JP6351414B2 - Combined heat source heat pump device - Google Patents

Description

  The present invention relates to a composite heat source heat pump device, and more particularly to a composite heat source heat pump device using air heat and underground heat as heat sources.

  Recently, “geothermal heat” stored in the earth under the heat of the sun has little change in temperature throughout the year, so geothermal heat pumps that can effectively use this geothermal energy are attracting attention. In particular, geothermal heat pumps have the property that they can be stably heated even in cold regions where the winter is cold.

Conventionally, a heat pump device has been devised in which a geothermal heat pump and an air heat heat pump are connected in series to a circulation circuit in which a heat medium (circulating fluid) on the heat dissipation terminal circulates (see, for example, Patent Document 1).
The heat pump device described in Patent Document 1 can perform efficient heating operation by selecting a heat pump with better heat collection efficiency as a heat source based on the outside air temperature when the heating load is small. When the load is large, the two compressors of the geothermal heat pump and the air heat heat pump are driven to perform the heating operation in which the temperature of the circulating fluid is heated to the target temperature.

Japanese Patent Laying-Open No. 2014-35109 (see paragraph 0023 of FIG. 1, FIG. 1)

  By the way, in the heating operation in which both the geothermal heat pump and the air heat pump are driven to heat the circulating fluid so as to reach the target temperature, the circulating fluid temperature is equal to the target temperature. If exceeded, for example, the compressor of one of the priority heat pumps with good heat collection efficiency is driven as it is, the rotational speed of the compressor of the other auxiliary heat pump is decelerated and finally stopped, and the temperature of the circulating fluid reaches the target When the temperature of the circulating fluid falls below the target temperature, start (drive) the compressor of the other auxiliary heat pump again and control the circulating fluid temperature to the target temperature. However, if it does so, the compressor of an auxiliary heat pump will repeat a stop and start, and the room temperature of the air-conditioned space will also fluctuate with the intermittent operation. Les may compromise feeling of warmth there is further compressor of the auxiliary heat pumps had an problem that deterioration in thermal efficiency due to repetition of start and stop (COP).

  This invention is made in view of such a background, and provides the composite heat source heat pump apparatus which performs the 2 unit drive normal operation which can adjust heating temperature suitably and can improve thermal efficiency. Let it be an issue.

In order to solve the above-mentioned problem, the invention according to claim 1 includes a heating circulation circuit that circulates a circulating liquid in a heat radiating terminal, a first heating heat exchanger as a condenser disposed in the heating circulation circuit, A second heating heat exchanger as a condenser disposed in the heating circulation circuit; and a first compressor for compressing a refrigerant circulating in the circuit using ground heat as a heat source, through the first heating heat exchanger. A first heat pump circuit for heating the circulating fluid and a second compressor for compressing a refrigerant circulating in the circuit using air heat as a heat source, and heating the circulating fluid via the second heating heat exchanger. 2 is a composite heat source heat pump device comprising: a heat pump circuit; a terminal temperature sensor that measures the temperature of the circulating fluid; an outside air temperature sensor that measures the outside air temperature; and a control device that controls the operation. The heat exchanger has the heating circulation. Are arranged in series on the upstream side of the second heating heat exchanger in the circuit, the control device of the prior SL first compressor and the second compressor outside air temperature the outside air temperature sensor has measured a reference In a priority circuit determination step of determining one as a priority power source and the other as an auxiliary power source, and a two-unit drive normal operation for driving both the priority power source and the auxiliary power source, the temperature of the circulating fluid is a predetermined target. When the temperature is exceeded, the lower limit operation step of the auxiliary power source for executing the lower limit operation for decelerating the rotation speed of the auxiliary power source with a predetermined lower limit rotation speed as a limit, and the rotation speed of the priority power source are predetermined. A lower limit operation step of a priority power source that executes a lower limit operation that decelerates the lower limit rotation speed of the lower limit rotation speed, and the auxiliary power source is driven at the predetermined lower limit rotation speed, and the priority operation When the source is driven at the predetermined lower limit revolution speed, when the temperature of the circulating fluid exceeds a predetermined target temperature, the so as to stop the auxiliary power source, said control device, said When the lower limit operation of the auxiliary power source and the lower limit operation of the priority power source are executed, the rotation speed of the auxiliary power source is first set to the predetermined lower limit rotation speed while maintaining the rotation speed of the priority power source. And thereafter, the rotational speed of the priority power source is decelerated to the predetermined lower limit rotational speed .

  In the composite heat source heat pump device according to the present invention, the first heating heat exchanger heated by the underground heat source is arranged in series upstream of the second heating heat exchanger heated by the air heat heat source in the heating circuit. Thus, in an environment where the outside air temperature is low and the heating load is excessive in a cold region in winter, the circulating fluid heated by the first heating heat exchanger can be further heated by the second heating heat exchanger. Therefore, the circulating fluid that increases the heating output and heats the heat radiating terminal can quickly reach the target temperature.

In the composite heat source heat pump device according to the present invention, one of the first compressor and the second compressor is determined as a priority power source and the other as an auxiliary power source based on the outside air temperature measured by the outside air temperature sensor. By providing a priority circuit determining step, when the outside air temperature is higher than a predetermined reference temperature, the second compressor is driven as a priority power source and the first compressor is driven as an auxiliary power source, When the outside air temperature is lower than a predetermined reference temperature, the first compressor can be driven as a priority power source and the second compressor can be driven as an auxiliary power source.
For this reason, since the composite heat source heat pump device according to the present invention can use a heat source with high heat collection efficiency as a priority power source, power consumption can be efficiently suppressed.

  The composite heat source heat pump device according to the present invention stops the auxiliary power source for the first time when the temperature of the circulating fluid exceeds the target temperature while both the auxiliary power source and the priority power source are driven at the lower limit rotational speed. Therefore, by using the auxiliary power source as soon as possible without stopping it, the auxiliary power source does not frequently stop and start, and the auxiliary power source is repeatedly stopped and started. It is possible to improve the overall thermal efficiency while preventing the deterioration of the thermal efficiency of the power source, and to prevent the auxiliary power source from being repeatedly stopped and started, thereby reducing the fluctuation of the heating temperature and suitably heating temperature. Can be adjusted.

  Thus, the composite heat source heat pump device according to the present invention can improve the thermal efficiency while suitably adjusting the heating temperature (room temperature) by reducing the fluctuation of the heating temperature during normal operation.

  The composite heat source heat pump device according to the present invention reduces the rotation speed of the auxiliary power source to the lower limit rotation speed while maintaining the rotation speed of the priority power source, so that the auxiliary power source is used preferentially. Is quickly reduced to the lower limit rotation speed, the rotation speed of the auxiliary power source is set to the lower limit rotation speed, and then the rotation speed of the priority power source is reduced to the predetermined lower limit rotation speed, so that the auxiliary power source is not stopped and the lower limit rotation speed is not stopped. By driving at a speed, the thermal efficiency of the auxiliary power source can be efficiently secured, and the overall thermal efficiency can be improved.

  The composite heat source heat pump device according to the present invention can improve the thermal efficiency while suitably adjusting the heating temperature (room temperature) by reducing fluctuations in the heating temperature during normal operation.

It is an external appearance block diagram which shows the main units of the composite heat source heat pump apparatus which concerns on embodiment of this invention. It is a block diagram which shows the whole structure of the composite heat source heat pump apparatus which concerns on embodiment of this invention. It is a graph which shows the basic operation at the time of low load in start-up operation control concerning the embodiment of the present invention, (a) shows change of the rotation speed of two compressors, and (b) shows the temperature of circulating fluid. Shows the transition. It is a graph which shows the basic operation at the time of high load in start-up operation control concerning the embodiment of the present invention, (a) shows change of the rotation speed of two compressors, and (b) shows the temperature of circulating fluid. Shows the transition. It is a flowchart which shows the operation | movement in the starting operation control which concerns on embodiment of this invention. It is a flowchart which shows operation | movement when the target temperature is exceeded in the 2 unit drive normal operation control which concerns on embodiment of this invention. It is a flowchart which shows operation | movement when the target temperature is not exceeded in the 2 unit drive normal operation control following FIG. It is a flowchart which shows operation | movement of 1 unit drive normal operation control at the time of transfering from 2 unit drive normal operation control which concerns on embodiment of this invention to 1 unit drive normal operation control.

The configuration of the composite heat source heat pump apparatus 1 according to the embodiment of the present invention will be described in detail with reference to FIGS. 1 and 2 as appropriate.
As shown in FIG. 1, the composite heat source heat pump apparatus 1 includes a heating heat exchanging unit 3 that circulates a circulating liquid L (for example, hot water) as a heat medium in the heat radiating terminal 2, and underground heat using ground heat as a heat source A heat pump device 4, an air heat heat pump device 5 using air heat as a heat source, a control device 6 (61, 62) that controls the operation, and a remote controller 60 that sends a signal to the control device 6 are provided.

  As shown in FIG. 2, the composite heat source heat pump device 1 is a hybrid heat pump device in which a ground heat heat pump device 4 as a first heat pump circuit and an air heat heat pump device 5 as a second heat pump circuit are connected in series. Although it can function as a heating device and a cooling device, in the following embodiments, components and operations when used mainly as a heating device will be described.

  As shown in FIG. 2, the heat dissipating terminal 2 (21, 22) is a floor heating panel or a panel convector that heats the air-conditioned space. Since it is not a thing, detailed description is abbreviate | omitted.

  The heating heat exchanging unit 3 includes a heating circulation circuit 31 that circulates the circulating liquid L in the heat radiating terminal 2, a heating circulation pump 32 that is disposed in the heating circulation circuit 31 and pumps the circulating liquid L, and a circulation that supplies the heat radiating terminal 2 The thermal valve 33 (33a, 33b) for controlling the supply of the liquid L, the terminal temperature sensor 34 for measuring the temperature of the circulating liquid L flowing out from the heat radiating terminal 2 and returning, and the pressure in the flow path are adjusted. And a cistern 35.

The heating circulation circuit 31 includes a first heating heat exchanger 41 as a condenser of the underground heat pump device 4 and a second heating heat exchanger 51 as a condenser of the air heat heat pump device 5.
The first heating heat exchanger 41 is disposed in series on the upstream side of the second heating heat exchanger 51 in the heating circuit 31.

  With such a configuration, the circulating fluid L heated by the first heating heat exchanger 41 is further heated by the second heating heat exchanger 51 in an environment where the outside air temperature is low and the heating load is excessive in a cold region in winter. Therefore, the circulating liquid L for heating the heat radiating terminal 2 can be quickly reached to the target temperature.

  The terminal temperature sensor 34 is disposed on the upstream side of the first heating heat exchanger 41 in the heating circuit 31 and is controlled so as to obtain a comfortable heating by detecting the temperature of the circulating liquid L flowing out from the heat radiating terminal 2. Control is performed by the device 6.

  The geothermal heat pump device 4 includes a refrigerant circulation path 42 that supplies a high-temperature refrigerant C1 (for example, an HFC refrigerant such as R410A or R32 or a carbon dioxide refrigerant) to the first heating heat exchanger 41, and a first heating heat exchange. The first compressor 43 that compresses and sends the refrigerant C1 to the compressor 41, the temperature sensor 42a that detects the temperature of the refrigerant C1 compressed by the first compressor 43, and the first heating heat exchanger 41 The first expansion valve 44 that decompresses the refrigerant C1, the temperature sensor 42b that detects the temperature of the low-temperature refrigerant C1 decompressed by the first expansion valve 44, and the low-temperature refrigerant C1 decompressed by the first expansion valve 44 are heated. The underground heat source heat exchanger 45, the heat medium circulation path 46 that supplies the heat medium H1 (for example, antifreeze) to the underground heat source heat exchanger 45, and the underground that pressure-feeds the heat medium H1 of the heat medium circulation path 46. Thermal circulation pump 47 and heating medium circulation path The underground heat exchanger 48 arranged in 6, and a cistern 49 for adjusting the pressure of the heating medium circulation path 46.

With this configuration, in the underground heat source heat exchanger 45, in the underground heat source heat exchanger 45, the heat medium H1 circulating in the heating medium circulation path 46 and the refrigerant C1 circulating in the refrigerant circulation path 42 face each other and heat Since the exchange is performed, the underground heat collected by the underground heat exchanger 48 is transmitted to the refrigerant C1. Then, the refrigerant C <b> 1 is compressed by the first compressor 43 and supplied to the first heating heat exchanger 41.
In the first heating heat exchanger 41, the high-temperature refrigerant C1 compressed by the first compressor 43 and the low-temperature circulating liquid L returned from the heat radiating terminal 2 through the heating circulation circuit 31 face each other to generate heat. Exchange is performed and the circulating fluid L is heated.

The air heat heat pump device 5 includes a refrigerant circulation path 52 that supplies a high-temperature refrigerant C2 (for example, an HFC refrigerant such as R410A or R32 or a carbon dioxide refrigerant) to the second heating heat exchanger 51, and a second heating heat exchanger. The second compressor 53 that compresses and sends the refrigerant C2 to 51, the temperature sensor 52a that detects the temperature of the refrigerant C2 compressed by the second compressor 53, and the refrigerant that flows out from the second heating heat exchanger 51 The second expansion valve 54 that depressurizes C2, the temperature sensor 52b that detects the temperature of the low-temperature refrigerant C2 depressurized by the second expansion valve 54, and the low-temperature refrigerant C2 depressurized by the second expansion valve 54 are heated. An air heat source heat exchanger 55, an outside air temperature sensor 57 that detects the outside air temperature, and a four-way valve 58 that switches between heating and cooling by changing the flow direction of the refrigerant C <b> 2 in the refrigerant circuit 52.
The air heat source heat exchanger 55 heats the refrigerant C2 by exchanging heat between the air blown from the blower fan 56 and the refrigerant C2.

  With this configuration, the air heat heat pump device 5 is configured such that, in the second heating heat exchanger 51, the high-temperature refrigerant C2 compressed by the second compressor 53 and the first heating heat disposed on the upstream side of the heating circuit 31. The circulating fluid L flowing out of the exchanger 41 flows oppositely to exchange heat, and the circulating fluid L heated by the first heating heat exchanger 41 can be further heated.

  The control device 6 includes a geothermal heat pump control device 61 that controls the operation of the heating heat exchanger 3 and the geothermal heat pump device 4, and an air heat heat pump control device 62 that controls the operation of the air heat heat pump device 5. I have. The control device 6 can control the operation of the composite heat source heat pump device 1 by receiving signals from the temperature sensors such as the outside air temperature sensor 57 and the temperature sensors 42a and 42b and the remote controller 60.

The control device 6 operates either the underground heat pump device 4 or the air heat heat pump device 5 and drives the heating circulation pump 32, or operates both the underground heat pump device 4 and the air heat heat pump device 5. In the heating operation of heating the circulating fluid L circulating in the heating circuit 31 by driving the heating circulation pump 32, the temperature of the circulating fluid L reaches the target temperature set by the remote controller 60 or the like at the start-up. Until this is done, start-up operation control (see FIG. 3 and FIG. 4) is executed, and after reaching the target temperature, only one compressor normal operation control (see FIG. 8) or priority driving that drives only the compressor HP1 of the priority power source. The process shifts to two-drive normal operation control (see FIGS. 6 and 7) for driving both the compressor HP1 as the power source and the compressor HP2 as the auxiliary power source.
Hereinafter, for convenience of explanation, the compressor of the priority power source among the first compressor 43 and the second compressor 53 is referred to as a compressor HP1, and the compressor of the auxiliary power source is referred to as a compressor HP2.

Since the two-unit drive normal operation control (see FIGS. 6 and 7) according to the embodiment of the present invention is executed continuously after the start-up operation control, the start-up operation control (see FIG. 5) is described and then 2 The table drive normal operation control (see FIGS. 6 and 7) will be described.
<Start-up operation control>
The start-up operation control includes a priority circuit determination step for determining one of the first compressor 43 and the second compressor 53 as the compressor HP1 as the priority power source and the other as the compressor HP2 as the auxiliary power source, and the maximum rotation speed. A priority circuit driving step for driving only the compressor HP1 of the priority power source by setting the rotation speed lower than the above, and when the temperature of the circulating fluid L has not reached the predetermined target temperature when a predetermined target time has elapsed The auxiliary circuit driving step for setting the rotational speed lower than the maximum rotational speed and further driving the compressor HP2 of the auxiliary power source, and the temperature of the circulating fluid L has reached the target temperature when a predetermined determination time has elapsed. If not, a priority circuit acceleration step for driving the compressor HP1 of the priority power source by setting it higher than the rotation speed in the priority circuit driving step, and the temperature of the circulating fluid L when a predetermined determination time has elapsed Wherein when it has not reached the target temperature includes an auxiliary circuit acceleration step of driving the compressor HP2 auxiliary power source is set higher than the rotational speed of the auxiliary circuit driving step.

<Priority circuit judgment step>
In the priority circuit determination step, it is determined which thermal efficiency (COP) of the geothermal heat pump device 4 or the air heat heat pump device 5 is higher according to the outside air temperature.

Specifically, in the priority circuit determination step, when the outside air temperature detected by the outside air temperature sensor 57 is higher than a predetermined reference temperature (for example, 5 degrees), the air heat heat pump device 5 uses the underground heat heat pump. Since the heat collection efficiency is higher than that of the device 4, the second compressor 53 is determined as a priority power source, and the first compressor 43 is determined as an auxiliary power source.
On the other hand, when the outside air temperature is lower than a predetermined reference temperature (for example, 5 degrees), the ground heat heat pump device 4 has higher heat collection efficiency than the air heat heat pump device 5, and therefore the first compressor 43 is installed. It determines with a priority power source, and determines the 2nd compressor 53 as an auxiliary power source.

<Priority circuit drive step>
In the priority circuit driving step, at the start of the heating operation, the rotational speed is set lower than the maximum rotational speed (for example, 90 rps), and only the compressor HP1 of the priority power source is driven (for example, 70 rps). The power source compressor HP2 is not driven.
Note that the maximum rotation speed is appropriately set in consideration of the specifications of the heat pump device and the performance of the compressor, and may be the maximum rotation speed of the compressor or may be set lower than the maximum rotation speed.

<Auxiliary circuit drive step>
In the auxiliary circuit driving step, when the heating operation is started, the temperature of the circulating fluid L reaches a predetermined target temperature (for example, a temperature set by the user) when a predetermined target time (for example, 3 minutes) has elapsed. If not, in order to improve the thermal efficiency of the compressor HP2 of the auxiliary power source, the rotational speed is set lower than the maximum rotation speed (for example, 90 rps) and the compressor HP2 of the auxiliary power source is driven ( For example, 50 rps).

  Further, in order to drive the compressor HP1 of the priority power source having high thermal efficiency with priority, the compressor HP2 of the auxiliary power source is set to have a lower rotational speed than the compressor HP1 of the priority power source. Instead, the rotational speed may be set to be the same as that of the compressor HP1 as the priority power source in consideration of improvement in the thermal efficiency of the compressor HP2 as the auxiliary power source.

In the present embodiment, it is determined whether or not the temperature of the circulating fluid L has reached the target temperature when a predetermined target time (for example, 3 minutes) has elapsed. However, the present invention is not limited to this. When the temperature increase rate of the temperature of the circulating fluid L within the time range is less than a predetermined threshold, the compressor HP2 as an auxiliary power source may be driven.
Specifically, for example, after a predetermined start-up time has elapsed (after 1 minute has elapsed), a temperature increase rate of the temperature of the circulating fluid L per minute is determined every predetermined elapsed time (every 30 seconds), When the rate of temperature increase is less than 1.0 degree in 30 seconds, the auxiliary power source compressor HP2 may be driven at 50 rps, for example.

<Priority circuit acceleration step>
If the temperature of the circulating fluid L has not reached the target temperature after a predetermined determination time (for example, 30 seconds) has elapsed after executing the auxiliary circuit driving step, the rotational speed (70 rps) in the priority circuit driving step is determined. The compressor HP1 as the priority power source is driven at a maximum rotational speed of 90 rps, for example.

In the present embodiment, it is determined whether or not the temperature of the circulating fluid L has reached a predetermined target temperature when a predetermined determination time (for example, 30 seconds) has elapsed, but is not limited thereto. When the rate of temperature rise of the circulating fluid L within a predetermined time range is less than a predetermined threshold value, the priority power source compressor HP1 may be driven at a maximum rotational speed, for example, 90 rps.
Specifically, for example, the temperature increase rate of the temperature of the circulating fluid L every 20 seconds is obtained every predetermined elapsed time (for example, every 20 seconds), and the temperature increase rate is 0.8 degrees in 20 seconds. If not, the compressor HP1 as the priority power source may be driven at the maximum rotation speed of 90 rps.

<Auxiliary circuit acceleration step>
If the temperature of the circulating fluid L has not reached the target temperature after a predetermined determination time (for example, 30 seconds) has elapsed after executing the priority circuit acceleration step, the rotational speed (50 rps) in the auxiliary circuit driving step The compressor HP2 of the auxiliary power source is driven at a higher setting (for example, the maximum rotation speed of 90 rps).
Since the auxiliary circuit acceleration step is the same as the priority circuit acceleration step described above, detailed description thereof is omitted.

  Next, the basic operation in the start-up operation control will be described with reference to FIGS. 3 and 4. FIG. 3 is a graph for explaining the basic operation when the heating load in the heat radiating terminal 2 is low. (A) shows the transition of the rotational speeds of the two compressors HP1 and HP2, and (b) shows the circulation. The transition of the temperature of the liquid L is shown. FIG. 4 is a graph for explaining the basic operation when the heating load in the heat radiating terminal 2 is high. (A) shows the transition of the rotational speeds of the two compressors HP1 and HP2, and (b) shows the circulation. The transition of the temperature of the liquid L is shown.

  The heating load is a load (amount of heat) necessary for heating an air-conditioned space (not shown) to be heated. The specification of the heat radiating terminal 2, the rotational speed of the compressor, the outside air temperature, and the like are set. It depends on the target temperature.

[Mainly basic operation at low load A]
As shown in FIG. 3, the composite heat source heat pump device 1 executes the priority circuit determination step and the priority circuit drive step at the time of starting the heating operation after the start of operation (t = 0), and the maximum rotation speed (for example, The rotational speed is set lower than 90 rps), and only the compressor HP1 of the priority power source is driven (activated) at 70 rps, for example (t1).

  At this time, when the heating load in the heat radiation terminal 2 (see FIG. 2) is low, the temperature of the circulating fluid L reaches the predetermined target temperature before a predetermined target time (for example, 3 minutes) elapses ( t2) At time t2, the control device 6 determines that the temperature of the circulating fluid L has reached the target temperature by the terminal temperature sensor 34 (see FIG. 2), and performs temperature control by the compressor HP1 of the priority power source. Migrate and manage (t2-). In FIG. 3A, the transition of the rotational speed of the compressor HP2 as the auxiliary power source is not drawn. This is because the temperature of the circulating fluid L is the target temperature only by driving the compressor HP1 as the priority power source. This is because the compressor HP2 of the auxiliary power source was not driven.

[Mainly basic operation B at high load]
In the basic operation B, as shown in FIG. 4, the composite heat source heat pump device 1 executes the priority circuit determination step and the priority circuit drive step at the time of starting the heating operation after the start of operation (t = 0). The rotational speed is set lower than the rotational speed (for example, 90 rps), and only the compressor HP1 as the priority power source is driven (activated) at, for example, 70 rps (t1).

  At this time, when the heating load in the heat radiating terminal 2 (see FIG. 2) is high, the temperature of the circulating fluid L does not reach the predetermined target temperature when a predetermined target time (for example, 3 minutes) has elapsed (t2). Therefore, at time t2, the control device 6 sets the rotation speed lower than the maximum rotation speed (for example, 90 rps) and drives (activates) the compressor HP2 of the auxiliary power source at, for example, 50 rps (t2 to t3).

  Even when the compressor HP2 of the auxiliary power source is driven at 50 rps by the auxiliary circuit driving step (t3 to t4), the temperature of the circulating fluid L becomes the target temperature at the elapse of a predetermined determination time (for example, 30 seconds) (t4). Is not set, the compressor HP1 of the priority power source is driven at, for example, the maximum rotation speed of 90 rps (t4 to t5) by setting higher than the rotation speed (70 rps) in the priority circuit driving step.

  Even if the compressor HP1 of the priority power source is driven at 90 rps by the priority circuit acceleration step (t5 to t6), the temperature of the circulating fluid L becomes the target at the elapse of a predetermined determination time (for example, 30 seconds) (t6). If the temperature has not been reached, it is set higher than the rotational speed (50 rps) in the auxiliary circuit driving step, and the compressor HP2 of the auxiliary power source is driven at a maximum rotational speed of 90 rps, for example (t6 to t7).

  After the priority circuit acceleration step and the auxiliary circuit acceleration step drive both the compressor HP1 of the priority power source and the compressor HP2 of the auxiliary power source at 90 rps (t7), the control device 6 at time t8 It is determined that the temperature of L has reached a predetermined target temperature (see FIG. 4B), and thereafter, the control proceeds to the two-unit drive normal operation control 6A (see FIG. 6) and is managed (from t8).

  In this embodiment, the compressor HP2 of the auxiliary power source is increased to the maximum rotational speed (90 rps, which is the same as the compressor HP1 of the priority power source). However, the present invention is not limited to this. The rotation speed may be lower than that of the machine HP1.

Next, an operation of the composite heat source heat pump device 1 according to the embodiment of the present invention that shifts from the startup operation to the normal operation in the heating operation will be described with reference mainly to FIGS.
As shown in FIG. 5, the composite heat source heat pump device 1 executes the priority circuit determination step after the heating operation is started by the control device 6 (see FIG. 2), and is preset with the outside air temperature detected by the outside air temperature sensor 57. The compressor HP1 as the priority power source and the compressor HP2 as the auxiliary power source are determined by comparing with a predetermined reference temperature (for example, 5 degrees) (S1).

  And the control apparatus 6 performs a priority circuit drive step, and drives compressor HP1 of a priority motive power source at 70 rps (S2).

Thereafter, the control device 6 compares the temperature of the circulating fluid L returned from the heat radiating terminal 2 detected by the terminal temperature sensor 34 with the set target temperature, and whether the temperature of the circulating fluid L has reached the target temperature. It is determined whether or not (S3).
In step S3, when the temperature of the circulating fluid L reaches the target temperature before a predetermined target time (for example, 3 minutes) has elapsed (Yes in S3), the control device 6 executes the basic operation A. Then (time t2 in FIG. 3), it jumps to D in FIG.

  In step S3, when the temperature of the circulating fluid L has not reached the target temperature when a predetermined target time (for example, 3 minutes) has elapsed (No in S3, S4), the control device 6 performs the basic operation B. The rotation speed is set lower than the maximum rotation speed (for example, 90 rps), and the auxiliary power source compressor HP2 is driven (started) at, for example, 50 rps (S5, t2 to t3 in FIG. 4).

  After the compressor HP2 of the auxiliary power source is started at 50 rps (S5), when the temperature of the circulating fluid L reaches the target temperature before a predetermined determination time (for example, 30 seconds) elapses (Yes in S6) ) It jumps to step S101 (refer FIG. 6) of 2 unit drive normal operation control (refer 6A of FIG. 6).

  In step S6, when the temperature of the circulating fluid L has not reached the target temperature after 30 seconds (No in S6, S7), the control device 6 sets the compressor HP1 of the priority power source to the maximum rotational speed (for example, , 90 rps) (S8, t4 to t5 in FIG. 4).

  In the present embodiment, the compressor HP1 as the priority power source is started at 70 rps (S2) and increased to the maximum rotation speed (for example, 90 rps) (S8). However, the present invention is not limited to this and priority is given. After starting the compressor HP1 of the power source (S2), the speed may be increased stepwise by ΔR1 rps up to the maximum rotation speed in step S8.

  After the compressor HP1 of the priority power source is driven at 90 rps (S8), when the temperature of the circulating fluid L reaches the target temperature before a predetermined determination time (for example, 30 seconds) elapses (Yes in S9) ) Shift to two-unit drive normal operation control (see 6A in FIG. 6).

  In step S9, when the temperature of the circulating fluid L has not reached the target temperature after 30 seconds (No in S9, S10), the control device 6 sets the auxiliary power source compressor HP2 to the maximum rotational speed (for example, , 90 rps) (S11, t6 to t7 in FIG. 4).

  In the present embodiment, the compressor HP2 of the auxiliary power source is started at 50 rps (S5) and increased to the maximum rotation speed (for example, 90 rps) (S11). However, the present invention is not limited to this. After starting the compressor HP2 of the power source (S5), the speed may be increased step by step by ΔR2 rps up to the maximum rotation speed in step S11.

  After the compressor HP2 of the auxiliary power source is driven at 90 rps (S11), when the temperature of the circulating fluid L reaches the target temperature (Yes in S12), two-unit drive normal operation control (see 6A in FIG. 6) The process jumps to step S101 (see FIG. 6). When the temperature of the circulating fluid L has not reached the target temperature (No in S12), the auxiliary power source compressor HP2 is directly driven at the maximum rotational speed (for example, 90 rps) (S12).

<Normal operation control>
The normal operation control is a control when the temperature of the circulating fluid L reaches the target temperature by the start-up operation control, and two units that drive both the compressor HP1 as the priority power source and the compressor HP2 as the auxiliary power source. Drive normal operation control (see FIG. 6 and FIG. 7), and single drive normal operation control (see FIG. 8) in which only the compressor HP1 of the priority power source is driven by one unit after shifting from the two drive normal operation control. Composed.

<Two drive normal operation control>
In the two-drive normal operation control according to the embodiment of the present invention, when the temperature of the circulating fluid L exceeds a predetermined target temperature, the rotational speed of the compressor HP2 of the auxiliary power source is set to a predetermined lower limit rotational speed N2 ( The lower limit operation step of the auxiliary power source that executes the lower limit operation that decelerates with reference to FIG. 4A) and the predetermined lower limit rotation speed N1 (see FIG. 4A) as the rotation speed of the priority power source. A lower limit operation step of a priority power source that executes a lower limit operation that decelerates as a limit, the auxiliary power source is driven at a predetermined lower limit rotational speed N2, and the priority power source is a predetermined lower limit rotational speed N1 When the temperature of the circulating fluid L exceeds a predetermined target temperature during driving at, the auxiliary power source is stopped.
Specifically, in the two-unit drive normal operation control (see 6A in FIG. 6), as shown in FIG. 4 (t8-) and FIGS. 6 and 7, the control device 6 (see FIG. 2) The temperature of the circulating fluid L returned from the heat radiation terminal 2 detected by the sensor 34 is compared with the set target temperature to determine whether the temperature of the circulating fluid L exceeds the target temperature (S101 in FIG. 6). ).

(When the target temperature is exceeded)
In this step S101, when the temperature of the circulating fluid L exceeds the target temperature after a predetermined determination time (for example, 30 seconds) has elapsed (Yes in S101), the rotational speed of the compressor HP2 of the auxiliary power source Priority to execute the lower limit operation of the auxiliary power source that decelerates the engine at a predetermined lower limit rotational speed N2 rps and the lower limit operation that decelerates the rotational speed of the compressor HP1 of the priority power source to the predetermined lower limit rotational speed N1 rps First, as shown in FIG. 6, it is determined whether or not the rotational speed of the compressor HP2 of the auxiliary power source has reached a predetermined lower limit rotational speed N2rps (S102, FIG. 4 ( a)).

Here, the predetermined lower limit rotational speed N2rps is set as a guideline for ensuring a predetermined thermal efficiency in the low-speed rotational range of the compressor HP2 of the auxiliary power source.
Specifically, the predetermined lower limit rotational speed N2 rps is a lower limit rotational speed that does not fall below when the compressor HP2 of the auxiliary power source is decelerated step by step by ΔR4 rps (see FIG. 4A). When the rotational speed is lower than N2 rps, the thermal efficiency is excessively lowered, and therefore, the rotational speed is a rotational speed that is a criterion for stopping without decelerating.

<Lower limit operation of auxiliary power source>
In step S102, when the rotational speed of the compressor HP2 as the auxiliary power source is not the lower limit rotational speed N2rps (No in S102), the rotational speed of the compressor HP2 as the auxiliary power source is lowered by one step by ΔR4rps ( S103, see FIG. 4A), the process returns to step S101 to determine whether or not the temperature of the circulating fluid L exceeds the target temperature.
Thus, in step S101, while determining whether or not the temperature of the circulating fluid L exceeds the target temperature, if it exceeds the target temperature (Yes in S101), the compressor HP1 of the priority power source While maintaining the rotation speed, the rotation speed of the compressor HP2 as the auxiliary power source is gradually decreased until the rotation speed reaches the lower limit rotation speed N2rps. (No in S102 to S103).
On the other hand, if the temperature of the circulating fluid L does not exceed the target temperature in step S101 (No in S101), the process jumps to A (control when not exceeding the target temperature) in FIG.

<Lower limit operation of priority power source>
In step S102, when the rotational speed of the compressor HP2 as the auxiliary power source becomes the lower limit rotational speed N2 rps (Yes in S102), the rotational speed of the compressor HP1 as the priority power source becomes the lower limit rotational speed N1 rps (FIG. 4 ( a) see)) (S104), and when the lower limit rotational speed N1 rps is reached (Yes in S104), the compressor HP2 of the auxiliary power source is stopped (S106), one-unit drive normal control 8A (See Fig. 8)

Here, the predetermined lower limit rotational speed N1 rps is set as a guideline for ensuring a predetermined thermal efficiency in the low speed rotation region of the compressor HP1 as the priority power source.
Specifically, the predetermined lower limit rotational speed N1rps is a lower limit rotational speed that does not fall below when the compressor HP1 of the priority power source is decelerated step by step by ΔR3 rps (see FIG. 4A). When the rotational speed is lower than N1 rps, the thermal efficiency is excessively lowered, and therefore, the rotational speed is a reference speed for determining to stop without decelerating.

  In FIG. 4A, the lower limit rotational speed N1 rps of the compressor HP1 as the priority power source is set to be higher than the lower limit rotational speed N2 rps of the compressor HP2 as the auxiliary power source. Instead, the lower limit rotational speed N1 rps of the compressor HP1 as the priority power source may be set to the same rotational speed as the lower limit rotational speed N2 rps of the compressor HP2 as the auxiliary power source.

On the other hand, when the rotational speed of the compressor HP1 as the priority power source is not the lower limit rotational speed N1 rps in step S104 (No in S104), the rotational speed of the compressor HP1 as the priority power source is further lowered by ΔR3 rps by one step. (S105), it returns to step S101 and it is determined whether the temperature of the circulating fluid L exceeds the target temperature.
When the temperature of the circulating fluid L exceeds the target temperature (Yes in S101), if the rotational speed of the compressor HP2 as the auxiliary power source is the lower limit rotational speed N2 rps (Yes in S102), the priority power source is compressed. Until the rotation speed of the machine HP1 reaches the lower limit rotation speed N1 rps, the rotation speed of the compressor HP1 as the priority power source is gradually reduced by ΔR3 rps.
In this way, while determining whether or not the target temperature is exceeded, if the target temperature is exceeded, the rotational speed of the compressor HP1 as the priority power source is lowered stepwise until it reaches the lower limit rotational speed N1rps.

  On the other hand, when the temperature of the circulating fluid L does not exceed the target temperature in step S101 (No in S101), the process jumps to step S117 (operation when the target temperature is not exceeded) in FIG.

(When the target temperature is not exceeded)
In step S101 (see FIG. 6), when the temperature of the circulating fluid L does not exceed the target temperature (No in S101), the compressor HP1 as the priority power source is driven at 70 rps or higher as shown in FIG. If the compressor HP1 of the priority power source is not driven at 70 rps or higher (No in S117), increase the rotational speed of the compressor HP1 of the priority power source by ΔR3 rps (No in S117) (S117). It returns to step S118) and step S101 (refer FIG. 6), and it is determined whether the temperature of the circulating fluid L exceeds target temperature.
That is, in step S117, when the compressor HP1 of the priority power source is not driven at 70 rps or higher (No in S117), the temperature of the circulating fluid L is set so that the compressor HP1 of the priority power source is 70 rps or higher. While determining whether the temperature is exceeded, the rotational speed is increased step by step by ΔR3 rps.

  In step S117, when the compressor HP1 of the priority power source is driven at 70 rps or higher (Yes in S117), the rotational speed of the compressor HP2 of the auxiliary power source is increased by one step by ΔR4 rps (S119), and the auxiliary power It is determined whether or not the rotational speed of the source compressor HP2 has reached 50 rps (S120).

In step S120, when the compressor HP2 of the auxiliary power source is not driven at 50 rps (No in S120), the process returns to step S101 (see FIG. 6) to determine whether or not the temperature of the circulating fluid L exceeds the target temperature. judge.
In step S120, when the compressor HP2 of the auxiliary power source is driven at 50 rps (Yes in S120), it is determined whether the temperature of the circulating fluid L exceeds the target temperature (S121), and the target temperature is set. If not exceeded (No in S121), is the rotational speed of the compressor HP1 of the priority power source increased by one step, for example, ΔR3 rps (S122), and is the rotation speed of the compressor HP1 of the priority power source driven at 90 rps? It is determined whether or not (S123). When the rotational speed of the compressor HP1 as the priority power source is not driven at 90 rps, the process returns to step 121.

In this way, when the temperature of the circulating fluid L does not exceed the target temperature in step 121 (No in S121), the rotational speed of the compressor HP1 as the priority power source becomes 90 rps step by step, for example, ΔR3 rps. Speed up.
On the other hand, when the temperature of the circulating fluid L exceeds the target temperature in Step 121 (Yes in S121), the process returns to Step S102 (see FIG. 6).

  In step S123, when the rotational speed of the compressor HP1 as the priority power source is driven at 90 rps (Yes in S123), it is determined whether or not the temperature of the circulating fluid L exceeds the target temperature (S124).

In step S124, when the temperature of the circulating fluid L exceeds the target temperature (Yes in S124), the process returns to step S102 (see FIG. 6).
In step S124, when the temperature of the circulating fluid L does not exceed the target temperature (No in S124), the rotational speed of the compressor HP2 of the auxiliary power source is increased by one step, for example, ΔR4 rps (S125), and the target temperature is reached. Until the target temperature is not reached even when the rotational speed of the compressor HP2 of the auxiliary power source reaches the maximum rotational speed (for example, 90 rps), the compression of the auxiliary power source is continued. The machine HP2 is driven at the maximum rotational speed.

Note that ΔR3 rps as a deceleration value of the rotational speed of the compressor HP1 as the priority power source is set to an arbitrary value, and is two steps from the maximum rotational speed as shown in FIG. It is not limited only to a value that results in a lower limit rotational speed N1 rps when decelerated. Similarly, an arbitrary value is set for ΔR3 rps as the acceleration value shown in the flowcharts of FIGS. Further, ΔR3 rps as the deceleration value of the rotational speed of the compressor HP1 as the priority power source and ΔR3 rps as the acceleration value may not be the same rotational speed range.
Furthermore, an arbitrary value is also set in ΔR4 rps as a deceleration value of the rotational speed of the compressor HP2 of the auxiliary power source, and three stages from the maximum rotational speed as shown in FIG. The speed is not limited to a value that results in a lower limit rotational speed N2 rps when the speed is reduced. Similarly, an arbitrary value is set for ΔR4 rps as the acceleration value shown in the flowcharts of FIGS. Further, ΔR4 rps as the deceleration value of the rotational speed of the compressor HP2 as the auxiliary power source and ΔR4 rps as the acceleration value may not be the same rotational speed range.

<Single drive normal operation control>
In step S104 of the two-drive normal operation control shown in FIG. 6, the rotational speed of the compressor HP1 as the priority power source becomes the lower limit rotational speed N1 rps (Yes in S104), and the compressor HP2 as the auxiliary power source is stopped. Sometimes (S106), the routine proceeds to the single drive normal control 8A (see FIG. 8).
As shown in FIG. 8, in the single drive normal operation control 8A, it is determined whether or not the temperature of the circulating fluid L exceeds the target temperature (S107), and the temperature of the circulating fluid L exceeds the target temperature. (Yes in S107), the compressor HP1 of the priority power source is stopped (S108).

After the compressor HP1 of the priority power source is stopped (S108), after a predetermined determination time (for example, 30 seconds) has elapsed, it is determined whether the temperature of the circulating fluid L exceeds the target temperature and the target temperature is set. If not exceeded (No in S109), the compressor HP1 of the priority power source is driven (started) at a rotational speed of 70 rps (S110), and after a predetermined determination time (for example, 30 seconds) has elapsed, the target temperature is reached. Is determined (S111).
When the target temperature is exceeded (Yes in S111), the compressor HP1 of the priority power source is further lowered by ΔR3 rps (see FIG. 4) step by step (S112), and the compressor HP1 of the priority power source is The rotation speed is decreased until N1 rps (No in S113).

  On the other hand, when the temperature of the circulating fluid L does not exceed the target temperature in step S107 (No in S107), it is determined whether or not the rotational speed of the compressor HP1 as the priority power source is 70 rps (S114). If the rotational speed of the compressor HP1 as the priority power source is 70 rps (Yes in S114), the compressor HP2 as the auxiliary power source is driven (started) at a rotational speed of 50 rps (S116), and the two-drive normal control 6A The process jumps to step S101 (see FIG. 6).

  In step S114, if the rotational speed of the compressor HP1 of the priority power source is not 70 rps (No in S114), the compressor HP1 of the priority power source is further increased stepwise by, for example, ΔR3 rps (S115) to exceed the target temperature. If not (No in S111), the compressor HP1 as the priority power source is increased until the rotational speed reaches 70 rps (S114 to S115).

  In step S109, when the temperature of the circulating fluid L exceeds the target temperature (Yes in S109), the compressor HP1 of the priority power source is stopped and waited (S108), and when the temperature drops from the target temperature (S109). No), the compressor HP1 of the priority power source is driven (activated) at a rotational speed of 70 rps (S110).

  The operation when the temperature of the circulating fluid L does not exceed the target temperature in Step S111 (No in S111) is the same as the operation when the temperature of the circulating fluid L does not exceed the target temperature in Step S107 (No in S107). Therefore, explanation is omitted.

  As mentioned above, although embodiment of this invention was described, this invention is not limited to above-described embodiment, It can change and implement suitably. For example, in the start-up control according to the above-described embodiment, the specification is set so that the maximum rotation speeds of the first compressor 43 and the second compressor 53 are the same (for example, 90 rps). The maximum rotational speeds of the first compressor 43 and the second compressor 53 may be different specifications depending on the usage conditions such as the area, weather, and compressor specifications. In such a case, the rotational speed of the compressor HP2 as the auxiliary power source may be higher or lower than the compressor HP1 as the priority power source. In short, the rotational speed is appropriately set in consideration of the thermal efficiency of the first compressor 43 and the second compressor 53.

DESCRIPTION OF SYMBOLS 1 Composite heat source heat pump apparatus 2 Radiation terminal 3 Heating heat exchange part 4 Geothermal heat pump apparatus 5 Air heat heat pump apparatus 6 Control apparatus 31 Heating circulation circuit 32 Heating circulation pump 34 Terminal temperature sensor 41 1st heating heat exchanger 42a, 42b Temperature Sensor 43 First compressor 44 First expansion valve 45 Ground heat source heat exchanger 46 Heat medium circulation path 47 Ground heat circulation pump 48 Ground heat exchanger 51 Second heating heat exchanger 52a, 52b Temperature sensor 53 Second Compressor 54 Second expansion valve 55 Air heat source heat exchanger 57 Outside air temperature sensor 61 Geothermal heat pump control device 62 Air heat heat pump control device C1, C2 Refrigerant H1 Heat medium HP1 Priority power source compressor HP2 Auxiliary power source Compressor L Circulating fluid

Claims (1)

A heating circuit that circulates the circulating fluid through the heat dissipation terminal;
A first heating heat exchanger as a condenser disposed in the heating circuit;
A second heating heat exchanger as a condenser disposed in the heating circulation circuit;
A first heat pump circuit that includes a first compressor that compresses a refrigerant that circulates in the circuit using geothermal heat as a heat source, and that heats the circulating fluid through the first heating heat exchanger;
A second heat pump circuit that includes a second compressor that compresses the refrigerant circulating in the circuit using air heat as a heat source, and that heats the circulating liquid via the second heating heat exchanger;
A terminal temperature sensor for measuring the temperature of the circulating fluid;
An outside air temperature sensor for measuring the outside air temperature,
A combined heat source heat pump device having a control device for controlling operation,
The first heating heat exchanger is disposed in series upstream of the second heating heat exchanger in the heating circulation circuit,
The control device has a priority circuit determination step of determining one of the first compressor and the second compressor as a priority power source and the other as an auxiliary power source based on the outside temperature measured by the outside air temperature sensor.
In two-drive normal operation for driving both the priority power source and the auxiliary power source, when the temperature of the circulating fluid exceeds a predetermined target temperature,
A lower limit operation operation step of the auxiliary power source for executing a lower limit operation for decelerating the rotation speed of the auxiliary power source with a predetermined lower limit rotation speed as a limit;
A lower limit operation operation step of the priority power source for executing a lower limit operation for decelerating the rotation speed of the priority power source with a predetermined lower limit rotation speed as a limit, and
When the auxiliary power source is driven at the predetermined lower limit rotational speed and the priority power source is driven at the predetermined lower limit rotational speed, the temperature of the circulating fluid exceeds a predetermined target temperature. In this case, stop the auxiliary power source,
When the control device executes the lower limit operation of the auxiliary power source and the lower limit operation of the priority power source,
First, while maintaining the rotational speed of the priority power source, the rotational speed of the auxiliary power source is reduced to the predetermined lower limit rotational speed,
Thereafter, reducing the rotational speed of the priority power source to the predetermined lower limit rotational speed,
A combined heat source heat pump device.

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