JP6134856B2 - Heat source equipment - Google Patents

Description

  The present invention relates to a heat source device including a plurality of heat source machines.

  2. Description of the Related Art A heat source device that includes a plurality of heat source devices and supplies hot or cold energy obtained by operating these heat source devices to a load side (use side) is known.

  The heat source machine takes in a heat medium (water, brine, etc.) by operating the pump, and heats or cools the captured heat medium by operating the heat pump refrigeration cycle.

  The heat source devices are connected in parallel to each other through a heat medium pipe, and the number of operating heat source devices is controlled according to the load.

JP 2008-224182 A

  When operating a plurality of heat source machines, the capacity of the pump of each heat source machine is controlled according to the required capacity on the load side.

  However, when the piping resistance of the plurality of heat source units to be operated is different from each other, there is a possibility that the flow rate of the heat medium flowing to each heat source unit will be different, and the pump of the heat source unit on the side with the lower flow rate may stall and stop abnormally .

  An object of the present embodiment is to provide a heat source device with excellent reliability capable of supplying an appropriate amount of hot or cold to the load side without causing an abnormal stop of the pump in the heat source machine.

The heat source device according to claim 1 is a heat medium heat exchanger through which a heat medium flows, a heat pump refrigeration cycle that heats or cools the heat medium in the heat medium heat exchanger, and a heat medium that sucks in a heat medium that has passed through a load side. A plurality of heat source devices including a pump that passes through a heat exchanger to the load side and is connected in parallel to each other; a first flow rate adjustment valve that adjusts the amount of the heat medium flowing to the load side; A flow rate detection unit that detects the amount of the heat medium that flows to the load side, a bypass pipe that bypasses the heat medium that flows to the load side, and a second flow rate adjustment that adjusts the amount of the heat medium that flows to the bypass pipe A first differential pressure detection unit that detects a pressure difference P of the heat medium between both ends of the valve, the bypass pipe, and a first differential pressure detection unit that detects the pressure difference Pw of the heat medium between both ends of each heat medium heat exchanger. 2 differential pressure detector and And a controller. A controller for detecting a load-side pipe resistance characteristic representing a relationship between an amount Q of the heat medium flowing to the load side and a pressure difference P of the heat medium between both ends of the bypass pipe; A first control unit that controls the number of operating heat source units and the opening of the first flow rate adjusting valve according to the required capacity on the side; the amount W of the heat medium that flows individually in each operating heat source unit In accordance with the detected flow difference Pw of the second pressure difference detection unit, the detected flow rate Qt of the flow rate detection unit and the load side pipe resistance characteristic detected by the first detection unit, A second control unit that controls the opening of the second flow rate adjustment valve; and the detected flow rate Qt of the flow rate detection unit is allocated to each of the heat source units that are in operation and assigned as the required flow rate Wt. Each detection flow rate W of the second detection unit is one. As to a third control unit for controlling the capacity of the pump in each of the heat source machines in operation; including.

The figure which shows the whole structure of one Embodiment. The figure which shows the structure of the refrigerating cycle of each heat-source equipment in one Embodiment. The flowchart which shows control of the controller in one Embodiment. The figure which shows the load side piping resistance characteristic in one Embodiment. The figure which shows the relationship between the flow volume of the water in each heat source machine of one Embodiment, and pump capability.

Hereinafter, an embodiment of a heat source device of the present invention will be described with reference to the drawings.
As shown in FIG. 1, load-side equipment is connected to a plurality of heat source units 1a, 1b,... 1n via a heat medium pipe (hereinafter referred to as water pipe) 2a and a heat medium pipe (hereinafter referred to as water pipe) 2b. For example, a plurality of air heat exchangers 3a, 3b,... 3n are connected. The heat source machines 1a, 1b,... 1n are connected in parallel to each other through the water pipes 2a, 2b. The air heat exchangers 3a, 3b,... 3n are also connected in parallel to each other through the water pipes 2a, 2b.

  The water pipe 2a includes a plurality of branch pipes 2aa, 2ab, ... 2an connected to the water inlets of the air heat exchangers 3a, 3b, ... 3n. The water pipe 2b includes a plurality of branch pipes 2ba, 2bb, ... 2bn connected to the water outlets of the air heat exchangers 3a, 3b, ... 3n.

  The heat source devices 1a, 1b,... 1n include a heat medium heat exchanger (water heat exchangers 60 and 30 described later), a heat pump refrigeration cycle, and a pump (a pump 80 described later), and a water pipe 2b passing through the load side. Water (heat medium) is introduced into the heat medium heat exchanger by the suction pressure of the pump, and the water in the heat medium heat exchanger is heated or cooled by the operation of the heat pump refrigeration cycle. The supplied water is supplied to the water pipe 2a by the discharge pressure of the pump.

  The air heat exchangers 3a, 3b,... 3n exchange the heat of the water flowing in from the water pipe 2a and the heat of the indoor air sent from the indoor fan, and flow out the water after the heat exchange to the water pipe 2b.

  .. 2bn are provided with variable flow rate adjusting valves (first flow rate adjusting valves) 4a, 4b,... 4n on the branch pipes 2ba, 2bb,. The flow rate adjusting valves 4a, 4b,... 4n adjust the amount of water flowing individually in the air heat exchangers 3a, 3b,.

  In the water pipe 2b, a flow rate sensor (flow rate detector) 5 is arranged at a position downstream of the branch pipes 2ba, 2bb,... 2bn. The flow sensor 5 detects the amount (total amount) of water flowing out from the air heat exchangers 3a, 3b,... 3n as the amount (total amount) of water flowing into the air heat exchangers 3a, 3b,.

  One end of the bypass pipe 6 is connected between the connection position of the heat source devices 1a, 1b,... 1n in the water pipe 2a and the connection position of the air heat exchangers 3a, 3b,. The other end of the bypass pipe 6 is connected to a position downstream of the flow rate sensor 5 in the water pipe 2b. The bypass pipe 6 bypasses the water flowing toward the air heat exchangers 3a, 3b, ... 3n from the heat source machines 1a, 1b, ... 1n and returns them to the heat source machines 1a, 1b, ... 1n side. A flow rate adjustment valve (second flow rate adjustment valve) 7 having a variable opening is disposed in the middle of the bypass pipe 6. The flow rate adjusting valve 7 is also referred to as a bypass valve, and adjusts the amount of water flowing through the bypass pipe 6 by changing the opening.

  When the flow rate adjustment valve 7 is fully closed, the water in the pipe 2 a flows to the load side without flowing into the bypass pipe 6. When the flow regulating valve 7 is opened, an amount of water in proportion to the opening of the flow regulating valve 7 out of the water in the pipe 2 a flows into the pipe 2 b through the bypass pipe 6. Of the water in the pipe 2a, the water that did not flow into the bypass pipe 6 flows to the load side.

  A differential pressure sensor 8 that is a first differential pressure detector is connected between both ends of the bypass pipe 6. The differential pressure sensor 8 detects a difference (pressure difference of water between both ends of the bypass pipe 6) P between the water pressure on one end side of the bypass pipe 6 and the water pressure on the other end side.

  As described above, the heat source units 1a, 1b,... 1n circulate water between the heat medium heat exchanger (water heat exchangers 60 and 30 described later) and the heat medium heat exchanger and the load side. A pump (a pump 80 described later) is provided, and water passing through the heat medium heat exchanger is heated or cooled by operation of a heat pump refrigeration cycle.

  FIG. 2 shows the configuration of the heat pump refrigeration cycle mounted on the heat source unit 1a. Each heat pump refrigeration cycle mounted on the heat source devices 1b,.

  The refrigerant discharged from the compressor 21 flows to the air heat exchangers 23a and 23b via the four-way valve 22, and the refrigerant passing through the air heat exchangers 23a and 23b passes through the electronic expansion valves 24a and 24b to the water heat exchanger (heat It flows to the first refrigerant flow path 30a of the medium heat exchanger 30). The refrigerant that has passed through the first refrigerant flow path 30 a is sucked into the compressor 21 through the four-way valve 22 and the accumulator 25. This refrigerant flow direction is at the time of cooling operation (cold water generation operation), and the air heat exchangers 23a and 23b function as condensers, and the first refrigerant flow path 30a of the water heat exchanger 30 functions as an evaporator. At the time of heating operation (warm water generation operation), the flow path of the four-way valve 22 is switched to reverse the flow direction of the refrigerant, and the first refrigerant flow path 30a of the water heat exchanger 30 is the condenser, the air heat exchanger 23a, 23b functions as an evaporator.

  The compressor 21, the four-way valve 22, the air heat exchangers 23a and 23b, the electronic expansion valves 24a and 24b, the first refrigerant flow path 30a of the water heat exchanger 30, and the accumulator 25 constitute a first heat pump refrigeration cycle. Is done.

  The refrigerant discharged from the compressor 41 flows to the air heat exchangers 43a and 43b via the four-way valve 42, and the refrigerant passing through the air heat exchangers 43a and 43b passes through the electronic expansion valves 44a and 44b. To the second refrigerant flow path 30b. The refrigerant that has passed through the second refrigerant flow path 30 b is sucked into the compressor 41 through the four-way valve 42 and the accumulator 45. This refrigerant flow direction is at the time of cooling operation (cold water generating operation), and the air heat exchangers 43a and 43b function as condensers, and the second refrigerant flow path 30b of the water heat exchanger 30 functions as an evaporator. At the time of heating operation (warm water generation operation), the flow path of the four-way valve 42 is switched to reverse the flow direction of the refrigerant, and the second refrigerant flow path 30b of the water heat exchanger 30 is the condenser, the air heat exchanger 43a, 43b functions as an evaporator.

  The compressor 41, the four-way valve 42, the air heat exchangers 43a and 43b, the electronic expansion valves 44a and 44b, the second refrigerant flow path 30b of the water heat exchanger 30, and the accumulator 45 constitute a second heat pump refrigeration cycle. Is done.

  The refrigerant discharged from the compressor 51 flows to the air heat exchangers 53a and 53b via the four-way valve 52, and the refrigerant passing through the air heat exchangers 53a and 53b passes through the electronic expansion valves 54a and 54b to the water heat exchanger (heat It flows to the first refrigerant flow path 60a of the medium heat exchanger 60). The refrigerant that has passed through the first refrigerant flow path 60 a is sucked into the compressor 51 through the four-way valve 52 and the accumulator 55. This refrigerant flow direction is at the time of cooling operation (cold water generation operation), the air heat exchangers 53a and 53b function as condensers, and the first refrigerant flow path 60a of the water heat exchanger 60 functions as an evaporator. During the heating operation (warm water generating operation), the flow path of the four-way valve 52 is switched to reverse the flow direction of the refrigerant, and the first refrigerant flow path 60a of the water heat exchanger 60 is the condenser, the air heat exchanger 53a, 53b functions as an evaporator.

  The compressor 51, the four-way valve 52, the air heat exchangers 53a and 53b, the electronic expansion valves 54a and 54b, the first refrigerant flow path 60a of the water heat exchanger 60, and the accumulator 55 constitute a third heat pump refrigeration cycle. Is done.

  The refrigerant discharged from the compressor 71 flows into the air heat exchangers 73a and 73b via the four-way valve 72, and the refrigerant passing through the air heat exchangers 73a and 73b passes through the electronic expansion valves 74a and 74b. To the second refrigerant flow path 60b. The refrigerant that has passed through the second refrigerant flow path 60 b is sucked into the compressor 71 through the four-way valve 72 and the accumulator 75. This refrigerant flow direction is at the time of cooling operation (cold water generating operation), and the air heat exchangers 73a and 73b function as condensers, and the second refrigerant flow path 60b of the water heat exchanger 60 functions as an evaporator. At the time of heating operation (warm water generating operation), the flow path of the four-way valve 72 is switched to reverse the flow direction of the refrigerant, and the second refrigerant flow path 60b of the water heat exchanger 60 is the condenser, the air heat exchanger 73a, 73b functions as an evaporator.

  The compressor 71, the four-way valve 72, the air heat exchangers 73a and 73b, the electronic expansion valves 74a and 74b, the second refrigerant flow path 60b of the water heat exchanger 60, and the accumulator 75 constitute a fourth heat pump refrigeration cycle. Is done.

  The water in the water pipe 2b flows through the water pipe 101 to the water flow path 60c of the water heat exchanger 60. The water flowing out from the water channel 60 c flows through the water pipe 102 to the water channel 30 c of the water heat exchanger 30. The water flowing out from the water channel 30c flows into the water pipe 2a. The water flow path 60 c of the water heat exchanger 60 and the water flow path 30 c of the water heat exchanger 30 are in a state of being connected in series via the water pipe 102.

  A pump 80 is disposed in the water pipe 101. The pump 80 sucks the water in the water pipe 2b into the water pipe 101, passes the sucked water through the water heat exchanger 60, the water pipe 102, the water heat exchanger 30, and the water pipe 103 and sends it out to the water pipe 2b. The pump 80 has a motor that is operated by the AC voltage supplied from the inverter 81, and the capacity (lift) changes according to the rotation speed of the motor. The inverter 81 rectifies the voltage of the commercial AC power supply 82, converts the rectified DC voltage into an AC voltage having a predetermined frequency by switching, and supplies the converted AC voltage as drive power to the motor of the pump 80. By changing the frequency (output frequency) F of the output voltage of the inverter 81, the rotational speed of the motor of the pump 80 changes.

  A differential pressure sensor 90 that is a second differential pressure detector is connected between the water pipe 101 and the water pipe 103 (between both ends of the water heat exchangers 60 and 30). The differential pressure sensor 90 detects a difference Pw between the pressure of water flowing into the water heat exchanger 60 and the pressure of water flowing out of the water heat exchanger 30. Based on the detected pressure difference Pw of the differential pressure sensor 90, the amount of water flowing to the water heat exchangers 60 and 30, that is, the amount Wa of water flowing to the heat source unit 1a can be detected.

  On the other hand, the controller 10 is connected to the heat source devices 1a, 1b,... 1n, the flow rate adjustment valves 4a, 4b,... 4n, the flow rate sensor 5, the flow rate adjustment valve 7, and the differential pressure sensor 8. These heat source units 1a, 1b,... 1n, water pipes 2a, 2b, flow rate adjusting valves 4a, 4b,... 4n, flow rate sensor 5, bypass pipe 6, flow rate adjusting valve 7, differential pressure sensor 8, and controller 10 Is configured.

  The controller 10 controls the operation of the heat source devices 1a, 1b,... 1n, the opening degree of the flow rate adjusting valves 4a, 4b,... 4n, and the opening degree of the flow rate adjusting valve 7. 11, a second detector 12, a first controller 13, a second controller 14, a third controller 15, and a memory 16.

  The first detection unit 11 operates the pumps 80 of the heat source devices 1a, 1b,..., 1n at their rated capacities (predetermined operating frequency F) during a trial operation after the heat source device is installed (after installation). Then, a load side pipe resistance characteristic (also referred to as a secondary side pipe resistance characteristic) representing the relationship between the amount Q of water flowing on the load side and the pressure difference P of water between both ends of the bypass pipe 6 is detected.

  The second detector 12 is operated by calculation based on the detected pressure difference Pw of each differential pressure sensor 90 in the heat source devices 1a, 1b,... 1n and the heat exchanger resistance characteristics in each of the heat source devices 1a, 1b,. The amount W of water flowing individually in each heat source machine is detected. The heat exchanger resistance characteristic is unique to the water heat exchangers 60 and 30, is actually measured in advance, and is stored in the memory 16 of the controller 10.

  The 1st control part 13 is heat source machine 1a, 1b, ... 1n according to the sum total of the required capacity | capacitance (difference between indoor air temperature Ta and set temperature Ts) of the air heat exchangers 3a, 3b, ... 3n of load side. , And the opening degree of the flow rate adjusting valves 4a, 4b,.

  The second control unit 14 detects the flow rate of the flow sensor 5 so that an optimal amount of water that matches the total required capacity of the air heat exchangers 3a, 3b,... 3n flows to the air heat exchangers 3a, 3b,. The opening degree of the flow rate adjusting valve (bypass valve) 7 is controlled in accordance with Qt and the load side pipe resistance characteristic detected by the first detection unit 11.

  The third control unit 15 allocates the detected flow rate Qt of the flow rate sensor 5 to each operating heat source unit among the heat source units 1a, 1b,. The capacity of the pump 80 (heat medium supply capacity) in each operating heat source apparatus is controlled so that the detected flow rates W of the second detection unit 12 coincide with Wt.

Next, the control executed by the controller 10 will be described with reference to the flowchart of FIG.
During the trial operation after the heat source device is installed (YES in step S1), the controller 10 detects the load-side pipe resistance characteristic by the following process (step S2).

  First, the controller 10 fully closes the flow rate adjustment valve 7 of the bypass pipe 6 and fully opens only the flow rate adjustment valve corresponding to the air heat exchanger having the largest pipe resistance among the flow rate adjustment valves 4a, 4b,. Fully close the remaining flow control valves. In this state, the controller 10 operates the pumps 80 of the heat source devices 1a, 1b,... 1n at their rated capacities (predetermined operating frequency F). ) A corresponding point (intersection) between Qn and the value Pn of the detected pressure difference P of the differential pressure sensor 8 is held in the memory 16 as the first characteristic point Sn shown in FIG. In this case, since the flow rate adjusting valve 7 is fully closed, all the water flowing out from the heat source units 1a, 1b,... 1n flows to the load side without being bypassed.

  As the air heat exchanger having the largest pipe resistance, for example, the air heat exchanger 3n existing at the end position where the pipe length from the heat source units 1a, 1b,. Alternatively, for example, the air heat exchanger 3b on the side closer to the heat source devices 1a, 1b,... 1n than the air heat exchanger 3n at the end position, the branch pipes 2ab, 2bb connected to the water pipes 2a, 2b are exchanged with other air. Depending on factors such as being thinner than the branch pipe on the vessel side, the air heat exchanger having the largest piping resistance may be selected in advance. The air heat exchanger having the largest piping resistance is selected based on the empirical rules and actual measurements of the workers when installing the heat source device. This selection result is stored in the memory 16 of the controller 10.

  Subsequently, the controller 10 fully opens all of the flow rate adjusting valves 4a, 4b,... 4n while the flow rate adjusting valve 7 of the bypass pipe 6 is fully closed. In this state, the controller 10 operates the pumps 80 of the heat source devices 1a, 1b,... 1n with their rated capacities, and the value (maximum flow rate) Qm of the detected flow rate Qt of the flow rate sensor 5 and the differential pressure sensor 8 at this time. The corresponding point (intersection) with the detected pressure difference P of Pm is held in the memory 16 as the second characteristic point Sm shown in FIG.

  Then, the controller 10 connects the held first characteristic point Sn and the second characteristic point Sm to “the amount Q of water flowing to the load side” and “the water pressure difference P between both ends of the bypass pipe 6”. A quadratic approximate curve that approximately represents the relationship is detected as a load-side piping resistance characteristic. The controller 10 stores the detected load side pipe resistance characteristic in the memory 16.

  On the other hand, during the normal operation after the trial operation is completed (NO in step S1), the controller 10 determines the required capacity of the load-side air heat exchangers 3a, 3b,... 3n (the difference between the indoor air temperature Ta and the set temperature Ts). ) And the opening degree of the flow rate adjusting valves 4a, 4b,... 4n are controlled (step S3).

  That is, the controller 10 increases the number of operating heat source units 1a, 1b,... 1n as the sum of the required capacities of the air heat exchangers 3a, 3b,... 3n increases, and requests the air heat exchangers 3a, 3b,. As the total capacity decreases, the number of operating heat source devices 1a, 1b,. Furthermore, the controller 10 increases the opening degree of the flow rate adjustment valve 4a (increases the flow rate) as the required capacity of the air heat exchanger 3a increases, and the flow rate adjustment valve 4a increases as the required capacity of the air heat exchanger 3a decreases. The opening degree of the is reduced (flow reduction). The opening degree of the flow rate adjusting valves 4b,... 4n corresponding to the air heat exchangers 3b,.

  Along with the execution number control and opening degree control, the flow rate sensor 5 detects the amount (total amount) Qt of water actually flowing to the air heat exchangers 3a, 3b,.

  The controller 10 obtains the “target pressure difference Pt of water between both ends of the bypass pipe 6” corresponding to the detected flow rate Qt of the flow sensor 5 from the load-side pipe resistance characteristics of FIG. S4). The controller 10 then opens the flow rate adjustment valve 7 so that the detected pressure difference of the differential pressure sensor 8 (pressure difference of water between both ends of the bypass pipe 6) P becomes the above-obtained target pressure difference Pt. Is controlled) (step S5).

  By setting the detected pressure difference P of the differential pressure sensor 8 to the target pressure difference Pt, an optimal amount of water corresponding to the total required capacity of the air heat exchangers 3a, 3b,. , ... flows to 3n. The excess water for the air heat exchangers 3a, 3b,..., 3n returns to one or more heat source units in operation through the bypass pipe 6.

  The controller 10 equally divides the detected flow rate Qt of the flow rate sensor 5 into one or a plurality of operating heat source units and assigns them as necessary flow rates Wt (step S6). For example, if the detected flow rate Qt of the flow sensor 5 is 1000 liters / h and the number of operating heat source devices 1a, 1b,... 1n is 5, 200 (= 1000/5) liters / h per heat source device Assigned as the required flow rate Wt. When the detected flow rate Qt of the flow sensor 5 is 1200 liters / h and the number of operating heat source devices 1a, 1b,... 1n is four, 300 (= 1200/4) liters / h is required per heat source device. Assigned as the flow rate Wt.

  The controller 10 detects the pressure difference Pw detected by the differential pressure sensor 90 in one or more heat source units in operation, and the water heat exchanger (the water heat exchanger 60, The amount W of water flowing individually in one or a plurality of heat source units in operation is detected by calculation based on the heat exchanger resistance characteristics of 30) (step S7).

  For example, when two heat source units 1a and 1b are in operation, the controller 10 reads the detected pressure difference Pwa of the differential pressure sensor 90 in the heat source unit 1a and the detected pressure difference Pwb of the differential pressure sensor 90 in the heat source unit 1b. The heat exchanger resistance characteristics in the heat source machine 1a and the heat exchanger resistance characteristics in the heat source machine 1b are read from the memory 16 and flow to the heat source machine 1a by calculation based on these detected pressure differences Pwa, Pwb and each heat exchanger resistance characteristic. The amount of water Wa and the amount of water Wb flowing to the heat source unit 1b are detected.

  The controller 10 controls the output frequency F of each inverter 81 in the heat source devices 1a and 1b so that the detected flow rates Wa and Wb respectively match the required flow rates Wt assigned to the heat source devices 1a and 1b (step S8). .

  Specifically, the controller 10 increases the output frequency F of the inverter 81 in the heat source unit 1a when the detected flow rate Wa is smaller than the necessary flow rate Wt allocated to the heat source unit 1a. Thereby, the capacity | capacitance of the pump 80 in the heat-source equipment 1a increases, and the quantity Wa of the water which flows into the heat-source equipment 1a changes to an increase direction. When the detected flow rate Wa is higher than the necessary flow rate Wt assigned to the heat source device 1a, the controller 10 decreases the output frequency F of the inverter 81 in the heat source device 1a. Thereby, the capacity | capacitance of the pump 80 in the heat-source equipment 1a reduces, and the flow volume Wa of the water which flows into the heat-source equipment 1a changes in the decreasing direction. When the detected flow rate Wa coincides with the required flow rate Wt assigned to the heat source unit 1a, the controller 10 holds the output frequency F of the inverter 81 in the heat source unit 1a at that time.

  Similarly, the controller 10 increases the output frequency F of the inverter 81 in the heat source unit 1b when the detected flow rate Wb is less than the required flow rate Wt allocated to the heat source unit 1b. When the detected flow rate Wb is larger than the necessary flow rate Wt assigned to the heat source device 1b, the controller 10 decreases the output frequency F of the inverter 81 in the heat source device 1b. When the detected flow rate Wb matches the required flow rate Wt assigned to the heat source device 1b, the controller 10 holds the output frequency F of the inverter 81 in the heat source device 1b at that time.

  The amount of water Wa, Wb,... Wn flowing through the heat source devices 1a, 1b,... 1n varies depending on the pipe resistance between the heat source devices 1a, 1b,. That is, the pipe resistance of the heat source device 1n existing at the end position farthest from the load side is large, and therefore the amount of water Wn flowing to the heat source device 1n is small. The pipe resistance of the heat source unit 1a on the side close to the load side is small, and therefore the amount of water Wa flowing to the heat source unit 1a is large.

  For example, when two heat source machines 1a and 1n are operating, the relationship between the amount of water Wa and Wn flowing through the heat source machines 1a and 1n and the capacity (pump capacity) of each pump 80 in the heat source machines 1a and 1n. FIG. 5 shows the heat exchanger resistances Ra and Rn in the heat source devices 1a and 1n as parameters. In order to make the amount Wa of the water flowing to the heat source unit 1a coincide with the required flow rate Wt assigned to the heat source unit 1a, the operating frequency F of the pump 80 in the heat source unit 1a may be set to a predetermined value Fa. In order to make the amount of water Wn flowing to the heat source device 1n at the end position coincide with the required flow rate Wt assigned to the heat source device 1n, the operating frequency F of the pump 80 in the heat source device 1n is set to a predetermined value Fn (> Fa). do it.

  Therefore, as described above, the amount (total amount) Qt of water flowing through the load-side air heat exchangers 3a, 3b,... 3n is detected, and the detected flow rate Qt is distributed to the operating heat source devices 1a, 1n, for example. By assigning the necessary flow rates Wt, and controlling the operating frequency F of each pump 80 in the heat source units 1a and 1n so that the water amounts Wa and Wn flowing through the heat source units 1a and 1n coincide with these necessary flow rates Wt. Even when the pipe resistance of the heat source unit 1a and the pipe resistance of the heat source unit 1n are different from each other, the amounts of water Wa and Wn flowing through the heat source units 1a and 1n can be made uniform.

  Since the amounts of water Wa and Wn flowing to the heat source devices 1a and 1n during operation become uniform, it is possible to prevent stalling and abnormal stop of each pump 80 in the heat source devices 1a and 1n. This makes it possible to always supply an appropriate amount of hot water or cold water to the air heat exchangers 3a, 3b,... 3n corresponding to the sum of the required capacities of the air heat exchangers 3a, 3b,.

  Since only the operating frequency F of each pump 80 is increased or decreased so as to obtain the required flow rate Wt, it is necessary to detect in advance the so-called heat source side pipe resistance characteristics (primary side pipe resistance characteristics) and the characteristics of each pump 80. Absent. Even in an installation environment where the heat source devices 1a, 1b,..., 1n are arranged in a complicated manner, it is not necessary to deal with countermeasures such as header construction for adjusting piping resistance and reverse turn piping.

[Modification]
In the embodiment described above, the heat source devices 1a, 1b,. The number of heat exchangers can be selected as appropriate.

  In the above-described embodiment, the case where the load-side device is an air heat exchanger has been described as an example, but the same can be applied to the case where the load-side device is, for example, a hot water storage tank.

  In the above-described embodiment, the amount of water flowing to the load side is detected, and the detected flow rate is equally divided and allocated to each operating heat source unit. However, even if it is not equal, each pump 80 is not stalled. Any distribution that can continue operation is acceptable.

  In the above embodiment, the load-side pipe resistance characteristic is detected by a trial operation after the installation of the heat source device. May be detected.

  In addition, the said embodiment and modification are shown as an example and are not intending limiting the range of invention. The novel embodiments and modifications can be implemented in various other forms, and various omissions, rewrites, and changes can be made without departing from the spirit of the invention. In these embodiments and modifications, the scope of the invention is included in the gist, and is included in the invention described in the claims and the equivalents thereof.

  The heat source device of the present invention can be used for an air conditioner, a water heater, and the like.

  1a, 1b, ... 1n ... heat source machine, 2a, 2b ... water pipe (heat medium pipe), 3a, 3b, ... 3n ... air heat exchanger (load side equipment), 4a, 4b, ... 4n ... Flow adjusting valve (first flow adjusting valve), 5 ... Flow sensor (flow detecting unit), 6 ... Bypass piping, 7 ... Flow adjusting valve (second flow adjusting valve), 8 ... Differential pressure sensor (first differential pressure detecting) Part), 10 ... controller, 11 ... first detection part, 12 ... second detection part, 13 ... first control part, 14 ... second control part, 15 ... third control part, 21, 41, 51, 71 ... Compressor, 30, 60 ... water heat exchanger (heat medium heat exchanger), 80 ... pump, 81 ... inverter, 82 ... commercial AC power supply, 90 ... differential pressure sensor (second differential pressure detector)

Claims (6)

A heat medium heat exchanger through which a heat medium flows, a heat pump refrigeration cycle for heating or cooling the heat medium in the heat medium heat exchanger, a heat medium that has passed through a load side is sucked through the heat medium heat exchanger, and the load A plurality of heat source devices including a pump for sending to the side and connected in parallel to each other ;
A first flow rate adjustment valve that adjusts the amount of the heat medium flowing to the load side;
A flow rate detector for detecting the amount of the heat medium flowing to the load side;
Bypass piping for bypassing the heat medium flowing to the load side;
A second flow rate adjustment valve that adjusts the amount of the heat medium flowing through the bypass pipe;
A first differential pressure detector that detects a pressure difference P of the heat medium between both ends of the bypass pipe;
A second differential pressure detector that detects a pressure difference Pw of the heat medium between both ends of each heat medium heat exchanger;
A controller,
Equipped with a,
The controller is
A first detector for detecting a load side pipe resistance characteristic representing a relationship between the amount Q of the heat medium flowing to the load side and the pressure difference P of the heat medium between both ends of the bypass pipe;
A first control unit for controlling the number of operating heat source units and the opening of the first flow rate adjustment valve according to the required capacity on the load side;
A second detection unit that detects the amount W of the heat medium individually flowing in each heat source unit during operation based on the detected pressure difference Pw of the second pressure difference detection unit;
A second control unit that controls the opening of the second flow rate adjustment valve according to the detected flow rate Qt of the flow rate detection unit and the load-side piping resistance characteristic detected by the first detection unit;
The detected flow rate Qt of the flow rate detection unit is allocated to each of the heat source devices in operation and assigned as the required flow rate Wt, and the detected flow rate W of the second detection unit matches the required flow rate Wt. A third control unit for controlling the capacity of the pump in each of the heat source units;
including,
A heat source device characterized by that. The first flow rate adjusting valve adjusts the amount of the heat medium flowing to the load side by changing the opening;
The bypass pipe bypasses the heat medium flowing from the heat source devices toward the load side and returns to the heat source device side.
The second flow rate adjustment valve adjusts the amount of the heat medium flowing through the bypass pipe by changing the opening;
The heat source device according to claim 1 . The heat source device according to claim 1, wherein the first detection unit detects the load-side pipe resistance characteristic during a trial operation. The second detection unit is configured to determine the amount W of the heat medium flowing individually in each heat source unit in operation, the detected pressure difference Pw of the second differential pressure detection unit, and the heat exchanger resistance characteristic in each heat source unit. The heat source device according to claim 1 , wherein the detection is based on the following. The flow rate detection unit detects the total amount of the heat medium flowing through a plurality of devices connected in parallel to each other on the load side;
2. The heat source device according to claim 1, wherein the first flow rate adjustment valve is a plurality of first flow rate adjustment valves, and adjusts the amount of the heat medium that flows individually in each of the devices by a change in opening degree. . The first detection unit includes:
During the trial operation of the heat source device, the second flow rate adjustment valve is fully closed and only one of the first flow rate adjustment valves corresponding to the device having the largest piping resistance among the devices is fully opened and the remaining one or A plurality of the first flow rate adjusting valves are fully closed, and in this state, the pumps in the heat source devices are operated with a rated capacity. The corresponding point with the value Pn of the detected pressure difference P of the pressure detector is held as the first characteristic point Sn,
Subsequently, with the second flow rate adjustment valve fully closed, all the first flow rate adjustment valves are fully opened, and in this state, the pumps in the heat source units are operated with rated capacity, A corresponding point between the value Qm of the detected flow rate Qt of the flow rate detector and the value Pm of the detected pressure difference P of the first differential pressure detector is held as a second characteristic point Sm,
Connecting the held first characteristic point Sn and the second characteristic point Sm, approximately the relationship between “the amount Q of water flowing to the load side” and “the water pressure difference P between both ends of the bypass pipe 6”. A quadratic approximate curve is detected as the load side pipe resistance characteristic,
The heat source device according to claim 5 .

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