, the target discharge temperature slightly decreases from 90 [° C.] at time T2, but then starts to increase, returns to 90 [° C.] at the subsequent time T3, and is maintained stably thereafter. ..

Further, for example, FIG. 16 shows a case where the rotation speed deviation becomes −20 [rps] due to, for example, a further significant reduction in the heating load. In this case, the control behavior in the second embodiment is different from the control behavior in the first embodiment.

That is, when the rotation speed of the compressor 7 decreases from 90 [rps] to 70 [rps] at time T1 as in FIG. 14, in the method of the first embodiment, the refrigerant discharge temperature is set to 90 [° C.].
The opening degree of the expansion valve 9 is controlled to be greatly reduced from 200 [pulse] to 120 [pulse] at once (see the broken line; the same applies hereinafter). As a result, the temperature of the refrigerant flowing into the heat source side heat exchanger 8 (indicated as "refrigerant temperature (evaporation)" in the figure) sharply drops and reaches -5 [° C.] in the time T11 immediately after that. However, since the temperature continues to drop and frost formation occurs, a separate defrosting operation may be required.

On the other hand, in the method of the second embodiment, as shown by the solid line, when the rotation speed of the compressor 7 decreases from 90 [rps] to 70 [rps] at time T1, the expansion valve 9 The opening degree is limited to a decrease from 200 [pulse] to 135 [pulse] (in this example, after the time T1, the normal control unit 62A performs the normal control in which the refrigerant discharge temperature becomes the target temperature, and the above-mentioned The opening degree of the expansion valve 9 is slightly gradually reduced from 135 [pulse]).
As a result, the target discharge temperature slightly decreases from 90 [° C.] at time T2, but then starts to increase, and then returns to 90 [° C.] at time T3. At this time, the temperature of the refrigerant discharged from the heat source side heat exchanger 8 keeps gradual, and after the temperature drops to 0 [° C.] in time T2, it becomes almost stable in this state.

<Example of heating operation behavior>
An example of the conceptual behavior of the heat pump type temperature control system 100 of the present embodiment during the heating operation, which is realized by the control of the present embodiment as described above, is shown in FIG. 17 corresponding to FIG. 10. Similar to FIGS. 10 (a) to 10 (f), FIG. 17 (a) shows the time course of the actual return temperature (denoted as “actual water temperature”), and FIG. 17 (b) shows the time course of the refrigerant discharge temperature. Is shown in FIG. 17 (
c) shows the time course of the temperature of the refrigerant flowing into the heat source side heat exchanger 8 (indicated as “refrigerant temperature (evaporation)” in the figure), and FIG. 17 (d) shows the time course of the rotation speed of the compressor 7. The transition is shown in Fig. 17
(E) shows the time course of the opening degree of the expansion valve 9, and FIG. 17 (f) shows the time course of the actual output during the heating operation (along with the target output).

In FIG. 17, the behavior of the times t1 to t2 is the same as that of FIG. 10 described above. That is, the actual return hot water temperature begins to deviate from the target return temperature of 40 ° C. due to the decrease in the heating load (FIG. 17).
(See time t1 to t2 in (a)), the rotation speed of the compressor 7 is 90 [rps] to 75 [rps].
(See time t2 in FIG. 17 (d)). Correspondingly, the opening degree of the expansion valve 9 is reduced from 300 [pulse] to 240 [pulse] by the control of the feedforward control unit 62B (see time t2 in FIG. 17E), so that the refrigerant is discharged. The temperature is kept almost constant (
17 (b) time t1 to t2).

Then, after the time t2, the actual return temperature continues to rise (time t in FIG. 17A).
Corresponding to (see 2 to t3), the rotation speed of the compressor 7 is 75 [r] due to the return temperature control.
When it further decreases from [ps] to 55 [rps] (see time t3 in FIG. 17D), in the present embodiment, the expansion valve control unit 62 is controlled in response to the decrease in the rotation speed by 20 [rps]. The opening degree of the expansion valve 9 is controlled to be further reduced from 240 [pulse] to 175 [pulse] (see time t3 in FIG. 17 (e)). As a result, the refrigerant discharge temperature is continuously kept substantially constant (see time t2 to t3 in FIG. 17B).

At this time, unlike the first embodiment, by reducing the reduction width of the opening degree of the expansion valve 9, the temperature of the refrigerant flowing into the heat source side heat exchanger 8 (denoted as “refrigerant temperature (evaporation)”) is changed. Time t1-t
It is maintained at about 0 [° C.] without a significant decrease during 3 (the same applies after time t3). As a result, unlike FIG. 10, the water-refrigerant heat exchanger 11 can sufficiently exchange heat, so that the decrease in heating output (denoted as “actual output” in the figure) is suppressed (see FIG. 17 (f)). After the time t3, the output remains almost equal to the target output.

Further, the rotation speed of the compressor 7 is 55 [r] due to the return temperature control of the compressor control unit 61.
Ps] is maintained as it is (see time t3 to t4 in FIG. 17 (d) and thereafter), and the opening degree of the expansion valve 9 is also maintained in the above 175 [pulse] (time t3 to t4 in FIG. 18 (e)). And later). As a result, the actual return temperature quickly returns to the target return temperature (40 [° C.]) and stabilizes thereafter (see time t3 to t4 in FIG. 17B and thereafter).

<Example of cooling operation behavior>
Further, FIG. 18 shows an example of the conceptual behavior of the heat pump type temperature control system 100 of the present embodiment during the cooling operation. In the illustration, FIG. 18 (a) shows the time course of the actual return temperature (denoted as “actual water temperature”) as in FIG. 17 (a), and FIG. 18 (b) is the above-mentioned FIG. 17 (b).
), The time course of the refrigerant discharge temperature is shown, and FIG. 18 (c) shows the water-refrigerant heat exchanger 11.
It shows the time course of the temperature of the refrigerant flowing into (indicated as "refrigerant temperature (evaporation)" in the figure). Further, FIG. 18 (d) shows the time course of the rotation speed of the compressor 7 as in FIG. 17 (d), and FIG. 18 (e) shows the expansion valve as in FIG. 17 (e). The time course of the opening degree of 9 is shown. Then, FIG. 18 (f) shows the time course (along with the target output) of the actual output during the cooling operation by the cold / hot water panel 51 and the fan coil unit 52.

In FIG. 18, the behavior of the times t1 to t2 is the same as that of FIG. 11 above. That is, the actual return hot water temperature begins to deviate from the target return temperature of 10 ° C. due to the decrease in the cooling load (FIG. 18).
(See time t1 to t2 in (a)), the rotation speed of the compressor 7 is 90 [rps] to 75 [rps].
(See time t2 in FIG. 18 (d)). Correspondingly, the opening degree of the expansion valve 9 is reduced from 300 [pulse] to 240 [pulse] by the control of the expansion valve control unit 62 (FIG. 18 (FIG. 18).
(See time t2 in e)), the refrigerant discharge temperature is kept substantially constant (see time t1 to t2 in FIG. 18B).

Then, after the time t2, the actual return temperature continues to decrease (time t in FIG. 18A).
Corresponding to (see 2 to t3), the rotation speed of the compressor 7 is 75 [r] due to the return temperature control.
When it further decreases from [ps] to 55 [rps] (see time t3 in FIG. 18D), the opening degree of the expansion valve 9 increases from 240 [pulse] to 175 [pulse] under the control of the expansion valve control unit 62. Decrease (see time t3 in FIG. 18 (e)). As a result, the refrigerant discharge temperature is continuously kept substantially constant (see time t2 to t3 in FIG. 18B).

Similar to the above, since the reduction in the opening degree of the expansion valve 9 is small, the temperature of the refrigerant flowing into the water-refrigerant heat exchanger 11 (denoted as “refrigerant temperature (evaporation)”) is large during the time t1 to t3. It is maintained at about 0 [° C.] without decreasing (the same applies after time t3). The decrease in the cooling output (denoted as "actual output" in the figure) is suppressed (see FIG. 18 (f)), and after the time t3, the cooling output remains substantially equal to the target output.

Further, similarly to the above, the rotation speed of the compressor 7 is maintained as it is at the 55 [rps] (FIG. 18).
(See time t3 to t4 in (d) and thereafter), the opening degree of the expansion valve 9 is also maintained by the 175 [pulse] (see time t3 to t4 in FIG. 18 (e) and thereafter). As a result, the actual return temperature quickly returns to the target return temperature (10 [° C.]) and is stabilized thereafter (FIG. 18).
See time t3 to t4 in (b) and beyond).

<Effect of the second embodiment>
Also in the present embodiment described above, the same effect as that of the first embodiment can be obtained.

Further, in addition to the above, according to the present embodiment, when the opening degree of the expansion valve 9 is changed to the closed side in accordance with the decrease in the rotation speed of the compressor 7 under the control of the compressor control unit 61. The feed forward control unit 62B has a decrease in the number of revolutions in the first range (in this example, a range in which the decrease is by 0 [rps] or more and less than 20 [rps]) in which the decrease in the number of revolutions of the compressor 7 is small. The opening degree of the expansion valve 9 is changed so as to have the same change pattern (first change pattern) as in the first embodiment with respect to the fluctuation range of. Then, in the second range (in this example, a range in which the reduction amount of the rotation speed of the compressor 7 is larger than the first range by 20 [rps] or more), the fluctuation range of the reduction amount of the rotation speed is described. The opening degree of the expansion valve 9 is changed so as to have a change pattern that is slower than the first change pattern, that is, a pattern in which the fluctuation range of the opening degree decrease amount is small (second change pattern).

That is, the expansion is divided into two, the first range in which the decrease in the rotation speed of the compressor 7 is relatively small and the second range in which the decrease in the rotation speed of the compressor 7 is relatively large. The control mode of the valve 9 is switched so that the expansion valve 9 has a gradual change pattern (the second change pattern) in which the fluctuation range of the opening reduction amount is smaller than that in the first range in the second range. The opening degree of is changed. As a result, the frost formation in the heat source side heat exchanger 8 and the freezing in the water-refrigerant heat exchanger 11 occur while stabilizing the load side output by suppressing the change in the refrigerant discharge temperature as described above. Can be prevented.

Further, in the present embodiment, in particular, in the first range, the feedforward control unit 62B uses the first coefficient k1 (k1≈4 in the above example) with respect to the fluctuation range of the decrease amount of the rotation speed. The fluctuation range of the opening degree of the expansion valve 9 is proportionally reduced, and in the second range, the second coefficient k2 (the above example) smaller than the first coefficient k1 with respect to the fluctuation range of the decrease amount of the rotation speed. Then k2 ≒ 1)
Is used to proportionally reduce the fluctuation range of the opening degree of the expansion valve 9. As a result, the compressor 7
When the opening degree of the expansion valve 9 is smoothly changed to the closed side by proportional control to finely follow the decrease in the number of rotations of the heat source side, the frost on the heat source side heat exchanger 8 and the water-refrigerant heat are generated. It is possible to prevent the occurrence of the freezing in the exchanger 11.

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 first embodiment and the second embodiment, the hot / cold 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 the return temperature sensor 56B, and the so-called return temperature control is performed to control the rotation speed of the compressor 7 according to the actual return temperature of the hot water or cold water detected by the return temperature sensor 56B. However, the temperature sensor 56A (FIGS. 3 (a) and 3 (b)) goes to the cold / hot water outflow pipe 2 (specifically, the common outbound pipe 2A) on the outlet side (outflow side) of the water-refrigerator heat exchanger 11. Middle 2
(Refer to the dotted line) may be provided to perform so-called forward temperature control in which the rotation speed of the compressor 7 is controlled according to the return temperature of hot water or cold water detected by the forward temperature sensor 56A.

Further, in the above description, the case where the cold / hot water panel 51 and the fan coil unit 52 are connected as the heat exchange terminal has been described as an example, but the present invention is not limited to this, and the other having at least one of the cooling / heating functions. The present invention may be applied when a terminal (heat absorbing / radiating terminal), for example, a heating panel, a floor heating panel, a radiator, a convector, or the like is connected. Further, in the above embodiment, the case where two heat exchange terminals are connected has been described as an example, but the present invention is not limited to this. That is, a configuration in which only three or more heat exchange terminals or one heat exchange terminal are connected may be used.

1 Outdoor unit (heat pump heat source unit)
7 Compressor 8 Heat source side heat exchanger 9 Expansion valve 11 Water-refrigerant heat exchanger 15 Refrigerant piping 61 Compressor control unit (compressor control means)
62 Expansion valve control unit 62A Normal control unit 62B Feedforward control unit (expansion valve control means)
k1 1st coefficient (predetermined coefficient)
k2 2nd coefficient (predetermined coefficient)

Claims (2)

A heat pump device that connects a compressor, expansion valve, and heat exchanger on the heat source side with a refrigerant pipe,
A water-refrigerant heat exchanger that generates hot or cold water by heat exchange with water by receiving a refrigerant supplied from the heat pump device via the refrigerant pipe.
A compressor control means for controlling the rotation speed of the compressor, and
Expansion valve control means for controlling the opening degree of the expansion valve,
In a heat pump heat source machine with
The expansion valve control means of the expansion valve is based on the amount of change in the number of revolutions of the compressor by the compressor control means, and according to the amount of increase in the number of revolutions of the compressor under the control of the compressor control means. The opening degree of the expansion valve is changed to the opening side, and the opening degree of the expansion valve is changed to the closing side according to the amount of decrease in the number of revolutions of the compressor under the control of the compressor control means . Control the opening and
When the opening degree of the expansion valve is changed to the closed side according to the amount of decrease in the rotation speed of the compressor by the control of the compressor control means, the expansion valve control means is used.
In the first range where the amount of decrease in the rotation speed is small, the fluctuation range of the amount of decrease in the opening degree is reduced so as to have the first change pattern with respect to the fluctuation range of the amount of decrease in the rotation speed.
In the second range where the amount of decrease in the rotation speed is larger than the first range, the fluctuation range of the amount of decrease in the opening degree is smaller than the fluctuation range of the amount of decrease in the number of rotations compared to the first change pattern. 2 A heat pump heat source machine characterized in that the fluctuation range of the amount of decrease in the opening degree is reduced so as to have a change pattern. The expansion valve control means is
In the first range, the fluctuation range of the decrease amount of the opening degree of the expansion valve is proportionally reduced by using the first coefficient with respect to the fluctuation range of the decrease amount of the rotation speed.
In the second range, the fluctuation range of the decrease amount of the opening degree of the expansion valve is proportionally reduced by using a second coefficient smaller than the first coefficient with respect to the fluctuation range of the decrease amount of the rotation speed. The heat pump heat source machine according to claim 1.

Images