JP6608353B2 - Temperature control system - Google Patents

Description

  The present invention relates to a temperature control system that drives a compressor that compresses refrigerant and controls the temperature by the heat of condensation or evaporation of the refrigerant, and more particularly to a temperature control system that includes both an engine-driven compressor and an electric compressor.

  As a temperature control system that drives a compressor that compresses a refrigerant to control the temperature by the heat of condensation or evaporation of the refrigerant, there is a system that includes both an engine-driven compressor and an electric compressor (see, for example, Patent Document 1).

Japanese Patent No. 5584024

  In such a temperature control system, the operating capacity of the electric compressor may be limited. Such restrictions include, for example, monitoring a demand value that is the maximum demand power of a power consumer [a maximum value of average power per demand time (specifically, 30 minutes) that is a predetermined predetermined monitoring time]. It is assumed to be performed by demand control that controls the operation capacity of the compressor.

  In this regard, Patent Literature 1 discloses a gas heat pump type first air conditioner that drives and drives an engine-driven compressor and an electric heat pump type second air conditioner that drives and conditioned an electric compressor. In the air conditioning system used together, the maximum power of the second air conditioner is suppressed to be smaller than the peak power in the past predetermined period by suppressing the operation capacity of the second air conditioner, and the insufficient operation capacity is reduced to the first. 1 discloses a configuration that is covered by the operating capacity of an air conditioner (see paragraphs [0009] and [0011] of Patent Document 1).

  By the way, in a temperature control system including both an engine-driven compressor and an electric compressor, when limiting the operating capacity of the electric compressor, the engine-driven compressor is in operation while both the engine-driven compressor and the electric compressor are in operation. If the operating capacity of the engine becomes the rated operating capacity of the engine-driven compressor, the operating capacity of the engine-driven compressor cannot cover the operating capacity of the limited amount of the electric compressor that limits the operating capacity. Inevitably, the demand for temperature control is sacrificed.

  Therefore, in a temperature control system including both an engine-driven compressor and an electric compressor, it is desirable to avoid sacrificing the temperature control request as much as possible when there are a plurality of sets of engine-driven compressors and electric compressors. It is.

  However, Patent Document 1 does not take into consideration that the temperature control request is not sacrificed as much as possible when a plurality of sets of engine-driven compressors and electric compressors are provided.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a temperature control system that includes both an engine-driven compressor and an electric compressor, and that can prevent a temperature control request from being sacrificed as much as possible. .

  In order to solve the above problems, a temperature control system according to the present invention is a temperature control system including both an engine-driven compressor and an electric compressor, and the engine-driven compressor and the electric compressor are commonly used. The engine-driven compressor and the electric compressor have a plurality of heat pumps that are housed in the package and circulate the refrigerant, and there is a power consumption suppression condition for suppressing the power consumption of the temperature control system. If established, the operating capacity of the electric compressor in the heat pump in which the operating capacity of the engine-driven compressor is smaller than the rated operating capacity of the engine-driven compressor among the heat pumps is preferentially limited. It is characterized by.

  According to the present invention, it is possible to minimize the temperature control request.

It is a schematic structure figure showing typically the temperature control system concerning an embodiment of the invention. It is a schematic block diagram of an example of the heat pump which comprises the temperature control system shown in FIG. It is a bar graph for demonstrating the priority order which restrict | limits the operation capacity of an electric compressor from which heat pump as demand control in order when a temperature control load of a heat pump differs in a some heat pump. It is a bar graph which shows the state which has enlarged the amount of restrictions of the operation capacity of an electric compressor, so that a demand warning level is large. FIG. 4 is a chart collectively showing the presence or absence of a temperature control request with respect to the priority order of the heat pump by the demand control shown in FIG. 3 and the effect of suppressing the power consumption of the electric compressor. It is a flowchart which shows an example of the control operation of demand control by the control apparatus in a temperature control system.

  Embodiments according to the present invention will be described below with reference to the drawings.

  FIG. 1 is a schematic configuration diagram schematically showing a temperature control system 300 according to an embodiment of the present invention.

  As shown in FIG. 1, the temperature control system 300 includes a plurality of heat pumps 100 (1) to 100 (n) (n is an integer of 2 or more, each including both the engine-driven compressor 11 and the electric compressor 12. In the example, n = 10) and the control device 200 are provided.

  In temperature control system 300, control device 200 is communicatively connected to a plurality of heat pumps 100 (1) to 100 (n) via communication line NT.

  In this example, the plurality of heat pumps 100 (1) to 100 (n) are communicatively connected to each other via the communication line NT and communicate with each other. Any one of the plurality of heat pumps 100 (1) to 100 (n) is designated as the heat pump 100 (j) (j is an integer from 1 to n, j = 1 in this example). ing. The heat pump 100 (j) of the parent device is connected to the control device 200 via the communication line NT, and the heat pump 100 (k) of the child device (other) (k is an integer excluding j from 1 to n). ) Communicate with each other.

  The control device 200 receives the operation information Dr of each of the heat pumps 100 (1) to 100 (n), while the instruction information Di based on the operation information Dr is the heat pump 100 (i) (i is from 1) corresponding to the instruction information Di. Any integer up to n) is transmitted and, as will be described later, the operating capacity of the electric compressor 12 in the heat pump 100 (i) is limited.

  In this example, the heat pump 100 (j) of the parent device collects the operation information Dr from the heat pump 100 (k) of the child device, and transmits it to the control device 200 together with its own operation information Dr. When the instruction information Di from the control device 200 is its own instruction information Di, the heat pump 100 (j) of the parent machine restricts the operating capacity of the electric compressor 12 by its own instruction information Di and performs control. When the instruction information Di from the device 200 is the instruction information Di of the slave unit heat pump 100 (k), the instruction information Di is transmitted to the slave unit heat pump 100 (k). The slave unit heat pump 100 (k) limits the operating capacity of the electric compressor 12 based on the instruction information Di sent from the master unit heat pump 100 (j). The limitation on the operation capacity of the electric compressor 12, the operation information Dr, and the instruction information Di will be described later in detail.

  The control device 200 includes a processing unit 210 including a microcomputer such as a CPU (Central Processing Unit), a non-volatile memory such as a ROM (Read Only Memory), and a storage unit 220 including a volatile memory such as a RAM (Random Access Memory). And has a timer function.

  In the control device 200, the processing unit 210 controls the operation of various components by loading a control program stored in advance in the ROM of the storage unit 220 onto the RAM of the storage unit 220 and executing it. .

(About heat pump)
Next, the configuration and operation of the heat pumps 100 (1) to 100 (n) constituting the temperature adjustment system 300 will be described below with reference to FIG. 2. FIG. 2 constitutes the temperature adjustment system 300 shown in FIG. It is a schematic block diagram of an example of heat pump 100 (1)-100 (n). The heat pumps 100 (1) to 100 (n) have substantially the same configuration, and will be described by using the heat pump 100 (i) as a representative in FIG.

  As shown in FIG. 2, the heat pump 100 (i) drives the compression unit 10 that compresses the refrigerant, and adjusts the temperature by the condensation heat or evaporation heat of the refrigerant. Here, temperature control is, for example, temperature control of indoor air or air in a refrigerator or freezer when the heat pump 100 (i) functions as an air conditioner, and the heat pump 100 (i) functions as a chiller. If it is, it is temperature control of the circulating fluid for the chiller. The circulating fluid may be any fluid as long as it acts as a heat medium, and representatively, water can be exemplified. However, it is not limited thereto, and the circulating fluid may be, for example, water containing an antifreeze.

  The heat pump 100 (i) includes a compressor 10 that sucks and discharges refrigerant, a heat source side heat exchanger 20 that exchanges heat between the refrigerant and air (specifically, outside air), and a heat source side heat exchanger 20. A heat source side heat exchanger fan 30 for adjusting, a regulating valve 40 for adjusting the flow rate of the refrigerant, a use side heat exchanger 50 for exchanging heat between the temperature adjustment target and the refrigerant, and a drive source for driving the compression unit 10 60, a refrigerant circuit 110 for circulating the refrigerant, and a control unit 120.

  Here, for example, when the heat pump 100 (i) functions as an air conditioner, the temperature adjustment target is indoor air or air in a refrigerator or freezer, and when the heat pump 100 (i) functions as a chiller. Is a circulating fluid.

  Then, the heat pump 100 (i) uses the refrigerant between the heat source side heat exchanger 20 and the use side heat exchanger 50 while repeating the state in which the refrigerant is depressurized to a low temperature and the state in which the refrigerant is pressurized to a high temperature. As described later, in the use-side heat exchange unit 101, the cooling operation for cooling the temperature adjustment target (for example, indoor air) and the temperature adjustment target (for example, indoor air) are performed. A heating operation for heating (for example, heating the room) is performed.

  The heat pump 100 (i) has both the engine-driven compressor 11 and the electric compressor 12, and is a so-called hybrid heat pump.

  The heat pump 100 (i) includes an engine-driven compressor 11 and an electric compressor 12 housed in a common package 102a (specifically, a casing), and a refrigerant circuit 110 that circulates the refrigerant is electrically connected to the engine-driven compressor 11 and the heat pump 100 (i). It is shared by the compressor 12.

  Specifically, the compression unit 10 includes an engine-driven compressor 11 that is a compressor driven by the engine 61 and an electric compressor 12 that is a compressor driven by the electric motor 62. The engine drive compressor 11 and the electric compressor 12 are connected in parallel.

  The drive source 60 includes an engine 61 that drives the engine-driven compressor 11 and an electric motor 62 that drives the electric compressor 12.

  The engine drive compressor 11 constituting the compression unit 10 is connected to the engine 61 via a clutch 11a. The clutch 11a is in a connected state in which driving force is transmitted from the engine 61 to the engine-driven compressor 11 and in a disconnected state in which transmission of driving force from the engine 61 to the engine-driven compressor 11 is interrupted by an instruction signal from the control unit 120. It is supposed to take.

  The engine-driven compressor 11 may be obtained by connecting a plurality of engine-driven compressors in parallel. Similarly, the electric compressor 12 may include a plurality of electric compressors connected in parallel. The regulating valve 40 functions as an expansion valve. The regulating valve 40 and the use side heat exchanger 50 constitute a use side heat exchange unit 101, and the use side heat exchange unit 101 is an indoor unit in this example. Moreover, the heat source side heat exchange part 102 provided with the structural member except the regulating valve 40, the utilization side heat exchanger 50, and a pair of connecting piping 110a, 110b among the structural members of the heat pump 100 (i) is, in this example, It is an outdoor unit.

  The engine 61 may be, for example, an engine using gas fuel as a fuel (so-called gas engine) or an engine using liquid fuel as fuel. In this example, the engine 61 is a gas engine. Therefore, the heat pump 100 (i) functions as a gas heat pump (GHP: Gas Heat Pump). The heat pump 100 (i) also functions as an electric heat pump (EHP) because the electric motor 62 is used in addition to the engine 61 as the drive source 60.

  The heat pump 100 (i) may be operated by both the engine driven compressor 11 and the electric compressor 12 when operated only by the engine driven compressor 11, when operated only by the electric compressor 12, and the like. When operating with both the engine-driven compressor 11 and the electric compressor 12, the ratios of the operating capacities of the engine-driven compressor 11 and the electric compressor 12 are the engine speed and the electric power, which are the engine speed of the engine 61 per unit time. This can be determined by controlling the motor rotation speed, which is the rotation speed per unit time of the motor 62.

  The control unit 120 includes a processing unit 121 including a microcomputer such as a CPU, and a storage unit 122 including a nonvolatile memory such as a ROM and a volatile memory such as a RAM.

  The control unit 120 controls the operation of various components by causing the processing unit 121 to load a control program stored in advance in the ROM of the storage unit 122 onto the RAM of the storage unit 122 and execute it. .

<Cooling operation>
In the heat pump 100 (i), when performing the cooling operation, the control unit 120 switches the four-way valve 111 to the first connection state (the state shown in FIG. 2) to communicate the first refrigerant path 111a and the second refrigerant path 111b. In addition, the third refrigerant path 111c and the fourth refrigerant path 111d are communicated. By doing so, the high-pressure gas refrigerant discharged from the compressor 10 (the engine-driven compressor 11 and / or the electric compressor 12) passes through the four-way valve 111 and the second refrigerant path 111b from the first refrigerant path 111a. It flows to the heat source side heat exchanger 20.

  The temperature of the high-pressure gas refrigerant flowing through the heat source side heat exchanger 20 is higher than the temperature of air (specifically, outside air) heat exchanged by the heat source side heat exchanger 20. For this reason, heat moves from the high-pressure gas refrigerant to the air (specifically, outside air). As a result, the high-pressure gas refrigerant loses heat of condensation and liquefies to become a high-pressure liquid refrigerant (hereinafter referred to as high-pressure liquid refrigerant). That is, in the cooling operation, the heat source side heat exchanger 20 functions as a refrigerant condenser that dissipates heat from the high-pressure gas refrigerant.

  The high-pressure liquid refrigerant passes through the regulating valve 40 from the heat source side heat exchanger 20 via one communication pipe 110a. In the regulating valve 40, the high-pressure liquid refrigerant expands to become a low-pressure gas-liquid two-phase refrigerant (hereinafter referred to as a low-pressure gas-liquid two-phase refrigerant), and the low-pressure gas-liquid two-phase refrigerant enters the use-side heat exchanger 50. Flowing.

  The temperature of the low-pressure gas-liquid two-phase refrigerant flowing to the refrigerant circuit 110 side of the use side heat exchanger 50 is lower than the temperature of the temperature adjustment target side (in this example, the indoor air side) of the use side heat exchanger 50. For this reason, heat moves from the temperature adjustment target side (in this example, the indoor air side) to the low-pressure gas-liquid two-phase refrigerant. As a result, the low-pressure gas-liquid two-phase refrigerant is vaporized by obtaining evaporation heat, and becomes a refrigerant in a low-pressure gas state (hereinafter referred to as a low-pressure gas refrigerant). On the other hand, the temperature adjustment target side (in this example, the indoor air side) is cooled by the endothermic action of the refrigerant. That is, in the cooling operation, the regulating valve 40 functions as an expansion valve that expands the high-pressure liquid refrigerant into a low-pressure gas-liquid two-phase refrigerant, and the use side heat exchanger 50 has a temperature at which the low-pressure gas-liquid two-phase refrigerant absorbs heat. It functions as a cooler for the adjustment target (in this example, indoor air).

  Thereafter, the low-pressure gas refrigerant flows from the use side heat exchanger 50 to the other communication pipe 110b, the fourth refrigerant path 111d, and the four-way valve 111. At this time, since the control unit 120 communicates the third refrigerant path 111c and the fourth refrigerant path 111d by the four-way valve 111, the low-pressure gas refrigerant passes through the third refrigerant path 111c from the four-way valve 111. The air is sucked into the compressor 10 (the engine driven compressor 11 and / or the electric compressor 12).

  Thereafter, in the heat pump 100 (i), the above-described series of cooling operation is repeated in the same manner.

  As described above, in the heat pump 100 (i), by appropriately performing the cooling operation, the temperature adjustment target (indoor air in this example) can be appropriately cooled by the use side heat exchanging unit 101 (in this example, the indoor unit). .

<Operation of heating operation>
In the heat pump 100 (i), when performing the heating operation, the control unit 120 switches the four-way valve 111 to the second connection state so that the first refrigerant path 111a and the fourth refrigerant path 111d are communicated and the second refrigerant path 111b. And the third refrigerant path 111c. By doing so, the high-pressure gas refrigerant discharged from the compressor 10 (the engine-driven compressor 11 and / or the electric compressor 12) is communicated from the first refrigerant path 111a to the four-way valve 111, the fourth refrigerant path 111d, and the other. It flows to the use side heat exchanger 50 via the pipe 110b.

  The temperature of the high-pressure gas refrigerant flowing to the refrigerant circuit 110 side of the use side heat exchanger 50 is higher than the temperature of the temperature adjustment target side (in this example, the indoor air side) of the use side heat exchanger 50. For this reason, heat moves from the high-pressure gas refrigerant to the temperature adjustment target side (in this example, the indoor air side). As a result, the high pressure gas refrigerant loses heat of condensation and liquefies to become a high pressure liquid refrigerant. On the other hand, the temperature adjustment target side (in this example, the indoor air side) is heated by the heat radiation action of the refrigerant. That is, in the heating operation, the use-side heat exchanger 50 functions as a heater for a temperature adjustment target (in this example, indoor air) radiated by the high-pressure gas refrigerant.

  The high-pressure liquid refrigerant passes through the regulating valve 40 from the use side heat exchanger 50. In the regulating valve 40, the high-pressure liquid refrigerant expands to become a low-pressure gas-liquid two-phase refrigerant, and the low-pressure gas-liquid two-phase refrigerant flows to the heat source side heat exchanger 20.

  The temperature of the low-pressure gas-liquid two-phase refrigerant flowing through the heat source side heat exchanger 20 is lower than the temperature of the air (specifically outside air) flowing through the heat source side heat exchanger 20. For this reason, heat moves from air (specifically, outside air) to the low-pressure gas-liquid two-phase refrigerant. As a result, the low-pressure gas-liquid two-phase refrigerant is vaporized by obtaining the evaporation heat, and becomes a low-pressure gas refrigerant. That is, in the heating operation, the heat source side heat exchanger 20 functions as a refrigerant evaporator that absorbs heat from the low-pressure gas-liquid two-phase refrigerant.

  Thereafter, the low-pressure gas refrigerant flows from the heat source side heat exchanger 20 to the second refrigerant path 111 b and the four-way valve 111. At this time, since the control unit 120 communicates the second refrigerant path 111b and the third refrigerant path 111c with the four-way valve 111, the low-pressure gas refrigerant passes through the third refrigerant path 111c from the four-way valve 111. Inhaled by the compression unit 10.

  Thereafter, in the heat pump 100 (i), the above-described series of heating operation is repeated in the same manner.

  As described above, in the heat pump 100 (i), by appropriately performing the heating operation, the temperature adjustment target (indoor air in this example) can be appropriately heated by the use side heat exchanging unit 101 (in this example, the indoor unit). .

(Regarding restrictions on the operating capacity of electric compressors)
Next, the limitation on the operation capacity of the electric compressor 12 in the temperature control system 300 will be described.

  In the temperature control system 300 illustrated in FIG. 1, the operation capacity of the electric compressor 12 may be limited. Such restrictions include, for example, monitoring a demand value that is the maximum demand power of a power consumer [a maximum value of average power per demand time (specifically, 30 minutes) that is a predetermined predetermined monitoring time]. It is assumed to be performed by demand control that controls the operation capacity of the compressor 12. Hereinafter, the limitation of the operation capacity of the electric compressor 12 will be described taking demand control as an example.

  Electricity charges are calculated mainly from basic charges and electricity charges. The electric power company measures the demand value for each predetermined demand time (specifically, 30 minutes) by the measuring means E such as a watt hour meter in order to determine the basic charge. The basic charge is determined based on the demand value. For this reason, the power consumer is required to perform demand control so that the demand value does not exceed a predetermined power value. The demand control is performed by the demand monitoring device M, for example. The demand monitoring apparatus M is configured to receive information related to the amount of power (specifically, a pulse signal related to the amount of power) from the measuring means E.

  In temperature control system 300 according to the present embodiment, control device 200 receives demand information Dd transmitted from demand monitoring device M.

  Here, the demand information Dd includes information indicating demand warning levels in a plurality of stages, which is an index indicating the degree of approach of the demand value to a predetermined power value. Specifically, multiple levels of demand alert levels 1 to m (m is an integer of 2 or more) can be set in advance. The multiple levels of demand alert levels 1 to m can be used as an index indicating that the demand value approaches the predetermined power value as the demand alert level increases.

  FIG. 3 shows that the heat compressors 100 (i) to 100 (n) have different temperature control loads L of the heat pumps 100 (i). It is a bar graph for demonstrating the priority of whether the operating capacity (phi) e is restrict | limited.

  FIG. 3 shows a state before limiting the operating capacity φe of the electric compressor 12 (before issuing a demand warning level). In FIG. 3, n is 10 and the vertical axis on the left is the temperature control load ratio between the engine-driven compressor 11 and the electric compressor 12 and the operation of the engine-driven compressor 11 and the electric compressor 12 with respect to the heat pump 100 (i). The capacity ratio (Rg: Re) is shown, the vertical axis on the right side shows the total operating capacity (φg + φe) of the engine-driven compressor 11 and the electric compressor 12, and the horizontal axis shows the individual heat pumps 100 (1) to 100 (10 ). A hatched portion drawn diagonally upward from left to right indicates the operating capacity φg of the engine-driven compressor 11, and a hatched portion drawn diagonally downward from left to right represents the operation of the electric compressor 12. Capacitance φe is shown. The meaning of the hatched portion is the same in FIG. 4 described later.

  FIG. 4 is a bar graph showing a state where the limit amount of the operating capacity φe of the electric compressor 12 is increased as the demand warning level is increased.

  FIG. 4 shows a state in which the electric compressor 12 is operated alone before the operating capacity φe of the electric compressor 12 is limited (before the demand warning level is issued). In FIG. 4, the left vertical axis represents the temperature control load of the heat pump 100 (i), the right vertical axis represents the total operating capacity of the engine-driven compressor 11 and the electric compressor 12 (φg + φe), and the horizontal axis represents Indicates demand warning level. On the horizontal axis, the demand warning level increases from left to right.

  As shown in FIG. 3, the control device 200 uses the electric compressor 12 alone (from the engine-driven compressor 11) until the temperature control load L of the heat pump 100 (i) reaches the rated operating capacity φemax of the electric compressor 12. (Refer to heat pumps 100 (1) to 100 (3) in the example shown in FIG. 3), and the temperature control load L of the heat pump 100 (i) exceeds the rated operating capacity φemax of the electric compressor 12, Both the electric compressor 12 and the engine drive compressor 11 are operated (see the heat pumps 100 (4) to 100 (10) in the example shown in FIG. 3).

  As shown in FIG. 4, when the operating capacity φe of the electric compressor 12 is limited and the operating capacity φe of the electric compressor 12 is insufficient, the control device 200 reduces the operating capacity of the engine-driven compressor 11. The operating capacity of φg is covered.

  Thus, in the configuration in which the electric compressor 12 is operated before the engine-driven compressor 11, the operating capacity corresponding to the shortage of the limited amount of the electric compressor 12 that limits the operating capacity φe is set to the engine-driven compressor 11. The operating capacity φg can be surely secured.

  As shown in FIG. 4, the control device 200 increases the limit amount of the operating capacity φe of the electric compressor 12 as the demand warning level value based on the demand information Dd from the demand monitoring device M is larger.

  In the example shown in FIG. 4, the control device 200 restricts the operating capacity φe of the electric compressor 12 at the demand warning level 1, further restricts the operating capacity φe of the electric compressor 12 at the demand warning level 2, and is insufficient. Is provided by the operating capacity φg of the engine-driven compressor 11.

  In temperature control system 300 according to the present embodiment, the operating capacity ratio (rated operating capacity ratio) of engine-driven compressor 11 and electric compressor 12 to the operating capacity (rated operating capacity) of heat pump 100 (i) (Rg: Re) (see FIG. 3) is preset.

  By doing so, it is possible to easily identify the heat pump 100 (i) that limits the operating capacity φe of the electric compressor 12 among the plurality of heat pumps 100 (1) to 100 (n).

  In this example, in any of the heat pumps 100 (1) to 100 (n), the operating capacity ratio Rg of the engine driven compressor 11 is set to 70%, and the operating capacity ratio Re of the electric compressor 12 is set to 30%. Yes. The operating capacity ratios (Rg: Re = 7: 3) of the engine driven compressor 11 and the electric compressor 12 are an example for the following explanation, and the operating capacities of the engine driven compressor 11 and the electric compressor 12 are described. The ratio (Rg: Re) is not limited to this. In this example, the operating capacity ratio (Rg: Re) between the engine-driven compressor 11 and the electric compressor 12 is constant in any of the plurality of heat pumps 100 (1) to 100 (n). The at least two of the plurality of heat pumps 100 (1) to 100 (n) may be different from each other.

  By the way, in the temperature control system 300 having the plurality of heat pumps 100 (1) to 100 (n) each including both the engine-driven compressor 11 and the electric compressor 12, it is possible to avoid sacrificing the temperature control request as much as possible. Is desired.

  However, as shown in the rightmost bar graph in FIG. 3, in the temperature control system 300, the engine among the heat pumps 100 (4) to 100 (10) operating both the engine-driven compressor 11 and the electric compressor 12. If the operating capacity φe of the electric compressor 12 in the heat pump 100 (10) in which the operating capacity φg of the drive compressor 11 is equal to the rated operating capacity φgmax of the engine-driven compressor 11 is limited first, the temperature is inevitably increased. The key requirement is sacrificed.

  In this regard, the control device 200 in the temperature control system 300 according to the present embodiment has a power consumption suppression condition for suppressing the power consumption of the temperature control system 300 (in this example, demand warning for demand control). The operating capacity φg of the engine-driven compressor 11 among the heat pumps 100 (1) to 100 (10) is the rated operation of the engine-driven compressor 11. The operating capacity φe of the electric compressor 12 in the heat pumps 100 (1) to 100 (9) (see α, β, γ shown in FIG. 3) that is smaller than the capacity φgmax is preferentially limited. That is, if the limiting rate of the operating capacity φe of the electric compressor 12 is δ [%], a relationship of φg + φemax × δ [%] <φgmax is established.

  In this way, depending on the limit amount of the electric compressor 12 that limits the operating capacity φe (in the heat pumps 100 (1) to 100 (7) surrounded by α and β shown in FIG. 3, the operating capacity of the electric compressor 12 is Even if φe is limited to zero, the heat pumps 100 (8) and 100 (9) surrounded by γ shown in FIG. 3 are insufficient until the operating capacity φg of the engine-driven compressor 11 reaches the rated operating capacity φgmax). The operating capacity of the engine can be covered by the operating capacity φg of the engine-driven compressor 11, so that the temperature control request can be avoided as much as possible. Moreover, in each of the heat pumps 100 (1) to 100 (10), the engine-driven compressor 11 and the electric compressor 12 are housed in a common package 102a, and the refrigerant circuit 110 that circulates the refrigerant is electrically connected to the engine-driven compressor 11. Since it is shared by the compressor 12, the operating capacity φe of the electric compressor 12 can be limited in units of each heat pump 100 (i).

  Here, the bar graph surrounded by α indicates the engine in the heat pumps 100 (1) to 100 (9) in which the operating capacity φg of the engine-driven compressor 11 is smaller than the rated operating capacity φgmax of the engine-driven compressor 11. Of the heat pumps 100 (4) to 100 (9) that are operating both the drive compressor 11 and the electric compressor 12, the temperature control load L of the heat pumps 100 (4) to 100 (9) is that of the engine drive compressor 11. The operating capacities φg and φe of the heat pumps 100 (4) to 100 (7) that are equal to or lower than the rated operating capacity φgmax (operating capacity ratio Rg = 70%) are shown. The bar graph surrounded by β indicates the operating capacity φe of the heat pumps 100 (1) to 100 (3) during the independent operation of the electric compressor 12. The bar graph surrounded by γ indicates that the engine-driven compressor in the heat pumps 100 (1) to 100 (9) in which the operating capacity φg of the engine-driven compressor 11 is smaller than the rated operating capacity φgmax of the engine-driven compressor 11. Among the heat pumps 100 (4) to 100 (9) that are operating both the motor 11 and the electric compressor 12, the temperature control load L of the heat pumps 100 (4) to 100 (9) is the rated operating capacity of the engine driven compressor 11. The operating capacities φg and φe of the heat pumps 100 (8) and 100 (9) that are larger than φgmax (operating capacity ratio Rg = 70%) are shown.

  Note that when the operating capacity φg of the engine-driven compressor 11 is smaller than the rated operating capacity φgmax of the engine-driven compressor 11, the engine-driven compressor 11 is not operated (the operating capacity φg is zero). State, see β in FIG. 3). The heat pump 100 (i) in which the operation capacity φe of the electric compressor 12 is limited is a heat pump that operates the electric compressor 12 that can limit the operation capacity φe.

(About priority)
Next, priority 1 to priority 3 indicating which of the heat pumps 100 (1) to 100 (10) the operating capacity φe of the electric compressor 12 is limited will be described. Here, the priority 1 means that the operating capacity φe of the electric compressor 12 is restricted first, and the priority 2 means that the operating capacity φe of the electric compressor 12 is restricted next to the priority 1. The priority 3 means that the operating capacity φe of the electric compressor 12 is restricted after the priority 2.

<Priority 1>
In the present embodiment, the control device 200 includes heat pumps 100 (4) to 100 (9) that are operating both the engine-driven compressor 11 and the electric compressor 12 (specifically, the electric compressor 12 has a rated operating capacity). temperature control load L of the heat pumps 100 (4) to 100 (9) (the operation capacity φg of the engine-driven compressor 11 and the operation capacity φe of the electric compressor 12). The operation capacity φe of the electric compressor 12 in the heat pumps 100 (4) to 100 (7) in which the total (φg + φe)] is equal to or less than the rated operation capacity φgmax (operation capacity ratio Rg = 70%) of the engine-driven compressor 11 Limit first (see α shown in FIG. 3).

  In this way, even if the operating capacity φe of the electric compressor 12 is limited to zero, the operating capacity of the engine-driven compressor 11 is reduced by the amount of the limited amount of the electric compressor 12 that limits the operating capacity φe. It can be covered by the operating capacity φg, thereby avoiding sacrificing the temperature control request. That is, the operating capacity φe of the electric compressor 12 can be limited without sacrificing the temperature control request. Further, among the heat pumps 100 (4) to 100 (9), the heat pump 100 (4) in which the temperature control load L of the heat pumps 100 (4) to 100 (9) is equal to or less than the rated operating capacity φgmax of the engine driven compressor 11. ) To 100 (7), since the electric compressor 12 is operated with the operating capacity φe of the rated operating capacity φemax, the amount of power consumption of the electric compressor 12 that limits the operating capacity φe is less than the rated operating capacity φemax. The amount of power consumption of the electric compressor 12 in the heat pumps 100 (1) and 100 (2) operating with a small operating capacity φe can be made larger. Such advantages can be obtained with the highest priority, the first priority.

<Rank in priority 1>
In the present embodiment, control device 200 includes heat pumps 100 (4) to 100 (9) among heat pumps 100 (4) to 100 (9) operating both engine-driven compressor 11 and electric compressor 12. Among the heat pumps 100 (4) to 100 (7) in which the temperature control load L is equal to or lower than the rated operating capacity φgmax of the engine driven compressor 11 (see α shown in FIG. 3), the operating capacity φg of the engine driven compressor 11 The operating capacity φe of the electric compressor 12 is limited in the order of the heat pumps 100 (4), 100 (5), 100 (6), and 100 (7) with sufficient margin.

  By doing so, it is possible to reduce the frequency of shifting to the next priority order by the margin of the operating capacity φg of the engine-driven compressor 11. Moreover, among the heat pumps 100 (4) to 100 (9) that are operating both the engine driven compressor 11 and the electric compressor 12, the temperature control load L of the heat pumps 100 (4) to 100 (9) is the engine driven compression. Heat pumps 100 (4), 100 (5), 100 (6), 100 (7) having a sufficient operating capacity φg in heat pumps 100 (4) to 100 (7) having a rated operating capacity φgmax or less of the machine 11 ), The operating capacity φe can be limited in order from the electric compressor 12, thereby having a likelihood (likelihood) for the fluctuation of the temperature control load L of the heat pumps 100 (4) to 100 (9). Can be made.

<Priority 2>
In the present embodiment, control device 200 includes heat pumps 100 (4) to 100 (9) among heat pumps 100 (4) to 100 (9) operating both engine-driven compressor 11 and electric compressor 12. Next to the heat pumps 100 (4) to 100 (7) in which the temperature control load L is equal to or less than the rated operating capacity φgmax of the engine-driven compressor 11, the heat pumps 100 (1) to 100 (1) to which the electric compressor 12 is operating independently. The operating capacity φe of the electric compressor 12 at 100 (3) is limited (see β shown in FIG. 3).

  By doing so, the operating capacity of the electric compressor 12 can be limited without sacrificing the temperature control request, and in the heat pumps 100 (1) to 100 (3) during the independent operation of the electric compressor 12. In the heat pump 100 (3) in which the electric compressor 12 is operated at the operating capacity φe of the rated operating capacity φemax, the amount of reduction in power consumption of the electric compressor 12 that limits the operating capacity is smaller than the rated operating capacity φemax. The amount of power consumption of the electric compressor 12 in the heat pumps 100 (1) and 100 (2) operating at the capacity φe can be made larger. In the heat pumps 100 (1) and 100 (2) in which the electric compressor 12 is operated with an operating capacity φe smaller than the rated operating capacity φemax, the electric compressor 12 is operated with an operating capacity φe of the rated operating capacity φemax. Although the amount of power consumption of the electric compressor 12 in the heat pump 100 (3) is smaller than the amount of power consumption, the power consumption of the electric compressor 12 that limits the operating capacity φe can be reliably reduced. Such advantages can be obtained with the second priority next to the first priority.

<Rank in priority 2>
In the present embodiment, the control device 200 has a large operating capacity φe of the electric compressor 12 among the heat pumps 100 (1) to 100 (3) during the independent operation of the electric compressor 12 (see β shown in FIG. 3). The operating capacity φe of the electric compressor 12 is limited in the order of the heat pumps 100 (3), 100 (2), and 100 (1).

  In this way, the heat pump having a larger operating capacity φe of the electric compressor 12 (that is, operating with a large amount of power consumption) can easily exert the effect of limiting the operating capacity φe of the electric compressor 12. Thus, it is possible to easily function as a restriction (in this example, demand control) of the operating capacity φe of the electric compressor 12.

<Priority 3>
In the present embodiment, the control device 200 is operating both the engine-driven compressor 11 and the electric compressor 12 next to the heat pumps 100 (1) to 100 (3) during the independent operation of the electric compressor 12. Among the heat pumps 100 (4) to 100 (9), the temperature control load L of the heat pumps 100 (4) to 100 (9) [the sum of the operating capacity φg of the engine-driven compressor 11 and the operating capacity φe of the electric compressor 12 ( φg + φe)] is larger than the rated operating capacity φgmax of the engine-driven compressor 11 (operating capacity ratio Rg = 70%). The operating capacity φe of the electric compressor 12 in the heat pumps 100 (8), 100 (9) is limited. (See γ shown in FIG. 3).

  In this case, the operating capacity of the engine-driven compressor 11 is reduced until the operating capacity φg of the engine-driven compressor 11 reaches the rated operating capacity φgmax due to the limited amount of the electric compressor 12 that limits the operating capacity φe. The operating capacity φg of the engine driven compressor 11 exceeds the rated operating capacity φgmax, and the operating capacity φg of the engine driven compressor 11 cannot be covered by the operating capacity φg of the engine driven compressor 11. The temperature control request will be sacrificed. In this regard, in the present embodiment, the priority order for limiting the operating capacity φe of the electric compressor 12 in the heat pumps 100 (8) and 100 (9) that cause such a situation is set lower than the second priority described above. Therefore, the possibility of not sacrificing the temperature control request can be reduced as much as possible.

<Rank in priority 3>
In the present embodiment, control device 200 includes heat pumps 100 (4) to 100 (9) among heat pumps 100 (4) to 100 (9) operating both engine-driven compressor 11 and electric compressor 12. Among the heat pumps 100 (8) and 100 (9) (see γ shown in FIG. 3), the operating capacity of the engine-driven compressor 11 is higher than the rated operating capacity φgmax of the engine-driven compressor 11 The operating capacity φe of the electric compressor 12 is limited in the order of the heat pumps 100 (8) and 100 (9) with a margin of φg.

  By doing so, it is possible to reduce the frequency of shifting to the next priority order by the margin of the operating capacity φg of the engine-driven compressor 11.

  Further, even if the operation capacity φe of the electric compressor 12 in the heat pumps 100 (8) and 100 (9) with the priority 3 is limited, the control device 200 further remains when the power consumption suppression condition is satisfied. Heat pump 100 (10) [i.e., among the heat pumps 100 (4) to 100 (10) operating both the engine driven compressor 11 and the electric compressor 12, the operating capacity φg of the engine driven compressor 11 is the engine driven compression. The operating capacity φe of the electric compressor 12 in the heat pump 100 (10)] having the rated operating capacity φgmax of the machine 11 is limited.

  FIG. 5 is a chart collectively showing whether or not the temperature control request is sacrificed for the priority order of the heat pumps 100 (1) to 100 (10) by the demand control shown in FIG. 3 and the effect of suppressing the power consumption of the electric compressor 12. .

  As shown in FIG. 5, in the demand control shown in FIG. 3, the heat pumps 100 (4), 100 (5), 100 (6), 100 (7), 100 (3), 100 (2), 100 (1) , 100 (8), 100 (9), 100 (10) in this order, the operating capacity φe of the electric compressor 12 is limited. At this time, in the heat pumps 100 (1) to 100 (7), no matter what the operating capacity φe of the electric compressor 12 is limited, the temperature adjustment request is not sacrificed. In the heat pumps 100 (8) and 100 (9), depending on the limit amount of the operating capacity φe of the electric compressor 12, a sacrifice of the temperature adjustment request may occur. On the other hand, in the heat pump 100 (10), if the operating capacity φe of the electric compressor 12 is limited, the sacrifice of the temperature adjustment request occurs. Further, the degree of suppression of power consumption is large in heat pumps 100 (3) to 100 (9), medium in heat pump 100 (2), and small in heat pump 100 (1).

(Control operation of demand control)
Next, the control operation of demand control by the control device 200 in the temperature control system 300 will be described below with reference to FIG.

  FIG. 6 is a flowchart illustrating an example of a control operation of demand control by the control device 200 in the temperature control system 300.

  In the control operation of demand control shown in FIG. 6, first, the control device 200 constantly monitors demand information Dd including information indicating demand warning levels at a plurality of stages (step S1), and measures a predetermined demand time determined in advance. Is started (step S2).

  Next, when the control device 200 determines that the demand warning level has increased and has reached the operating capacity limit level that limits the operating capacity φe of the electric compressor 12 (step S3: Yes), the heat pump 100 (1 ) To 100 (n) to obtain driving information (step S4).

  Here, the operation information includes the temperature control load L, the operation capacity ratio (Rg: Re) between the engine drive compressor 11 and the electric compressor 12, the rated operation capacity φgmax of the engine drive compressor 11, and the rating of the electric compressor 12. It includes information such as the operating capacity φemax, the operating capacity φg of the engine-driven compressor 11, and the operating capacity φe of the electric compressor 12.

  Next, the control device 200 selects the priority order of the heat pumps 100 (1) to 100 (n) based on the operation information acquired in step S4 (step S5). This will be described taking the demand control shown in FIG. 3 as an example.

  That is, in step S5, the control device 200 operates the electric compressor 12 that can limit the operating capacity φe among the heat pumps 100 (1) to 100 (10) as the first priority priority 1, and the engine. The heat pumps 100 (1) to 100 (9) in which the operation capacity φg of the drive compressor 11 is smaller than the rated operation capacity φgmax of the engine drive compressor 11 are specified. The control device 200 specifies the heat pumps 100 (4) to 100 (9) that are operating both the engine-driven compressor 11 and the electric compressor 12 in the specified heat pumps 100 (1) to 100 (9). In the control device 200, the temperature control load L of the heat pumps 100 (4) to 100 (9) among the specified heat pumps 100 (4) to 100 (9) becomes equal to or less than the rated operating capacity φgmax of the engine drive compressor 11. The heat pumps 100 (4) to 100 (7) are specified. The control device 200 includes the heat pumps 100 (4), 100 (5), 100 (6), 100 (7) in which the operating capacity φg of the engine-driven compressor 11 is small among the identified heat pumps 100 (4) to 100 (7). ) In that order.

  In addition, the control device 200 identifies the heat pumps 100 (1) to 100 (3) during the independent operation of the electric compressor 12 as the second priority priority 2 that is prioritized after the first priority. The control device 200 selects the heat pumps 100 (3), 100 (2), and 100 (1) in the order from the heat pumps 100 (1) to 100 (3) that have the large operating capacity φe of the electric compressor 12.

  In addition, the control device 200 operates the electric compressor 12 capable of limiting the operating capacity φe among the heat pumps 100 (1) to 100 (10) as the third priority priority 3 that is given next to the second priority. Thus, the heat pumps 100 (1) to 100 (9) in which the operating capacity φg of the engine-driven compressor 11 is smaller than the rated operating capacity φgmax of the engine-driven compressor 11 are specified. The control device 200 specifies the heat pumps 100 (4) to 100 (9) that are operating both the engine-driven compressor 11 and the electric compressor 12 in the specified heat pumps 100 (1) to 100 (9). In the control device 200, the temperature control load L of the heat pumps 100 (4) to 100 (9) among the specified heat pumps 100 (4) to 100 (9) is larger than the rated operating capacity φgmax of the engine drive compressor 11. The heat pumps 100 (8) and 100 (9) are identified. The control device 200 selects the heat pumps 100 (8) and 100 (9) in the order from the identified heat pumps 100 (8) and 100 (9) in which the operating capacity φg of the engine-driven compressor 11 is small.

  In addition, the control device 200 has the remaining heat pump 100 (10) next to the third priority [that is, the heat pumps 100 (4) to 100 (10) that are operating both the engine-driven compressor 11 and the electric compressor 12. Among them, the heat pump 100 (10)] in which the operating capacity φg of the engine-driven compressor 11 is the rated operating capacity φgmax of the engine-driven compressor 11 is selected.

  Next, the control device 200 limits the operating capacity φe of the electric compressor 12 in the heat pump 100 (i) selected in step S5 (step S6). Here, the limit amount of the operating capacity φe of the electric compressor 12 increases as the demand warning level increases.

  Next, when the control device 200 determines that the demand warning level is not lower than the operating capacity limit level before a predetermined determination time (for example, about 5 minutes) elapses (step S7: No). On the other hand, if the processing from step S4 to step S7 is repeated and the demand warning level is determined to be lower than the operating capacity limit level by the time the predetermined determination time has elapsed (step S7: Yes), the process proceeds to step S3.

  Next, when it is determined in step S3 that the demand warning level has not reached the operating capacity limit level (step S3: No), the control device 200 determines a predetermined demand time (specifically, 30) from the start of measurement. (Step S8: No), the processing from step S3 to step S8 is repeated, and when a predetermined demand time has elapsed from the start of measurement (step S8: Yes), the electric compressor in the heat pump 100 (i) The restriction on the operating capacity φe of 12 is released (step S9), the measurement of a predetermined demand time is reset (step S10), and the process proceeds to step S3.

  In addition, the control apparatus 200 can control as follows, when a demand alert level exceeds a predetermined alert level. That is, the control device 200 operates the electric compressor 12 that can limit the operating capacity φe among the heat pumps 100 (1) to 100 (10), and the operating capacity φg of the engine-driven compressor 11 is the engine-driven compressor. The operating capacity φe of the electric compressor 12 in all the heat pumps 100 (1) to 100 (9) that is smaller than the rated operating capacity φgmax of 11 can be limited. And / or the control apparatus 200 shortens the interval of the determination time (for example, about 5 minutes) until it restrict | limits the operation capacity (phi) e of the electric compressor 12 in the following heat pump 100 (1) -100 (10) (for example, 2). In minutes).

  In the present embodiment, the number n of the heat pumps 100 (1) to 100 (n) has been described as 10 here, but of course, it may be 2 or more and 9 or less, or 11 or more.

  The present invention is not limited to the embodiment described above, and can be implemented in various other forms. Therefore, such an embodiment is merely an example in all respects and should not be interpreted in a limited manner. The scope of the present invention is shown by the scope of claims, and is not restricted by the text of the specification. Further, all modifications and changes belonging to the equivalent scope of the claims are within the scope of the present invention.

DESCRIPTION OF SYMBOLS 10 Compression part 11 Engine drive compressor 11a Clutch 12 Electric compressor 20 Heat source side heat exchanger 30 Heat source side heat exchanger fan 100 (i) Heat pump 101 Use side heat exchange part 102 Heat source side heat exchange part 102a Package 110 Refrigerant circuit 110a One communication pipe 110b The other communication pipe 111 Four-way valve 111a First refrigerant path 111b Second refrigerant path 111c Third refrigerant path 111d Fourth refrigerant path 120 Control unit 121 Processing unit 122 Storage unit 200 Control device 210 Processing unit 220 Storage unit 300 Temperature Control System 40 Regulating Valve 50 Use-side Heat Exchanger 60 Drive Source 61 Engine 62 Electric Motor Dd Demand Information Di Instruction Information Dr Operation Information E Measuring Means L Temperature Control Load M Demand Monitoring Device NT Communication Line Rg Engine Drive Compressor Operating capacity ratio Re Electric compressor operation Power ratio φe electric compressor operation capacity φemax electric compressor operating capacity φgmax rated operating capacity of the engine-driven compressor of the rated operation capacity φg engine-driven compressor of the

Claims (1)

A temperature control system including both an engine driven compressor and an electric compressor,
The engine-driven compressor and the electric compressor are housed in a common package, and the engine-driven compressor and the electric compressor have a plurality of heat pumps that share a refrigerant circuit for circulating the refrigerant.
When the power consumption suppression condition for suppressing the power consumption of the temperature control system is satisfied, the operating capacity of the engine-driven compressor is smaller than the rated operating capacity of the engine-driven compressor in the heat pump. A temperature control system that preferentially restricts the operating capacity of the electric compressor in the heat pump.

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