KR20160096691A - Heat source device - Google Patents

Abstract

The controller controls the number of operations of the plurality of heat sources and the flow rate of the heat medium to the load side according to the required capability of the load side. The controller detects the amount of heat medium flowing on the load side and controls the amount of bypass of the heat medium flowing on the load side according to the detected flow rate. The controller allocates the sensing flow rate to each heat source during operation and allocates it, and controls the ability of the pump in each heat source during operation according to the assigned flow rate.

Description

HEAT SOURCE DEVICE

The present invention relates to a heat source device having a plurality of heat sources.

There is known a heat source device which has a plurality of heat source units and supplies heat or cold heat obtained by operation of these heat source units to the load side (use side).

The heat source unit blows a heating medium (such as water or brine) by the operation of the pump and heats or heats the introduced heating medium by the operation of the heat pump type refrigeration cycle.

The respective heat source groups are connected in parallel to each other via the heat medium pipe, and the number of operation of these heat source units is controlled in accordance with the load.

Japanese Patent Application Laid-Open No. 2008-224182

When a plurality of heat sources are operated, the capability of the pump of each heat source is controlled according to the required capacity of the load side.

However, when the piping resistances of the plurality of heat sources to be operated are different from each other, there is a difference in the flow rate of the heat medium flowing in each heat source unit, so that the pump of the heat source unit having a smaller flow rate stalls and there is a possibility of an abnormal stop.

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

The heat source device according to claim 1 includes: a plurality of heat source units for supplying a heating medium to a load side; a first flow rate adjusting valve for adjusting an amount of the heating medium flowing to the load side; A bypass pipe for bypassing the heat medium flowing to the load side, a second flow rate adjusting valve for adjusting an amount of the heat medium flowing through the bypass pipe, and a controller. The controller controls the number of operations of the respective heat sources and the adjustment amount of the first flow rate adjusting valve in accordance with the demanded capability of the load side and adjusts the adjustment amount of the second flow rate adjustment valve in accordance with the detected flow rate of the flow rate detection unit And distributes and allocates the detected flow rate of the flow rate detecting unit to each of the heat source units in operation and controls the supply capability of the heat medium in each of the heat source units in operation according to the allocated amount.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a diagram showing an overall configuration of an embodiment; Fig.
2 is a diagram showing the configuration of a refrigeration cycle of each heat source in one embodiment;
3 is a flow chart showing control of the controller in one embodiment;
4 is a view showing a load-side piping resistance characteristic in an embodiment.
5 is a diagram showing the relationship between the flow rate of water and the pump capacity in each heat source unit in one embodiment;

Hereinafter, one embodiment of the heat source device of the present invention will be described with reference to the drawings.

(Hereinafter referred to as a water piping) 2a and a heating medium piping (hereinafter referred to as a water piping) 2b are connected to a plurality of heat sources 1a, 1b, ... 1n, For example, a plurality of air heat exchangers (3a, 3b, ... 3n) are connected to the load side. The heat source units 1a, 1b, ... 1n are connected in parallel to each other via the water pipes 2a, 2b. The air heat exchangers 3a, 3b, ... 3n are also connected in parallel to each other via the water pipes 2a, 2b.

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

The heat source units 1a, 1b, ... 1n are provided with a heat medium heat exchanger (water heat exchangers 60 and 30 described later), a heat pump type refrigeration cycle and a pump (a pump 80 described later) Water (heat medium) in the water pipe 2b is introduced into the heat medium heat exchanger by the suction pressure of the pump, and water in the heat medium heat exchanger is heated or cooled by the operation of the heat pump type refrigeration cycle, And a 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 from the water pipe 2a and the heat of the room air discharged from the indoor fan, and the water after the heat exchange flows out to the water pipe 2b.

(First flow rate adjusting valves) 4a, 4b, ... 4n, which are variable in opening degree, are disposed in the branch pipes 2ba, 2bb, ... 2bn of the water pipe 2b. The flow control valves 4a, 4b, ... 4n adjust the amount of water flowing through each of the air heat exchangers 3a, 3b, ... 3n by changing the opening degree.

In the water pipe 2b, a flow rate sensor (flow rate detecting portion) 5 is disposed at a position on the downstream side of the branch pipes 2ba, 2bb, ... 2bn. The flow sensor 5 calculates the amount of water (total amount) flowing out of the air heat exchangers 3a, 3b, ... 3n as the amount of water (total amount) Qt flowing in the air heat exchangers 3a, 3b, ... 3n Detection.

One end of the bypass pipe 6 is connected between the connecting positions of the heat sources 1a, 1b, ... 1n in the water pipe 2a and the connecting positions of the air heat exchangers 3a, 3b, ... 3n, do. The other end of the bypass pipe 6 is connected to a position on the downstream side of the flow rate sensor 5 in the water pipe 2b. The bypass piping 6 bypasses water flowing from the heat source units 1a to 1n to the air heat exchangers 3a to 3n and supplies the water to the heat sources 1a to 1n Back. A flow regulating valve (second flow regulating valve) 7 of variable opening degree is disposed in the middle portion of this bypass piping 6. The flow control 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 degree.

When the flow regulating valve 7 is fully closed, the water in the piping 2a flows to the load side without flowing into the bypass piping 6. An amount of water in proportion to the degree of opening of the flow rate adjusting valve 7 in the water in the pipe 2a flows into the pipe 2b through the bypass pipe 6 when the flow rate adjusting valve 7 is opened . The water in the pipe 2a that has not flowed into the bypass pipe 6 flows to the load side.

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

As described above, the heat source units 1a, 1b, ... 1n include a heat medium heat exchanger (water heat exchangers 60 and 30 described later) and a pump for circulating water between the heat medium heat exchanger and the load side Pump 80) so that the water passing through the heat medium-water heat exchanger is heated or cooled by the operation of the heat pump type refrigeration cycle.

Fig. 2 shows the structure of a heat pump type refrigeration cycle mounted on the heat source 1a. Also, each heat pump type refrigeration cycle mounted on the heat source units 1b, ... 1n has the same configuration.

The refrigerant discharged from the compressor 21 flows into the air heat exchangers 23a and 23b through the four-way valve 22 and the refrigerant passing through the air heat exchangers 23a and 23b flows through the electronic expansion valves 24a and 24b, Flows into the first refrigerant passage (30a) of the heat exchanger (heat medium heat exchanger) (30). The refrigerant passing through the first refrigerant passage 30a passes through the four-way valve 22 and the accumulator 25 and is sucked into the compressor 21. [ The air heat exchangers 23a and 23b function as a condenser and the first refrigerant flow path 30a of the water heat exchanger 30 functions as an evaporator. In the heating operation (hot water generation operation), the flow path of the four-way valve 22 is switched and the flow direction of the refrigerant is reversed so that the first refrigerant flow path 30a of the water heat exchanger 30 is connected to the condenser and the air heat exchanger 23a, and 23b function as an evaporator.

The first refrigerant passage 30a and the accumulator 25 of the compressor 21, the four-way valve 22, the air heat exchangers 23a and 23b, the electronic expansion valves 24a and 24b, the water heat exchanger 30, The first heat pump type refrigeration cycle is constituted.

The refrigerant discharged from the compressor 41 flows to the air heat exchangers 43a and 43b through the four-way valve 42 and the refrigerant passing through the air heat exchangers 43a and 43b flows through the electronic expansion valves 44a and 44b And flows into the second refrigerant passage 30b of the water heat exchanger 30. [ The refrigerant passing through the second refrigerant passage 30b passes through the four-way valve 42 and the accumulator 45 and is sucked into the compressor 41. [ The air heat exchangers 43a and 43b function as a condenser and the second refrigerant flow path 30b of the water heat exchanger 30 functions as an evaporator when the refrigerant flow direction is a cooling operation (cold water generating operation). In the heating operation (hot water generation operation), the flow path of the four-way valve 42 is switched so that the flow direction of the refrigerant is reversed and the second refrigerant flow path 30b of the water heat exchanger 30 is connected to the condenser, 43a, 43b function as an evaporator.

The first refrigerant passage 30b and the second refrigerant passage 30b of the water heat exchanger 30 and the accumulator 45 are connected to the compressor 41, the four-way valve 42, the air heat exchangers 43a and 43b, the electronic expansion valves 44a and 44b, The second heat pump type refrigeration cycle is constituted.

The refrigerant discharged from the compressor 51 flows to the air heat exchangers 53a and 53b through the four-way valve 52 and the refrigerant passing through the air heat exchangers 53a and 53b flows through the electronic expansion valves 54a and 54b, Flows into the first refrigerant passage (60a) of the heat exchanger (heat medium heat exchanger) (60). The refrigerant passing through the first refrigerant passage (60a) passes through the four-way valve (52) and the accumulator (55) and is sucked into the compressor (51). The air heat exchangers 53a and 53b function as a condenser and the first refrigerant passage 60a of the water heat exchanger 60 functions as an evaporator. In the heating operation (hot water generating operation), the flow path of the four-way valve 52 is switched so that the flow direction of the refrigerant is reversed and the first refrigerant passage 60a of the water heat exchanger 60 is connected to the condenser, 53a and 53b function as an evaporator.

The first refrigerant passage 60a and the accumulator 55 of the compressor 51, the four-way valve 52, the air heat exchangers 53a and 53b, the electronic expansion valves 54a and 54b, the water heat exchanger 60, The third heat pump type refrigeration cycle is constituted.

The refrigerant discharged from the compressor 71 flows to the air heat exchangers 73a and 73b through the four-way valve 72 and the refrigerant passing through the air heat exchangers 73a and 73b flows through the electronic expansion valves 74a and 74b To the second refrigerant passage (60b) of the water heat exchanger (60). The refrigerant passing through the second refrigerant passage 60b passes through the four-way valve 72 and the accumulator 75 and is sucked into the compressor 71. [ The air heat exchangers 73a and 73b function as a condenser and the second refrigerant passage 60b of the water heat exchanger 60 functions as an evaporator. In the heating operation (hot water generating operation), the flow path of the four-way valve 72 is switched so that the flow direction of the refrigerant is reversed, and the second refrigerant passage 60b of the water heat exchanger 60 is connected to the condenser, 73a, 73b function as an evaporator.

The first refrigerant passage 60b and the second refrigerant passage 60b of the compressor 71, the four-way valve 72, the air heat exchangers 73a and 73b, the electronic expansion valves 74a and 74b, The fourth heat pump type refrigeration cycle is constituted.

The water in the water pipe 2b flows into the water channel 60c of the water heat exchanger 60 through the water pipe 101. [ Water flowing out of the water passage 60c flows into the water passage 30c of the water heat exchanger 30 through the water pipe 102. [ Water flowing out of the water passage 30c flows into the water pipe 2a. The water passage 60c of the water heat exchanger 60 and the water passage 30c of the water heat exchanger 30 are 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 and supplies the sucked water to the water heat exchanger 60, the water pipe 102, the water heat exchanger 30, 103 to the water pipe 2b. The pump 80 has a motor operated by the AC voltage supplied from the inverter 81, and the capacity (head) varies according to the number of revolutions of the motor. The inverter 81 rectifies the voltage of the commercial AC power source 82, converts the rectified DC voltage to an AC voltage of a predetermined frequency by switching, converts the converted AC voltage to driving power for the motor of the pump 80 . By changing the frequency (output frequency) F of the output voltage of the inverter 81, the number of rotations of the motor of the pump 80 is changed.

A differential pressure sensor 90, which is a second differential pressure detecting part, is connected between the water pipe 101 and the water pipe 103 (between both ends of the water heat exchanger 60, 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. [ It is possible to detect the amount of water flowing in the water heat exchangers 60 and 30, that is, the amount Wa of the water flowing in the heat source 1a, based on the detection pressure difference Pw of the differential pressure sensor 90.

On the other hand, the controller 10 is connected to the heat source units 1a, 1b, ... 1n, the flow rate regulating valves 4a, 4b, ... 4n, the flow rate sensor 5, the flow rate regulating valve 7, . The flow rate control valves 4a, 4b, ... 4n, the flow rate sensor 5, the bypass piping 6, the flow rate adjusting valves 7a, 7b, ..., ), The differential pressure sensor 8, and the controller 10 constitute a heat source device.

The controller 10 controls the operation of the heat sources 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, The first control unit 13, the second control unit 14, the third control unit 15, and the memory 16 as functions of the first detection unit 11, the second detection unit 12,

The first detection unit 11 is configured to set each of the pumps 80 of the heat sources 1a, 1b, ... 1n to rated power (predetermined operating frequency F) at the time of trial operation after the heat source device is installed Side piping resistance characteristic (also referred to as secondary piping resistance characteristic) indicating the relationship between the amount Q of water flowing to the load side and the pressure difference P of water between both ends of the bypass piping 6 is detected do.

The second detecting section 12 detects the difference between the detection pressure Pw of the respective differential pressure sensors 90 in the heat sources 1a, 1b, ... 1n and the detection pressure difference Pw of the respective heat sources 1a, 1b, ... 1n The amount W of water flowing in each of the heat source units during operation is detected by calculation based on the heat exchanger resistance characteristic. The heat exchanger resistance characteristics are inherent to the water heat exchangers 60 and 30 and are actually measured and stored in the memory 16 of the controller 10. [

The first control unit 13 controls the temperature of the heat source 1a (1b) according to the total sum of the required capacity (difference between the indoor air temperature Ta and the set temperature Ts) of the air heat exchangers 3a, 3b, ... 3n on the load side 1b, ... 1n, and the opening degrees of the flow control valves 4a, 4b, ... 4n.

The second control unit 14 controls the flow rate of the air to be supplied to the air heat exchangers 3a, 3b, ..., 3n so that the optimum amount of water suitable for the total sum of the required capacities of the air heat exchangers 3a, The opening degree of the flow control valve (the bypass valve) 7 is controlled in accordance with the detection flow rate Qt of the flow rate control valve 5 and the load-side pipe resistance characteristic detected by the first detection unit 11. [

The third control unit 15 distributes the detected flow rate Qt of the flow rate sensor 5 to each of the heat source units in operation among the heat source units 1a, 1b, ... 1n to equalize the required flow rate Wt) and the capacity of the pump 80 (supply capacity of the heat medium) in each heat source during operation so that the respective detected flow W of the second detection part 12 coincides with the assigned flow rate Wt, .

Next, the control executed by the controller 10 will be described with reference to the flowchart of Fig.

Upon commissioning (in step S1) after the heat source device is installed, the controller 10 detects the load-side pipe resistance characteristic by the following process (step S2).

First, the controller 10 completely closes the flow rate adjusting valve 7 of the bypass pipe 6, and furthermore, determines the flow rate corresponding to the air heat exchanger having the largest pipe resistance among the flow rate adjusting valves 4a, 4b, ... 4n Only the control valve is fully open and the remaining flow control valve is fully closed. In this state, the controller 10 operates the respective pumps 80 of the heat sources 1a, 1b, ... 1n with rated power (predetermined operating frequency F), and the flow sensor 5 (Intersection point) between the value (minimum flow rate) Qn of the detection flow rate Qt of the differential pressure sensor 8 and the value Pn of the detection pressure difference P of the differential pressure sensor 8 is the first characteristic point Sn To the memory 16 as shown in FIG. In this case, since the flow regulating valve 7 is completely closed, all of the water flowing out of the heat sources 1a, 1b, ... 1n flows to the load side without being bypassed.

The air heat exchanger 3n in which the piping length from the heat sources 1a, 1b, ... 1n is the longest end position is selected in advance as the air heat exchanger having the largest piping resistance. The air heat exchanger 3b closer to the heat source 1a, 1b, ... 1n than the air heat exchanger 3n at the end position is connected to the branch pipes 2a, 2b connected to the water pipes 2a, 2ab, and 2bb is smaller than the other branch pipes on the side of the air heat exchanger, it may be preliminarily selected as the air heat exchanger having the largest piping resistance. The selection of the air heat exchanger having the largest piping resistance is made on the basis of empirical rules and actual measurements at the time of installation of 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 regulating valves 4a, 4b, ... 4n with the flow regulating valve 7 of the bypass pipe 6 fully closed. In this state, the controller 10 operates the respective pumps 80 of the heat sources 1a, 1b, ... 1n with their respective rated powers and calculates the value of the detected flow rate Qt of the flow sensor 5 at this time (Intersection point) between the value (maximum flow rate) Qm of the differential pressure sensor 8 and the value Pm of the detection pressure difference P of the differential pressure sensor 8 is stored in the memory 16 as the second characteristic point Sm shown in Fig. 4 .

The controller 10 connects the held first characteristic point Sn with the second characteristic point Sm to determine the relationship between the amount of water flowing on the load side Q and the distance between the both ends of the bypass pipe 6 The controller 10 detects a second approximate curve that approximates the relationship between the water pressure difference P of the water on the load side and the water pressure difference P of the water on the load side.

On the other hand, when the normal operation after the trial operation is completed (NO in step S1), the controller 10 calculates the demanded capacity (indoor air temperature Ta and set temperature) of the air heat exchangers 3a, 4b, ... 4n) of the heat sources 1a, 1b, ... 1n is controlled in accordance with the total sum of the flow rate control valves 4a, 4b, ... 4n.

That is, the controller 10 increases the number of heat sources 1a, 1b, ... 1n as the total sum of the demand capacities of the air heat exchangers 3a, 3b, ... 3n increases, 3b, ..., 3n is reduced, the number of heat sources 1a, 1b, ... 1n is reduced. In addition, the controller 10 increases the opening degree of the flow rate adjusting valve 4a (increases the flow rate) as the demanded capacity of the air heat exchanger 3a increases, and as the required capacity of the air heat exchanger 3a becomes smaller, The opening degree of the valve 4a is reduced (the flow rate is reduced). The opening degrees of the flow rate regulating valves 4b to 4n corresponding to the air heat exchangers 3b to 3n are similarly controlled.

The amount of water (total amount) Qt actually flowing in the air heat exchangers 3a, 3b, ... 3n is detected by the flow rate sensor 5 in accordance with the execution of the drive logarithmic control and the opening degree control.

The controller 10 detects the target pressure difference Pt of the water between the both ends of the bypass pipe 6 corresponding to the detected flow rate Qt of the flow sensor 5 at the time of trial operation and stores (Step S4). The controller 10 calculates the target pressure difference Pt so that the detected pressure difference (pressure difference between water at both ends of the bypass pipe 6) P of the differential pressure sensor 8 becomes the obtained target differential pressure Pt, (The amount of bypass of the water) of the opening 7 (step S5).

By setting the detection pressure difference P of the differential pressure sensor 8 to the target pressure difference Pt, an optimum amount of water suitable for the total sum of the demand capacities of the air heat exchangers 3a, 3b, ... 3n is supplied to the air Flows into the heat exchangers 3a, 3b, ... 3n. The excess water in the air heat exchangers (3a, 3b, ... 3n) passes through the bypass pipe (6) and returns to one or more heat sources during operation.

The controller 10 allocates the detected flow rate Qt of the flow rate sensor 5 to the one or more heat source units during operation as the required flow rate Wt of each of the uniform resolution units (step S6). For example, when the detected flow rate Qt of the flow sensor 5 is 1000 liters / h and the number of operations of the heat sources 1a, 1b, ... 1n is 5, 200 (= 1000/5) liters / h As a required flow rate Wt per one heat source period. When the detected flow rate Qt of the flow sensor 5 is 1200 liters / h and the number of the heat sources 1a, 1b ... 1n is 4, 300 (= 1200/4) liters / And is allocated as a required flow rate Wt per unit.

The controller 10 determines whether or not the detection pressure difference Pw of the differential pressure sensor 90 in one or more heat sources during operation and the difference between the detection pressure difference Pw of the water heat exchanger (Step S7) by calculation based on the heat exchanger resistance characteristics of the heat exchanger (60, 30) in operation.

For example, when the two heat sources 1a and 1b are in operation, the controller 10 determines whether or not the detection pressure difference Pwa of the differential pressure sensor 90 in the heat source 1a and the detection pressure difference Pwa of the heat source 1b The detection pressure difference Pwb of the differential pressure sensor 90 in the heat source 1a and the heat exchanger resistance characteristic in the heat source 1b are stored in the memory 16 And calculates the amount Wa of the water flowing in the heat source 1a and the amount of water flowing in the heat source 1b by the calculation based on the detection pressure differences Pwa and Pwb and the characteristics of the heat exchanger resistance Wb.

The controller 10 controls each of the inverters 81 of the heat sources 1a and 1b so that the detected flow rates Wa and Wb coincide with the required flow rates Wt assigned to the heat sources 1a and 1b, (Step S8).

Specifically, when the detected flow rate Wa is smaller than the required flow rate Wt assigned to the heat source 1a, the controller 10 sets the output frequency of the inverter 81 in the heat source 1a F). As a result, the ability of the pump 80 in the heat source 1a increases and the amount Wa of water flowing in the heat source 1a changes in the increasing direction. The controller 10 decreases the output frequency F of the inverter 81 in the heat source 1a when the detected flow rate Wa is larger than the required flow rate Wt assigned to the heat source 1a . As a result, the ability of the pump 80 in the heat source 1a is reduced, and the flow rate Wa of the water flowing in the heat source 1a changes in the decreasing direction. When the detected flow rate Wa agrees with the required flow rate Wt assigned to the heat source 1a, the controller 10 calculates the output frequency of the inverter 81 in the heat source 1a at that time F).

Likewise, when the detected flow rate Wb is smaller than the required flow rate Wt assigned to the heat source 1b, the controller 10 calculates the output frequency F of the inverter 81 in the heat source 1b, . The controller 10 decreases the output frequency F of the inverter 81 in the heat source 1b when the detected flow rate Wb is larger than the required flow rate Wt assigned to the heat source 1b . When the detected flow rate Wb coincides with the required flow rate Wt assigned to the heat source 1b, the controller 10 calculates the output frequency of the inverter 81 in the heat source 1b at that time F).

In addition, the amounts of water (Wa, Wb, ... Wn) flowing to the heat source units 1a, 1b, ... 1n differ depending on the pipe resistance between the heat sources 1a, 1b, ... 1n and the load side. That is, the piping resistance of the heat source 1n at the farthest end position from the load side is large, and therefore the amount Wn of water flowing to the heat source 1n becomes a small amount of flow. The pipe resistance of the heat source 1a close to the load side is small and therefore the amount Wa of the water flowing to the heat source 1a becomes a large flow rate.

The amount of water (Wa, Wn) flowing through the heat sources 1a and 1n and the amount of water flowing through each of the heat sources 1a and 1n in the heat sources 1a and 1n 5 shows the relationship between the capacity (pump capacity) of the heat sources 1a and 1n and the heat exchanger resistance Ra and Rn in the heat source units 1a and 1n as parameters. The operation frequency F of the pump 80 in the heat source 1a is set to be equal to the required flow rate Wt assigned to the heat source 1a of the heat source 1a, May be set to a predetermined value Fa. In order to match the amount Wn of water flowing in the heat source 1n at the end position with the required flow rate Wt assigned to the heat source 1n, the operation of the pump 80 in the heat source 1n The frequency F may be set to a predetermined value Fn (> Fa).

Therefore, it is possible to detect the amount (total amount) Qt of the water flowing in the air heat exchangers 3a, 3b, ... 3n on the load side as described above and detect the detected flow rate Qt, 1n are allocated as the required flow rates Wt and the heat sources 1a and 1n are controlled so that the amounts of water flowing in the heat source units 1a and 1n coincide with the required flow rates Wt, Even if the piping resistance of the heat source 1a and the piping resistance of the heat source 1n are different from each other by controlling the operation frequency F of each pump 80 in the heat sources 1a and 1n, The amounts Wa and Wn of the water flowing in the first and second passages can be made uniform.

The amounts Wa and Wn of the water flowing in the heat source units 1a and 1n during operation are made uniform so that stall and abnormal stopping of the pumps 80 in the heat sources 1a and 1n can be prevented. This makes it possible to supply the appropriate amount of hot water or cold water to the air heat exchangers 3a, 3b, ... 3n in accordance with the total sum of the required capacities of the air heat exchangers 3a, 3b, ... 3n.

Since only the operation frequency F of each pump 80 is increased or decreased so that the required flow rate Wt can be obtained, the so-called heat source side pipe resistance characteristic (primary pipe resistance characteristic) and the characteristic of each pump 80 are detected You do not need to. Even in an installation environment in which the heat sources 1a, 1b, ... 1n are complicatedly arranged, a countermeasure treatment such as a header construction for setting the piping resistance or a reverse turn piping is not required.

[Modifications]

In the above embodiment, the heat source units 1a, 1b, ... 1n having four heat pump type refrigeration cycles and two water heat exchangers 30, 60 are described as an example. However, in each heat source unit, The number of water heat exchangers and the number of water heat exchangers can be appropriately selected.

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

In the above embodiment, the amount of water flowing on the load side is detected, and the detection flow rate is allocated to each heat source during operation. However, even if the amount is not even, .

In the above embodiment, the load-side piping resistance characteristic is detected by trial operation after the installation of the heat source device. However, the present invention is not limited thereto, and the load-side piping resistance characteristic may be detected at the time of the expansion of the air- .

In addition, the above-described embodiments and modifications are provided by way of example, and are not intended to limit the scope of the invention. This new embodiment and modifications can be implemented in various other forms, and various omissions, modifications, and alterations can be made without departing from the gist of the invention. These embodiments and modifications are included in the scope of the invention and are included in the scope of equivalents to the invention described in claims.

[Industrial applicability]

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

1a, 1b, ... 1n ... : Heat source unit, 2a, 2b: water pipe (heat medium pipe), 3a, 3b, ... 3n ... : Air heat exchanger (load side device), 4a, 4b, ... 4n ... 6: Bypass piping 7: Flow rate regulating valve (second flow rate regulating valve) 8: Differential pressure sensor (first differential pressure detecting section) 7: Flow rate adjusting valve (first flow rate adjusting valve) The present invention relates to a compressor and a method of controlling the same in a compressor and a compressor and a method of controlling the same. (Heat medium exchanger), 80: pump, 81: inverter, 82: commercial AC power source, 90: differential pressure sensor (second differential pressure detector)

Claims (10)

A plurality of heat source units for supplying the heat medium to the load side,
A first flow rate adjusting valve for adjusting an amount of the heat medium flowing on the load side,
A flow rate detecting unit for detecting an amount of the heat medium flowing on the load side,
A bypass pipe for bypassing the heat medium flowing on the load side,
A second flow rate adjusting valve for adjusting an amount of the heat medium flowing through the bypass pipe,
Controls an amount of operation of each of the heat sources and an amount of adjustment of the first flow rate adjusting valve in accordance with a demanded capability of the load side and controls an amount of adjustment of the second flow rate adjusting valve in accordance with a detected flow rate of the flow rate detecting unit, And a controller that allocates and allocates the detected flow rate of the flow rate detecting unit to each of the heat source units in operation and controls the supply capacity of the heating medium in each of the heat source units in operation according to the allocated amount
Heat source device. The method according to claim 1,
Each of the heat source groups includes:
A heat medium heat exchanger through which the heat medium flows,
A heat pump type refrigeration cycle for heating or cooling the heating medium in the heat medium body heat exchanger,
And a pump that sucks the heating medium passed through the load side and sends it to the load side through the heat medium body heat exchanger
Heat source device. 3. The method of claim 2,
Wherein the first flow rate adjusting valve adjusts an amount of the heat medium flowing on the load side by a change in opening degree,
Wherein the bypass piping bypasses the heating medium flowing from the respective heat source units toward the load side to return them to the respective heat source side,
And the second flow rate adjusting valve adjusts the amount of the heat medium flowing through the bypass pipe by a change in opening degree
Heat source device. The method of claim 3,
The controller includes a first control unit for controlling the number of operations of the heat source units and the opening degree of the first flow rate adjusting valve in accordance with the demanded capability of the load side,
A second controller for controlling the opening degree of the second flow rate adjusting valve in accordance with the detected flow rate of the flow rate detector,
And a third control unit for allocating and allocating the detected flow rate of the flow rate detecting unit to each of the heat source units in operation and controlling the capability of the pump in each of the heat source units in operation according to the allocated amount
Heat source device. 3. The method of claim 2,
Characterized in that the heat source units are connected to each other in parallel by piping
Heat source device. 6. The method of claim 5,
A first pressure difference detection unit for detecting a pressure difference (P) of the heat medium between both ends of the bypass pipe;
Further comprising a second differential pressure detecting part for detecting a pressure difference (Pw) of the heat medium between both ends of each of the heat medium body heat exchangers,
The controller comprising:
A first detecting section that detects a load-side piping resistance characteristic that indicates a relationship between a quantity (Q) of the heat medium flowing on the load side and a pressure difference (P) of the heat medium between both ends of the bypass piping;
A first control unit for controlling the number of operations of each of the heat sources and the opening degree of the first flow rate adjusting valve in accordance with the demanded capability of the load side,
A second detecting section for detecting the amount (W) of the heat medium flowing through each of the heat source units during operation based on a detection pressure difference (Pw) of the second pressure difference detection section;
A second control section for controlling the opening degree of the second flow rate adjusting valve in accordance with the detected flow rate (Qt) of the flow rate detecting section and the load-side pipe resistance characteristic detected by the first detecting section;
The detection flow rate Qt of the flow rate detection unit is distributed to each of the heat source units in operation and allocated as the required flow rate Wt so that the detected flow rate Wt of the second detection unit coincides with the required flow rate Wt And a third control unit for controlling the capability of the pump in each of the heat source units during operation
Heat source device. The method according to claim 6,
And the first detecting section detects the load-side piping resistance characteristic at the time of trial operation
Heat source device. The method according to claim 6,
Wherein the second detection unit detects the amount W of the heating medium flowing through each of the heat source units during operation to the detection pressure difference Pw of the second differential pressure detection unit and the heat exchanger resistance characteristics of the respective heat source units And the detection is performed based on
Heat source device. The method according to claim 6,
Wherein 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,
Wherein the first flow rate adjusting valve is a plurality of first flow rate adjusting valves and adjusts the amount of the heat medium flowing in each of the devices by the change in opening degree
Heat source device. 10. The method of claim 9,
Wherein the first detection unit comprises:
When the heat source device is started up, the second flow rate adjustment valve is completely closed, and only one of the first flow rate adjustment valves corresponding to the device with the largest pipe resistance among the above devices is fully opened, The first flow rate adjusting valve is fully closed and the pumps in the respective heat source units are operated at rated power, and the value Qn of the detected flow rate Qt of the flow rate detecting unit at this time is compared with the value Qn The corresponding point of the value Pn of the detection pressure difference P of the differential pressure detecting portion is held as the first characteristic point Sn,
Subsequently, the entire first flow rate regulating valve is fully opened while the second flow rate regulating valve is fully closed, and the respective pumps in the respective heat source units are operated with rated power in this state, The value Qm of the detected flow rate Qt of the flow rate detection unit and the value Pm of the detection pressure difference P of the first differential pressure detection unit are regarded as the second characteristic point Sm,
(P) between the amount of water flowing on the load side (Q) and the both ends of the bypass pipe (6) by connecting the held first characteristic point (Sn) and the second characteristic point (Sm) Quot; is approximated to a second-order approximate curve that approximates the relationship of "
Heat source device.

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