JP5734424B2 - Air conditioning and hot water supply complex system - Google Patents

Description

  The present invention relates to an air conditioning and hot water supply combined system that can provide an air conditioning load and a hot water supply load by connecting a hot water supply device to an air conditioner equipped with a heat pump cycle.

  Conventionally, there is an air-conditioning and hot-water supply complex system that can simultaneously provide a cooling load, a heating load, and a hot water supply load by a unified refrigeration cycle. As such, “comprising a refrigerant circuit comprising one compressor and connecting the compressor to an outdoor heat exchanger, an indoor heat exchanger, a cold storage heat tank, and a hot water supply heat exchanger, A "multifunctional heat pump system that constitutes a refrigeration cycle that enables independent operation of air conditioning, hot water supply, heat storage, and cold storage and their combined operation by switching the flow of refrigerant to the heat exchanger" has been proposed ( For example, see Patent Document 1).

Japanese Patent Laid-Open No. 11-270920 (page 3-4, FIG. 1)

  The multi-function heat pump system described in Patent Document 1 is configured to provide a cooling load, a heating load, and a hot water supply load simultaneously by a single refrigeration cycle, that is, one refrigeration cycle. However, in such a system, since the temperature of the heat dissipation process for heating the heat medium and the temperature of the heat dissipation process for heating are substantially the same, the flow rate of the heat medium heated by the hot water supply function is constant. In this case, the degree of superheating of the heat medium is also uniquely determined. Therefore, such a system has a problem that it can be heated only at a constant temperature.

  Moreover, about the multifunction heat pump system as described in patent document 1, it is common to install the refrigerant | coolant circuit which heats, and the circuit of the heating medium heated, by a different contractor. For example, even when replacing or investigating the hot water supply system on the refrigerant circuit side, not only the final adjustment of the flow rate of the heat medium but also the pressure loss on the refrigerant circuit side is adjusted by a contractor on the heat medium circuit side. There was a need to do. In other words, there is a problem that the burden on the contractor is large.

  The present invention has been made to solve the above-described problem, and an object of the present invention is to provide an air conditioning and hot water supply combined system capable of adjusting the flow rate of the heat medium on the circuit side of the heat medium of the hot water supply apparatus.

In the combined air conditioning and hot water supply system according to the present invention, a compressor, an outdoor heat exchanger, an indoor heat exchanger, and a throttle means for air conditioning are piped in series, and the compressor, the outdoor heat exchanger, and a refrigerant The refrigerant side flow path of the heat medium heat exchanger, and the hot water supply throttling means are connected in series, and a refrigeration cycle for circulating the refrigerant, a circulation pump, the heat medium flow path of the refrigerant-heat medium heat exchanger, And a hot water supply load circuit in which a heat medium flow control device is connected in series and circulates the heat medium, and the refrigeration cycle and the hot water supply load circuit are the refrigerant-heat medium heat exchanger, and the refrigerant And the heat medium are cascade-connected so as to perform heat exchange, and include a control device for controlling the opening degree of the air conditioning throttle means, the hot water supply throttle means, and the heat medium flow control device, The control device is set in advance. In order to set the outlet temperature TH22 at the outlet of the heat medium side of the refrigerant-heat medium heat exchanger to the target temperature To, the subcool of the refrigerant-heat medium heat exchanger satisfies the target subcool by the hot water supply throttle means. And adjusting the heat medium flow rate according to the temperature difference between the outlet temperature TH22 of the heat medium side outlet of the refrigerant-heat medium heat exchanger and the target temperature To by the heat medium flow rate adjusting device. When the outlet temperature TH22 of the outlet of the medium heat exchanger on the heat medium side is set to the target temperature To and the temperature difference To-TH22 is equal to or greater than a (a is a preset constant, a> 0), subcool control is performed. The opening degree of the hot water supply throttle means is increased so as to reduce the target value, and the temperature difference To-TH22 is equal to or larger than a preset value -b (b is a preset constant, b> 0), but more than the constant a. small Itoki, maintaining the control target value of the subcooling, when the temperature difference the To-TH22 is less than -b, a feature reducing the opening degree of the hot water supply throttle means so as to increase the control target value of the subcooling To do.

  According to the combined air conditioning and hot water supply system according to the present invention, the hot water supply load is provided with the heat medium flow rate adjustment device, and the flow rate of the heat medium can be adjusted on the hot water supply load side. The outlet temperature can be adjusted. Therefore, it is possible to deal with a wide range of user load fluctuations.

It is a circuit diagram which shows roughly the refrigerant circuit structure of the air conditioning hot-water supply complex system which concerns on Embodiment 1 of this invention. It is a flowchart which shows the flow of the process of the control which the air conditioning hot-water supply complex system which concerns on Embodiment 1 of this invention performs. It is a circuit diagram which shows roughly an example of the circuit structure of the hot water supply load of the air-conditioning hot-water supply complex system which concerns on Embodiment 2 of this invention. It is a circuit diagram which shows roughly an example of the circuit structure of the hot water supply load of the air-conditioning hot-water supply complex system which concerns on Embodiment 3 of this invention. It is a circuit diagram which shows roughly an example of the circuit structure of the hot water supply load of the air-conditioning hot water supply complex system which concerns on Embodiment 4 of this invention. It is a circuit diagram which shows roughly an example of the circuit structure of the hot water supply load of the air-conditioning hot water supply complex system which concerns on Embodiment 5 of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
Embodiment 1 FIG.
FIG. 1 is a circuit diagram schematically showing a refrigerant circuit configuration of an air conditioning and hot water supply complex system 100 according to Embodiment 1 of the present invention. Based on FIG. 1, the refrigerant circuit structure and operation | movement of the air-conditioning / hot-water supply complex system 100 are demonstrated. In addition, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one.

  The air conditioning and hot water supply complex system 100 is installed in a building, a condominium, or the like, and can simultaneously supply a cooling load, a heating load, and a hot water supply load by using a refrigeration cycle that circulates a refrigerant. The air conditioning and hot water supply complex system 100 includes a refrigeration cycle 1 and a hot water supply load circuit 2. The refrigeration cycle 1 and the hot water supply load circuit 2 are configured to perform heat exchange in the refrigerant-heat medium heat exchanger 41 without mixing each other's refrigerant or heat medium (for example, water or brine). Yes.

  The air conditioning and hot water supply complex system 100 is provided with a control device 50 that performs overall control of the operation of the air conditioning and hot water supply complex system 100. The control device 50 controls the driving frequency of the compressor 101, the rotational speed of the blower (not shown), the switching of the four-way valve 102, the opening of each throttle means, the driving frequency of the circulation pump 21, the opening and closing of the valve means 109a and the valve means 109b. Control etc. That is, the control device 50 is configured by a microcomputer or the like, and based on detection information from various detection devices (not shown) and instructions from the remote controller, each actuator (driving components constituting the air-conditioning and hot water supply combined system 100). And the operation of the air conditioning and hot water supply combined system 100 is executed (described in detail in FIG. 2).

{Configuration of refrigeration cycle 1}
The refrigeration cycle 1 includes a heat source unit A, a plurality of indoor units B, a hot water supply device C, and a relay unit D. Among these, the indoor unit B and the hot water supply device C are connected to the heat source unit A in parallel. And by switching the refrigerant | coolant flow with the relay machine D installed between the heat source machine A, the indoor unit B, and the hot water supply apparatus C, the indoor unit B is made to function as a heating indoor unit or a cooling indoor unit. It has become.

[Heat source machine A]
In the heat source machine A, a compressor 101, a four-way valve 102 which is a flow path switching unit, an outdoor heat exchanger 103, and an accumulator 104 are connected in series. The heat source unit A has a function of supplying a heat source (cold heat or hot heat) to the indoor unit B and the hot water supply device C. Although not shown, a blower such as a fan for supplying air to the outdoor heat exchanger 103 may be provided in the vicinity of the outdoor heat exchanger 103.

  Further, in the heat source unit A, a reverse flow that allows the refrigerant to flow only in a predetermined direction (direction from the heat source unit A to the relay unit D) in the high-pressure side connection pipe 106 between the outdoor heat exchanger 103 and the relay unit D. The check valve 105a includes a check valve 105b that allows a refrigerant flow only in a predetermined direction (direction from the relay machine D to the heat source machine A) to the low-pressure side connection pipe 107 between the four-way valve 102 and the relay machine D. , Each provided. The high-pressure side connection pipe 106 and the low-pressure side connection pipe 107 are opposite to the first connection pipe 130 that connects the upstream side of the check valve 105a and the upstream side of the check valve 105b, and the downstream side of the check valve 105a. The second connection pipe 131 is connected to the downstream side of the stop valve 105b.

  The first connection pipe 130 is provided with a check valve 105 d that allows the refrigerant to flow only in the direction from the low pressure side connection pipe 107 to the high pressure side connection pipe 106. The second connection pipe 131 is also provided with a check valve 105 c that allows the refrigerant to flow only in the direction from the low-pressure side connection pipe 107 to the high-pressure side connection pipe 106. In addition, since the flow of the refrigerant | coolant at the time of heating main operation is shown in FIG. 1, the check valve 105a and the check valve 105b are closed (shown in black), the check valve 105b and the check valve 105c. Is open (shown in white).

  The compressor 101 sucks refrigerant and compresses the refrigerant to a high temperature and high pressure state. The four-way valve 102 switches the refrigerant flow. The outdoor heat exchanger 103 functions as an evaporator or a radiator (condenser), performs heat exchange between air supplied from a blower (not shown) and the refrigerant, and converts the refrigerant into evaporated gas or condensates. It is. The accumulator 104 is disposed on the suction side of the compressor 101 and stores excess refrigerant. The accumulator 104 may be any container that can store excess refrigerant.

[Indoor unit B]
In the indoor unit B, an air conditioning throttle means 117 and an indoor heat exchanger 118 are mounted connected in series. The indoor unit B has a function of receiving a cooling load from the heat source unit A and taking charge of a cooling load, or receiving a supply of warm heat from the heat source unit A and taking charge of a heating load. A blower such as a fan for supplying air to the indoor heat exchanger 118 may be provided in the vicinity of the indoor heat exchanger 118. In the figure, an example is shown in which four air conditioning throttle means 117 and four indoor heat exchangers 118 are mounted in parallel. Furthermore, for the sake of convenience, the connection pipe connecting the relay machine D to the indoor heat exchanger 118 is called a connection pipe 133, and the connection pipe connecting the relay machine D to the air conditioning throttle means 117 is called a connection pipe 134. .

  The air-conditioning throttle means 117 has a function as a pressure reducing valve or an expansion valve, and expands the refrigerant by decompressing it. The air-conditioning throttle means 117 may be constituted by a controllable opening degree, for example, a precise flow rate control means using an electronic expansion valve, an inexpensive refrigerant flow rate control means such as a capillary tube, or the like. The indoor heat exchanger 118 functions as a radiator (condenser) and an evaporator, exchanges heat between air supplied from a blower means (not shown) and the refrigerant, and condenses or liquefies the refrigerant. Is.

[Hot water supply device C]
The hot water supply apparatus C includes a refrigerant-heat medium heat exchanger 41, hot water supply throttle means 119 installed on the refrigerant flow path side of the refrigerant-heat medium heat exchanger 41, and a heat medium of the refrigerant-heat medium heat exchanger 41. A heat medium flow control device 22 installed on the flow path side is mounted. The hot water supply apparatus C accommodates a part of the configuration of the refrigeration cycle 1 and a part of the configuration of the hot water supply load circuit 2 to be described later. And has a function of supplying to the hot water supply load circuit 2. The refrigeration cycle 1 and the hot water supply load circuit 2 are cascade-connected by a refrigerant-heat medium heat exchanger 41. The hot water supply device C also functions as a chiller by the flow of the refrigerant. For convenience, the connection pipe connected from the relay D to the refrigerant-heat medium heat exchanger 41 is connected to the connection pipe 135, and the connection pipe connected from the relay D to the hot water supply throttle means 119 is connected to the connection pipe. 136.

  The hot water supply throttle means 119 has a function as a pressure reducing valve or an expansion valve, like the air conditioning throttle means 117, and expands the refrigerant by decompressing it. The hot water supply throttling means 119 is preferably constituted by a controllable opening degree, for example, a precise flow rate control means using an electronic expansion valve, an inexpensive refrigerant flow rate control means such as a capillary. The refrigerant-heat medium heat exchanger 41 functions as a radiator (condenser) or an evaporator, and heats between the refrigerant circulating in the refrigeration cycle of the refrigeration cycle 1 and the heat medium circulating in the hot water supply load circuit 2. It is supposed to exchange. The heat medium flow control device 22 will be described in detail in the section of the hot water supply load circuit 2.

  The water heater C is provided with four temperature sensors. The first temperature sensor 27 is installed between the refrigerant-heat medium heat exchanger 41 and the second distributor 110 and mainly detects the temperature of the refrigerant flowing out of the refrigerant-heat medium heat exchanger 41. . The second temperature sensor 28 is installed between the refrigerant-heat medium heat exchanger 41 and the first distributor 109, and mainly detects the temperature of the refrigerant flowing into the refrigerant-heat medium heat exchanger 41. . The third temperature sensor 29 is installed between a circulation pump 21 described later and the refrigerant-heat medium heat exchanger 41 and detects the temperature of the heat medium flowing into the refrigerant-heat medium heat exchanger 41. . The fourth temperature sensor 30 is installed between the refrigerant-heat medium heat exchanger 41 and the heat medium flow control device 22 and detects the temperature of the heat medium flowing out of the refrigerant-heat medium heat exchanger 41. .

  Information (temperature information) detected by these temperature sensors is sent to a control device 50 that performs overall control of the operation of the air conditioning and hot water supply complex system 100, and is used for control of each actuator constituting the air conditioning and hot water supply complex system 100. Will be.

[Repeater D]
The relay unit D has a function of connecting the indoor unit B and the hot water supply device C to the heat source unit A. Further, the relay unit D causes the indoor unit B to function as a heating indoor unit or a cooling indoor unit by selectively opening or closing either the valve unit 109a or the valve unit 109b of the first distribution unit 109, and a hot water supply device Decide whether C is a chiller or a water heater. The relay D includes a gas-liquid separator 108, a first distributor 109, a second distributor 110, a first internal heat exchanger 111, a first relay throttle means 112, a second internal The heat exchanger 113 and the second relay expansion means 114 are mounted.

  In the first distribution unit 109, a connection pipe 133 and a connection pipe 135 are branched into two, one connected to the low-pressure side connection pipe 107 and the other connected to the gas-liquid separator 108 (connection It is connected to the pipe 132). The connecting pipe 133 and the connecting pipe 135 connected to the low-pressure side connecting pipe 107 are provided with valve means 109b that is controlled to be opened and closed so as not to conduct the refrigerant. The connecting pipe 133 and the connecting pipe 135 connected to the connecting pipe 132 are also provided with valve means 109a that is controlled to be opened and closed so as not to conduct the refrigerant.

  In the second distribution unit 110, the connection pipe 134 and the connection pipe 136 are branched into two, one being connected by the first meeting part 115 and the other being connected by the second meeting part 116. . In addition, a check valve 110a that allows refrigerant to flow only in one side is provided in the connection pipe 134 and the connection pipe 136 that are connected at the first meeting portion 115. The connection pipe 134 and the connection pipe 136 connected by the second meeting part 116 are also provided with a check valve 110b that allows only one refrigerant to flow. The flow path may be switched more reliably by using valve means such as an electromagnetic valve instead of the check valve 110a and the check valve 110b.

The first meeting unit 115 connects the second distribution unit 110 to the gas-liquid separator 108 via the first relay squeezing means 112 and the first internal heat exchanger 111. The second meeting unit 116 connects the second distribution unit 110 to the second meeting unit 115 via the second internal heat exchanger 113.
Moreover, the 2nd meeting part 116 is branched between the 2nd distribution part 110 and the 2nd internal heat exchanger 113 (henceforth the branch piping 116a). The branch pipe 116 a is connected to the low-pressure side connection pipe 107 via the second relay expansion means 114, the second internal heat exchanger 113, and the first internal heat exchanger 111.

  The gas-liquid separator 108 has a function of separating the flowing refrigerant into a gas refrigerant and a liquid refrigerant. The gas-liquid separator 108 is provided in the high-pressure side connection pipe 106, one of which is connected to the valve means 109 a of the first distribution unit 109 and the other is connected to the second distribution unit 110 via the first meeting unit 115. . The first distribution unit 109 has a function of opening / closing one of the valve means 109a and the valve means 109b alternatively according to the required loads of the indoor unit B and the hot water supply device C. The 2nd distribution part 110 has a function which permits the flow of a refrigerant to either one by check valve 110a and check valve 110b.

  The first internal heat exchanger 111 includes a refrigerant that is conducted through the first meeting section 115 between the gas-liquid separator 108 and the first relay throttle means 112, and a downstream side of the second internal heat exchanger 113. Heat exchange is performed with the refrigerant that is conducted through the branch pipe 116a. The first repeater throttle means 112 is provided in the first meeting part 115 between the first internal heat exchanger 111 and the second distribution part 110, and expands the refrigerant by decompressing it. The first repeater throttle means 112 may be configured with a variable opening degree controllable means, for example, a precise flow rate control means using an electronic expansion valve, an inexpensive refrigerant flow rate control means such as a capillary tube, or the like.

  The second internal heat exchanger 113 exchanges heat between the refrigerant that is conducted through the second meeting part 116 and the refrigerant that is conducted through the branch pipe 116a on the downstream side of the second relay throttle unit 114. Is to execute. The second relay throttling means 114 is provided in the second meeting part 116 between the second internal heat exchanger 113 and the second distribution part 110, functions as a pressure reducing valve or an expansion valve, and decompresses the refrigerant. And expand. As with the first relay unit throttle unit 112, the second relay unit throttle unit 114 can be controlled to have a variable opening, for example, a precise flow rate control unit using an electronic expansion valve, or a low cost such as a capillary tube. The refrigerant flow rate adjusting means may be used.

  As described above, the refrigeration cycle 1 includes the compressor 101, the four-way valve 102, the indoor heat exchanger 118, the air conditioning throttle means 117, and the outdoor heat exchanger 103 connected in series, and the compressor 101, the four-way valve 102. The refrigerant-heat medium heat exchanger 41, the hot water supply throttle means 119, and the outdoor heat exchanger 103 are connected in series. The refrigeration cycle 1 is configured such that the indoor heat exchanger 118 and the refrigerant-heat medium heat exchanger 41 are connected in parallel via the relay unit D.

The compressor 101 is not particularly limited as long as it can compress the sucked refrigerant into a high-pressure state. For example, various types such as reciprocating, rotary, scroll, or screw can be used. The compressor 101 may be configured as a type in which the rotational speed can be variably controlled by an inverter, or may be configured as a type in which the rotational speed is fixed. Further, the type of refrigerant circulating in the refrigeration cycle 1 is not particularly limited. For example, natural refrigerants such as carbon dioxide (CO ₂ ), hydrocarbons, and helium, alternative refrigerants that do not contain chlorine such as HFC410A, HFC407C, and HFC404A, Alternatively, any of CFC-based refrigerants such as R22 and R134a used in existing products may be used.

  Moreover, although the case where the excess refrigerant | coolant was stored by the liquid receiver (accumulator 104) in the refrigerating cycle 1 was shown, it is not restricted to this, It is made to store with the heat exchanger used as a heat radiator in a refrigerating cycle. For example, the accumulator 104 may be removed. Further, FIG. 1 shows an example in which four or more indoor units B are connected, but the number of connected units is not particularly limited. And the capacity | capacitance of each indoor unit B which comprises the refrigerating cycle 1 may be made all the same, and may be made to differ from large to small.

{Operation of refrigeration cycle 1}
Here, the operation of the refrigeration cycle 1 when the heating operation is executed by all the driven indoor units B and the hot water supply operation is executed by the hot water supply apparatus C will be described.

  The refrigerant in the high-pressure gas state that has been brought to a high temperature and high pressure by the compressor 101 is discharged from the compressor 101, passes through the four-way valve 102, is conducted through the check valve 105 c, is guided to the high-pressure side connection pipe 106, and is overheated. It flows into the gas-liquid separator 108 of the repeater D in a gas state. The superheated gas refrigerant flowing into the gas-liquid separator 108 flows through the connection pipe 132 and is distributed to a circuit in which the valve means 109a of the first distribution unit 109 is open.

  The refrigerant flowing into the indoor unit B dissipates heat in the indoor heat exchanger 118 (that is, warms the indoor air), is depressurized by the air conditioning throttle means 117, and joins at the first meeting part 115. Further, the refrigerant flowing into the hot water supply device C dissipates heat in the refrigerant-heat medium heat exchanger 41 (that is, gives heat to the hot water supply load circuit 2), is depressurized by the hot water supply throttle means 119, and flows out of the indoor unit B. The refrigerant and the first meeting part 115 merge.

  On the other hand, part of the superheated gas refrigerant that has flowed into the gas-liquid separator 108 flows through the first meeting part 115, and the first internal heat exchanger 111 reduces the temperature to low temperature and low pressure by the second relay throttle unit 114. A degree of supercooling is obtained by exchanging heat with the expanded refrigerant. The refrigerant passes through the first repeater throttle means 112, merges with the refrigerant flowing out from the indoor unit B and the hot water supply device C at the first meeting unit 115, and flows into the second internal heat exchanger 113. The refrigerant flowing into the second internal heat exchanger 113 has a degree of supercooling by performing heat exchange with the refrigerant expanded to low temperature and low pressure in the second relay heat exchanger 113 in the second internal heat exchanger 113. obtain. And this refrigerant | coolant flows to the throttle means 114 side for 2nd relay machines. At this time, if there is an indoor unit B that is performing the cooling operation, the refrigerant is distributed to the second distribution unit 110 side.

  The refrigerant conducted through the second relay throttle unit 114 passes through the branch pipe 116a, exchanges heat in the second internal heat exchanger 113 and the first internal heat exchanger 111, and evaporates. Thereafter, the refrigerant is guided to the low-pressure side connection pipe 107, led to the outdoor heat exchanger 103 through the check valve 105 d, and then returns to the compressor 101 through the four-way valve 102 and the accumulator 104.

{Configuration of hot water supply load circuit 2}
The hot water supply load circuit 2 is configured by being connected by a circulation pump 21, a heat medium flow path side of the refrigerant-heat medium heat exchanger 41, a heat medium flow control device 22, and a heat medium pipe 202. That is, the hot water supply load circuit 2 includes the circulation pump 21, the heat medium flow path side of the refrigerant-heat medium heat exchanger 41, and the heat medium flow rate adjustment device 22 connected in series by the heat medium pipe 202, thereby providing a heat medium circuit. It is configured to form.

  The type of the heat medium that circulates through the heat medium pipe 202 is not particularly limited. For example, the refrigerant (the same kind or various kinds of refrigerant as the refrigerant circulating in the refrigeration cycle 1), brine (antifreeze), water, brine And a mixture of water and an additive having a high anticorrosion effect can be used. Further, the heat medium pipe 202 may be constituted by, for example, a copper pipe, a stainless pipe, a steel pipe, a vinyl chloride pipe, or the like.

  The circulation pump 21 sucks the heat medium flowing through the heat medium pipe 202, pressurizes the heat medium, and circulates the heat medium pipe 202. The circulation pump 21 may be configured as a type in which the rotational speed can be variably controlled by an inverter, or may be configured as a type in which the rotational speed is fixed. The circulation pump 21 is not particularly limited as long as it is capable of delivering a heat medium.

  As described above, the refrigerant-heat medium heat exchanger 41 exchanges heat between the heat medium circulating in the hot water supply load circuit 2 and the refrigerant circulating in the refrigeration cycle 1.

  The heat medium flow control device 22 adjusts the flow rate of the heat medium circulating through the heat medium pipe 202. The heat medium flow control device 22 is configured by a device whose opening degree can be variably controlled, for example, an electronic expansion valve. Therefore, the heat medium flow control device 22 is capable of adjusting the flow rate of the heat medium by the opening degree being variably controlled by the control device 50.

{Operation of hot water supply load circuit 2}
The heat medium sent out from the circulation pump 21 flows into the heat medium flow path side of the refrigerant-refrigerant heat exchanger 41. In the refrigerant-refrigerant heat exchanger 41, the heat medium circulating in the hot water supply load circuit 2 is heated by the refrigerant circulating in the refrigeration cycle 1. The heated heat medium passes through the heat medium flow control device 22 and is sent to each load (for example, a faucet, shower, hot water storage tank, floor heating, etc.) connected to the heat medium pipe 202. Then, the heat medium used in each load and a new heat medium supplied from a water supply pipe (not shown) are taken into the circulation pump 21 again and circulates through the heat medium pipe 202.

  As described above, in the air conditioning and hot water supply complex system 100, for example, when there is a demand for hot water supply during the air conditioning cooling operation in summer, it has been necessary to provide the hot water conventionally by a boiler or the like. Since the hot water is recovered and reused, the system COP is greatly improved and energy is saved.

  FIG. 2 is a flowchart showing a flow of control processing executed by the air conditioning and hot water supply complex system 100. Based on FIG. 2, the characteristic control content which the air-conditioning hot-water supply complex system 100 performs is demonstrated in detail. 2, (TH22) is the heat medium outlet temperature, (TH22) ′ is the heat medium outlet temperature before changing the opening of the heat medium flow control device 22, and (To) is the heat medium outlet. (SCm) represents a subcool target value, a to d represent a constant (positive), n represents a count number (positive), and N represents a target count number (positive).

  Control device 50 starts the control process from detecting that hot water supply device C is in the heating operation (hot water supply operation) (step ST1). The control device 50 controls the opening degree of the hot water supply throttling means 119 so as to satisfy the target subcool, and controls the opening degree of the heat medium flow control device 22 to the maximum opening degree (step ST2). Then, the control device 50 detects the outlet temperature TH22 on the heat medium side of the refrigerant-heat medium heat exchanger 41 (step ST3). The outlet temperature on the heat medium side of the refrigerant-heat medium heat exchanger 41 may be detected by the fourth temperature sensor 30.

  Next, the control device 50 uses a preset temperature difference To-TH22 between the target temperature To of the heat medium side outlet of the refrigerant-heat medium heat exchanger 41 and the detected outlet temperature TH22 as a criterion. The temperature difference To-TH22 is compared with a constant. Specifically, the control device 50 determines whether (1) the temperature difference To−TH22 is a or more ((To−TH22) ≧ a), or (2) the temperature difference To−TH22 is −b or more, but more than a. It is determined whether it is small (−b ≦ (To−TH22) <a) or (3) the temperature difference To−TH22 is smaller than −b (−b> (To−TH22)) (step ST4).

  The control device 50 determines whether or not the determination in step ST4 is (2) (step ST5). When the process in step ST4 is (2) (step ST5; YES), the controller 50 determines that the outlet temperature on the heat medium side of the refrigerant-heat medium heat exchanger 41 becomes the target heat medium outlet temperature. Therefore, the user's request is satisfied, the current control target value is maintained (SCm = SCm), and feedback is applied to step ST3. On the other hand, when the process in step ST4 is not (2) (step ST5; NO), the control device 50 determines whether or not the process in step ST4 is (3) (step ST6).

  When the determination in step ST4 is (3) (step ST6; YES), the control device 50 causes the heat medium side outlet temperature of the refrigerant-heat medium heat exchanger 41 to be higher than the target heat medium outlet temperature. Therefore, the currently set subcool target is increased (SCm = SCm + d), the opening degree of the hot water supply throttle means 119 is reduced (decreased) (step ST7), and feedback is applied to step ST3.

  On the other hand, when the process in step ST4 is not (3) (step ST6; NO), the control device 50 determines that the process in step ST4 is (1), and the refrigerant-heat medium heat exchanger 41. Since the outlet temperature on the heat medium side is lower than the target heat medium outlet temperature, the currently set subcool target is reduced (SCm = SCm-c), and the opening degree of the hot water supply throttle means 119 is increased ( (Step ST8).

  Then, the control device 50 holds the heat medium outlet temperature (TH22) ′ before changing the opening of the heat medium flow control device 22 as TH22 (step ST9). Next, the control device 50 detects the outlet temperature TH22 on the heat medium side at the current time (step ST10). Then, the control device 50 determines whether or not the current outlet temperature TH22 on the heat medium side is higher than the outlet temperature (TH22) 'on the heat medium side at the previous time (step ST11). Specifically, the control device 50 determines whether TH22 is higher than (TH22) 'based on whether the difference between TH22 and (TH22)' is larger than a constant e.

When the current outlet temperature TH22 on the heat medium side is higher than the outlet temperature (TH22) ′ on the heat medium side at the previous time (step ST11; YES), the count is set to n = 0 (step ST12). Then, feedback is applied to step ST3 to continue the current control.
On the other hand, when the current outlet temperature TH22 on the heat medium side is not higher than the outlet temperature (TH22) ′ on the heat medium side at the previous time (step ST11; NO), the number of times that the condition is not satisfied with n = n + 1 Is counted (step ST13).

  Control device 50 determines whether or not the count exceeds a preset number (set number of times (target count number N)) (step ST14). When the count exceeds the target count number N (step ST14; YES), the change in the opening degree of the heat medium flow control device 22 is reduced, and the outlet temperature on the heat medium side of the refrigerant-heat medium heat exchanger 41 reaches the target value. Control is performed so as to be satisfied (step ST15).

In step ST15, in order to make the outlet temperature TH22 on the heat medium side reach the target outlet temperature on the heat medium side, control is performed to reduce the opening degree of the heat medium flow control device 22. The variation range of the throttle opening is determined by the difference between the target outlet temperature T _O of the heat medium and the outlet temperature TH22 on the heat medium side (in this case, always the target outlet temperature T _{O of the} heat medium> the outlet temperature TH22 on the heat medium side). Therefore, the outlet temperature TH22 on the heat medium side can approach the target outlet temperature earlier when the temperature difference is large. In addition, about the opening degree of the heat medium flow control apparatus 22, it is also possible to maintain a certain amount of heat by setting the minimum opening degree.

As for the formula of step ST15, the formulas (1) and (2) indicate that the temperature difference between the target outlet temperature T _O of the heat medium and the outlet temperature TH22 on the heat medium side is determined by the throttle opening. . Generally, the hot water supply capacity is represented by the following formula (1). Note that Q is capacity, Cp is volume specific heat, v is the heat medium flow rate, and ΔT is the degree of superheat of the heat medium (difference between the heat medium outlet temperature and the heat medium inlet temperature).
Q = Cp × v × ΔT (1)
Therefore, when formula (1) is modified, formula (2) below is obtained.
ΔT = Q / Cp × 1 / v (2)
In step ST15, the amount of heat that can be received by the heat medium side from the refrigerant side is substantially constant, and Cp is a constant. Therefore, Equation (2) shows that ΔT is inversely proportional to the heat medium flow rate. Therefore, if the flow rate is reduced by reducing the throttle opening, a temperature difference is produced.

  As described above, according to the air conditioning and hot water supply complex system 100, the hot water supply load circuit 2 is provided with the heat medium flow rate adjusting device 22 so that the flow rate of the heat medium can be adjusted on the hot water supply load circuit 2 side. It is possible to adjust the outlet temperature of the heat medium. Therefore, it is possible to deal with a wide range of user load fluctuations.

Embodiment 2. FIG.
FIG. 3 is a circuit diagram schematically showing an example of a circuit configuration of a hot water supply load circuit (hereinafter referred to as hot water supply load circuit 2A) of the air-conditioning and hot water combined system according to Embodiment 2 of the present invention. Based on FIG. 3, the configuration of hot water supply load circuit 2 </ b> A of the air conditioning and hot water combined system according to Embodiment 2 will be described. The portions other than the hot water supply load circuit 2A of the combined air conditioning and hot water supply system according to Embodiment 2 are the same as those of the combined air conditioning and hot water supply system 100 according to Embodiment 1. Therefore, the second embodiment will be described with a focus on differences from the first embodiment, and the same parts as those in the first embodiment will be denoted by the same reference numerals and the description thereof will be omitted.

  Usually, when a hot water heater is used, it is a general method to always use for hot water supply by setting a constant temperature regardless of the outside air temperature. Therefore, in the air conditioning and hot water supply complex system according to Embodiment 2, as shown in FIG. 3, a tank 23A is installed in the hot water supply load circuit 2A. The tank 23A stores the heat medium heated by the refrigerant-heat medium heat exchanger 41, and functions as a buffer for hot water supply. The tank 23A is connected so that the lower part is on the upstream side of the circulation pump 21 via the heat medium pipe 202, and the upper part is on the downstream side of the heat medium flow control device 22 via the heat medium pipe 202. It is connected.

  When the tank 23A is used, it is necessary to sterilize Legionella spp. Generated in the tank 23A. It is well known that the optimum temperature for propagation of Legionella is 35-36 ° C. In addition, it is well known that the recommended temperature for suppressing the growth of Legionella is 62 ° C., and it is necessary to heat to about 50-60 ° C. When it is necessary to heat to about 60 ° C. in order to sterilize the tank, it is common to install an auxiliary heating device (for example, a heater) in the tank to raise the temperature of the heat medium.

  On the other hand, in the air conditioning and hot water supply complex system according to the second embodiment, the temperature of the heat medium can be adjusted using the heat medium flow rate adjusting device 22, and therefore the temperature in the tank 23A is made as high as possible. be able to. Therefore, according to the air-conditioning and hot water supply complex system according to the second embodiment, the auxiliary superheater is not provided, or even if it is provided, only a small capacity is required, and cost reduction can be realized.

  As described above, according to the air conditioning and hot water supply complex system according to the second embodiment, in addition to the effects of the air conditioning and hot water supply complex system 100 according to the first embodiment, the tank 23A that functions as a buffer for hot water supply use is provided. The range of applications will be further expanded. Moreover, since the temperature of the heat medium can be adjusted using the heat medium flow control device 22, it is possible to realize a reduction in capital investment for suppressing the growth of Legionella spp.

Embodiment 3 FIG.
FIG. 4 is a circuit diagram schematically showing an example of a circuit configuration of a hot water supply load circuit (hereinafter, referred to as a hot water supply load circuit 2B) of an air conditioning and hot water supply complex system according to Embodiment 3 of the present invention. Based on FIG. 4, the structure of the hot water supply load circuit 2B of the air-conditioning and hot water combined system according to Embodiment 3 will be described. The portions other than the hot water supply load circuit 2B of the air conditioning and hot water supply complex system according to Embodiment 3 are the same as those of the air conditioning and hot water supply complex system 100 according to Embodiment 1. Therefore, the third embodiment will be described with a focus on differences from the first and second embodiments, and the same parts as those of the first and second embodiments will be denoted by the same reference numerals and the description thereof will be omitted. I am going to do it.

  As described in the second embodiment, when the tank is used, it is necessary to sterilize by heating the temperature of the heat medium in the tank. Therefore, in the air conditioning and hot water supply complex system according to Embodiment 3, a tank 23B is installed in the hot water supply load circuit 2B as shown in FIG. The tank 23B stores the heat medium heated by the refrigerant-heat medium heat exchanger 41 in the same manner as the tank 23A of the second embodiment, and functions as a buffer in hot water supply applications. The tank 23B is connected so that one of the bottoms (the right side on the paper) is on the upstream side of the flow path switching valve 24 and the flow path switching valve 25 via the heat medium pipe 202, and the other bottom (the left side on the paper) is heated. They are connected to the downstream side of the heat medium flow control device 22 via the medium pipe 202.

  That is, in the combined air conditioning and hot water supply system according to Embodiment 3, two flow path switching devices (flow path switching valve 24, flow path switching) that switch the flow path of the heat medium between the tank 23B and the circulation pump 21. It is different from the air-conditioning and hot water supply combined system according to Embodiment 2 in that the valve 25) is provided. As the flow path switching valve 24 and the flow path switching valve 25, a stepping motor driven type that can control the flow rate of the heat medium flowing through the heat medium pipe 202 may be used. Further, a two-way valve or a three-way valve with one end closed may be used. Further, as the flow path switching valve 24 and the flow path switching valve 25, those that open and close a two-way flow path such as an open / close valve may be used, and the average flow rate may be controlled by repeating ON / OFF.

  In the above configuration, when hot water is supplied by the hot water supply apparatus C, the heat medium heated by the heat medium-refrigerant heat exchanger 41 is opened by opening the flow path switching valve 24 and closing the flow path switching valve 25. Can cover the heating load by passing through the entire hot water supply load circuit 2B. Further, when only heating the heat medium stored in the tank 23B, the temperature of the heat medium in the tank 23B is raised by closing the flow path switching valve 24 and opening the flow path switching valve 25. That's fine. In addition, the opening degree of the flow path switching valve 24 and the flow path switching valve 25 is controlled by the control device 50.

  As described above, according to the combined air conditioning and hot water supply system according to Embodiment 3, in addition to the effects of the combined air conditioning and hot water supply system according to Embodiment 3, the flow path of the heat medium in hot water supply load circuit 2B can be switched. Therefore, it is possible to adjust the heating of the heat medium according to the required load, and it is possible to further contribute to energy saving.

Embodiment 4 FIG.
FIG. 5 is a circuit diagram schematically showing an example of a circuit configuration of a hot water supply load circuit (hereinafter, referred to as a hot water supply load circuit 2C) of an air conditioning and hot water combined system according to Embodiment 4 of the present invention. Based on FIG. 5, a configuration of hot water supply load circuit 2 </ b> C of the air-conditioning and hot water combined system according to Embodiment 4 will be described. Note that the air conditioning and hot water supply complex system according to Embodiment 4 includes a plurality of hot water supply devices C, and the heat medium pipe 202 connected to each hot water supply device C is joined by the hot water supply load circuit 2 to provide one tank. 23C is provided. Therefore, the fourth embodiment will be described focusing on the differences from the first to third embodiments, and the same parts as those in the first to third embodiments will be denoted by the same reference numerals and the description thereof will be omitted. I am going to do it.

  In the air conditioning and hot water supply combined system according to Embodiments 1 to 3, a plurality of hot water supply apparatuses C can be connected. Therefore, the combined air conditioning and hot water supply system according to Embodiment 4 is different from the combined air conditioning and hot water supply systems according to Embodiments 1 to 3 in that a plurality of hot water supply apparatuses C are connected. The plurality of hot water supply apparatuses C are connected in parallel to the heat source apparatus A via the relay machine D. For convenience, the hot water supply device C on the upper side of the paper is referred to as a hot water supply device C1, the hot water supply device C in the center of the paper is referred to as a hot water supply device C2, and the hot water supply device C on the lower side of the paper is referred to as a hot water supply device C3. Each element accommodated in the hot water supply device C1 contains “a” after the reference numeral, and each element accommodated in the hot water supply device C2 contains “b” after the reference numeral in the hot water supply apparatus C3. “C” is appended to each element.

  As in Embodiment 2 or 3, a tank may be connected to each hot water supply load. However, in this case, it is necessary to secure a space for installing a plurality of tanks, and there is a possibility of increasing the cost. Therefore, as in the air conditioning and hot water supply complex system according to the fourth embodiment, the hot water supply load circuit 2c may be configured by connecting a common large-capacity tank 23C to the hot water supply device C1, the hot water supply device C2, and the hot water supply device C3. . 5 shows an example in which each of the hot water supply device C1, the hot water supply device C2, and the hot water supply device C3 includes the heat medium flow rate adjusting device 22, but there is one in the junction of the heat medium pipe 202. A plurality of them may be provided. In this way, the number of the heat medium flow control devices 22 can be reduced, and the increase in cost can be reduced.

  As mentioned above, according to the air-conditioning hot-water supply complex system which concerns on Embodiment 4, in addition to the effect which the air-conditioning hot-water supply complex system which concerns on Embodiment 1- Embodiment 3 has, the omission of installation space and the further reduction of a cost increase are further reduced. You can plan.

Embodiment 5 FIG.
FIG. 6 is a circuit diagram schematically showing an example of a circuit configuration of a hot water supply load circuit (hereinafter referred to as hot water supply load circuit 2D) of the air conditioning and hot water supply complex system according to Embodiment 5 of the present invention. Based on FIG. 6, the structure of hot water supply load circuit 2D of the air-conditioning hot-water supply complex system according to Embodiment 5 will be described. The portions other than the hot water supply load circuit 2D of the combined air conditioning and hot water supply system according to Embodiment 5 are the same as those of the combined air conditioning and hot water supply system 100 according to Embodiment 1. Therefore, in the fifth embodiment, differences from the first to fourth embodiments will be mainly described, and the same parts as those in the first to fourth embodiments are denoted by the same reference numerals and description thereof is omitted. I am going to do it.

  By the way, when installing an air conditioning and hot water supply complex system, the refrigerant pipe on the refrigerant circuit side for heating and the heat medium pipe on the circuit side of the heating medium to be heated are generally installed by different contractors. . Therefore, when exchanging the hot water supply device or investigating the hot water supply device, it is necessary to adjust the pressure loss or the like on the refrigerant circuit side by a contractor installing the heat medium pipe on the heat medium circuit side.

  Therefore, in the air conditioning and hot water supply complex system according to the fifth embodiment, as shown in FIG. 6, the hot water supply load circuit 2D is provided with a pipe 202a that is in parallel with the heat medium flow path of the refrigerant-heat medium heat exchanger 41, The pipe 202a is provided with a pressure gauge 26 that detects the pressure of the heat medium. By doing so, a supplier who replaces the hot water supply device C can adjust the pressure loss in the hot water supply load circuit 2 </ b> D with the heat medium flow control device 22 while checking the pressure gauge 26. 6 shows an embodiment using the pressure gauge 26. Instead of the pressure gauge 26, a heat medium water amount measuring device is installed in the circuit of the hot water supply load circuit 2D, and the pressure in the hot water supply load circuit 2D. It is also possible to adjust the loss.

  As mentioned above, according to the air-conditioning / hot-water supply combined system which concerns on Embodiment 5, in addition to the effect which the air-conditioning / hot-water supply complex system which concerns on Embodiment 1-4 has, it becomes possible to reduce a contractor's burden significantly.

  In addition, although the air-conditioning / hot-water supply combined system according to the present invention has been described separately for the embodiments, the air-conditioning / hot-water supply combined system may be configured by appropriately combining the features of the embodiments. If the embodiments are appropriately combined, the effects of the features of the embodiments can be obtained in a superimposed manner. In each embodiment, an air conditioning and hot water supply combined system capable of simultaneous cooling and heating operations has been described. However, a heating operation in an air conditioning and hot water supply combined system capable of switching between cooling and heating may be performed. Needless to say, it can also be used in the case of an air conditioning complex system.

  DESCRIPTION OF SYMBOLS 1 Refrigeration cycle, 2 Hot-water supply load circuit, 2A Hot-water supply load circuit, 2B Hot-water supply load circuit, 2C Hot-water supply load circuit, 2D Hot-water supply load circuit, 21 Circulation pump, 22 Heat medium flow control device, 23A tank, 23B tank, 23C tank, 24 flow switching valve, 25 flow switching valve, 26 pressure gauge, 41 refrigerant-heat medium heat exchanger, 50 control device, 100 air-conditioning hot water supply combined system, 101 compressor, 102 four-way valve, 103 outdoor heat exchanger, 104 Accumulator, 105a Check valve, 105b Check valve, 105c Check valve, 105d Check valve, 106 High-pressure side connection piping, 107 Low-pressure side connection piping, 108 Gas-liquid separator, 109 First distribution section, 109a Valve means 109b valve means, 110 second distributor, 110a check valve, 110b check valve, 111 first internal heat exchanger , 112 First relay device throttle means, 113 Second internal heat exchanger, 114 Second relay throttle device, 115 First meeting part, 116 Second meeting part, 116a Branch pipe, 117 Air conditioning throttle means, 118 Indoor heat exchanger, 119 Hot water supply throttle means, 130 First connection pipe, 131 Second connection pipe, 132 Connection pipe, 133 Connection pipe, 134 Connection pipe, 135 Connection pipe, 136 Connection pipe, 202 Heat medium pipe, 202a pipe , A heat source machine, B indoor unit, C hot water supply device, C1 hot water supply device, C2 hot water supply device, C3 hot water supply device, D relay machine.

Claims (7)

The compressor, the outdoor heat exchanger, the indoor heat exchanger, and the air-conditioning throttle means are connected in series with each other, and the compressor, the outdoor heat exchanger, and the refrigerant side flow path of the refrigerant-heat medium heat exchanger A refrigeration cycle in which the hot water supply throttling means is piped in series to circulate the refrigerant;
A circulation pump, a heat medium flow path of the refrigerant-heat medium heat exchanger, and a heat medium flow control device connected in series with a hot water supply load circuit for circulating the heat medium,
The refrigeration cycle and the hot water supply load circuit are cascade connected so that the refrigerant and the heat medium exchange heat in the refrigerant-heat medium heat exchanger,
A controller for controlling the opening degree of the air conditioning throttle means, the hot water supply throttle means, and the heat medium flow control device;
The controller is
In order to set the outlet temperature TH22 at the outlet of the heat medium side of the refrigerant-heat medium heat exchanger set in advance to the target temperature To,
The subcooling of the refrigerant-heat medium heat exchanger is controlled by the hot water supply throttling means so as to satisfy the target subcooling,
By adjusting the heat medium flow rate according to the temperature difference between the outlet temperature TH22 of the heat medium side outlet of the refrigerant-heat medium heat exchanger and the target temperature To by the heat medium flow control device, the refrigerant-heat medium heat exchanger. The outlet temperature TH22 at the outlet of the heat medium side is set to the target temperature To ,
When the temperature difference To-TH22 is equal to or greater than a (a is a preset constant, a> 0), the opening degree of the hot water throttling means is increased so as to reduce the subcool control target value,
When the temperature difference To-TH22 is equal to or larger than a preset -b (b is a preset constant, b> 0) but smaller than the constant a, the subcool control target value is maintained,
When the temperature difference To-TH22 is smaller than -b, the air conditioning and hot water supply combined system reduces the opening degree of the hot water supply throttle means so as to increase the subcool control target value . The controller is
When the opening of the hot water supply throttle means is increased so as to reduce the control target value of the subcool,
Comparing the outlet temperature TH22 ′ of the outlet of the heat medium side of the refrigerant-heat medium heat exchanger before changing the opening of the hot water throttle means, and the outlet temperature TH22;
When the outlet temperature TH22 is equal to or higher than the outlet temperature TH22 ′ and the counted number exceeds the set number, the degree of superheat of the heat medium is adjusted by reducing the opening of the heat medium flow control device. Item 2. The combined air conditioning and hot water supply system according to item 1 . The compressor, the outdoor heat exchanger, the indoor heat exchanger, and the air-conditioning throttle means are connected in series with each other, and the compressor, the outdoor heat exchanger, and the refrigerant side flow path of the refrigerant-heat medium heat exchanger A refrigeration cycle in which the hot water supply throttling means is piped in series to circulate the refrigerant;
A circulation pump, a heat medium flow path of the refrigerant-heat medium heat exchanger, and a heat medium flow control device connected in series with a hot water supply load circuit for circulating the heat medium,
The refrigeration cycle and the hot water supply load circuit are cascade connected so that the refrigerant and the heat medium exchange heat in the refrigerant-heat medium heat exchanger,
A controller for controlling the opening degree of the air conditioning throttle means, the hot water supply throttle means, and the heat medium flow control device;
The controller is
In order to set the outlet temperature TH22 at the outlet of the heat medium side of the refrigerant-heat medium heat exchanger set in advance to the target temperature To,
The subcooling of the refrigerant-heat medium heat exchanger is controlled by the hot water supply throttling means so as to satisfy the target subcooling,
By adjusting the heat medium flow rate according to the temperature difference between the outlet temperature TH22 of the heat medium side outlet of the refrigerant-heat medium heat exchanger and the target temperature To by the heat medium flow control device, the refrigerant-heat medium heat exchanger. The outlet temperature TH22 at the outlet of the heat medium side is set to the target temperature To,
A pressure gauge for detecting a pressure difference between the upstream side and the downstream side of the refrigerant-heat medium heat exchanger is provided in the hot water supply load circuit,
By controlling the heat medium flow control device, the pressure loss of the refrigerant-heat medium heat exchanger is adjusted, and the amount of water can be adjusted.
Air-conditioning hot-water supply complex system. The air conditioning and hot water supply complex system according to any one of claims 1 to 3, wherein a tank for storing a heat medium is provided in the hot water supply load circuit including the heat medium flow control device. Installing the heat medium flow control device in the hot water supply load circuit, adjusting the flow rate of the heat medium using the heat medium flow control device, switching the hot water supply load circuit, and not supplying the heat medium to the load side The air conditioning and hot water supply combined system according to claim 4, wherein the temperature of the heat medium in the tank is increased. A plurality of the refrigerant-heat medium heat exchangers each having the heat medium flow control device are provided,
The air conditioning and hot water supply combined system according to claim 4 or 5, wherein the tank is shared by a plurality of the refrigerant-heat medium heat exchangers. The hot water supply load circuit is provided with a pressure gauge for detecting a pressure difference between the upstream side and the downstream side of the refrigerant-heat medium heat exchanger,
The combined air-conditioning and hot-water supply system according to claim 3 , wherein the heat medium flow control device is controlled to adjust a pressure loss of the refrigerant-heat medium heat exchanger to adjust a water amount.

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