JP2018009736A - Composite heat source heat pump device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a composite heat source heat pump device that suppresses undershooting and overshooting although a target temperature is speedily reached during a startup of a cooling/heating operation.SOLUTION: A control unit 6 of a composite heat source heat pump device 1 performs startup operation control including: a priority circuit determination step of assigning one of a first compressor 43 and a second compressor 53 as a priority power source HP1 and the other as an auxiliary power source HP2 according to outside-air temperature during a start-up of a cooling/heating operation; a priority circuit driving step of setting a rotating speed lower than a maximum rotating speed and driving only the priority power source HP1; and an auxiliary circuit driving step of setting the rotating speed lower than the maximum rotating speed and driving the auxiliary power source HP2 if a circulating liquid temperature does not reach a target temperature a target time later, a rotating speed of the auxiliary power source HP2 in the auxiliary circuit driving step in cooling operation being set to a rotating speed lower than a rotating speed of the auxiliary power source HP2 in the auxiliary circuit driving step in heating operation.SELECTED DRAWING: Figure 6

Description

  The present invention includes a heat pump circuit that uses a predetermined heat source other than outside air as a heat source and a heat pump circuit that uses outside air as a heat source, and supplies air to the heat exchange terminal by supplying the circulating fluid on the load side heated or cooled by heat exchange to the heat exchange terminal. The present invention relates to a composite heat source heat pump device capable of performing the above.

  Conventionally, in this type of composite heat source heat pump device, a heat-exchange terminal includes a load-side heat exchanger of a heat pump circuit that uses a predetermined heat source other than outside air as a heat source, and a load-side heat exchanger of a heat pump circuit that uses outside air as a heat source. Connected in series to the circulation circuit through which the circulating fluid on the side circulates, and by comparing the outside air temperature with the reference temperature, the compressor of one of the heat pump circuits is the priority power source, and the compressor of the other heat pump circuit is the auxiliary power source When the heating operation for heating the circulating fluid supplied to the heat exchange terminal is started, only the priority power source is first driven at a predetermined priority rotational speed, and the temperature of the circulating fluid when a predetermined target time elapses. Does not reach the predetermined target temperature, or when the temperature change rate of the circulating fluid within the predetermined time range does not reach the predetermined threshold value, the auxiliary power source also has the predetermined auxiliary rotational speed. I had to perform raising control to be driven. (For example, refer to Patent Document 1.)

Japanese Patent Laid-Open No. 2016-23827

  By the way, in recent years, not only a heating operation for heating the circulating fluid and supplying it to the heat exchange terminal, but also a heat pump device that can also perform a cooling operation for cooling the circulating fluid and supplying it to the heat exchange terminal has become widespread. Therefore, it has been considered to apply the startup control of the heating operation in the conventional one to the cooling operation.

  Here, when the start-up control of the heating operation is applied to the cooling operation as it is, first, only the priority power source is driven at a predetermined priority rotation speed, and the temperature of the circulating fluid when a predetermined target time elapses is set to a predetermined target. When the temperature has not reached or when the temperature change rate of the circulating fluid within a predetermined time range is less than a predetermined threshold, the auxiliary power source is also driven at a predetermined auxiliary rotational speed. Considering the temperature, the indoor set temperature, and the target set temperature of the circulating fluid, the cooling load is smaller than the heating load, and if the same start-up control is performed during the cooling operation as in the heating operation, the output will be excessive, and the circulating fluid temperature will be the target. After reaching the temperature, it undershoots greatly, and there is a problem that it takes time to stabilize to the target temperature, resulting in an increase in useless power.

  The present invention has been made in view of such a background, and at the time of start-up of cooling operation and heating operation, the temperature of the circulating fluid is quickly reached to the target temperature by simple control, and the load during cooling operation is It is an object of the present invention to provide a composite heat source heat pump device that can effectively suppress undershoot from the target temperature of the side circulating fluid and overshoot from the target temperature of the load side circulating fluid during heating operation.

  In order to solve the above problems, the present invention provides a first heat source, a first four-way valve, a first load side heat exchanger, a first expansion valve, and a predetermined heat source different from outside air. A first heat pump circuit in which heat exchangeable first heat source side heat exchangers are connected by a first refrigerant pipe, a second compressor, a second four-way valve, a second load side heat exchanger, a second expansion valve, and A second heat pump circuit in which a second heat source side heat exchanger capable of exchanging heat with the outside air is connected by a second refrigerant pipe, the first load side heat exchanger, the second load side heat exchanger, and a heat exchange terminal A load-side circulation circuit that circulates circulating fluid cooled or heated by the first load-side heat exchanger or the second load-side heat exchanger to the heat exchange terminal, and external air An outside air temperature detecting means for detecting the temperature, and a control device for controlling the operation of the cooled circulating fluid In a combined heat source heat pump apparatus that performs a cooling operation to be supplied to the heat exchange terminal and a heating operation to supply the heated circulating fluid to the heat exchange terminal, the control device is configured to start the cooling operation and the heating operation. A priority circuit determining step for 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 air temperature detected by the outside air temperature detecting means; A priority circuit driving step for driving only the priority power source by setting the rotational speed lower than the speed, and when the temperature of the circulating fluid does not reach the predetermined target temperature when a predetermined target time elapses, or predetermined When the temperature change rate of the circulating fluid within the time range of less than a predetermined threshold value, the rotational speed is set lower than the maximum rotational speed and the auxiliary power source is turned on. An auxiliary circuit driving step that operates, and a start-up operation control including the auxiliary circuit driving step, and the rotational speed of the auxiliary power source in the auxiliary circuit driving step during the cooling operation is determined as the auxiliary power in the auxiliary circuit driving step during the heating operation. The rotation speed was set to be lower than the rotation speed of the source.

  According to the first aspect of the present invention, the control device executes the start-up operation control including the priority circuit determination step, the priority circuit drive step, and the auxiliary circuit drive step at the start-up of the cooling operation and the heating operation. In addition, the rotation speed of the auxiliary power source in the auxiliary circuit driving step during the cooling operation is set to a lower rotation speed than the rotation speed of the auxiliary power source in the auxiliary circuit driving step during the heating operation. In some cases, the temperature of the circulating fluid quickly reaches the target temperature by simple control, but the cooling load is smaller than the heating load, so the rotation speed of the auxiliary power source in the auxiliary circuit driving step is lowered. Since the cooling output is suitable for the cooling load, it is possible to suppress the temperature of the circulating fluid from significantly undershooting from the target temperature, and during heating operation. Therefore, since the rotation speed of the auxiliary power source in the auxiliary circuit driving step is larger than that in the cooling operation, the heating output corresponding to the heating load larger than the cooling load can be obtained, and the circulating fluid can be controlled by simple control. It is possible to suppress the temperature of the circulating fluid from greatly overshooting from the target temperature while quickly reaching the target temperature.

The external appearance block diagram which shows the main units of the composite heat source heat pump apparatus which concerns on embodiment of this invention. The block diagram which shows the whole structure of a composite heat source heat pump apparatus. Explanatory drawing explaining the operation | movement at the time of heating operation. Explanatory drawing explaining the operation | movement at the time of air_conditionaing | cooling operation. It is a graph which shows the starting control of embodiment in heating operation, (a) shows transition of the rotational speed of two compressors, (b) shows transition of the temperature of load side circulating fluid. It is a graph which shows the starting control of the 1st comparative example and embodiment in air_conditionaing | cooling operation, (a) shows transition of the rotational speed of two compressors, (b) shows transition of the temperature of load side circulating fluid. Show.

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 device 1 includes a ground heat pump unit 4 including a first heat pump circuit 40 (see FIG. 2) and an air heat heat pump unit including a second heat pump circuit 50 (see FIG. 2). 5. The composite heat source heat pump device 1 also operates the load side circulation circuit 30 that circulates the load side circulation liquid L (for example, water or antifreeze liquid) through the heat exchange terminal 36, the heat source side circulation circuit 20, and the operation of the composite heat source heat pump device 1. The control device 6 (61, 62) as a control means for controlling the air conditioner and the remote controller 60 for sending a signal to the control device 6 are used to heat or cool the room where the heat exchange terminal 36 is installed. is there.

  As shown in FIG. 2, the composite heat source heat pump device 1 according to this embodiment heats or cools the load-side circulating liquid L on the heat exchange terminal 36 side using a heat source different from the outside air, here, a ground heat source. The first load side heat exchanger 41 of the first heat pump circuit 40 that performs the second load side of the second heat pump circuit 50 that heats or cools the load side circulating liquid L on the heat exchange terminal 36 side using outside air as a heat source The heat exchanger 51 is arranged in series with the load-side circulation circuit 30, and the first load-side heat exchanger 41 is second with respect to the flow of the load-side circulation liquid L circulating through the load-side circulation circuit 30. It is arranged upstream of the load side heat exchanger 51. This composite heat source heat pump device 1 can function as a heating device and a cooling device.

  The first heat pump circuit 40 includes a first compressor 43 having a variable rotation speed for compressing the first refrigerant C1, a first four-way valve 44, a first load side heat exchanger 41, and a first decompression unit. An expansion valve 45, a first heat source side heat exchanger 46, and a first refrigerant pipe 42 that connects these in an annular shape are configured.

  The first four-way valve 44 provided in the first refrigerant pipe 42 has a function as a switching valve for switching the flow direction of the first refrigerant C1 in the first heat pump circuit 40, and is discharged from the first compressor 43. The first refrigerant C1 is circulated in the order of the first load-side heat exchanger 41, the first expansion valve 45, and the first heat-source-side heat exchanger 46 to form a flow path that returns to the first compressor 43 (heating operation) State) and the first refrigerant C1 discharged from the first compressor 43 is circulated in the order of the first heat source side heat exchanger 46, the first expansion valve 45, and the first load side heat exchanger 41, It can be switched to a state (state during cooling operation) in which a flow path returning to the compressor 43 is formed.

  In the underground heat pump unit 4 shown in FIG. 2, reference numeral 42a is a first refrigerant discharge temperature sensor that detects the temperature of the first refrigerant C1 discharged from the first compressor 43, and reference numeral 42b is a first refrigerant discharge temperature sensor. The first refrigerant pipe 42 from the first expansion valve 45 to the first heat source side heat exchanger 46 detects the temperature of the first refrigerant C1 on the low pressure side during the heating operation or the high pressure side during the cooling operation. It is a refrigerant temperature sensor.

  The second heat pump circuit 50 includes a second compressor 53 having a variable rotational speed that compresses the second refrigerant C2, a second four-way valve 54, a second load-side heat exchanger 51, and a second decompression unit. The second heat source side heat exchanger 57 that performs heat exchange between the expansion valve 55 and the outside air that is sent by the operation of the blower fan 56, and a second refrigerant pipe 52 that connects these in an annular shape are configured.

  The second four-way valve 54 provided in the second refrigerant pipe 52 has a function as a switching valve for switching the flow direction of the second refrigerant C2 in the second heat pump circuit 50 and is discharged from the second compressor 53. A state in which the second refrigerant C2 is circulated in the order of the second load side heat exchanger 51, the second expansion valve 55, and the second heat source side heat exchanger 57 to form a flow path returning to the second compressor 53 (heating operation) And the second refrigerant C2 discharged from the second compressor 53 are circulated in the order of the second heat source side heat exchanger 57, the second expansion valve 55, and the second load side heat exchanger 51, 2 It can be switched to a state in which a flow path returning to the compressor 53 is formed (a state during cooling operation).

  In the air heat heat pump unit 5 shown in FIG. 2, reference numeral 52a is a second refrigerant discharge temperature sensor that detects the temperature of the second refrigerant C2 discharged from the second compressor 53, and reference numeral 52b is a second refrigerant discharge temperature sensor. A second refrigerant that is provided in the second refrigerant pipe 52 from the expansion valve 55 to the second heat source side heat exchanger 57 and detects the temperature of the second refrigerant C2 on the low pressure side during the heating operation or the high pressure side during the cooling operation. Reference numeral 52c denotes an outside air temperature sensor as outside air temperature detecting means for detecting outside air temperature.

  In addition, as a refrigerant | coolant of the 1st heat pump circuit 40 and the 2nd heat pump circuit 50, arbitrary refrigerant | coolants, such as HFC refrigerant | coolants, such as R410A and R32, and a carbon dioxide refrigerant | coolant, can be used.

  The first load side heat exchanger 41, the first heat source side heat exchanger 46, and the second load side heat exchanger 51 are constituted by, for example, plate heat exchangers. In this plate heat exchanger, a plurality of heat transfer plates are stacked, and a refrigerant flow path for circulating a refrigerant and a fluid flow path for circulating a fluid such as a circulating liquid are alternately formed with each heat transfer plate as a boundary. ing.

  The heat source side circulation circuit 20 serves as a heat source for exchanging heat with the heat source side circulation pump 22 having a variable rotation speed, the first heat source side heat exchanger 46, and the first refrigerant C1 flowing through the first heat source side heat exchanger 46. A ground heat exchanger 23 installed (in the ground in this example) is connected in a ring shape by a heat source side pipe 21 as a heat medium pipe. The heat source side circulation pump 22 circulates the heat source side circulating fluid H (water or antifreeze) as a heat medium in the heat source side piping 21, and also stores the heat source side circulating fluid H to adjust the pressure of the heat source side circulation circuit 20. A heat source side cistern 24 to be adjusted is provided. The underground heat exchanger 23 is not limited to be provided in the ground, and may be provided in a water source such as a lake, a reservoir, a well, or the like.

  The load-side circulation circuit 30 includes a first load-side heat exchanger 41, a second load-side heat exchanger 51, and a heat exchange terminal 36 as a load terminal capable of heating and cooling such as a cold / hot water panel and a fan coil. The load side piping 31 is connected in an annular shape in order from the upstream side. The load side piping 31 is provided with a load side circulation pump 32 that circulates the load side circulating fluid L in the load side circulation circuit 30, and each of the load side piping 31 branched for each heat exchange terminal 36 includes: A thermal valve 33 is provided as an opening / closing means for controlling supply of the load-side circulating fluid L to the heat exchange terminal 36 by the opening / closing thereof. The thermal valve 33 has a predetermined temperature at which the heat exchange terminal 36 is installed. Opening and closing is controlled so as to reach a temperature, and although it is provided outside the heat exchange terminal 36 in FIG. 2, it may be built in the heat exchange terminal 36. In addition, although the two heat exchange terminals 36 are provided in FIG. 2, one may be sufficient and three or more may be sufficient, and quantity and a specification are not specifically limited.

  In the load-side circulation circuit 30 shown in FIG. 2, reference numeral 34 detects the temperature of the load-side circulating fluid L that is provided in the load-side pipe 31 and flows into the first load-side heat exchanger 41 from the heat exchange terminal 36. A return temperature sensor 35 is a load-side systern that stores the load-side circulating fluid L and adjusts the pressure of the load-side circulation circuit 30.

  The control device 6 includes a geothermal heat pump control device 61 that controls the operation of the heat source side circulation circuit 20, the load side circulation circuit 30, and the first heat pump circuit 40, and an air heat heat pump that controls the operation of the second heat pump circuit 50. And a control device 62. The control device 6 includes a storage unit that stores various types of data and programs, and a control unit that performs calculation / control processing. Upon receiving a signal from a temperature sensor such as the outside air temperature sensor 52c and the remote controller 60, The operation of the composite heat source heat pump device 1 can be controlled.

  Next, the state at the time of heating operation is demonstrated using FIG. During the heating operation, in the first heat pump circuit 40, as shown in the drawing, the first four-way valve 44 is switched to the state during the heating operation and is compressed by the first compressor 43 in a high-temperature / high-pressure gaseous state. The first refrigerant C1 is discharged from the first compressor 43, and the first refrigerant C1 exchanges heat with the load-side circulating fluid L flowing through the load-side circulation circuit 30 in the first load-side heat exchanger 41 functioning as a condenser. To release the heat to the load-side circulating fluid L and change it to a high-pressure refrigerant in a gas-liquid mixed state while heating. Then, the first refrigerant C1 in this state is decompressed by the first expansion valve 45 to become a low-pressure refrigerant and easily evaporates. In the first heat source side heat exchanger 46 functioning as an evaporator, the heat source side circulation circuit Heat exchange is performed with the heat-source-side circulating fluid H flowing through 20, and heat is absorbed from the heat-source-side circulating fluid H to become a low-temperature / low-pressure gaseous first refrigerant C1 and return to the first compressor 43 again.

  On the other hand, in the second heat pump circuit 50, the high-temperature and high-pressure gaseous second refrigerant C2 compressed by the second compressor 53 is discharged from the second compressor 53, and the second refrigerant C2 functions as a condenser. In the two-load-side heat exchanger 51, heat is exchanged with the load-side circulating fluid L flowing through the load-side circulating circuit 30, and heat is released to the load-side circulating fluid L to heat and heat the gas in a gas-liquid mixed state while heating. To change. Then, the second refrigerant C2 in this state is decompressed by the second expansion valve 55 to become a low-pressure refrigerant and easily evaporates. In the second heat source side heat exchanger 57 functioning as an evaporator, It exchanges heat with the outside air sent by operation, absorbs heat from the outside air, becomes a low-temperature, low-pressure gaseous second refrigerant C2, and returns to the second compressor 53 again.

  Further, in the heat source side circulation circuit 20, the ground heat is collected by the underground heat exchanger 23, and the heat source side circulation liquid H having the heat is driven by the heat source side circulation pump 22 to be the first heat source side heat exchanger. 46. Then, heat exchange is performed between the first refrigerant C1 and the heat source side circulating fluid H in the first heat source side heat exchanger 46, and the underground heat collected in the underground heat exchanger 23 is the first refrigerant C1 side. The first refrigerant C1 is heated and evaporated.

  In the load-side circulation circuit 30, the load-side circulating liquid L that has flowed into the first load-side heat exchanger 41 by driving the load-side circulation pump 32 that is driven at a constant rotational speed is a first load that functions as a condenser. After heat exchanged with the first refrigerant C1 in the side heat exchanger 41, heat was exchanged with the second refrigerant C2 in the second load side heat exchanger 51 functioning as a condenser, and further heated and heated. Thereafter, the load-side circulating fluid L is supplied to the heat exchange terminal 36 to heat the room, and the load-side circulating fluid L whose heat has been radiated and lowered in temperature at the heat exchange terminal 36 is again the first load-side heat exchanger 41. Return to

  In addition, in the above, although the state at the time of the heating operation which operated both the underground heat pump unit 4 and the air heat heat pump unit 5 was demonstrated, it is not restricted to this. That is, a heating operation in which only the geothermal heat pump unit 4 is operated or a heating operation in which only the air heat heat pump unit 5 is operated is possible.

  Next, the state at the time of air_conditionaing | cooling operation is demonstrated using FIG. During the cooling operation, in the first heat pump circuit 40, as shown in the drawing, the first four-way valve 44 is switched to the state during the cooling operation and is compressed by the first compressor 43 in a high-temperature / high-pressure gaseous state. The first refrigerant C1 is discharged from the first compressor 43, and the first refrigerant C1 exchanges heat with the heat source side circulating fluid H flowing through the heat source side circulation circuit 20 in the first heat source side heat exchanger 46 functioning as a condenser. And the heat source side circulating fluid H is discharged to change to a high-pressure refrigerant in a gas-liquid mixed state. Then, the first refrigerant C1 in this state is decompressed by the first expansion valve 45 to become a low-pressure refrigerant and easily evaporates. In the first load-side heat exchanger 41 functioning as an evaporator, the load-side circulation circuit Heat exchange is performed with the load-side circulating fluid L flowing through 30, and the heat is absorbed from the load-side circulating fluid L to become a low-temperature, low-pressure gaseous first refrigerant C1, and returns to the first compressor 43 again.

  On the other hand, in the second heat pump circuit 50, the high-temperature and high-pressure gaseous second refrigerant C2 compressed by the second compressor 53 is discharged from the second compressor 53, and the second refrigerant C2 functions as a condenser. In the two heat source side heat exchanger 57, heat is exchanged with the outside air sent by the operation of the blower fan 56, and the heat is released to the outside air, and the refrigerant is changed into a high-pressure refrigerant in a gas-liquid mixed state. Then, the second refrigerant C2 in this state is decompressed by the second expansion valve 55 to become a low-pressure refrigerant and easily evaporates. In the second load-side heat exchanger 51 functioning as an evaporator, the load-side circulation circuit Heat exchange is performed with the load-side circulating fluid L flowing through 30, and the heat is absorbed from the load-side circulating fluid L to become a low-temperature, low-pressure gaseous second refrigerant C2, and then returns to the second compressor 53 again.

  In the heat source side circulation circuit 20, the heat source side circulation liquid H is supplied to the first heat source side heat exchanger 46 by driving the heat source side circulation pump 22. Then, heat exchange is performed between the first refrigerant C1 and the heat source side circulating fluid H in the first heat source side heat exchanger 46, and the heat of the first refrigerant C1 at a high temperature is radiated to the heat source side circulating fluid H side. After the first refrigerant C1 is cooled and condensed, the heat of the heat source side circulating liquid H is radiated to the ground by the underground heat exchanger 23.

  In the load-side circulation circuit 30, the load-side circulating liquid L that has flowed into the first load-side heat exchanger 41 by driving the load-side circulation pump 32 that is driven at a constant rotational speed is a first load that functions as an evaporator. After the heat exchange with the first refrigerant C1 in the side heat exchanger 41 and cooling, the second load side heat exchanger 51 functioning as an evaporator exchanges heat with the second refrigerant C2 and further cooled and cooled. Thereafter, the load-side circulating fluid L is supplied to the heat exchange terminal 36 to cool the room, and the load-side circulating fluid L that has absorbed heat at the heat exchange terminal 36 and has risen in temperature again becomes the first load-side heat exchanger 41. Return to

  In addition, in the above, although the state at the time of the air_conditionaing | cooling operation which operated both the underground heat pump unit 4 and the air heat heat pump unit 5 was demonstrated, it is not restricted to this. That is, a cooling operation in which only the geothermal heat pump unit 4 is operated or a cooling operation in which only the air heat heat pump unit 5 is operated is possible.

Next, start-up operation control at the start of heating operation will be described.
The control device 6 operates either the underground heat pump unit 4 or the air heat pump unit 5 and drives the load-side circulation pump 32, or both the underground heat pump unit 4 and the air heat heat pump unit 5. In the heating operation in which the load-side circulating pump 32 is driven to heat the load-side circulating fluid L circulating in the load-side circulating circuit 30, the temperature of the load-side circulating fluid L is set to the remote controller 60 or the like. The start-up operation control (see FIG. 5) is executed until the target temperature set by is reached. After reaching the target temperature, one drive normal operation control for driving only the compressor HP1 of the priority power source, or two drive normal for driving both the compressor HP1 of the priority power source and the compressor HP2 of the auxiliary power source Shifting to operation control, in any case, the rotational speed of the compressor is adjusted so that the temperature of the load-side circulating fluid L becomes the target temperature.
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.

  In the start-up operation control at the start of the heating operation, priority circuit determination is performed to determine 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. A step, a priority circuit driving step for driving only the compressor HP1 of the priority power source by setting the rotation speed lower than the maximum rotation speed, and the temperature of the load-side circulating fluid L at a predetermined target time when a predetermined target time elapses. If the temperature has not been reached, at least an auxiliary circuit driving step of driving the compressor HP2 of the auxiliary power source by setting the rotational speed lower than the maximum rotational speed is included.

  In the priority circuit determination step, it is determined which of the ground heat heat pump unit 4 and the air heat heat pump unit 5 has higher thermal efficiency (COP) based on the outside air temperature.

Specifically, in the priority circuit determination step during heating operation, the outside air temperature detected by the outside air temperature sensor 52c is compared with a predetermined reference temperature (for example, 5 ° C.), and the outside air temperature detected by the outside air temperature sensor 52c is predetermined. If the air temperature heat pump unit 5 is higher than the ground temperature heat pump unit 4, the heat extraction efficiency is higher than that of the underground heat pump unit 4. Therefore, the second compressor 53 is determined as the 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 ° C.), the ground heat heat pump unit 4 has higher heat collection efficiency than the air heat heat pump unit 5, and therefore the first compressor 43 is prioritized. The power source is determined and the second compressor 53 is determined as an auxiliary power source.

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), and the auxiliary power The 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.

  In the auxiliary circuit driving step, when the heating operation is started, the temperature of the load-side circulating fluid L is set to 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 compressor HP2 of the auxiliary power source is driven by setting the rotational speed lower than the maximum rotational speed (for example, 90 rps). (For example, 50 rps).

In the present embodiment, it is determined whether or not the temperature of the load-side circulating fluid L has reached the target temperature when a predetermined target time (for example, 3 minutes) has elapsed, but is not limited thereto. When the temperature change of the temperature of the load-side circulating fluid L within a predetermined time range (here, the temperature increase rate) is less than a predetermined threshold, the auxiliary power source compressor HP2 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 load-side circulating fluid L is obtained every predetermined elapsed time (every 30 seconds), and the temperature increase rate , The auxiliary power source compressor HP2 may be driven at 50 rps, for example.

  If the temperature of the load-side circulating fluid L has not reached the target temperature after a predetermined determination time (for example, 3 minutes) has elapsed after executing the auxiliary circuit driving step, the priority circuit driving step The compressor HP1 as the priority power source is driven at a maximum rotational speed of 90 rps, for example, by setting it higher than the rotational speed (70 rps). Here, it is determined whether or not the temperature of the load-side circulating fluid L has reached the target temperature when a predetermined determination time (for example, 3 minutes) has elapsed, but the load within a predetermined time range (for example, every 30 seconds) When the rate of temperature change (here, the rate of temperature increase) of the side circulating fluid L is less than a predetermined threshold value (for example, 0.8 ° C.), the compressor HP1 of the priority power source is driven at a maximum rotational speed of 90 rps. May be.

  Then, after the compressor HP1 of the priority power source is driven at the maximum rotational speed as described above, the temperature of the load-side circulating fluid L has reached the target temperature when a predetermined determination time (for example, 1 minute) has elapsed. If not, the compressor HP2 of the auxiliary power source is driven at a higher speed than the rotational speed (50 rps) in the auxiliary circuit driving step (for example, 90 rps of the maximum rotational speed). Here, it is determined whether or not the temperature of the load-side circulating fluid L has reached the target temperature when a predetermined determination time (for example, 1 minute) has elapsed, but the load within a predetermined time range (for example, every 30 seconds) When the rate of temperature rise of the side circulating fluid L is less than a predetermined threshold (for example, 0.8 ° C.), the auxiliary power source compressor HP2 may be driven at a maximum rotational speed of 90 rps.

  Subsequently, a basic operation in the start-up operation control during the heating operation will be described with reference to FIG. FIG. 5A shows changes in the rotational speeds of the two compressors HP1 and HP2, and FIG. 5B shows changes in the temperature of the load-side circulating fluid L.

  As shown in FIG. 5, the composite heat source heat pump device 1 executes the priority circuit determination step and the priority circuit drive step at the start of the heating operation after the start of operation (t = 0), and the maximum rotation speed (for example, 90 rps). ) And the compressor HP1 as the priority power source alone is driven at, for example, 70 rps (t1).

  At this time, when the heating load of the air-conditioned space where the heat exchange terminal 36 is installed is large, the temperature of the load-side circulating fluid L is predetermined when a predetermined target time (for example, 3 minutes) has elapsed (t2). Since the target temperature is not reached, the controller 6 sets the rotational speed lower than the maximum rotational speed (for example, 90 rps) and drives the auxiliary power source compressor HP2 at, for example, 50 rps at time t2 (t2 to t3). ).

  The auxiliary power source compressor HP2 is driven at 50 rps by the auxiliary circuit driving step (t3 to t4), and the temperature of the load-side circulating fluid L is set to a predetermined target temperature before a predetermined determination time (for example, 3 minutes) elapses. (T4), the control device 6 determines that the temperature of the load-side circulating fluid L detected by the return temperature sensor 34 has reached the target temperature at time t4, and thereafter the compressor of the priority power source Control is performed by shifting to the temperature control of two units of the HP 1 and the compressor HP 2 of the auxiliary power source (from t4). Here, after time t4, when the temperature of the load-side circulating fluid L exceeds the target temperature, the rotational speed of the compressor HP2 of the auxiliary power source is set to be higher than the compressor HP1 of the priority power source. Auxiliary power source with low heat collection efficiency while maintaining the work amount of the compressor HP1 as a priority power source with good heat collection efficiency by controlling the temperature of the load side circulating fluid L to be the target temperature by reducing the temperature. The amount of work of the compressor HP2 is reduced, and an efficient operation is performed.

Next, start-up operation control at the start of cooling operation will be described.
The control device 6 operates either the underground heat pump unit 4 or the air heat pump unit 5 and drives the load-side circulation pump 32, or both the underground heat pump unit 4 and the air heat heat pump unit 5. And the load side circulating pump 32 is driven to cool the load side circulating fluid L circulating in the load side circulating circuit 30. At the start-up, the temperature of the load side circulating fluid L is set to the remote controller 60 or the like. The start-up operation control (see FIG. 6) is executed until the target temperature set by is reached. After reaching the target temperature, one drive normal operation control for driving only the compressor HP1 of the priority power source, or two drive normal for driving both the compressor HP1 of the priority power source and the compressor HP2 of the auxiliary power source Shifting to operation control, in any case, the rotational speed of the compressor is adjusted so that the temperature of the load-side circulating fluid L becomes the target temperature.
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.

  The start-up operation control at the start of the cooling operation is a priority circuit determination in which one of the first compressor 43 and the second compressor 53 is the compressor HP1 as the priority power source and the other is the compressor HP2 as the auxiliary power source. A step, a priority circuit driving step for driving only the compressor HP1 of the priority power source by setting the rotation speed lower than the maximum rotation speed, and the temperature of the load-side circulating fluid L at a predetermined target time when a predetermined target time elapses. If the temperature has not been reached, at least an auxiliary circuit driving step of driving the compressor HP2 of the auxiliary power source by setting the rotational speed lower than the maximum rotational speed is included.

  In the priority circuit determination step, it is determined which of the ground heat heat pump unit 4 and the air heat heat pump unit 5 has higher thermal efficiency (COP) based on the outside air temperature.

Specifically, when the outside air temperature is relatively high (when the temperature is 30 ° C. or higher), the heat radiation efficiency to the outside air becomes low. Therefore, the priority circuit determination step during the cooling operation is detected by the outside air temperature sensor 52c. When the outside air temperature is compared with a predetermined reference temperature (for example, 30 ° C.) and the outside air temperature detected by the outside air temperature sensor 52c is equal to or higher than the predetermined reference temperature, the ground heat heat pump unit 4 is more preferable than the air heat heat pump unit 5. Since the heat dissipation efficiency is high, the first compressor 43 is determined as the priority power source, and the second compressor 53 is determined as the auxiliary power source.
On the other hand, when the outside air temperature is lower than a predetermined reference temperature (for example, 30 ° C.), the air heat heat pump unit 5 has higher heat radiation efficiency than the underground heat pump unit 4, and therefore the second compressor 53 is prioritized. The power source is determined, and the first compressor 43 is determined as an auxiliary power source.

In the priority circuit driving step, at the start of the cooling 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), and the auxiliary power The 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.

  In the auxiliary circuit driving step, the temperature of the load-side circulating fluid L is set to a predetermined target temperature (for example, a temperature set by the user) when a predetermined target time (for example, 3 minutes) has elapsed at the start of the cooling operation. If not, in order to improve the thermal efficiency of the compressor HP2 of the auxiliary power source, the compressor HP2 of the auxiliary power source is driven by setting the rotational speed lower than the maximum rotational speed (for example, 90 rps). (For example, 35 rps).

In the present embodiment, it is determined whether or not the temperature of the load-side circulating fluid L has reached the target temperature when a predetermined target time (for example, 3 minutes) has elapsed, but is not limited thereto. When the temperature change rate (here, the temperature decrease rate) of the load-side circulating fluid L within a predetermined time range is less than a predetermined threshold, the auxiliary power source compressor HP2 may be driven.
Specifically, for example, after a predetermined start-up time has elapsed (after 1 minute has elapsed), the temperature decrease rate of the temperature of the load-side circulating fluid L is determined every predetermined elapsed time (every 30 seconds). , The auxiliary power source compressor HP2 may be driven at 35 rps, for example.

  If the temperature of the load-side circulating fluid L has not reached the target temperature after a predetermined determination time (for example, 3 minutes) has elapsed after executing the auxiliary circuit driving step, the priority circuit driving step The compressor HP1 as the priority power source is driven at a maximum rotational speed of 90 rps, for example, by setting it higher than the rotational speed (70 rps). Here, it is determined whether or not the temperature of the load-side circulating fluid L has reached the target temperature when a predetermined determination time (for example, 3 minutes) has elapsed, but the load within a predetermined time range (for example, every 30 seconds) When the rate of temperature change (here, the rate of temperature decrease) of the side circulating fluid L is less than a predetermined threshold (for example, 0.8 ° C.), the compressor HP1 of the priority power source is driven at a maximum rotational speed of 90 rps. May be.

  Then, after the compressor HP1 of the priority power source is driven at the maximum rotational speed as described above, the temperature of the load-side circulating fluid L has reached the target temperature when a predetermined determination time (for example, 1 minute) has elapsed. If not, the compressor HP2 of the auxiliary power source is driven at a higher speed than the rotational speed (35 rps) in the auxiliary circuit driving step (for example, 90 rps of the maximum rotational speed). Here, it is determined whether or not the temperature of the load-side circulating fluid L has reached the target temperature when a predetermined determination time (for example, 1 minute) has elapsed, but the load within a predetermined time range (for example, every 30 seconds) When the temperature decrease rate of the temperature of the side circulating fluid L is less than a predetermined threshold (for example, 0.8 ° C.), the auxiliary power source compressor HP2 may be driven at a maximum rotational speed of 90 rps.

  Subsequently, the basic operation in the startup operation control during the cooling operation will be described with reference to FIG. 6. First, as a first comparative example of the present embodiment, the startup control during the heating operation is performed during the cooling operation. The transition of the rotational speeds of the compressors HP1 and HP2 and the transition of the temperature of the load-side circulating fluid L when applied to the start-up control as they are will be described with reference to a graph indicated by a broken line. 6A shows changes in the rotational speeds of the two compressors HP1 and HP2, and FIG. 6B shows changes in the temperature of the load-side circulating fluid L.

  As indicated by a broken line in FIG. 6, the composite heat source heat pump device 1 executes the priority circuit determination step and the priority circuit drive step at the start of the cooling operation after the start of operation (t = 0), and the maximum rotation speed ( The rotational speed is set lower than (for example, 90 rps), and only the compressor HP1 of the priority power source is driven at, for example, 70 rps (t1).

  At this time, when the cooling load of the air-conditioned space in which the heat exchange terminal 36 is installed is large, the temperature of the load-side circulating fluid L is predetermined at a predetermined target time (for example, 3 minutes) (t2). Since the target temperature is not reached, the control device 6 sets the rotational speed lower than the maximum rotational speed (for example, 90 rps) and drives the auxiliary power source compressor HP2 at, for example, 50 rps at time t2 (t2 to t4). ).

  The auxiliary power source compressor HP2 is driven at 50 rps by the auxiliary circuit driving step (t4 to t5), and the temperature of the load-side circulating fluid L becomes the predetermined target temperature before a predetermined determination time (for example, 3 minutes) elapses. (T5), the control device 6 determines that the temperature of the load-side circulating fluid L detected by the return temperature sensor 34 has reached the target temperature at time t5, and thereafter the compressor of the priority power source. Control is performed by shifting to the temperature control of the two HP1 and the compressor HP2 of the auxiliary power source (t5).

  Here, in the first comparative example, after time t5 when the temperature of the load-side circulating fluid L reaches the predetermined target temperature, the load-side circulating fluid L greatly undershoots from the target temperature, and the compressor HP2 of the auxiliary power source It takes time to stabilize the target temperature even if the rotational speed of the is reduced. This means that the cooling output by the composite heat source heat pump device 1 is excessive. Considering the outside air temperature, the indoor set temperature, and the target set temperature of the load-side circulating fluid L, the cooling load is larger than the heating load. Therefore, when the same start-up control as in the heating operation is applied during the cooling operation as in the first comparative example, the temperature of the load-side circulating fluid L greatly undershoots after reaching the target temperature. As a result, there is a risk of increasing wasteful power.

  Therefore, in the present embodiment, in order to suppress the undershoot as described above, the same start-up control as in the heating operation is applied during the cooling operation as in the first comparative example, and the assistance during the cooling operation is performed. The rotational speed of the compressor HP2 of the auxiliary power source in the circuit driving step is not set to the same rotational speed (50 rps) as the rotational speed of the compressor HP2 of the auxiliary power source in the auxiliary circuit driving step during heating operation. The rotational speed of the compressor HP2 of the auxiliary power source in the auxiliary circuit driving step during operation is set to a rotational speed (for example, 35 rps) lower than the rotational speed of the compressor HP2 of the auxiliary power source in the auxiliary circuit driving step during heating operation. Then, the compressor HP2 of the auxiliary power source is driven. Thus, unlike the first comparative example, the behavior is as shown in the solid line graph of FIG.

  That is, in the present embodiment, as indicated by a solid line in FIG. 6, the composite heat source heat pump device 1 performs the priority circuit determination step and the priority circuit drive step when starting the cooling operation after the start of operation (t = 0). The rotation speed is set lower than the maximum rotation speed (for example, 90 rps), and only the compressor HP1 as the priority power source is driven at, for example, 70 rps (t1).

  Then, since the temperature of the load-side circulating fluid L does not reach the predetermined target temperature when a predetermined target time (for example, 3 minutes) has elapsed (t2), the control device 6 performs the maximum rotation speed (for example, the time t2). , 90 rps) and the compressor HP2 of the auxiliary power source is driven at 35 rps, for example (t2 to t3).

  In the auxiliary circuit driving step, the compressor HP2 of the auxiliary power source is driven at 35 rps (t3 to t6), and the temperature of the load-side circulating fluid L is set to a predetermined target temperature before a predetermined determination time (for example, 3 minutes) elapses. (T6), the controller 6 determines that the temperature of the load-side circulating fluid L detected by the return temperature sensor 34 has reached the target temperature at time t6, and thereafter the compressor of the priority power source. Control is performed by shifting to the temperature control of two units of the HP 1 and the compressor HP 2 of the auxiliary power source (from t6).

  Here, in the auxiliary circuit driving step, the rotational speed of the compressor HP2 of the auxiliary power source is driven lower than that in the first comparative example, so that the temperature of the load-side circulating fluid L can quickly reach the target temperature. In addition, undershoot from the target temperature after the temperature of the load-side circulating fluid L reaches the target temperature can be suppressed, and wasteful power consumption can be suppressed.

  If the temperature of the load-side circulating fluid L is lower than the target temperature after time t6, the rotational speed of the auxiliary power source compressor HP2 is reduced before the priority power source compressor HP1. Since the load-side circulating fluid L is controlled so as to reach the target temperature, the compressor of the auxiliary power source inferior in heat dissipation efficiency is maintained while maintaining the work amount of the compressor HP1 as a priority power source with good heat dissipation efficiency. The work amount of HP2 is reduced and efficient operation is performed.

  From the above, when the heating operation and the cooling operation are started up, the auxiliary circuit drive includes the priority circuit determination step, the priority circuit drive step, and the auxiliary circuit drive step. By setting the rotation speed of the compressor HP2 of the auxiliary power source at the step to a lower rotation speed during the cooling operation than during the heating operation, the load side can be reduced by simple control during the cooling operation. While the temperature of the circulating fluid L quickly reaches the target temperature, since the cooling load is smaller than the heating load, the rotation speed of the compressor HP2 of the auxiliary power source in the auxiliary circuit driving step is lowered to the cooling load. By setting a suitable cooling output, the temperature of the load-side circulating fluid L can be prevented from greatly undershooting from the target temperature, and during heating operation, Since the rotation speed of the compressor HP2 of the auxiliary power source in the auxiliary circuit driving step is larger than that in the cooling operation, it is possible to obtain a heating output corresponding to a heating load larger than the cooling load, and load by simple control. While causing the temperature of the side circulating fluid L to quickly reach the target temperature, it is possible to suppress the temperature of the load side circulating fluid L from greatly overshooting from the target temperature.

  Further, in the present embodiment shown in FIGS. 5 and 6 described above, the load-side circulating fluid L does not reach the target temperature when only the compressor HP1 as the priority power source is driven, and the compressor HP2 as the auxiliary power source. In the priority circuit drive step, the compressor HP1 of the priority power source is driven and a predetermined target time (for example, 3 minutes) has elapsed. If the temperature of the load-side circulating fluid L reaches a predetermined target temperature before starting, the temperature of the load-side circulating fluid L is maintained at the target temperature by adjusting the rotational speed of the compressor HP1 as the priority power source. The auxiliary power source compressor HP2 is not driven.

  Note that the present invention is not limited to the above-described embodiment, and in the present embodiment, the underground heat exchanger 23 is shown as the heat source of the underground heat pump unit 4, but as the heat source, In addition to medium heat, water heat sources such as lakes, reservoirs, and wells can also be used, and any type can be used as long as they use heat sources other than outside air, and the first heat source side heat exchanger 46 The heat source side circulating fluid H supplied to the heat source side circulating fluid H does not have to be circulated in a closed circuit such as the heat source side circulating circuit 20, and the heat source side circulating fluid H is heat exchanged by the first heat source side heat exchanger 46. It may be an open type that is discharged to the outside.

DESCRIPTION OF SYMBOLS 1 Composite heat source heat pump apparatus 6 Control apparatus 30 Load side circulation circuit 31 Load side piping 36 Heat exchange terminal 40 1st heat pump circuit 41 1st load side heat exchanger 42 1st refrigerant | coolant piping 43 1st compressor 44 1st four-way valve 45 First expansion valve 46 First heat source side heat exchanger 50 Second heat pump circuit 51 Second load side heat exchanger 52 Second refrigerant pipe 52c Outside air temperature sensor 53 Second compressor 54 Second four-way valve 55 Second expansion valve 57 Second heat source side heat exchanger L Load side circulating fluid HP1 Priority power source compressor HP2 Auxiliary power source compressor

Claims (1)

A first refrigerant, a first four-way valve, a first load side heat exchanger, a first expansion valve, and a first heat source side heat exchanger capable of exchanging heat with a predetermined heat source different from outside air A first heat pump circuit connected by piping;
A second heat pump in which a second compressor, a second four-way valve, a second load side heat exchanger, a second expansion valve, and a second heat source side heat exchanger capable of exchanging heat with outside air are connected by a second refrigerant pipe. Circuit,
The first load-side heat exchanger, the second load-side heat exchanger, and the heat exchange terminal are connected by a load-side pipe and cooled by the first load-side heat exchanger or the second load-side heat exchanger. Alternatively, a load-side circulation circuit that circulates the heated circulating fluid to the heat exchange terminal;
Outside temperature detecting means for detecting outside temperature;
And a combined heat source heat pump for performing a cooling operation for supplying the cooled circulating fluid to the heat exchange terminal and a heating operation for supplying the heated circulating fluid to the heat exchange terminal. In the device
The control device, when starting up the cooling operation and the heating operation, one of the first compressor and the second compressor based on the outside air temperature detected by the outside air temperature detecting means, a priority power source, A priority circuit determination step of determining the other as an auxiliary power source;
A priority circuit driving step of setting only the priority power source by setting the rotation speed lower than the maximum rotation speed;
When the temperature of the circulating fluid does not reach the predetermined target temperature when the predetermined target time has elapsed, or the temperature change rate of the circulating fluid within the predetermined time range is less than the predetermined threshold value, the maximum An auxiliary circuit driving step of setting the rotational speed lower than the rotational speed and driving the auxiliary power source;
Start-up operation control including
The rotational speed of the auxiliary power source in the auxiliary circuit driving step during the cooling operation is set to be lower than the rotational speed of the auxiliary power source in the auxiliary circuit driving step during the heating operation. Combined heat source heat pump device.

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