JP6208086B2 - Combined heat source heat pump device - Google Patents

Description

  The present invention relates to a composite heat source heat pump device, and in particular, when a second heat pump circuit using an air heat source operates independently and performs a heating operation, the defrost operation of the air heat source heat exchanger is performed. In operation, the present invention relates to a composite heat source heat pump device that operates a first heat pump circuit that uses a ground heat source to back up heating operation.

  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 ground having a first compressor, a first heating heat exchanger, a first expansion valve, and a ground heat source heat exchanger in order to support the ground heat heat pump and further improve the heating output by the air heat heat pump. A heat heat pump, a second compressor, a second heating heat exchanger, a second expansion valve, and an air heat heat pump having an air heat source heat exchanger, the first heating heat exchanger and the second heating heat as a condenser An exchanger is connected in series to a heating circulation circuit having a heating circulation pump that circulates the circulating fluid to the heat radiating terminal, and a heat source with high heat collection efficiency is selected according to the outside air temperature, and a geothermal heat pump or air Either one of the heat heat pumps is operated and the heating circulation pump is driven, or both the underground heat pump and the air heat heat pump are operated and applied depending on the size of the heating load. The circulating pump is driven, the heat radiation terminal side of the heating medium heat pump apparatus which performs by heating (circulating fluid) heating operation is supplied to the heat radiating terminal is devised. (For example, patent document 1).

JP 2014-35109 A

  By the way, in such a conventional heat pump cycle device, when the air heat heat pump operates alone and performs heating operation, the air heat source constituting the air heat heat pump depending on conditions such as the outside air temperature and the size of the heating load. The heat exchanger may be frosted, and if the air heat source heat exchanger is frosted, the heat exchange efficiency is lowered, so the air heat source heat exchanger needs to be defrosted.

  As the defrosting operation, the second expansion valve constituting the air heat heat pump is fully opened, and the refrigerant flow direction of the air heat heat pump is reversed from the refrigerant flow direction during the heating operation. The discharged high-temperature refrigerant is directly supplied to the air heat source heat exchanger to melt the frost generated in the air heat source heat exchanger, and the refrigerant flowing out of the air heat source heat exchanger is decompressed by the second expansion valve. Instead, the second expansion valve is passed, the second heating heat exchanger is circulated, and returned to the second compressor again. (Defrosting operation)

  If driving of the heating circulation pump is stopped when performing this defrosting operation, the circulating fluid is not supplied to the heat radiating terminal side, so that no heating is performed and frost generated in the air heat source heat exchanger in the second heating heat exchanger Although the heat exchange is initially performed between the refrigerant whose temperature has been lowered to melt the refrigerant and the circulating fluid staying in the second heating heat exchanger, the temperature of the circulating fluid continues to decrease, Less heat is absorbed from the circulating fluid side to the refrigerant side, and heat used for defrosting the air heat source heat exchanger cannot be taken, resulting in prolonged defrosting operation time. Even when the operation is resumed, since the circulating fluid having a low temperature is supplied to the heat radiation terminal at the beginning of the operation, there is a problem that the feeling of heating is greatly impaired.

  On the other hand, even if the heating circulation pump is continuously driven when the defrosting operation is performed, the refrigerant and the circulating liquid, which have undergone heat exchange to melt the frost generated in the air heat source heat exchanger, become the second heating. Heat is exchanged in the heat exchanger, the circulating fluid is cooled, and the circulating fluid having a low temperature that flows out of the second heating heat exchanger is supplied to the heat radiating terminal. In addition, since the circulating fluid that has flowed out of the heat radiating terminal is not heated, the circulating fluid that flows into the second heating heat exchanger again remains at a low temperature. Therefore, in the second heating heat exchanger, there is also little heat absorbed from the circulating fluid side to the refrigerant side, and heat used for defrosting of the air heat source heat exchanger cannot be taken, and the defrosting operation time is prolonged. It was a thing.

The present invention has been made in view of such a background, and it is an object of the present invention to provide a composite heat source heat pump device in which heating of an air-conditioned space is continued even during a defrosting operation and the defrosting operation time is not prolonged. And
Further, the driving of the underground heat circulation pump is controlled so that the transition of the heating operation after the defrosting operation is stably and smoothly shifted.

  In order to solve the above-described problems, the present invention provides a heating circuit having a heating circulation pump for circulating a circulating liquid in a heat radiating terminal, and a first heating as a condenser disposed in the heating circuit. A heat exchanger, a second heating heat exchanger as a condenser disposed in the heating circulation circuit, a ground heat circulation pump for circulating heat medium and collecting heat from the ground, and this ground heat circulation A ground heat source heat exchanger that heats the first refrigerant circulating in the circuit with a heat medium circulated by a pump, a first compressor that compresses the first refrigerant, and the first compressor that is discharged from the first compressor The first heating heat exchanger for circulating the first refrigerant, and a first expansion valve for depressurizing the first refrigerant flowing out of the first heating heat exchanger, and through the first heating heat exchanger A first heat pump circuit for heating the circulating fluid and collecting heat from the outside air An air heat source heat exchanger that heats the second refrigerant that circulates; a second compressor that compresses the second refrigerant; and the second heating heat exchange that circulates the second refrigerant discharged from the second compressor. A second expansion valve that depressurizes the second refrigerant that has flowed out of the second heating heat exchanger, and a switching valve that switches a flow direction of the second refrigerant, and the second heating heat exchanger A second heat pump circuit that heats the circulating fluid via a control device and a control device that controls the operation, wherein the first heating heat exchanger is connected in series to the upstream side of the second heating heat exchanger in the heating circulation circuit. In the combined heat source heat pump apparatus that operates the second heat pump circuit and drives the heating circulation pump to perform the heating operation for heating the circulating fluid, the control device includes the switching valve and the second heat pump circuit. 2 Flow direction of refrigerant Switching to be opposite to the flow direction of the second refrigerant during the heating operation, the second refrigerant discharged from the second compressor is supplied to the air heat source heat exchanger to exchange the air heat source heat. A defrosting operation control means for driving the heating circulation pump during the defrosting operation and performing the defrosting operation for melting the frost generated in the cooler, and the defrosting operation control means during the heating operation is the defrosting operation Is performed, the first heat pump circuit is operated, and after the defrosting operation is completed, the first refrigerant is decompressed after the geothermal circulation pump is driven at the maximum rotational speed for a certain period of time. The rotational speed is decreased stepwise so that the temperature reaches a predetermined temperature.

  According to a second aspect of the present invention, when the control device determines that a predetermined defrosting start condition for starting the defrosting operation is satisfied, the control device starts the operation of the first heat pump circuit, and the first heat pump circuit. After a predetermined time has elapsed since the start of the operation, the defrosting operation control means starts the defrosting operation.

  According to a third aspect of the present invention, the defrosting operation control means drives the heating circulation pump during the defrosting operation at a predetermined defrosting rotation speed, and the predetermined defrosting rotation speed is determined during the heating operation. The rotation speed was set to a lower value.

  According to a fourth aspect of the present invention, the control device drives the first compressor of the first heat pump circuit at a maximum rotational speed during the defrosting operation.

  According to a fifth aspect of the present invention, when the control device determines that a predetermined defrosting termination condition for ending the defrosting operation is satisfied, the control valve is set so that the flow direction of the second refrigerant is the heating operation. Switching to be the flow direction of the second refrigerant at the time, restarting the operation of the second heat pump circuit as the heating operation, and after resuming the operation of the second heat pump circuit, until a certain time elapses, The operation of the first heat pump circuit was continued.

  Moreover, in Claim 6, the said control apparatus restarts the operation | movement of a said 2nd heat pump circuit, and after the said fixed time passes, the target hot water temperature to which the temperature of the said circulating fluid which circulates through the said heating circulation circuit was set. , The rotational speed of the first compressor is gradually decreased to stop the operation of the first heat pump circuit.

  According to the first aspect of the present invention, the frost generated in the air heat source heat exchanger is melted when the second heat pump circuit is operated and the heating circulation pump is driven to perform the heating operation for heating the circulating fluid. In the case where the defrosting operation is performed, when the defrosting operation is performed, the heating operation performed by the operation of the second heat pump circuit before the defrosting operation is performed by operating the first heat pump circuit. 1 Heat pump circuit is activated and backed up, stable heating output is secured, heating operation can be continued during the defrosting operation, and heat used for defrosting of the air heat source heat exchanger is 2 It can be given from the circulating fluid side to the second refrigerant side via the heating heat exchanger, so that the time during which the defrosting operation is performed is not prolonged, and the fixed time after the defrosting operation is completed is , The second heat pump is driven by driving the underground heat circulation pump of the 1 heat pump circuit at the maximum rotation speed and then decreasing the rotation speed stepwise so that the decompressed first refrigerant reaches a predetermined temperature. Until the heating operation of the circuit starts up, the amount of heat supplied from the first heat pump circuit to the heating circulation circuit is supplemented so that the heating operation of the second heat pump circuit can be started up stably and smoothly. .

  According to claim 2, when it is determined that a predetermined defrosting start condition for starting the defrosting operation is established, the operation of the first heat pump circuit is started and the operation of the first heat pump circuit is started. Since the defrosting operation is started after a predetermined time has elapsed, the defrosting operation is started until the time when the first heat pump circuit operating as a backup can output a stable heating output has elapsed. Since it waits, a defrosting operation can be started in a state where a stable heating output is secured, and the heating operation can be continued even during the defrosting operation.

  According to claim 3, the heating circulation pump during the defrosting operation is driven at a predetermined defrosting rotational speed, and the predetermined defrosting rotational speed is set to a rotational speed set lower than that during the heating operation. Therefore, compared with the heating operation, the circulating flow rate of the circulating fluid per unit time is reduced and the temperature efficiency is increased. Therefore, the temperature of the circulating fluid flowing out of the first heating heat exchanger is increased, and the second heating heat is increased. Since the temperature of the circulating fluid flowing into the exchanger becomes higher, more heat is absorbed from the circulating fluid side to the second refrigerant side in the second heating heat exchanger, and is discharged from the second compressor to be exchanged with the air heat source. Because the temperature of the second refrigerant supplied to the cooler also rises, the frost generated in the air heat source heat exchanger is easily melted, the defrosting operation time can be shortened, and the defrosting operation time is not prolonged. It is.

  According to the fourth aspect of the present invention, the amount of heating output of the second heat pump circuit before the defrosting operation is performed by driving the first compressor of the first heat pump circuit at the maximum rotation speed during the defrosting operation. Since the first heat pump circuit is operated so as to cover as much as possible and the temperature of the circulating fluid flowing out from the first heating heat exchanger can be further increased, the temperature of the circulating fluid flowing into the second heating heat exchanger becomes higher. The temperature of the circulating fluid flowing out of the second heating heat exchanger can be kept high, the temperature drop of the circulating fluid supplied to the heat radiating terminal can be suppressed as much as possible, and the heating operation can be continued so as not to impair the feeling of heating as much as possible. Is. Furthermore, since the temperature of the circulating fluid flowing out from the first heating heat exchanger can be increased, the temperature of the circulating fluid flowing into the second heating heat exchanger becomes higher, so the circulating fluid side in the second heating heat exchanger Since the heat absorbed from the refrigerant to the second refrigerant side increases, the temperature of the second refrigerant also rises by that amount, and the temperature of the second refrigerant discharged from the second compressor and supplied to the air heat source heat exchanger also rises. Further, frost generated in the air heat source heat exchanger is also easily melted, the time during which the defrosting operation is performed can be shortened, and the defrosting operation time is not prolonged.

  Further, according to claim 5, when it is determined that a predetermined defrosting termination condition for ending the defrosting operation is satisfied, the switching valve is set so that the flow direction of the second refrigerant is the flow of the second refrigerant during the heating operation. The operation of the second heat pump circuit is resumed as a heating operation, and the operation of the first heat pump circuit is continued until a certain time has elapsed after the operation of the second heat pump circuit is resumed. As a result, the operation of the first heat pump circuit operating as a backup is continued until the time when the second heat pump circuit can output a stable heating output elapses. Thus, the heating output can be secured and the heating operation can be continued.

  According to the sixth aspect of the present invention, after the operation of the second heat pump circuit is resumed and a predetermined time has elapsed, when the temperature of the circulating fluid circulating in the heating circulation circuit reaches the set target hot water temperature, the first By gradually reducing the rotation speed of the compressor and stopping the operation of the first heat pump circuit, the operation of the first heat pump circuit that was operating as a backup after the defrosting operation is gradually limited. As a result, only the second heat pump circuit can be operated to smoothly shift to the heating operation state.

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 the composite heat source heat pump apparatus which concerns on embodiment of this invention. The circuit diagram which shows the defrost operation which concerns on embodiment of this invention. The time chart which shows operation | movement in case defrosting operation is performed at the time of the heating operation which act | operates the 2nd heat pump circuit which concerns on embodiment of this invention.

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 includes a heating circulation circuit 30 as a load-side circulation circuit that circulates a circulation liquid L (for example, hot water or antifreeze liquid) as a heat medium in the heat radiating terminal 36, and a ground heat as a heat source-side circulation circuit. It has a circulation circuit 20, a control device 6 (61, 62, 63) as control means for controlling the operation of the composite heat source heat pump device 1, and a remote controller 60 that sends a signal to the control device 6.

  As shown in FIG. 2, the composite heat source heat pump apparatus 1 according to the present embodiment uses a ground heat source to heat the circulating liquid L on the heat radiating terminal 36 side, and the first heating heat exchanger 41 of the first heat pump circuit 40. And a combined heat source heat pump device in which a second heating heat exchanger 51 of a second heat pump circuit 50 that heats the circulating fluid L on the heat radiation terminal 36 side using an air heat source is connected in series to the heating circulation circuit 30. In addition, the first heating heat exchanger 41 is disposed on the upstream side of the second heating heat exchanger 51 with respect to the flow of the circulating liquid L circulating in the heating circulation circuit 30. The composite heat source heat pump device 1 can function as a heating device and a cooling device, but in the following embodiments, components and operations when mainly used as a heating device will be described.

  The first heat pump circuit 40 circulates the first variable-capacity compressor 43 that compresses the first refrigerant C1 and the high-temperature first refrigerant C1 discharged from the first compressor 43, and the high-temperature first refrigerant C1. And a first heating heat exchanger 41 as a first condenser that performs heat exchange between the circulating fluid L flowing in the heating circulation circuit 30 and a first refrigerant C1 that flows out of the first heating heat exchanger 41 is depressurized. As a first expansion valve 44 that performs heat exchange between the first expansion valve 44 serving as a decompression unit, the decompressed low-temperature first refrigerant C1 from the first expansion valve 44, and the heat medium H1 that flows through the underground heat circulation circuit 20. The underground heat source heat exchanger 45 and a first refrigerant pipe 42 that connects these in an annular shape are configured. The first heat pump circuit 40 circulates the first refrigerant C1 and heats the circulating liquid L flowing through the heating circulation circuit 30 via the first heating heat exchanger 41.

  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. 1st refrigerant | coolant temperature sensor provided in the 1st refrigerant | coolant piping 42 from the 1 expansion valve 44 to the underground heat source heat exchanger 45, ie, the 1st refrigerant | coolant piping 42 of a low voltage | pressure side, and detects the temperature of the 1st refrigerant | coolant C1 of a low voltage | pressure side. It is.

  The second heat pump circuit 50 circulates the variable-capacity second compressor 53 that compresses the second refrigerant C2 and the high-temperature second refrigerant C2 discharged from the second compressor 53, and this high-temperature second refrigerant C2 And the second heating heat exchanger 51 as a second condenser for exchanging heat with the circulating liquid L flowing through the heating circulation circuit 30, and the second refrigerant C2 flowing out from the second heating heat exchanger 51 is depressurized. The heat of the second expansion valve 54 serving as a decompression means and the low-temperature second refrigerant C2 decompressed from the second expansion valve 54 circulates and the air sent by the operation of the low-temperature second refrigerant C2 and the blower fan 56. An air heat source heat exchanger 55 serving as a second evaporator that performs exchange and a second refrigerant pipe 52 that connects these in an annular shape are configured. The second heat pump circuit 50 circulates the second refrigerant C2 and heats the circulating liquid L flowing through the heating circulation circuit 30 via the second heating heat exchanger 51.

The second refrigerant pipe 52 is provided with a four-way valve 58 as a switching valve for switching the flow direction of the second refrigerant C2 in the second heat pump circuit 50, and the four-way valve 58 is discharged from the second compressor 53. The second refrigerant C2 is circulated in the order of the second heating heat exchanger 51, the second expansion valve 54, and the air heat source heat exchanger 55 to form a flow path that returns to the second compressor 53 (state during heating operation) ) And the second refrigerant C2 discharged from the second compressor 53 are circulated in the order of the air heat source heat exchanger 55, the second expansion valve 54, and the second heating heat exchanger 51, and returned to the second compressor 53. It can be switched to a state where a flow path is formed (a state during a defrosting operation).
In the present embodiment, when the air heat source heat exchanger 55 becomes low temperature and frost is formed, the four-way valve 58 so that the second refrigerant C2 discharged from the second compressor 53 flows toward the air heat source heat exchanger 55. Is switched, and the frost generated in the air heat source heat exchanger 55 is melted by the high-temperature second refrigerant C2 from the second compressor 53.

  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. The second refrigerant temperature sensor is provided in the second refrigerant pipe 52 from the expansion valve 54 to the air heat source heat exchanger 55, that is, the second refrigerant pipe 52 on the low pressure side, and detects the temperature of the second refrigerant C2 on the low pressure side. Reference numeral 57 denotes an outside air temperature sensor for detecting the 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 1st heating heat exchanger 41, the underground heat source heat exchanger 45, and the 2nd heating heat exchanger 51 are comprised by the plate type heat exchanger, for example. 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 as a heat medium are alternately formed with each heat transfer plate as a boundary. ing.

  The underground heat circulation circuit 20 includes an underground heat source heat exchanger 45, an underground heat exchanger 23 installed in the ground as a heat source for heating the first refrigerant C1 flowing through the underground heat source heat exchanger 45, It is provided with the underground heat piping 21 which connects these cyclically | annularly. In addition, the underground heat pipe 21 has a variable rotation speed (the number of rotations per unit time) for circulating an antifreeze liquid in which ethylene glycol, propylene glycol or the like is added as a heat medium H1 to the underground heat circulation circuit 20. A pump 22 is provided. In addition, the code | symbol 24 in FIG. 2 is the underground system turn which adjusts the pressure of the underground heat circulation circuit 20 by storing the heat medium H1.

  Here, in the underground heat circulation circuit 20, when performing the heating operation, the underground heat exchanger 23 collects the underground heat from the ground, and the heat medium H <b> 1 with the heat is the underground heat circulation pump 22. Is supplied to the underground heat source heat exchanger 45. In the underground heat source heat exchanger 45, the first refrigerant C1 that flows through the refrigerant flow path of the underground heat source heat exchanger 45 and the heat medium H1 that flows through the fluid flow path of the underground heat source heat exchanger 45 are Heat exchange is performed by flowing in the opposite direction, the underground heat collected by the underground heat exchanger 23 is pumped to the first refrigerant C1 side, the first refrigerant C1 is heated, and the underground heat source heat exchanger 45 functions as an evaporator.

  The heating circuit 30 includes a first heating heat exchanger 41 as a first condenser, a second heating heat exchanger 51 as a second condenser, a floor heating panel and a panel convector for heating the air-conditioned space, etc. The heat radiating terminal 36 as a load terminal and a heating pipe 31 that connects these in a circular shape in order from the upstream side are provided. The heating pipe 31 is provided with a heating circulation pump 32 that circulates the circulating liquid L in the heating circulation circuit 30. Each of the heating pipes 31 branched for each heat radiation terminal 36 is opened and closed to open the heat radiation terminal 36. Thermally operated valves 33 are provided for controlling the supply of the circulating fluid L to each. In addition, although the two heat radiating 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.

  Thus, in the heating circulation circuit 30, the first heating heat exchanger 41 as the first condenser and the second heating heat exchanger 51 as the second condenser are connected in series, and the heating circulation circuit 30 is The circulating liquid L to be circulated is configured to be supplied to the heat radiating terminal 36 through the second heating heat exchanger 51 after flowing through the first heating heat exchanger 41.

  In the heating circulation circuit 30 shown in FIG. 2, reference numeral 34 denotes a return hot water temperature sensor that detects the temperature of the circulating fluid L that is provided in the heating pipe 31 and flows into the first heating heat exchanger 41 from the heat radiating terminal 36. Reference numeral 35 denotes a heating system that stores the circulating fluid L and adjusts the pressure of the heating circulation circuit 30.

  The control device 6 includes a geothermal heat pump control device 61 that controls the operation of the underground heat circulation circuit 20, the first heat pump circuit 40, and the heating circulation circuit 30, and an air heat heat pump that controls the operation of the second heat pump circuit 50. A control device 62 and a defrosting operation control device 63 as defrosting operation control means for controlling the defrosting operation are provided. The control device 6 includes a storage unit that stores various data and programs, and a control unit that performs calculation / control processing. Each temperature sensor such as the outside air temperature sensor 57 and the temperature sensors 42a and 42b, and the remote control 60 The operation of the composite heat source heat pump device 1 can be controlled in response to the signal from.

  During the heating operation, the control device 6 sets the detection value of the return hot water temperature sensor 34 that detects the temperature of the circulating fluid L immediately upstream of the first heating heat exchanger 41 based on the set temperature of the remote controller 60. In the heating operation by the operation of the first heat pump circuit 40, the rotation speed of the first compressor 43 is controlled so as to reach the target hot water temperature, and in the heating operation by the operation of the second heat pump circuit 50, the second compressor. 53, the rotational speed of the first compressor 43 and the second compressor 53 is controlled when both the first heat pump circuit 40 and the second heat pump circuit 50 are operating. That is, the control device 6 is installed in the heating circulation circuit 30 immediately upstream of the first heating heat exchanger 41, and the detection value of one return hot water temperature sensor 34 that detects the temperature of the circulating fluid L that has flowed out from the heat radiation terminal 36. To determine the overall heating load, and control the operation of either the first heat pump circuit 40 or the second heat pump circuit 50, or both the first heat pump circuit 40 and the second heat pump circuit 50 according to this. It is configured as follows.

The defrosting operation control device 63 drives the heating circulation pump 32 at a predetermined defrosting rotation speed and continues the heating operation by the heat radiating terminal 36, so that the high-temperature second refrigerant C2 discharged from the second compressor 53 is continued. Is supplied to the air heat source heat exchanger 55 to perform a defrosting operation for melting frost generated in the air heat source heat exchanger 55.
The predetermined defrosting rotation speed of the heating circulation pump 32 is set lower than the rotation speed during the heating operation. For example, when the rotation speed of the heating circulation pump 32 in the heating operation is 3500 rpm, the defrosting rotation speed of the heating circulation pump 32 during the defrosting operation can be set to 2500 rpm, which is lower than 3500 rpm.

  In the present embodiment, the rotation speed of the heating circulation pump 32 during heating operation is set to 3500 rpm, and the defrosting rotation speed of the heating circulation pump 32 during the defrosting operation is set to 2500 rpm. The rotational speed of the heating circulation pump 32 and the defrosting rotational speed in the heating operation are not limited to the required heating output while taking into consideration the specifications of the heat pump device, the performance of the compressor, the installation environment, the thermal load, etc. It is set as appropriate in consideration of the balance with the defrosting operation time.

  As shown in FIG. 3, the defrosting operation is a mode in which the second refrigerant C2 is circulated in the direction opposite to that during the heating operation (see the air-heat heat pump unit 5 in FIG. 1). The defrosting operation shown in FIG. 3 is such that the second expansion valve 54 is expanded to a predetermined opening than the heating operation before the defrosting operation, here it is fully opened, and the four-way valve 58 is brought into a state during the defrosting operation. The second refrigerant C2 is switched so that the flow direction of the second refrigerant C2 is opposite to the flow direction of the second refrigerant C2 during the heating operation, and the high-temperature second refrigerant C2 discharged from the second compressor 53 is converted into an air heat source heat exchanger. The frost generated in the air heat source heat exchanger 55 is melted by supplying the heat directly to the heat exchanger 55. The low-temperature second refrigerant C <b> 2 that has fallen in temperature due to heat exchange with frost in the air heat source heat exchanger 55 and has flowed out of the air heat source heat exchanger 55 is not decompressed by the second expansion valve 54, and the second expansion valve 54. , Passes through the second heating heat exchanger 51 and returns to the second compressor 53 again.

  The start of the defrosting operation is, for example, whether or not the outside air temperature detected by the outside air temperature sensor 57 has reached a preset defrosting starting temperature, or the outside air temperature and the second refrigerant temperature detected by the outside air temperature sensor 57. The control device 6 determines whether or not the refrigerant temperature detected by the sensor 52b has reached a preset defrost start temperature, that is, the control device 6 determines whether or not a predetermined defrost start condition is satisfied. When it is determined that the defrosting start condition is satisfied, the defrosting operation can be started. The completion of the defrosting operation is whether or not the temperature of the second refrigerant C2 that has passed through the air heat source heat exchanger 55 detected by the second refrigerant temperature sensor 52b has reached a preset defrosting end temperature. Is determined by the control device 6, that is, the control device 6 determines whether or not a predetermined defrosting termination condition is satisfied. If it is determined that the defrosting termination condition is satisfied, the defrosting operation is terminated and the heating operation is restarted. .

  Further, the control device 6 drives the underground heat circulation pump 22 of the underground heat circulation circuit 20 at the maximum number of rotations for a fixed time after the defrosting operation of the second heat pump circuit 50 is completed, here for 5 to 10 minutes. Then, after the rotational speed is decreased stepwise, the second heat pump is controlled by controlling the rotational speed so that the decompressed first refrigerant detected by the temperature sensor 42b reaches a predetermined temperature, here 0.5 ° C. Until the heating operation of the circuit 50 starts up, the amount of heat supplied from the first heat pump circuit 40 to the heating circulation circuit 30 is supplemented so that the heating operation of the second heat pump circuit 50 can be started up stably and smoothly. It is a thing.

Next, the operation of the composite heat source heat pump apparatus 1 shown in FIGS. 1 and 2 will be described.
When the remote control 60 gives an instruction to heat the air-conditioned space by the heat radiating terminal 36, the control device 6 uses the ground heat source and the first heat pump circuit 40 and the air heat source based on the outside air temperature detected by the outside air temperature sensor 57. Of the second heat pump circuits 50 using the above, the one having the better heat collection efficiency is selected and operated as the heat source.

  For example, when the outside air temperature is not so low (for example, 5 ° C. or more) as in spring or autumn, and the heating load is small, the control device 6 operates only the second heat pump circuit 50 using the air heat source. Let In this case, the control device 6 starts driving the second compressor 53, the second expansion valve 54, the blower fan 56, and the heating circulation pump 32, and the heating operation is started. When the heating operation is started, the second heating heat exchanger 51 exchanges heat between the circulating liquid L circulated by the heating circulation pump 32 and the high-temperature and high-pressure second refrigerant C2 discharged from the second compressor 53, The heated circulating liquid L is supplied to the heat radiating terminal 36 to heat the air-conditioned space, and in the air heat source heat exchanger 55, the air sent by driving the blower fan 56 and the low-temperature and low-pressure discharged from the second expansion valve 54. The second refrigerant C2 is heat-exchanged, and the second refrigerant C2 is heated and evaporated by air heat. In this case, the circulating liquid L circulating in the heating circuit 30 also passes through the first heating heat exchanger 41. At this time, since the first heat pump circuit 40 is not operated, the first heating heat is not supplied. The exchanger 41 passes without being heated.

  On the other hand, when the outside air temperature is low as in winter (for example, 5 ° C. or less), the control device 6 operates only the first heat pump circuit 40 that uses the underground heat source. In this case, the control device 6 starts driving the first compressor 43, the first expansion valve 44, the underground heat circulation pump 22, and the heating circulation pump 32, and the heating operation is started. When the heating operation is started, the first heating heat exchanger 41 exchanges heat between the circulating liquid L circulated by the heating circulation pump 32 and the high-temperature and high-pressure first refrigerant C1 discharged from the first compressor 43, The heated circulating liquid L is supplied to the heat radiating terminal 36 to heat the air-conditioned space, and in the underground heat source heat exchanger 45, it is circulated by the underground heat circulation pump 22 and underground through the underground heat exchanger 23. The heat medium H1 that has collected heat and the low-temperature and low-pressure first refrigerant C1 discharged from the first expansion valve 44 exchange heat, and the first refrigerant C1 is heated and evaporated by underground heat. In this case, the circulating fluid L circulating in the heating circulation circuit 30 also passes through the second heating heat exchanger 51. At this time, since the second heat pump circuit 50 is not operated, the second heating heat The exchanger 51 passes through without being heated.

  Further, when the heating operation is started up or when either the first heat pump circuit 40 or the second heat pump circuit 50 is operated to perform the heating operation, the outside air temperature further decreases, and the heating load is increased. Thus, when a desired heating output cannot be obtained by only one operation, the control device 6 performs the heating operation in which both the first heat pump circuit 40 and the second heat pump circuit 50 are operated. In the case of the heating operation in which both the first heat pump circuit 40 and the second heat pump circuit 50 are operated as an example, the control device 6 includes the first compressor 43, the first expansion valve 44, the underground heat circulation pump 22, the first The 2 compressor 53, the 2nd expansion valve 54, the ventilation fan 56, and the heating circulation pump 32 are driven, and heating operation is performed. During the heating operation, in the first heating heat exchanger 41, the circulating fluid L circulated by the heating circulation pump 32 and the high-temperature and high-pressure first refrigerant C1 discharged from the first compressor 43 flow oppositely to generate heat. Exchange is performed and the circulating liquid L is heated, and in the second heating heat exchanger 51, the circulating liquid L circulated by the heating circulation pump 32 and the high-temperature and high-pressure second refrigerant discharged from the second compressor 53. C2 flows oppositely, heat exchange is performed, and the circulating liquid L is heated. As described above, the circulating liquid L circulating in the heating circuit 30 is heated by the first heating heat exchanger 41 and then further heated by the second heating heat exchanger 51 to be supplied to the heat radiating terminal 36. When the circulation liquid 36 is circulated, the heat of the circulating liquid L is radiated to the air-conditioned space, whereby the air-conditioned space is heated.

  Next, as a characteristic operation, a defrosting operation for melting frost generated in the air heat source heat exchanger 55 when only the second heat pump circuit 50 used by the air heat source is operated to perform the heating operation is executed. The operation of the composite heat source heat pump device 1 will be described with reference to the time chart of FIG. Note that the time t0 in FIG. 4 is an arbitrary time after the heating operation performed by operating only the second heat pump circuit 50 is stabilized.

  The heating operation of operating the second heat pump circuit 50 and driving the heating circulation pump 32 to heat the circulating fluid L in the second heating heat exchanger 51 and supplying the heated circulating fluid L to the heat radiating terminal 36. When the control device 6 determines that the defrosting start condition is satisfied from the outside air temperature detected by the outside air temperature sensor 57 during the operation (time t1), the first compressor 43, the first expansion valve 44, the operation of the first heat pump circuit 40 is started by starting the driving of the underground heat circulation pump 22 (time t1). At this time, the heating circulation pump 32 remains driven.

  After the operation of the first heat pump circuit 40 is started, for example, after 5 minutes have passed as a preset first time (t1 time to time t2), the second compressor 53, the second expansion valve 54, The driving of the blower fan 56 is stopped, and the operation of the second heat pump circuit 50 is once stopped (time t2). When the operation of the second heat pump circuit 50 is stopped, the opening of the second expansion valve 54 is fully opened, and waits for a preset second time (time t2 to time t3) to elapse. However, this eliminates the differential pressure between the discharge side (high pressure side) and the suction side (low pressure side) of the second compressor 53 by waiting for a predetermined time with the opening of the second expansion valve 54 fully open, This is performed in order to safely start the functional components such as the second compressor 53 at the next startup. In the present embodiment, the operation of the second heat pump circuit 50 is stopped during the period from time t2 to time t3. During this period, the opening degree of the second expansion valve 54 is maintained while the second compressor 53 is driven. Is fully opened, and the differential pressure between the discharge side (high pressure side) and the suction side (low pressure side) of the second compressor 53 is waited for a preset second time (time t2 to time t3) to elapse. Therefore, it is possible to shift to the next operation while operating the second heat pump circuit 50.

  When the control device 6 determines that a predetermined time (time t1 to time t3) has elapsed since the start of the operation of the first heat pump circuit 40, the defrosting operation control device 63 causes the four-way valve 58 to operate during the defrosting operation. The defrosting operation is started by switching to this state, and the heating circulation pump 32 is driven at a predetermined defrosting rotation speed (here, 2500 rpm) (time t3). At this time, since the heating circulation pump 32 is driven and the first heat pump circuit 40 is also operating, the defrosting operation is performed while the heating operation is continued.

  In the defrosting operation, as described above with reference to FIG. 3, the second expansion valve 54 is fully opened and the four-way valve 58 is switched to the state during the defrosting operation so that the flow direction of the second refrigerant C2 is changed. The high-temperature second refrigerant C2 discharged from the second compressor 53 is directly supplied to the air heat source heat exchanger 55 so as to be opposite to the flow direction of the second refrigerant C2 during the heating operation. The frost generated in the heat exchanger 55 is melted, and the second refrigerant C2 flowing out of the air heat source heat exchanger 55 is allowed to pass through the second expansion valve 54 without being depressurized by the second expansion valve 54. The exchanger 51 is circulated and returned to the second compressor 53 again.

  During this defrosting operation, in the second heating heat exchanger 51, heat exchange is performed between the second refrigerant C2 and the circulating fluid L, and the heat of the circulating fluid L is absorbed into the second refrigerant C2 side, Although heat is used for defrosting of the air heat source heat exchanger 55, the heating circulation pump 32 when performing the defrosting operation is the rotational speed during the heating operation before the defrosting operation is performed. It is driven at a predetermined defrosting rotation speed (here 2500 rpm) lower than (here 3500 rpm). Here, assuming that the temperature of the circulating fluid L flowing into the first heating heat exchanger 41 is constant and a certain amount of heat is given from the refrigerant C1 to the circulating fluid L in the first heating heat exchanger 41, For example, when the rotational speed of the circulation pump 32 is lowered to 2500 rpm rather than 3500 rpm, the circulation flow rate of the circulating liquid L per unit time decreases and the temperature efficiency increases. Therefore, the first heating heat exchanger The temperature of the circulating fluid L flowing out from 41 increases. Therefore, when the heating circulation pump 32 is driven at a predetermined defrosting rotation speed during the defrosting operation, the circulation flow rate of the circulating fluid L per unit time is reduced as compared with the heating operation before the defrosting operation is performed. Since the temperature efficiency is increased, the temperature of the circulating fluid L flowing out from the first heating heat exchanger 41 is increased, that is, the temperature of the circulating fluid L flowing into the second heating heat exchanger 51 is increased. In the 2-heating heat exchanger 51, the heat absorbed from the circulating fluid L side to the second refrigerant C2 side increases, and the temperature of the second refrigerant C2 also rises by that amount, and is discharged from the second compressor 53 to be air heat source heat. Since the temperature of the second refrigerant C2 supplied to the exchanger 55 also rises, frost generated in the air heat source heat exchanger 55 is easily melted. Therefore, the rotational speed of the heating circulation pump 32 during the defrosting operation is set to a predetermined value that is set lower than that during the heating operation in which the second heat pump circuit 50 is operated before the defrosting operation is performed. When driven at the frost rotation speed, the defrosting operation time can be shortened, and the defrosting operation time is not prolonged.

In addition, during the defrosting operation, the first compressor 43 of the first heat pump circuit 40 is driven at the maximum rotational speed (for example, 90 rps), so that the second heat pump before the defrosting operation is performed. Since the first heat pump circuit 40 is operated so as to cover the heating output of the circuit 50 as much as possible, the temperature of the circulating liquid L flowing out from the first heating heat exchanger 41 can be further increased, so that the second heating heat exchanger The temperature of the circulating liquid L flowing into the 51 becomes higher, the temperature of the circulating liquid L flowing out of the second heating heat exchanger 51 can be kept high, and the temperature of the circulating liquid L supplied to the heat radiation terminal 36 can be lowered as much as possible. It is possible to suppress the heating and continue the heating operation so as not to impair the feeling of heating as much as possible. Furthermore, since the temperature of the circulating fluid L flowing out from the first heating heat exchanger 41 can be increased, the temperature of the circulating fluid L flowing into the second heating heat exchanger 51 is increased, so that the second heating heat exchanger In 51, the heat absorbed from the circulating fluid L side to the second refrigerant C2 side increases, and the temperature of the second refrigerant C2 rises by that amount, and is discharged from the second compressor 53 and supplied to the air heat source heat exchanger 55. Since the temperature of the second refrigerant C2 to be increased also increases, the frost generated in the air heat source heat exchanger 55 is easily melted, the time during which the defrosting operation is performed can be shortened, and the defrosting operation time can be prolonged. There is no.
Note that the maximum rotation speed of the first compressor 43 is not strictly applied, and includes an allowable rotation speed and a value that allows for a safety factor from the allowable rotation speed.

  When the defrosting operation is performed, a predetermined defrosting termination condition is established from the temperature of the second refrigerant C2 that has flowed through the air heat source heat exchanger 55 detected by the second refrigerant temperature sensor 52b. When it is determined that the second compressor 53 has been driven, the defrosting operation is terminated, and at the same time, the operation of the second heat pump circuit 50 is temporarily stopped (time t4). At this time, the rotation speed of the heating circulation pump 32 is returned from the predetermined defrost rotation speed (2500 rpm) to the rotation speed (3500 rpm) in the heating operation before the defrost operation is performed (time t4).

  When the operation of the second heat pump circuit 50 is stopped at time t4, the opening of the second expansion valve 54 is fully open, and the preset third time (time t4 to time t5) has elapsed. This waits for the difference between the discharge side (high pressure side) and the suction side (low pressure side) of the second compressor 53 by waiting for the passage of a predetermined time with the opening of the second expansion valve 54 fully opened. This is performed in order to eliminate the pressure and to safely start the functional components such as the second compressor 53 at the next start-up. In the present embodiment, the operation of the second heat pump circuit 50 is temporarily stopped during the time t4 to the time t5. However, during the defrosting operation, the opening degree of the second expansion valve 54 is fully open, Since there is no differential pressure between the discharge side (high pressure side) and the suction side (low pressure side) of the compressor 53, the preset third time (time t4 to time t5) is omitted when the defrosting operation is completed. Then, the four-way valve 58 can be switched to the heating operation state and the next operation can be performed while the second heat pump circuit 50 is operated without stopping the driving of the second compressor 53.

  When the control device 6 determines that the third time has elapsed, the four-way valve 58 is switched to the heating operation state, and the second compressor 53, the second expansion valve 54, and the blower fan 56 are restarted. Then, the operation of the second heat pump circuit 50 is restarted (time t5), and after the operation of the second heat pump circuit 50 is restarted, for example, 5 minutes elapses as a predetermined time (time t5 to time t7). When it is determined that the first compressor 43, the first expansion valve 44, and the underground heat circulation pump 22 are stopped, the operation of the first heat pump circuit 40 is stopped (time t7), and only the second heat pump circuit 50 is detected. It returns to the heating operation by operating (time t7-).

  In the present embodiment, the control device 6 stops the operation of the first heat pump circuit 40 when it is determined that the predetermined time has elapsed. However, when the predetermined time has elapsed, the terminal temperature sensor 34 is stopped. When the temperature of the circulating fluid L detected in step S1 reaches the target hot water temperature, the operation of the first heat pump circuit 40 may be stopped, and when the predetermined time has elapsed, the terminal temperature sensor If the temperature of the circulating fluid L detected at 34 has reached the target hot water temperature, the rotational speed of the first compressor 43 is gradually decreased, and the operation of the first heat pump circuit 40 is finally stopped. If the temperature of the circulating fluid L detected by the terminal temperature sensor 34 does not reach the target hot water temperature when the predetermined time has elapsed, the terminal temperature sensor 3 Both the first heat pump circuit 40 and the second heat pump circuit 50 are operated until the temperature of the circulating fluid L detected in step S1 reaches the target hot water temperature, and the temperature of the circulating fluid L detected by the terminal temperature sensor 34 is the target. When the hot water temperature is reached, the operation of the first heat pump circuit 40 is stopped, or the rotation speed of the first compressor 43 is gradually decreased to finally stop the operation of the first heat pump circuit 40. It may be. Note that, as described above, when the temperature of the circulating fluid L reaches the set target hot water temperature, the control is performed such that the rotation speed of the first compressor 43 is gradually decreased and the operation of the first heat pump circuit 40 is stopped. What is to be performed is that after the defrosting operation is completed, the operation of the first heat pump circuit 40 that has been operated as a backup is gradually limited, and only the second heat pump circuit 50 as the main power source is operated to perform the heating operation. It is possible to smoothly shift to the state.

  A predetermined time after the defrosting operation of the second heat pump circuit 50 is completed. Here, for 5 to 10 minutes (t4 to t6), the underground heat circulation pump 22 of the underground heat circulation circuit 20 is driven at the maximum rotation speed. After the rotational speed is decreased stepwise, the second heat pump circuit 50 is controlled by controlling the rotational speed so that the decompressed first refrigerant detected by the temperature sensor 42b has a predetermined temperature, here 0.5 ° C. The amount of heat supplied from the first heat pump circuit 40 to the heating circuit 30 is supplemented until the heating operation of the second heat pump circuit 40 is started, so that the heating operation of the second heat pump circuit 50 can be started stably and smoothly. It is.

  As described above, the defrosting operation is performed when the defrosting operation for melting the frost generated in the air heat source heat exchanger 55 is performed when the heating operation is performed by operating only the second heat pump circuit 50. Is performed (time t3 to time t4) by operating the second heat pump circuit 50 before the defrosting operation by operating the first heat pump circuit 40 and driving the heating circulation pump 32. The heating operation can be backed up by operating the first heat pump circuit 40, and the heating operation can be continued even during the defrosting operation by securing a stable heating output by the operation of the first heat pump circuit 40. Heat used for defrosting of the heat exchanger 55 can be applied from the circulating fluid L side to the second refrigerant C2 side via the second heating heat exchanger 51, and a defrosting operation is performed. It is that there is no possible to prolong the time.

  In addition, after a predetermined time (time t1 to time t3) has elapsed since the operation of the first heat pump circuit 40 has started, the defrosting operation control device 63 starts the defrosting operation as a backup. Since the start of the defrosting operation is waited until the time when the operating first heat pump circuit 40 can output a stable heating output elapses, the defrosting operation can be started with a stable heating output secured. The heating operation can be continued even during the defrosting operation.

  When the defrosting operation is completed, the operation of the second heat pump circuit 50 that has been operating as the main power source of the heating operation before the defrosting operation is resumed, and after the operation of the second heat pump circuit 50 is resumed, a certain time (time Until the time t5 to the time t7) elapses, the operation of the first heat pump circuit 40 is continued so that the second heat pump circuit 50 as the main power source can output a stable heating output. Until then, the operation of the first heat pump circuit 40 operated as a backup is continued, so that stable heating output can be secured even after the defrosting operation is completed, and the heating operation can be continued. is there.

DESCRIPTION OF SYMBOLS 1 Composite heat source heat pump apparatus 6 Control apparatus 22 Geothermal circulation pump 30 Heating circulation circuit 32 Heating circulation pump 36 Heat radiation terminal 40 1st heat pump circuit 41 1st heating heat exchanger 43 1st compressor 44 1st expansion valve 45 Underground Heat source heat exchanger 50 Second heat pump circuit 51 Second heating heat exchanger 53 Second compressor 54 Second expansion valve 55 Air heat source heat exchanger 58 Four-way valve 61 Ground heat heat pump control device 62 Air heat heat pump control device 63 Frost operation control device C1 First refrigerant C2 Second refrigerant L Circulating fluid

Claims (6)

  A heating circulation circuit having a heating circulation pump that circulates a circulating liquid in a heat radiating terminal, a first heating heat exchanger as a condenser disposed in the heating circulation circuit, and a condenser disposed in the heating circulation circuit As a second heating heat exchanger, a ground heat circulation pump that circulates the heat medium and collects heat from the ground, and a first refrigerant that circulates in the circuit with the heat medium circulated by the ground heat circulation pump A ground heat source heat exchanger for heating the first refrigerant, a first compressor for compressing the first refrigerant, the first heating heat exchanger for circulating the first refrigerant discharged from the first compressor, A first expansion valve for depressurizing the first refrigerant flowing out from the first heating heat exchanger, and a first heat pump circuit for heating the circulating fluid via the first heating heat exchanger; An air source heat exchanger that heats and heats the second refrigerant circulating in the circuit; A second compressor that compresses the second refrigerant; the second heating heat exchanger that causes the second refrigerant discharged from the second compressor to flow; and the second that flows out of the second heating heat exchanger. A second heat pump circuit that has a second expansion valve that depressurizes the refrigerant and a switching valve that switches a flow direction of the second refrigerant, and that heats the circulating fluid via the second heating heat exchanger; The first heating heat exchanger is arranged in series upstream of the second heating heat exchanger in the heating circulation circuit, operates the second heat pump circuit and the heating In the combined heat source heat pump apparatus that performs a heating operation in which a circulating pump is driven to heat the circulating liquid, the control device is configured to switch the switching valve, and the flow direction of the second refrigerant is that of the second refrigerant during the heating operation. Opposite to the flow direction And the defrosting operation for supplying the second refrigerant discharged from the second compressor to the air heat source heat exchanger to melt the frost generated in the air heat source heat exchanger and performing the removal. A defrosting operation control means for driving the heating circulation pump during a frost operation; and when the defrosting operation control means executes the defrosting operation during the heating operation, the first heat pump circuit is operated, Furthermore, after the defrosting operation is completed, after the geothermal circulation pump is driven at the maximum rotation speed, the rotation speed is decreased stepwise so that the decompressed first refrigerant reaches a predetermined temperature. A composite heat source heat pump device characterized by that.   When the control device determines that a predetermined defrosting start condition for starting the defrosting operation is satisfied, it starts the operation of the first heat pump circuit and starts the operation of the first heat pump circuit. The composite heat source heat pump device according to claim 1, wherein the defrosting operation control means starts the defrosting operation after a predetermined time has elapsed.   The defrosting operation control means drives the heating circulation pump at the time of the defrosting operation at a predetermined defrosting rotation speed, and the predetermined defrosting rotation speed is set to be lower than that at the time of the heating operation. The composite heat source heat pump device according to claim 1, wherein the heat source heat pump device is a composite heat source heat pump device.   4. The combined heat source heat pump according to claim 1, wherein the control device drives the first compressor of the first heat pump circuit at a maximum rotational speed during the defrosting operation. 5. apparatus.   When the control device determines that a predetermined defrosting termination condition for ending the defrosting operation is satisfied, the control device causes the switching valve to switch the second refrigerant when the flow direction of the second refrigerant is in the heating operation. Switching to the flow direction, the operation of the second heat pump circuit as the heating operation is restarted, and the operation of the first heat pump circuit is continued until a certain time has elapsed after the operation of the second heat pump circuit is restarted. The composite heat source heat pump device according to any one of claims 1 to 4, wherein   The control device restarts the operation of the second heat pump circuit, and after the predetermined time has elapsed, when the temperature of the circulating fluid circulating in the heating circulation circuit reaches a set target hot water temperature, the first control device 6. The composite heat source heat pump device according to claim 5, wherein the operation of the first heat pump circuit is stopped by gradually decreasing the rotational speed of the compressor.

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