JP2019168169A - Heat pump cold source machine - Google Patents

Abstract

To suppress a refrigerant discharge temperature being controlled wastefully high more than necessary, and to prevent deterioration in efficiency of an entire cold source machine.SOLUTION: When controlling a valve opening of a first expansion valve 44 so that an actual discharge temperature of a refrigerant becomes a target discharge temperature, a target discharge temperature determination unit 61Ba determines the target discharge temperature by using the temperature of a refrigerant flowing out from an underground heat source heat exchanger 45. Thereby, the target discharge temperature setting including the actual temperature state underground can be performed, and efficiency of an entire heat pump cool source machine 1 can be improved.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a heat pump cooling / heating source device that performs cooling operation at a load terminal.

  Conventionally, in this type of heat pump cold heat source device, as described in Patent Document 1, there is one that controls the opening degree of the expansion valve so that the actual discharge temperature of the refrigerant from the compressor becomes the target discharge temperature. .

JP-A-2015-129616 (paragraph 0036, etc.)

  However, in this conventional apparatus, the target discharge temperature is set based on the rotation speed of the compressor and the remote controller set temperature without taking into consideration the actual temperature state in the ground as a heat source. For this reason, during the cooling operation, the target discharge temperature is set in accordance with the highest underground temperature that can be assumed (for example, about 30 ° C.). As a result, in some cases, the refrigerant discharge temperature is unnecessarily controlled to be unnecessarily high, and there is a problem in that the efficiency of the entire cold heat source apparatus is reduced.

  In order to solve the above-described problems, in claim 1 of the present invention, a compressor, a load-side heat exchanger that functions as an evaporator, a decompression unit, and a heat-source-side heat exchanger that functions as a condenser are combined with refrigerant piping. Connect to form a heat pump circuit, connect the load side heat exchanger and load terminal with circulating fluid piping to form a load side circuit, heat the heat source side heat exchanger and heat source In the heat pump cold / hot heat source machine connected by the medium pipe to form the heat source connection path, in the heat pump circuit, the discharge temperature detection means for detecting the actual discharge temperature of the refrigerant discharged from the compressor, and the temperature of the heat source Heat source index detection means for detecting an estimable heat source index; target discharge temperature determination means for determining a target discharge temperature of refrigerant discharged from the compressor according to the heat source index detected by the heat source index detection means; , Pressure reducing control means for controlling the opening degree of the pressure reducing means so that the actual discharge temperature detected by the discharge temperature detecting means becomes the target discharge temperature determined by the target discharge temperature determining means. It is.

  Further, in claim 2, the heat source connection path is a ground heat circulation circuit in which a ground heat exchanger as the heat source and the heat source side heat exchanger are connected by the heat medium pipe, and the heat source index detection The means is a ground return temperature detecting means for detecting a return temperature of the heat medium returning from the heat source side heat exchanger to the underground heat exchanger via the heat medium pipe, or the heat from the underground heat exchanger. The underground temperature detection means for detecting the temperature of the heat medium going to the heat source side heat exchanger via the medium pipe, or the temperature of the refrigerant flowing out from the heat source side heat exchanger via the refrigerant pipe Refrigerant temperature detection means, or condensation temperature detection means for detecting the condensation temperature of the refrigerant condensed in the heat source side heat exchanger.

  Further, in claim 3, the target discharge temperature determining means corresponds to the operation of the operating means capable of operating the load terminal, the heat source index detected by the heat source index detecting means, the rotation speed of the compressor, and the load terminal. The target discharge temperature is determined according to the target circulating fluid temperature of the circulating fluid.

  According to a fourth aspect of the present invention, the target discharge temperature determining means includes the temperature coefficient X corresponding to each of a plurality of temperature zones related to the heat source index detected by the heat source index detection means, and the target discharge temperature To , A rotational speed coefficient Y previously associated with each of a plurality of rotational speed zones related to the rotational speed of the compressor, and a circulating fluid temperature previously associated with each of the plurality of circulating fluid temperature zones related to the target circulating fluid temperature This is calculated by the equation To = X + Y + Z using the coefficient Z.

  Further, according to a fifth aspect of the present invention, there is provided a heat medium pump provided in the heat medium pipe of the heat source connection path, and the decompression control unit is configured to perform the actual operation after a predetermined period has elapsed after the heat medium pump is started. The opening degree of the decompression means is controlled so that the discharge temperature becomes the target discharge temperature.

  According to the first aspect of the present invention, the cooling operation at the load terminal is performed by heat exchange between the heat pump circuit and the heat source connection path and the load side circuit in the load side heat exchanger.

  That is, during operation, in the heat pump circuit, after the refrigerant in the gas state sucked at low temperature and low pressure is compressed by the compressor to become high temperature and high pressure gas, in the heat source side heat exchanger functioning as a condenser The heat medium flowing through the heat medium pipe dissipates heat to become a high-pressure liquid, absorbs heat from the circulating fluid flowing through the load-side circuit in the load-side heat exchanger functioning as an evaporator, and is compressed again as low-temperature and low-pressure gas Return to the machine. At this time, in the heat source connection path, the heat medium flowing through the heat medium pipe absorbs heat from the refrigerant having a high temperature in the heat source side heat exchanger, and the heat medium having the heat is guided through the heat medium pipe. The heat is radiated to a heat source (for example, an underground heat exchanger provided in the ground).

  At this time, in order to perform heat radiation to the heat source (for example, heat radiation to the ground), the temperature of the heat medium needs to be higher than the temperature of the heat source (for example, the ground temperature). The opening degree of the decompression means is controlled so that the actual discharge temperature of the refrigerant from the compressor becomes a target discharge temperature in consideration of the temperature of the heat medium. However, when the actual temperature state of the heat source is not taken into account, the target discharge temperature is set according to the maximum temperature of the heat source that can be assumed (for example, about 30 ° C. in the case of the underground temperature). As a result, in some cases, the refrigerant discharge temperature is controlled to be unnecessarily high, and the efficiency (for example, COP) of the entire cold heat source apparatus is reduced.

  Therefore, according to claim 1, a heat source index detecting means is provided, and a heat source index capable of estimating the temperature of the heat source (for example, the temperature of the heat medium going to the underground heat exchanger, the heat returning from the underground heat exchanger) The return temperature of the medium, the temperature of the refrigerant flowing out of the heat source side heat exchanger, the condensation temperature of the refrigerant in the heat source side heat exchanger, and the like) are detected. Then, the target discharge temperature determination means determines the target discharge temperature according to the heat source index detected by the heat source index detection means, and the pressure reduction control means determines the actual discharge temperature detected by the discharge temperature detection means. The pressure reducing means is controlled so that the target discharge temperature is reached. Thereby, unlike the above-described method, the target discharge temperature can be set in consideration of the actual temperature state of the heat source, so that the efficiency of the entire cold heat source apparatus can be improved.

  Further, according to claim 2, when radiating heat into the ground, as a heat source index, the return temperature of the heat medium to the underground heat exchanger, the temperature of the heat medium coming from the underground heat exchanger, or the heat source side heat By using the refrigerant temperature flowing out of the exchanger or the refrigerant condensing temperature in the heat source side heat exchanger, it is possible to accurately grasp the underground temperature state and set an appropriate target discharge temperature to ensure efficiency. Can be improved.

  According to the third aspect, the target discharge temperature is determined in correspondence with the heat source index, the compressor rotation speed, and the target circulating fluid temperature corresponding to the operation of the operating means. Thereby, it is possible to set the target discharge temperature with higher accuracy in consideration of the setting of the cooling capacity by the user and the operation state of the compressor in the heat pump circuit.

  According to claim 4, the temperature coefficient X associated with the temperature zone, the rotational speed coefficient Y associated with the rotational speed zone of the compressor, and the circulating fluid temperature coefficient Z associated with the circulating fluid temperature zone. By calculating the target discharge temperature To with the formula To = X + Y + Z using, it is possible to execute reliable and quick pressure reduction control with a simple calculation.

  In the underground heat circulation circuit, there is usually a certain length of ground section in the heat medium pipe connecting the heat source side heat exchanger located on the ground side and the underground heat exchanger. Or even if it is arranged in the ground, its depth is shallow and there is a section that is affected by outside air (that is, strictly speaking, it cannot be said that heat is exchanged only with the ground). The heat medium existing in those sections of the heat medium pipe may not correctly reflect the temperature in the ground. Corresponding to this, according to the fifth aspect, after the activation of the heat medium pump of the heat medium pipe, the opening control of the decompression means by the decompression control means is started after a predetermined period has elapsed. As a result, the above-described control is performed after the flow of the heat medium has progressed and the underground temperature is correctly reflected. Can be done.

1 is an external configuration diagram of a main unit of a heat pump cold heat source apparatus according to an embodiment of the present invention. Circuit diagram of the entire heat pump cooling heat source machine The figure explaining the action at the time of cooling operation Functional configuration diagram of geothermal control device Functional configuration diagram of air heat control device The figure showing matching with a refrigerant temperature and a refrigerant temperature zone, and a correspondence with a refrigerant temperature zone and the value of a refrigerant temperature coefficient. The figure showing the association between the compressor rotational speed and the rotational speed zone, and the correspondence between the rotational speed zone and the rotational speed coefficient value The figure showing the correspondence of the circulating fluid temperature zone and the value of the circulating fluid temperature coefficient Z by the temperature range set by the main remote controller The graph which shows the COP improvement effect at the time of air conditioning in contrast with a comparative example Circuit configuration diagram of the entire heat pump cold heat source machine in a modification using the underground temperature as a heat source index Functional configuration diagram of geothermal control device Circuit configuration diagram of the entire heat pump cold heat source machine in a modification using the underground return temperature as a heat source index Functional configuration diagram of geothermal control device Circuit configuration diagram of the entire heat pump cold heat source machine in a modification using the condensation temperature as a heat source index Functional configuration diagram of geothermal control device

  Hereinafter, an embodiment of the present invention will be described with reference to FIGS.

  This embodiment is an embodiment when the present invention is applied to a composite heat source type heat pump cold heat source machine. FIG. 1 shows an external configuration of a main unit of the heat pump cold heat source apparatus 1 of the present embodiment. In FIG. 1, the heat pump cold heat source unit 1 of the present embodiment is a load that circulates a circulating liquid L (for example, water or antifreeze liquid) through the geothermal heat pump unit 4, the air heat heat pump unit 5, and the heat exchange terminal 36. It has a terminal circulation circuit 30 as a side circuit and a ground heat circulation circuit 20 as a heat source connection path.

  FIG. 2 shows a circuit configuration of the entire heat pump cold heat source apparatus 1 of the present embodiment. As shown in FIG. 2, the heat pump cold heat source unit 1 is provided in the geothermal heat pump unit 4 and is capable of heating or cooling the circulating liquid L on the heat exchange terminal 36 side using a geothermal heat source. 1 heat pump circuit 40 (corresponding to a heat pump circuit), a second heat pump circuit 50 provided in the air heat heat pump unit 5 and capable of heating or cooling the circulating liquid L on the heat exchange terminal 36 side using an air heat source; The terminal circulation circuit 30 and the underground heat circulation circuit 20 are included.

  In FIG. 2, the first heat pump circuit 40 includes a variable capacity first compressor 43, a first heat exchanger 41 as a load side heat exchanger, a first expansion valve 44 as a decompression means, and heat source side heat. An underground heat source heat exchanger 45 as an exchanger is connected in an annular shape by a first refrigerant pipe 42 (corresponding to a refrigerant pipe). The first refrigerant pipe 42 is provided with a four-way valve 46 as a switching valve for switching the flow direction of the first refrigerant C1 (see FIG. 3 described later) in the first heat pump circuit 40.

  The first heat exchanger 41 and the underground heat source heat exchanger 45 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 through which the first refrigerant C1 flows and a fluid flow path through which the circulating liquid L flows alternately with each heat transfer plate as a boundary. Is formed.

  Further, the temperature of the first refrigerant C1 discharged from the first compressor 43 (corresponding to the actual discharge temperature) is detected by a first refrigerant discharge temperature sensor 42a as discharge temperature detection means. Similarly, of the refrigerant temperature sensors 42c and 42b provided in the first refrigerant pipe 42 from the first heat exchanger 41 to the underground heat source heat exchanger 45 through the first expansion valve 44, the first expansion is performed. By the first refrigerant temperature sensor 42b provided in the first refrigerant pipe 42 from the valve 44 to the underground heat source heat exchanger 45, the temperature of the first refrigerant C1 on the low pressure side (during heating) or high pressure side (during cooling) can be adjusted. Detected. The detection results of the first refrigerant discharge temperature sensor 42a and the first refrigerant temperature sensor 42b are input to the underground heat control device 61. The temperature of the first refrigerant C1 detected by the first refrigerant temperature sensor 42b corresponds to the heat source index in this embodiment, and the first refrigerant temperature sensor 42b corresponds to the refrigerant temperature detection means and detects the heat source index. It also corresponds to means.

  In the second heat pump circuit 50, a variable capacity second compressor 53, a second heat exchanger 51, a second expansion valve 54, and an air heat source heat exchanger 55 are annularly connected by a second refrigerant pipe 52. Has been. 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 (see FIG. 3 described later) in the second heat pump circuit 50.

  As described above, the second heat exchanger 51 is configured by, for example, a plate heat exchanger, and each of the refrigerant flow path through which the second refrigerant C2 flows and the fluid flow path through which the circulating liquid L flows. It is formed alternately with the heat transfer plate as a boundary.

  The temperature of the second refrigerant C2 discharged from the second compressor 53 is detected by the second refrigerant discharge temperature sensor 52a. Similarly, the second refrigerant temperature sensor 52b provided in the second refrigerant pipe 52 from the second expansion valve 54 to the air heat source heat exchanger 55 causes a second low pressure side (during heating) or high pressure side (during cooling). The temperature of the refrigerant C2 is detected. Furthermore, the outside air temperature is detected by the outside air temperature sensor 57. The detection results of the second refrigerant discharge temperature sensor 52 a and the outside air temperature sensor 57 are input to the air heat control device 62.

  As the first refrigerant C1 of the first heat pump circuit 40 and the second refrigerant C2 of the second heat pump circuit 50, for example, an arbitrary refrigerant such as an HFC refrigerant such as R410A or R32 or a carbon dioxide refrigerant is used. Can be used.

  The underground heat circulation circuit 20 includes an underground heat circulation pump 22 (corresponding to a heat medium pump) as a heat source side circulation pump whose rotation speed (number of rotations per unit time) is variable, and an underground as a heat source side heat exchanger. A heat source heat exchanger 45 and an underground heat exchanger 23 installed as a heat source (in this example, underground) as a heat source for exchanging heat with the first refrigerant C1 flowing through the underground heat source heat exchanger 45 It is connected in an annular shape by a ground heat pipe 21 as a pipe. An antifreeze liquid to which ethylene glycol, propylene glycol, or the like is added is circulated as a heat medium H1 (see FIG. 3 to be described later) by the geothermal circulation pump 22, and the heat medium H1 is supplied to the underground heat pipe 21. An underground system turn 24 that stores and adjusts the pressure of the underground heat circulation circuit 20 is provided. The underground heat exchanger 23 is not limited to being provided in the ground, but is provided in a relatively large capacity water source such as a lake, a reservoir, a river, the sea, a hot spring, a well, and the like. You may make it heat.

  In the terminal circulation circuit 30, the first heat exchanger 41, the second heat exchanger 51, and a heat exchange terminal 36 as a load terminal such as a fan coil, a floor heating panel, a panel convector, etc. Are connected in an annular form in order from the upstream side. The load pipe 31 includes a circulating fluid circulating pump 32 as a load-side circulating pump that circulates the circulating fluid L in the terminal circulating circuit 30, and an air conditioning system that stores the circulating fluid L and adjusts the pressure of the terminal circulating circuit 30. 35 is provided. In this example, the circulating fluid circulation pump 32 is configured to rotate at a constant speed (a constant rotational speed). The heat exchange terminal 36 can be operated by a terminal remote controller 60b. In addition, although the one heat exchange terminal 36 is provided in FIG. 2, two or more may be sufficient and quantity and specification are not specifically limited.

  At this time, in the terminal circulation circuit 30, the first heat exchanger 41 and the second heat exchanger 51 are connected in series, and as described above, the circulating fluid that circulates in the terminal circulation circuit 30. The first heat exchanger 41 is disposed upstream of the second heat exchanger 51 with respect to the flow of L. That is, the heat pump cold heat source unit 1 uses the first heat exchanger 41 of the first heat pump circuit 40 that heats or cools the circulating liquid L on the heat exchange terminal 36 side using an underground heat source, and an air heat source. Thus, the second heat exchanger 51 of the second heat pump circuit 50 that heats or cools the circulating liquid L on the heat exchange terminal 36 side is connected to the terminal circulation circuit 30 in series to form a composite heat source heat pump device. It is what.

  The load pipe 31 is provided with a return hot water temperature sensor 34 as a circulating fluid temperature detecting means for detecting the temperature of the circulating fluid L flowing into the first heat exchanger 41 from the heat exchange terminal 36. The detection result is input to the underground heat control device 61 and the air heat control device 62. In addition, the structure which acquires the detection result of the return hot water temperature sensor 34 via the said underground heat control apparatus 61 may be sufficient as the air heat control apparatus 62 not connected directly to the return hot water temperature sensor 34.

  Here, the heat pump cooling / heating source device 1 can selectively function as a cooling device that performs a cooling operation by switching the four-way valves 46 and 58 or a heating device that performs a heating operation.

  FIG. 3 shows a state during the cooling operation. Note that various signal lines shown in FIG. 2 are omitted in order to prevent the illustration from being complicated. In the cooling operation shown in FIG. 3, the first heat pump circuit 40 switches the four-way valve 46 as shown in the figure, so that the first refrigerant C1 discharged from the first compressor 43 is discharged into the ground. After the heat source heat exchanger 45, the first expansion valve 44, and the first heat exchanger 41 are circulated in this order, a flow path that returns to the first compressor 43 is formed. Thereby, after the 1st refrigerant | coolant C1 of the gas state suck | inhaled at low temperature and low pressure is compressed by the said 1st compressor 43 and becomes high temperature and high pressure gas, the said underground heat source heat exchanger 45 which functions as a condenser is obtained. The heat medium H1 flowing through the underground heat circulation circuit 20 is exchanged with heat to release the heat to the heat medium H1 and change into a high-pressure liquid. Thus, the first refrigerant C1 that has become liquid is decompressed by the first expansion valve 44 and becomes a low-pressure liquid that easily evaporates. In the first heat exchanger 41 that functions as an evaporator, the terminal circulation circuit Heat is exchanged with the circulating fluid L flowing through 30 to evaporate and change into a gas to absorb heat and cool the circulating fluid L, and then return to the first compressor 43 again as a low-temperature and low-pressure gas.

  On the other hand, in the second heat pump circuit 50, when the four-way valve 58 is switched as shown in the figure, the second refrigerant C2 discharged from the second compressor 53 is supplied to the air heat source heat exchanger 55 and the second expansion valve. 54 and the 2nd heat exchanger 51 are distribute | circulated in order, Then, the flow path which returns to the 2nd compressor 53 is formed. Thereby, the second refrigerant C2 in the gas state sucked at a low temperature and a low pressure is compressed by the second compressor 53 to become a high temperature and a high pressure gas, and then the air heat source heat exchanger 55 functioning as a condenser. , The heat exchange with the air sent by the operation of the blower fan 56 is performed to change the liquid into a high-pressure liquid while releasing heat to the outside air. The second refrigerant C2 that has become liquid in this manner is reduced in pressure by the second expansion valve 54, becomes a low-pressure liquid, and easily evaporates. In the second heat exchanger 51 that functions as an evaporator, the terminal circulation circuit Heat is exchanged with the circulating liquid L flowing through 30 to evaporate and change into gas, thereby absorbing the heat and cooling the circulating liquid L, and then returning to the second compressor 53 again as a low-temperature and low-pressure gas.

  In the underground heat circulation circuit 20, the heat medium H <b> 1 is supplied to the underground heat source heat exchanger 45 by the underground heat circulation pump 22. In the underground heat source heat exchanger 45 that functions as a condenser, the first refrigerant C1 that flows through the refrigerant flow path of the underground heat source heat exchanger 45 and the fluid flow path of the underground heat source heat exchanger 45 are provided. After the circulating heat medium H1 faces and exchanges heat, the heat of the first refrigerant C1 at a high temperature is dissipated to the heat medium H1 side and the first refrigerant C1 is cooled, The heat of the medium H1 is radiated to the ground by the underground heat exchanger 23.

  In the terminal circulation circuit 30, the circulating liquid L that has flowed into the first heat exchanger 41 by the circulating liquid circulation pump 32 is heated in the first heat exchanger 41 that functions as an evaporator. In the second heat exchanger 51 functioning as an evaporator, the air heat source heat exchanger in the second heat exchanger 51 after being cooled by performing heat exchange with the first refrigerant C1 that has been heat-exchanged with the medium H1 and cooled as described above. At 55, heat is exchanged with the outside air, and heat is exchanged with the second refrigerant C2 cooled as described above to further cool. The circulating fluid L thus cooled is then supplied to the heat exchange terminal 36 to cool the air-conditioned space.

  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 pump unit 5 was demonstrated and demonstrated in FIG. 3, 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.

  In the above description, the cooling operation has been described as an example. However, when the four-way valve 46 is switched, the first refrigerant C1 discharged from the first compressor 43 is replaced with the first heat exchanger 41 and the first expansion valve 44. After passing through the underground heat source heat exchanger 45 in this order, a flow path returning to the first compressor 43 can be formed to perform the heating operation (detailed description is omitted).

  Next, the underground heat control device 61 and the air heat control device 62 in this embodiment will be described. Although not shown in detail, the underground heat control device 61 and the air heat control device 62 include a storage unit that stores various data and programs, and a control unit that performs calculation / control processing. Functional configurations of the underground heat control device 61 and the air heat control device 62 will be described with reference to FIGS. 4 and 5.

  As shown in FIG. 4, the underground heat control device 61 functionally includes a compressor control unit 61A, an expansion valve control unit 61B, and a pump control unit 61C as compressor control means. The underground heat control device 61 is communicably connected to a terminal control device 36a and a main remote controller 60a (corresponding to an operation means) provided in the heat exchange terminal 36 (see FIG. 2).

  The compressor control unit 61 </ b> A controls the rotation speed of the first compressor 43 according to the temperature of the circulating fluid L detected by the return hot water temperature sensor 34. Particularly in this example, the compressor control unit 61A determines that the temperature of the circulating fluid L detected by the return hot water temperature sensor 34 is, for example, a desired target temperature corresponding to the operation of the main remote controller 60a. The number of rotations of one compressor 43 is controlled.

  The expansion valve control unit 61B includes a target discharge temperature determination unit 61Ba (corresponding to target discharge temperature determination means) that determines a target discharge temperature of the refrigerant discharged from the first compressor 43, and the first refrigerant discharge temperature sensor 42a. The opening control unit 61Bb (pressure reduction control) that controls the valve opening of the first expansion valve 44 so that the actual discharge temperature detected by the target discharge temperature becomes the target discharge temperature determined by the target discharge temperature determination unit 61Ba. Equivalent to the means). The details of the target discharge temperature determination method by the target discharge temperature determination unit 61Ba will be described later.

  The pump control unit 61C controls the rotation speed of the underground heat circulation pump 22 according to the temperature of the first refrigerant C1 detected by the first refrigerant temperature sensor 42b (see also FIG. 2). In particular, in this example, the pump control unit 61C is configured so that the rotation speed of the underground heat circulation pump 22 is such that the temperature of the first refrigerant C1 detected by the first refrigerant temperature sensor 42b becomes a substantially constant value. To control.

  As shown in FIG. 5, the air heat controller 62 functionally includes a compressor controller 62A, an expansion valve controller 62B, and a fan controller 62C. The air heat control device 62 is communicably connected to the underground heat control device 61 (see FIG. 2).

  The compressor control unit 62 </ b> A controls the rotational speed of the second compressor 53 according to the temperature of the circulating fluid L detected by the return hot water temperature sensor 34. In particular, in this example, the compressor control unit 62A determines that the temperature of the circulating fluid L detected by the return hot water temperature sensor 34 is, for example, a desired target temperature corresponding to the operation of the main remote controller 60a. 2 The rotational speed of the compressor 53 is controlled. The compressor control unit 62A of the air heat control device 62 and the compressor control unit 61A of the geothermal heat control device 61 cooperate with each other as necessary, and the target first compressor 43 or The second compressor 53 is controlled.

  The expansion valve control unit 62B controls the valve opening degree of the second expansion valve 54 in accordance with the temperature of the second refrigerant C2 detected by the second refrigerant discharge temperature sensor 52a. In particular, in this example, the expansion valve control unit 62B causes the temperature of the second refrigerant C2 detected by the second refrigerant discharge temperature sensor 52a to be a control target temperature corresponding to, for example, the operation of the main remote controller 60a. The valve opening degree of the second expansion valve 54 is controlled. Note that the expansion valve control unit 62B of the air heat control device 62 and the expansion valve control unit 61B of the underground heat control device 61 cooperate with each other as necessary, and the target first expansion valve 44 or The second expansion valve 54 is controlled.

  The fan control unit 62C controls the rotational speed of the blower fan 56 according to the temperature of the outside air detected by the outside air temperature sensor 57 (see also FIG. 2).

  In the heat pump cooling / heating source unit 1 having the above basic configuration and operation, the main part of the present embodiment is that the target discharge temperature from the first compressor 43 is a temperature that takes into account the actual underground temperature as a heat source. And the opening degree of the first expansion valve 44 is controlled by the opening degree control part 61Bb so that the actual discharge temperature becomes the target discharge temperature. It is in. Hereinafter, the details will be described in order.

  That is, in the present embodiment, during the cooling operation, in order to perform heat radiation to the ground as a heat source, the temperature of the heat medium H1 needs to be higher than the ground temperature that is the heat source temperature. Therefore, normally, in the first heat pump circuit 40, the opening degree of the first expansion valve 44 is set so that the actual discharge temperature of the refrigerant from the first compressor 43 becomes a target discharge temperature in consideration of the temperature of the heat medium H1. Is controlled.

  However, in the case where the actual temperature state in the ground, which is a heat source, is not taken into account, the target discharge temperature is set in accordance with the maximum underground temperature (for example, about 30 ° C.) that can be assumed. As a result, in some cases, the refrigerant discharge temperature is unnecessarily controlled to be unnecessarily high, and the efficiency (for example, COP described later, which is a coefficient of performance, etc.) of the entire cold heat source apparatus is reduced.

  Therefore, in the present embodiment, the temperature of the refrigerant flowing out of the underground heat source heat exchanger 45 (detected by the first refrigerant temperature sensor 42b) is used as a heat source index capable of estimating the underground temperature as a heat source. The target discharge temperature is determined by the target discharge temperature determination unit 61Ba in accordance with the temperature of the refrigerant. Then, the expansion valve control unit 61B controls the first expansion valve so that the detected actual discharge temperature becomes the determined target discharge temperature. Hereinafter, details of the target discharge temperature determination method by the target discharge temperature determination unit 61Ba will be described with reference to FIGS.

The target discharge temperature determination unit 61Ba calculates the target discharge temperature To by the following formula 1.
To = X + Y + Z Equation 1
(However, X: refrigerant temperature coefficient, Y: rotational speed coefficient, Z: circulating fluid temperature coefficient)

  The refrigerant temperature coefficient X is associated in advance with each of a plurality of refrigerant temperature zones related to the temperature of the refrigerant detected by the first refrigerant temperature sensor 42b during the cooling operation. FIG. 6A shows an example of correspondence between the refrigerant temperature and the refrigerant temperature zone.

  As shown in the table of FIG. 6A, as the refrigerant temperature zones corresponding to the refrigerant temperatures detected by the first refrigerant temperature sensor 42b, five refrigerant temperatures are arranged in order from the highest to the lowest. A refrigerant temperature zone, that is, a refrigerant temperature zone I, a refrigerant temperature zone II, a refrigerant temperature zone III, a refrigerant temperature zone IV, and a refrigerant temperature zone V are defined.

  At that time, hysteresis is provided at the boundary between the refrigerant temperature zones I to V, and the boundary between the zones when the refrigerant temperature zone is switched in the direction in which the refrigerant temperature decreases and the refrigerant temperature increases. The boundary between the zones when the refrigerant temperature zone switches in the direction is different. That is, the boundary at the time of switching from the refrigerant temperature zone V where the refrigerant temperature value is the lowest to the refrigerant temperature zone IV adjacent to the side where the refrigerant temperature value is higher is refrigerant temperature = 15 [° C.] (in other words, the refrigerant temperature When the temperature gradually rises from a low state and reaches 15 [° C.], the refrigerant temperature zone V is switched to the refrigerant temperature zone IV). Similarly, the boundary when the refrigerant temperature zone IV is switched to the refrigerant temperature zone III is the refrigerant temperature = 20 [° C.], and the boundary when the refrigerant temperature zone III is switched to the refrigerant temperature zone II is the refrigerant temperature = 26 [° C.]. The boundary when the refrigerant temperature zone II switches to the refrigerant temperature zone I is refrigerant temperature = 30 [° C.].

  On the contrary, the boundary when the refrigerant temperature zone I at which the refrigerant temperature is highest switches to the refrigerant temperature zone II adjacent to the side where the refrigerant temperature value is low is refrigerant temperature = 28 [° C.] (in other words, refrigerant When the temperature gradually decreases from a high temperature and reaches 28 ° C., the refrigerant temperature zone I is switched to the refrigerant temperature zone II). Similarly, the boundary when the refrigerant temperature zone II is switched to the refrigerant temperature zone III is the refrigerant temperature = 24 [° C.], and the boundary when the refrigerant temperature zone III is switched to the refrigerant temperature zone IV is the refrigerant temperature = 18 [° C.]. The boundary when the refrigerant temperature zone IV switches to the refrigerant temperature zone V is refrigerant temperature = 13 [° C.]. The refrigerant temperature zones I to V correspond to a plurality of temperature zones related to the heat source index, and the refrigerant temperature coefficient X corresponds to a temperature coefficient associated with each of the plurality of temperature zones in advance.

  FIG. 6B shows an example of correspondence between each of the refrigerant temperature zones I to V and the value of the refrigerant temperature coefficient X. As shown in the table of FIG. 6B, the value of the refrigerant temperature coefficient X is 40 for the refrigerant temperature zone I, 36 for the refrigerant temperature zone II, 32 for the refrigerant temperature zone III, 28 is associated with the temperature zone IV and 26 is associated with the refrigerant temperature zone V, respectively. That is, the refrigerant temperature coefficient X increases as the refrigerant temperature detected by the first refrigerant temperature sensor 42b increases.

  The rotational speed coefficient Y is associated in advance with each of a plurality of rotational speed zones related to the rotational speed of the first compressor 43 during the cooling operation. FIG. 7A shows an example of correspondence between the rotation speed of the first compressor 43 and the rotation speed zone.

  As shown in the table of FIG. 7A, the rotation speed of the first compressor 43 by the compressor control section 61A (that is, the control value of the rotation speed in detail. Determination of the target discharge temperature from the compressor control section 61A). Output to the unit 61Ba), the rotation speed zones corresponding to the three rotation speed zones in order from the higher rotation speed to the lower rotation speed zone, that is, the rotation speed zone C, the rotation speed zone B, and the rotation speed zone. A is defined.

  At that time, hysteresis is provided at the boundary between the rotation speed zones A to C, and the rotation speed is increased when the rotation speed zone is switched in the direction in which the rotation speed decreases. The boundary between the zones when the rotation speed zone is switched in the direction is different. That is, the boundary at the time of switching from the rotation speed zone A at which the rotation speed value is lowest to the rotation speed zone B adjacent to the rotation speed value is higher is rotation speed = 40.0 [rps] (in other words, When the rotational speed of the first compressor 43 gradually increases from a low state and reaches 40.0 [rps], the rotational speed zone A is switched to the rotational speed zone B). Similarly, the boundary at the time of switching from the rotation speed zone B to the rotation speed zone C is rotation speed = 60.0 [rps].

  On the contrary, the boundary at the time of switching from the rotation speed zone C at which the rotation speed is the highest to the rotation speed zone B adjacent to the side where the rotation speed value is low is rotation speed = 58.0 [rps] (in other words, When the rotational speed gradually decreases from a high state and reaches 58.0 [rps], the rotational speed zone C is switched to the rotational speed zone B). Similarly, the boundary at the time of switching from the rotational speed zone B to the rotational speed zone A is the rotational speed = 38.0 [rps].

  FIG. 7B shows an example of correspondence between each of the rotation speed zones A to C and the value of the rotation speed coefficient Y. As shown in the table of FIG. 7B, the value of the rotational speed coefficient Y is 0 for the rotational speed zone A, 0 for the rotational speed zone B, and 2 for the rotational speed zone C. It is associated. That is, the higher the rotational speed of the first compressor 43, the larger the rotational speed coefficient Y.

  Further, the circulating fluid temperature coefficient Z is associated in advance with each of a plurality of circulating fluid temperature zones related to the circulating fluid target circulating fluid temperature corresponding to the operation of the main remote controller 60a. FIG. 8 shows an example of correspondence between each of the plurality of circulating fluid temperature zones and the value of the circulating fluid temperature coefficient Z.

  As shown in the table of FIG. 8, as the circulating fluid temperature zone related to the target circulating fluid temperature corresponding to the operation of the main remote controller 60a, the remote controller set temperature is less than 10 degrees. ), Remote control set temperature of 10 degrees or more and less than 20 degrees (however, for the sake of simplification, it is shown as “10-19” in the figure), remote control set temperature of 20 degrees or more (however, simplification of illustration) Therefore, three circulating fluid temperature zones are defined as shown in FIG.

  Then, as shown in the table of FIG. 8, the value of the circulating fluid temperature coefficient Z is 2 for the zone where the remote controller set temperature is less than 10 degrees, 0 for the zone where the remote controller set temperature is 10 degrees or more and less than 20 degrees, Zeros are associated with the zones where the remote control set temperature is 21 degrees or higher. That is, the circulating fluid temperature coefficient Z increases as the remote control set temperature decreases.

  As described above, according to the heat pump cold heat source apparatus 1 of the present embodiment, when the opening degree of the first expansion valve 44 is controlled so that the actual discharge temperature of the refrigerant becomes the target discharge temperature, The target discharge temperature is determined using the temperature of the refrigerant flowing out of the underground heat source heat exchanger 45 (detected by the first refrigerant temperature sensor 42b) as a heat source index with which the underground temperature can be estimated. It is determined by the part 61Ba. Thereby, unlike the above-described normal method, the target discharge temperature can be set in consideration of the actual temperature state in the ground as a heat source, so that the efficiency of the heat pump cold heat source apparatus 1 as a whole can be improved. Can do.

This effect will be described with reference to FIG. 9 using a comparative example. FIG. 9 shows the case where the vertical axis represents the actual discharge temperature of the first refrigerant C1 discharged from the first compressor 43 and the horizontal axis represents the COP (coefficient of performance) of the underground heat pump unit 4. In the case of the present embodiment using the coefficients X, Y, and Z that are variably set by the above-described method, and the case of the comparative example in which the refrigerant temperature coefficient X is fixedly set among the coefficients X, Y, and Z, It is the graph shown in comparison. The COP of the geothermal heat pump unit 4 at this time is
COP = Cooling capacity [kW] of the underground heat pump unit 4 / (Power consumption [kW] of the first compressor 43 + Power consumption [kW] of the underground heat control device 61).
It is represented by In addition, the example shown in figure has shown the case where underground temperature is 20 [degreeC] as an example.

  As shown in FIG. 9, in the case of the method of the comparative example, the actual discharge temperature is controlled in the range of 45 to 42 [° C.], and the COP remains at about 4.3 to 4.9. On the other hand, in the above-described embodiment, as a result of the actual discharge temperature being controlled in a relatively low temperature range of 33 to 29 [° C.], the COP reaches about 4.8 to 5.5, and the comparative example is described above. It can be seen that it is improved by about 0.5 to 0.6.

  In the present embodiment, in particular, the temperature of the refrigerant flowing out from the underground heat source heat exchanger 45 is used as the heat source index. Thereby, the underground temperature state can be accurately grasped, and an appropriate target discharge temperature can be set to reliably improve the efficiency.

  Further, in the present embodiment, as described above with reference to FIGS. 6 to 9, as the heat source index, the refrigerant temperature flowing out from the underground heat source heat exchanger 45, the rotation speed of the first compressor 43, the main The target discharge temperature is determined corresponding to the target circulating fluid temperature corresponding to the user operation on the remote controller 60a. Thereby, the setting of the target discharge temperature with higher accuracy can be performed in consideration of the setting of the cooling capacity by the user and the operation state of the first compressor 43 in the first heat pump circuit 40.

  Further, in the present embodiment, in particular, as described above using Equation 1, the refrigerant temperature coefficient X associated with the refrigerant temperature zone, and the rotational speed coefficient Y associated with the rotational speed zone of the first compressor 43. The target discharge temperature To is calculated by an equation using the circulating fluid temperature coefficient Z associated with the circulating fluid temperature zone. Thereby, reliable and quick decompression control can be executed with a simple calculation.

  In addition, this invention is not limited to the said embodiment, A various change is possible in the range which does not change the summary of invention. Hereinafter, the various modifications will be described in order. In the following description, parts equivalent to those in the above-described embodiment are denoted by the same reference numerals, and description thereof is omitted or simplified as appropriate.

(1) When the underground temperature is used as a heat source index FIG. 10 corresponding to FIG. 2 shows a circuit configuration of the entire heat pump cold heat source apparatus 1 according to this modification. 10, in this modification, in the underground heat circulation circuit 20, the going-out temperature of the heat medium H1 from the underground heat exchanger 23 to the underground heat source heat exchanger 45 through the underground heat pipe 21 The underground temperature sensor 92a (underground temperature detecting means, which corresponds to the heat source index detecting means in this modification) detects between the underground heat circulation pump 22 and the underground heat source heat exchanger 45. Is provided.

  In this case, as shown in FIG. 11 corresponding to FIG. 4, the target discharge temperature determination unit 61Ba of the expansion valve control unit 61B replaces the refrigerant temperature flowing out of the above-described underground heat source heat exchanger 45, Corresponding to the underground temperature of the circulating fluid L by the forward temperature sensor 92a (corresponding to the heat source index in this modification), the rotation speed of the first compressor 43, and the user operation on the main remote controller 60a already described. The target discharge temperature of the refrigerant discharged from the first compressor 43 is determined based on the target circulating fluid temperature. As in the embodiment, the opening degree control unit 61Bb is configured so that the actual discharge temperature detected by the first refrigerant discharge temperature sensor 42a becomes the target discharge temperature determined by the target discharge temperature determination unit 61Ba. The valve opening degree of the first expansion valve 44 is controlled.

  In this modification, the temperature of the underground side is accurately grasped by using the temperature of the heat transfer medium from the underground heat exchanger 23 as a heat source index, and an appropriate target discharge temperature is set and reliably set. Efficiency can be improved.

(2) When underground return temperature is used as a heat source index The circuit configuration of the entire heat pump cold heat source apparatus 1 according to this modification is shown in FIG. 12 corresponding to FIG. 2 and FIG. In FIG. 12, in this modification, in the underground heat circulation circuit 20, the return temperature of the heat medium H1 returning from the underground heat source heat exchanger 45 to the underground heat exchanger 23 via the underground heat pipe 21. The underground return temperature sensor 92b (underground return temperature detection means, which corresponds to the heat source index detection means in this modification) detects between the underground heat source heat exchanger 45 and the underground heat exchanger 23. Is provided.

  In this case, as shown in FIG. 13 corresponding to FIG. 4 and FIG. 11, the target discharge temperature determination unit 61Ba of the expansion valve control unit 61B replaces the refrigerant temperature flowing out of the above-described underground heat source heat exchanger 45. The underground return temperature of the circulating fluid L by the underground return temperature sensor 92b (corresponding to the heat source index in this modification), the rotation speed of the first compressor 43, and the user operation with the main remote controller 60a already described. The target discharge temperature of the refrigerant discharged from the first compressor 43 is determined based on the target circulating fluid temperature corresponding to. As in the embodiment, the opening degree control unit 61Bb is configured so that the actual discharge temperature detected by the first refrigerant discharge temperature sensor 42a becomes the target discharge temperature determined by the target discharge temperature determination unit 61Ba. The valve opening degree of the first expansion valve 44 is controlled.

  In this modification, by using the heat medium return temperature to the underground heat exchanger 23 as the heat source index, the underground temperature state is accurately grasped and an appropriate target discharge temperature is set to ensure Efficiency can be improved.

(3) When using the condensation temperature in the condenser as the heat source index The circuit configuration of the entire heat pump cold heat source unit 1 according to this modification is shown in FIG. 14 corresponding to FIG. 2, FIG. 10, and FIG. In FIG. 14, in this modification, in the first heat pump circuit 40, a condensation temperature sensor 92c (condensation temperature detection means, which detects the condensation temperature of the first refrigerant C1 condensed in the underground heat source heat exchanger 45). (Corresponding to the heat source index detecting means in this modification) is provided on the first refrigerant pipe 42 side of the underground heat source heat exchanger 45.

  In this case, as shown in FIG. 15 corresponding to FIG. 4, FIG. 11, and FIG. 13, the target discharge temperature determination unit 61Ba of the expansion valve control unit 61B Instead of the above, the condensing temperature by the condensing temperature sensor 92c (corresponding to the heat source index in this modification), the rotation speed of the first compressor 43, and the target corresponding to the user operation on the main remote controller 60a already described. The target discharge temperature of the refrigerant discharged from the first compressor 43 is determined based on the circulating fluid temperature. As in the embodiment, the opening degree control unit 61Bb is configured so that the actual discharge temperature detected by the first refrigerant discharge temperature sensor 42a becomes the target discharge temperature determined by the target discharge temperature determination unit 61Ba. The valve opening degree of the first expansion valve 44 is controlled.

  In this modification, by using the refrigerant condensing temperature in the underground heat source heat exchanger 45 as a heat source indicator, it is possible to accurately grasp the underground temperature state and set an appropriate target discharge temperature to ensure The efficiency can be improved.

(4) In the case where the control waiting time is provided after the pump is started. That is, when the control method according to the above-described embodiment or the modified examples of (1) to (3) is executed, a predetermined period ( The valve opening degree of the first expansion valve 44 may be controlled after waiting for e.g. 3 minutes). This has the following significance.

  That is, in the underground heat circulation circuit 20, the ground section of a certain length is usually also in the underground heat pipe 21 connecting the underground heat source heat exchanger 45 and the underground heat exchanger 23 located on the ground side. (For example, the section Lab between ab and the section Lcd between cd shown in FIG. 1). Or even if it is arranged in the ground, its depth is shallow and there is a section that is affected by outside air (that is, strictly speaking, it cannot be said that heat is exchanged only with the ground). The heat medium H1 existing in those sections of the underground heat pipe 21 may not correctly reflect the temperature in the ground.

  In the present modification, corresponding to the above, the actual temperature detected by the first refrigerant discharge temperature sensor 42a after the predetermined period has elapsed after the geothermal circulation pump 22 of the geothermal heat pipe 21 is started. The opening of the first expansion valve 44 by the expansion valve control unit 61B (particularly, the opening control unit 61Bb) described above so that the discharge temperature becomes the target discharge temperature determined by the target discharge temperature determination unit 61Ba. Start control. As a result, the above-described control is performed after the flow of the heat medium H1 proceeds and correctly reflects the temperature in the ground. Therefore, it is possible to set the target discharge temperature with high accuracy and reliably avoiding the above-described risk. It can be done reliably. During the predetermined time (3 minutes in the above example) after the geothermal circulation pump 22 is activated, the first expansion valve 44 is fixed to a predetermined level by the opening degree control unit 61Bb of the expansion valve control unit 61B. It is controlled so as to have an opening.

(5) Others In the above, in the terminal circulation circuit 30, the first heat exchanger 41 is disposed upstream of the second heat exchanger 51 with respect to the flow of the circulating liquid L that circulates. However, the present invention is not limited to this, and the second heat exchanger 51 may be disposed upstream of the first heat exchanger 41. Further, in the terminal circulation circuit 30, the first heat exchanger 41 and the second heat exchanger 51 may be connected in parallel.

  In addition, in the above, a ground heat exchanger 23 is provided in the ground or the relatively large capacity water source, and the heat medium H1 heat-exchanged with the ground or the water source by the ground heat exchanger 23 is provided. Although it was made to circulate in the underground heat circulation circuit 20, it is not restricted to this. That is, instead of configuring such a circulation circuit, an open type pipe line may be connected to the underground heat circulation pump 22. In this case, the upstream side (pump inflow side) and the downstream side (pump outflow side) of the geothermal circulation pump 22 are supplied with water sources (or constant temperature water) such as the aforementioned lakes, reservoirs, rivers, seas, hot springs and wells, respectively. It may be connected to a chilled water supply), and the water from the water source or the like is directly pumped by the geothermal circulation pump 22 and used. That is, water such as the water source is supplied to the underground heat circulation pump 22 through a pipe line (upstream pipe line) connected to the pump upstream side, and a pipe line (downstream pipe line) connected to the pump downstream side. ), And is then guided to the underground heat source heat exchanger 45 provided in the downstream pipe line to exchange heat with the first refrigerant C1, and further through the downstream pipe line, the water source. And so on. In this case, the water source and the like connected to the upstream pipeline and the water source and the like connected to the downstream pipeline may be the same or different. In this case, the upstream pipe line and the downstream pipe line correspond to the heat source connection path described in each claim.

  In the above description, the case where only one underground heat exchanger 23 is provided in the ground is described as an example. However, the present invention is not limited to this, and a plurality of underground heat exchangers 23 are provided in the ground. May be. In that case, the plurality of underground heat exchangers 23 may be connected in parallel to each other or may be connected in series.

  In the above description, the case where the present invention is applied to the composite heat source type heat pump apparatus including the first heat pump circuit 40 using the underground heat and the second heat pump circuit 50 using the air heat has been described as an example. However, it is not limited to this. That is, the present invention may be applied to a single heat source type heat pump apparatus including only the first heat pump circuit 40 using the underground heat. Conversely, the present invention may be applied to a composite heat source type heat pump device including the first heat pump circuit 40 and including three or more heat pump circuits.

1 Heat pump cold heat source machine 20 Ground heat circulation circuit (heat source connection path)
21 Underground heat pipe (heat medium pipe)
22 Geothermal circulation pump (heat medium pump)
23 Ground heat exchanger (heat source)
30 Terminal circulation circuit (load side circuit)
31 Load piping (circulating fluid piping)
32 Circulating fluid circulation pump 34 Return hot water temperature sensor 36 Heat exchange terminal (load terminal)
40 1st heat pump circuit (heat pump circuit)
41 1st heat exchanger (load side heat exchanger)
42 First refrigerant piping (refrigerant piping)
42a First refrigerant discharge temperature sensor (discharge temperature detection means)
42b First refrigerant temperature sensor (refrigerant temperature detection means, heat source index detection means)
43 First compressor (compressor)
44 1st expansion valve (pressure reduction means)
45 Ground heat source heat exchanger (heat source side heat exchanger)
60a Main remote control (operation means)
61Ba Target discharge temperature determination unit (target discharge temperature determination means)
61Bb Opening control unit (pressure reduction control means)
92a Underground temperature sensor (underground temperature detector, heat source index detector)
92b Underground return temperature sensor (underground return temperature detection means, heat source index detection means)
92c Condensation temperature sensor (condensation temperature detection means, heat source index detection means)
C1 1st refrigerant C2 2nd refrigerant H1 Heat medium L Circulating fluid To Target discharge temperature X Refrigerant temperature coefficient Y Rotational speed coefficient Z Circulating fluid temperature coefficient

Claims (5)

A compressor, a load-side heat exchanger that functions as an evaporator, a decompression unit, and a heat-source-side heat exchanger that functions as a condenser are connected by a refrigerant pipe to form a heat pump circuit,
The load side heat exchanger and the load terminal are connected by circulating fluid piping to form a load side circuit,
In the heat pump cold heat source machine in which the heat source side heat exchanger and the heat source are connected by a heat medium pipe to form a heat source connection path,
In the heat pump circuit, discharge temperature detection means for detecting an actual discharge temperature of the refrigerant discharged from the compressor,
Heat source index detecting means for detecting a heat source index capable of estimating the temperature of the heat source;
Target discharge temperature determining means for determining a target discharge temperature of the refrigerant discharged from the compressor according to the heat source index detected by the heat source index detecting means;
A decompression control means for controlling an opening degree of the decompression means so that the actual discharge temperature detected by the discharge temperature detection means becomes the target discharge temperature determined by the target discharge temperature determination means;
A heat pump cold heat source machine characterized by comprising: The heat source connection path is
A ground heat circulation circuit in which a ground heat exchanger as the heat source and the heat source side heat exchanger are connected by the heat medium pipe,
The heat source index detection means includes
Underground return temperature detection means for detecting the return temperature of the heat medium returning from the heat source side heat exchanger to the underground heat exchanger via the heat medium pipe, or
Underground temperature detection means for detecting the temperature of the heat medium going from the underground heat exchanger to the heat source side heat exchanger via the heat medium pipe, or
Refrigerant temperature detection means for detecting the temperature of the refrigerant flowing out from the heat source side heat exchanger via the refrigerant pipe, or
The heat pump cold / heat source apparatus according to claim 1, wherein the heat pump cold / heat source unit is a condensing temperature detecting unit that detects a condensing temperature of the refrigerant condensed in the heat source side heat exchanger. The target discharge temperature determining means includes
The target according to the heat source index detected by the heat source index detection means, the rotational speed of the compressor, and the target circulating fluid temperature corresponding to the operation of the operating means capable of operating the load terminal. 3. The heat pump cold heat source apparatus according to claim 1, wherein a discharge temperature is determined. The target discharge temperature determining means includes
The target discharge temperature To is
The temperature coefficient X previously associated with each of the plurality of temperature zones related to the heat source index detected by the heat source index detection means, and the rotation previously associated with each of the plurality of rotation speed zones related to the rotation speed of the compressor A formula using a number coefficient Y and a circulating fluid temperature coefficient Z previously associated with each of a plurality of circulating fluid temperature zones related to the target circulating fluid temperature To = X + Y + Z
The heat pump cold heat source apparatus according to claim 3, wherein the heat pump cold heat source apparatus is calculated by: A heat medium pump provided in the heat medium pipe of the heat source connection path;
The decompression control means includes
5. The heat pump cooling / heating source according to claim 4, wherein after the heat medium pump is started and a predetermined period has elapsed, an opening degree of the pressure reducing means is controlled so that the actual discharge temperature becomes the target discharge temperature. Machine.

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