US20130312443A1

US20130312443A1 - Refrigeration cycle apparatus and refrigeration cycle control method

Info

Publication number: US20130312443A1
Application number: US13/983,583
Authority: US
Inventors: Shogo Tamaki; Makoto Saito; Masanobu Baba
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2011-02-14
Filing date: 2011-02-14
Publication date: 2013-11-28
Also published as: EP2677251A4; CN103370584A; WO2012111063A1; EP2677251B1; EP2677251A1; JP5642207B2; JPWO2012111063A1; CN103370584B; ES2562276T3

Abstract

A combined air-conditioning and hot water supply system includes a refrigeration cycle mechanism, a hot water storage tank, and a controller. The refrigeration cycle mechanism has a compressor whose operating frequency can be controlled, a plate water-heat exchanger that heats water, a hot water supply pressure-reducing mechanism, and an outdoor heat exchanger. The controller includes a clock section, a computing section, a memory section, and a controlling section. The clock section measures time. The computing section calculates the actual hot water supply load. The memory section stores information related to the hot water supply load calculated by the computing section. The controlling section controls the operating frequency of the compressor based on the quantity of heat storage, the hot water supply load, and a preset hot water supply time.

Description

TECHNICAL FIELD

The present invention relates to a combined air-conditioning and hot water supply system that can execute an air-conditioning operation (cooling operation or heating operation) and a hot water supply operation simultaneously. More specifically, the present invention relates to a combined air-conditioning and hot water supply system that computes the minimum required hot water supply capacity by using information on the heat consumed by a user in the past, and performs operation in accordance with an air conditioning load and the computed hot water supply capacity when the combined air-conditioning and hot water supply system is in hot water supply operation or combined air-conditioning and hot water supply operation.

BACKGROUND ART

In related art, there are heat pump systems adapted for hot water supply that are equipped with a refrigerant circuit formed by connecting a hot water supply unit (hot water supply device) to a heat source unit (outdoor unit) by pipes to thereby enable a hot water supply operation. For hot water supply systems, various attempts have been made in related art to increase energy saving performance (see, for example, Patent Literatures 1 to 4).
There are also combined air-conditioning and hot water supply systems that are equipped with a refrigerant circuit formed by connecting a use unit (indoor unit) by pipes in addition to a hot water supply unit, thereby enabling simultaneous execution of an air-conditioning operation and a hot water supply operation. Such systems allow waste heat generated in cooling to be used as hot water supply operation. For such systems as well, attempts have been made to increase energy saving performance in hot water supply operation (see, for example, Patent Literature 5).

CITATION LIST

Patent Literature

Patent Literature 1: Japanese Unexamined Patent Application Publication No. 2007-147246
Patent Literature 2: Japanese Patent No. 3855985
Patent Literature 3: Japanese Unexamined Patent Application Publication No. 2004-340532
Patent Literature 4: Japanese Unexamined Patent Application Publication No. 2003-139391
Patent Literature 5: Japanese Unexamined Patent Application Publication No. 2007-218463

SUMMARY OF INVENTION

Technical Problem

The hot water supply device of a hot water storage tank type described in Patent Literature 1 achieves improved energy saving performance by boiling up water in accordance with the heat usage condition. Specifically, a day is divided into a plurality of time slots, and a boiling operation is controlled in accordance with the required heat calculated on the basis of the actual past heat usage in each divided time slot. In this way, the time from storage of heat in the hot water storage tank to its use can be shortened, and heat rejection can be reduced, thereby improving energy saving performance. However, the method of operating the hot water supply device is not controlled on the basis of the actual heat usage in the past. Consequently, in hot water supply operation, the operating frequency of the compressor becomes high, resulting in poor operation efficiency.
In the heat pump hot water supply device described in Patent Literature 2, in accordance with the life pattern in a day,
when there is a fear that hot water may run out, an operation that draws out the heating capacity of the heat pump cycle is given priority to thereby prevent running out of hot water, and when there is no fear of running out of hot water, an operation that gives priority to the operation efficiency of the heat pump cycle is carried out. According to this known technique, during the operation that draws out heating capacity, the operating frequency of the compressor needs to be controlled to a high frequency in order to secure hot water supply capacity. Therefore, a deterioration of operation efficiency is unavoidable.
In the heat pump hot water supply device described in Patent Literature 3, hot water exit flow rate, hot water exit temperature, and hot water exit time are learned on a time-by-time basis, and the operational state is set in accordance with each corresponding time point. In addition, the frequency of the compressor is set from the inlet/outlet water temperature of the heat exchanger. This operation improves the controllability of hot water exit temperature and durability for a wide range of hot water supply loads. This known technique leads to an operational state with poor efficiency at times when the hot water supply load is high.
In the heat pump hot water supply unit described in Patent Literature 4, the boiling operation time is estimated from the amount of hot water boiled per unit time, the capacity of the hot water storage tank, and the remaining amount of hot water. Although the operation time for completing storage of heat in the hot water storage tank can be determined by using this known technique, it is not possible to determine the hot water supply operation time and the hot water supply start time that are appropriate to prevent running out of hot water at a predetermined hot water supply capacity, which makes it impossible to perform a hot water supply operation while raising operation efficiency.
In the heat pump hot water supply and cooling/heating device described in Patent Literature 5, from the amount of used hot water and the cooling operation time on the previous day, the cooling operation time on the following day is predicted and the amount of hot water to be stored by using the waste heat generated in cooling is set, and the amount of stored hot water to be boiled by hot water storage operation during the nighttime is determined, thereby reducing power consumption and preventing running out of hot water in the hot water storage tank. However, because heat is stored during the nighttime, radiation loss occurs, leading to deterioration of energy saving performance.
The present invention computes the minimum hot water supply capacity target required for avoiding running out of hot water, from the actual hot water usage by the user in the past, the heat stored in the hot water storage tank, and the hot water supply time, and performs a hot water supply operation in such a way that the hot water supply capacity becomes the target value. Accordingly, it is an object of the present invention to achieve high operation efficiency by lowering the operating frequency of the compressor in accordance with the hot water supply capacity.

Solution to Problem

A refrigeration cycle apparatus according to the present invention is a refrigeration cycle apparatus through which a refrigerant is circulated, including:
a refrigeration cycle mechanism that has a compressor whose operating frequency can be controlled, a first radiator that supplies heat by means of the refrigerant to tank water that is water stored in a hot water storage tank, a first pressure-reducing mechanism, and a first evaporator, the refrigerant circulating in an order of the compressor, the first radiator, the first pressure-reducing mechanism, and the first evaporator; and
a controller,
wherein the controller includes
a memory section that stores control period information indicating a preset control period, and is capable of storing other information,
a computing section that calculates heat supply indicating a quantity of heat that has been supplied to the tank water from the first radiator with reference to a predetermined time, on a basis of a predetermined heat supply calculation rule, stores the calculated outgoing heat supply into the memory section, and computes current heat storage in the tank water on a basis of a predetermined heat storage calculation rule, and
a controlling section that controls an operating frequency of the compressor on a basis of the control period information stored in the memory section, the outgoing heat supply stored in the memory section, and the current heat storage calculated by the computing section.

Advantageous Effects of Invention

The present invention can provide a refrigeration cycle apparatus that makes it possible to avoid running out of hot water, and perform a hot water supply operation with high operation efficiency.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a schematic diagram illustrating the refrigerant circuit configuration of a combined air-conditioning and hot water supply system 100 according to Embodiment 1.

FIG. 2 is a schematic diagram illustrating the flow of water from a hot water supply unit 304 to a tank unit 305 according to Embodiment 1.

FIG. 3 schematically illustrates a controller 110 according to Embodiment 1.

FIG. 4 illustrates the operations of a four-way valve and solenoid valves with respect to operation modes according to Embodiment 1.

FIG. 5 illustrates the heat consumption of a hot water storage tank 27 at various times in a given day, according to Embodiment 1.

FIG. 6 schematically illustrates a hot water supply operation according to Embodiment 1.

FIG. 7 illustrates a method of computing heat stored in the hot water storage tank 27 according to Embodiment 1.

FIG. 8 is a flowchart of control of a compressor in a simultaneous heating and hot water supply operation mode D according to Embodiment 1.

FIG. 9 is a flowchart of control of the compressor in a simultaneous cooling and hot water supply operation mode E according to Embodiment 1.

DESCRIPTION OF EMBODIMENTS

Embodiment

1

Hereinafter, Embodiment 1 will be described with reference to the drawings.
FIG. 1 is a refrigerant circuit diagram of a combined air-conditioning and hot water supply system 100 (refrigeration cycle apparatus) according to Embodiment 1. In the drawings below including FIG. 1, the relative sizes of various components may sometimes differ from the actuality. Further, in this specification, for those symbols used in mathematical expressions which appear for the first time in the specification, the units for the corresponding symbols are written inside [ ]. Dimensionless quantities (no units) will be represented as [-].
FIG. 2 is a schematic diagram illustrating the flow of water from a hot water supply unit 304 to a tank unit 305 in the combined air-conditioning and hot water supply system 100.
FIG. 3 schematically illustrates various sensors and a controller 110 of the combined air-conditioning and hot water supply system 100. Hereinafter, the configuration of the combined air-conditioning and hot water supply system 100 will be described with reference to FIGS. 1 to 3. The combined air-conditioning and hot water supply system 100 is a three-pipe multi-system combined air-conditioning and hot water supply system that can simultaneously handle a selected cooling operation or heating operation in a use unit and a hot water supply operation in a hot water supply unit, by carrying out a vapor compression refrigeration cycle operation. In hot water supply operation, the combined air-conditioning and hot water supply system 100 lowers the frequency of a compressor to perform hot water supply with high efficiency, thereby preventing running out of hot water. Moreover, the combined air-conditioning and hot water supply system 100 can also avoid running out of hot water by lowering the frequency of the compressor in accordance with the cooling load, in the simultaneous operation of cooling and hot water supply.

The combined air-conditioning and hot water supply system 100 has a heat source unit 301, a branch unit 302, use units 303 a and 303 b, the hot water supply unit 304, and the tank unit 305. The heat source unit 301 and the branch unit 302 are connected via a liquid extension pipe 7 that is a refrigerant pipe, and a gas extension pipe 13 that is a refrigerant pipe. One side of the hot water supply unit 304 is connected to the heat source unit 301 via a hot water supply gas extension pipe 16 that is a refrigerant pipe, and the other side of the hot water supply unit 304 is connected to the branch unit 302 via a hot water supply liquid pipe 19 that is a refrigerant pipe. The use units 303 a and 303 b and the branch unit 302 are connected via indoor gas pipes 12 a and 12 b that are refrigerant pipes, and indoor liquid pipes 9 a and 9 b that are refrigerant pipes, respectively. The tank unit 305 and the hot water supply unit 304 are connected by an upstream water pipe 22 that is a water pipe, and a downstream water pipe 23 that is a water pipe. The upstream water pipe 22 and the downstream water pipe 23 form a water flow path that is a flow path for water that enters a plate water-heat exchanger 17 from a hot water storage tank 27, passes through the plate water-heat exchanger 17, and returns to the hot water storage tank 27.
While Embodiment 1 is directed to a case where a single heat source unit, two use units, a single hot water supply unit, and a single tank unit are connected, the present invention is not limited to this case. The numbers of these components may be more than or equal to, or less than or equal to those illustrated in the drawings. The refrigerant used in the combined air-conditioning and hot water supply system 100 is R410A. The refrigerant used in the combined air-conditioning and hot water supply system 100 is not limited to this but may be, for example, a hydrofluorocarbon (HFC) refrigerant such as R407C or R404A, a hydrochlorofluorocarbon (HCFC) refrigerant such as R22 or R134a, or a refrigerant that operates at a critical pressure or more such as CO2 refrigerant.
The combined air-conditioning and hot water supply system 100 includes a controller 110 as illustrated in FIG. 1. The controller 110 includes a measuring section 101, a computing section 102, a controlling section 103, a memory section 104, and a clock section 105. Various controls described below are all executed by the controller 110. While the controller 110 is arranged in the heat source unit 301 in FIG. 1, this is merely an example. The location where the controller 110 is arranged is not limited.

Operation modes that can be executed by the combined air-conditioning and hot water supply system 100 will be briefly described. In the combined air-conditioning and hot water supply system 100, the operation mode of the heat source unit 301 is determined in accordance with the hot water supply request on the hot water supply unit 304 being connected, and the presence/absence of a cooling load or heating load on the use units 303 a and 303 b. The combined air-conditioning and hot water supply system 100 is capable of executing five operation modes described below.
The five operation modes are a cooling operation mode A, a heating operation mode B, a hot water supply operation mode C, a simultaneous heating and hot water supply operation mode D, and a simultaneous cooling and hot water supply operation mode E.
(1) The cooling operation mode A is an operation mode of the heat source unit 301 when there is no hot water supply request signal (also referred to as hot water supply request) and the use units 303 a and 303 b execute a cooling operation.
(2) The heating operation mode B is an operation mode of the heat source unit 301 when there is no hot water supply request signal and the use units 303 a and 303 b execute a heating operation.
(3) The hot water supply operation mode C is an operation mode of the heat source unit 301 when there is no air conditioning load and the hot water supply unit 304 executes a hot water supply operation.
(4) The simultaneous heating and hot water supply operation mode D is an operation mode of the heat source unit 301 when executing a simultaneous operation of a heating operation by the use units 303 a and 303 b and a hot water supply operation by the hot water supply unit 304.
(5) The simultaneous cooling and hot water supply operation mode E is an operation mode of the heat source unit 301 when executing a simultaneous operation of a cooling operation by the use units 303 a and 303 b and a hot water supply operation by the hot water supply unit 304.
<Use Units 303 a and 303 b>
The use units 303 a and 303 b are connected to the heat source unit 301 via the branch unit 302. The use units 303 a and 303 b are installed in a location that allows the use units 303 a and 303 b to blow conditioned air to an air-conditioned area (for example, concealed or suspended on the ceiling inside a building, or hung on the wall surface). The use units 303 a and 303 b are connected to the heat source unit 301 via the branch unit 302, the liquid extension pipe 7, and the gas extension pipe 13, and constitute a part of the refrigerant circuit.
Each of the use units 303 a and 303 b includes an indoor-side refrigerant circuit that constitutes a part of the refrigerant circuit. This indoor-side refrigerant circuit is configured by indoor heat exchangers 10 a and 10 b each serving as a use-side heat exchanger. In addition, the use units 303 a and 303 b are provided with indoor air-sending devices 11 a and 11 b for supplying conditioned air that has exchanged heat with the refrigerant in the indoor heat exchangers 10 a and 10 b, respectively, to an air-conditioned area such as an indoor area.
Each of the indoor heat exchangers 10 a and 10 b can be configured by, for example, a cross-fin type fin-and-tube heat exchanger including a heat-transfer tube and a number of fins. Each of the indoor heat exchangers 10 a and 10 b may be also configured by a micro-channel heat exchanger, a shell-and-tube heat exchanger, a heat-pipe heat exchanger, or a double-pipe heat exchanger. When the operation mode executed by the use units 303 a and 303 b is the cooling operation mode A, the indoor heat exchangers 10 a and 10 b each function as an evaporator for the refrigerant to cool the air in the air-conditioned area, and when the operation mode executed by the use units 303 a and 303 b is the heating operation mode B, the indoor heat exchangers 10 a and 10 b each function as a condenser (or a radiator) for the refrigerant to heat the air in the air-conditioned area.
The indoor air-sending devices 11 a and 11 b respectively have the function of causing indoor air to be sucked into the use units 303 a and 303 b, and after making the indoor air exchange heat with the refrigerant in the indoor heat exchangers 10 a and 10 b, supplying the air to the air-conditioned area as conditioned air. That is, in the use units 303 a and 303 b, heat can be exchanged between the indoor air introduced by the indoor air-sending devices 11 a and 11 b, and the refrigerant flowing through the indoor heat exchangers 10 a and 10 b, respectively. The indoor air-sending devices 11 a and 11 b are configured to be able to vary the flow rates of conditioned air supplied to the indoor heat exchangers 10 a and 10 b, respectively. For example, the indoor air-sending devices 11 a and 11 b each include a fan such as a centrifugal fan or a multi-blade fan, and a motor that drives this fan, for example, a DC fan motor.

(Sensors)

Further, the use units 303 a and 303 b are respectively provided with various sensors described below:
(1) indoor liquid temperature sensors 206 a and 206 b that are provided on the liquid side of the indoor heat exchangers 10 a and 10 b (the liquid side of the indoor heat exchangers 10 a and 10 b when acting as a radiator), and detect the temperature of a liquid refrigerant;
(2) indoor gas temperature sensors 207 a and 207 b that are provided on the gas side of the indoor heat exchangers 10 a and 10 b (the gas side of the indoor heat exchangers 10 a and 10 b when acting as a radiator), and detect the temperature of a gas refrigerant; and
(3) indoor suction temperature sensors 208 a and 208 b that are provided on the suction port side of the indoor air of the use units 303 a and 303 b, and detect the temperature of the indoor air entering the unit.
As illustrated in FIG. 3, the operations of the indoor air-sending devices 11 a and 11 b are controlled by the controlling section 103 that functions as normal operation control means for performing normal operation of the use units 303 a and 303 b including the cooling operation and the heating operation.

The hot water supply unit 304 is connected to the heat source unit 301 via the branch unit 302. As illustrated in FIG. 2, the hot water supply unit 304 has the function of supplying hot water to the tank unit 305 that is installed outside a building, for example, and heating and boiling the water in the hot water storage tank 27. The plate water-heat exchanger 17 of the hot water supply unit 304 includes a connecting part 24 (water inflow pipe connecting part) to which the upstream water pipe 22 (water inflow pipe) connects, and a connecting part 25 (water outflow pipe connecting part) to which the downstream water pipe 23 (water outflow pipe) connects. One side of the hot water supply unit 304 is connected to the heat source unit 301 via the hot water supply gas extension pipe 16, and the other side of the hot water supply unit 304 is connected to the branch unit 302 via the hot water supply liquid pipe 19. The hot water supply unit 304 constitutes a part of the refrigerant circuit in the combined air-conditioning and hot water supply system 100.
The hot water supply unit 304 includes a hot water supply-side refrigerant circuit that constitutes a part of the refrigerant circuit. This hot water supply-side refrigerant circuit has, as its constituent function, the plate water-heat exchanger 17 serving as a hot water supply-side heat exchanger. In addition, the hot water supply unit 304 is provided with a water supply pump 18 for sending water for supplying hot water that has exchanged heat with the refrigerant in the plate water-heat exchanger 17 to the tank unit 305 or the like.
In the hot water supply operation mode C executed by the hot water supply unit 304, the plate water-heat exchanger 17 functions as a condenser for the refrigerant, and heats the water supplied by the water supply pump 18. The water supply pump 18 has the function of supplying water into the hot water supply unit 304, causing the water to exchange heat in the plate water-heat exchanger 17 and turn into hot water, and thereafter supplying the hot water into the tank unit 305 for heat exchange with the water in the hot water storage tank 27 (tank water). That is, in the hot water supply unit 304, heat can be exchanged between the water supplied from the water supply pump 18 and the refrigerant flowing through the plate water-heat exchanger 17, and also heat can be exchanged between the water supplied from the water supply pump 18 and the water in the hot water storage tank 27. Moreover, the hot water supply unit 304 is configured to be able to vary the flow rate of water supplied to the plate water-heat exchanger 17.

(Sensors)

The hot water supply unit 304 is also provided with various sensors described below:
(1) a hot water supply liquid temperature sensor 209 that is provided on the liquid side of the plate water-heat exchanger 17, and detects the temperature of a liquid refrigerant;
(2) an inlet water temperature sensor 210 (inlet temperature sensor) that is provided in the water inflow part, and detects the inlet temperature of water entering the hot water supply unit 304;
(3) an outlet water temperature sensor 211 (outlet temperature sensor) that is provided in the water outflow part, and detects the outlet temperature of water exiting the hot water supply unit 304; and
(4) an intermediate water flow meter 219 (FIG. 2) that is provided in the water inflow part, and detects the volume flow rate of water entering the hot water supply unit 304.
As illustrated in FIG. 3, the operation of the water supply pump 18 is controlled by the controlling section 103 that functions as normal operation control means for performing normal operation of the hot water supply unit 304 including the hot water supply operation mode.

The tank unit 305 is installed outside a building, for example, and has the function of storing hot water boiled by the hot water supply unit 304. As illustrated in FIG. 2, the tank unit 305 has the hot water storage tank 27 for storing hot water. One side of the tank unit 305 is connected to the hot water supply unit 304 via the upstream water pipe 22, and the other side of the tank unit 305 is connected to the hot water supply unit 304 via the downstream water pipe 23. The tank unit 305 constitutes a part of a water circuit in the combined air-conditioning and hot water supply system 100. The hot water storage tank 27 is of an always-full type. As the user consumes water, hot water exits from the top of the tank, and city water is supplied from the bottom of the tank in accordance with the amount of the consumed hot water.
The water fed by the water supply pump 18 in the hot water supply unit 304 is heated by the refrigerant in the plate water-heat exchanger 17 and turns into hot water, and enters the hot water storage tank 27 via the downstream water pipe 23. The hot water exchanges heat with the water in the hot water storage tank 27 as intermediate water and turns into cold water, without mixing with the water in the hot water storage tank 27. Thereafter, the cold water exits the hot water storage tank 27, and enters the hot water supply unit 304 again via the upstream water pipe 22. After being fed again by the water supply pump 18, the cold water turns into hot water in the plate water-heat exchanger 17. Through this process, hot water is boiled in the tank unit 305.
The method of heating the water in the tank unit 305 is not limited to the heat exchange method using intermediate water as in Embodiment 1. Alternatively, a heating method may be employed in which the water in the hot water storage tank 27 is directly passed through a pipe so as to exchange heat and turn into hot water in the plate water-heat exchanger 17, and returned to the hot water storage tank 27 again.

(Sensors)

The tank unit 305 is also provided with various sensors described below:
(1) a first hot-water-storage-tank water temperature sensor 212 that is provided on a side surface of the hot water storage tank 27, and detects the hot water temperature of an upper side surface of the hot water storage tank 27;
(2) a second hot-water-storage-tank water temperature sensor 213 that is provided on a side surface of the hot water storage tank 27, and detects the hot water temperature of the side surface of a portion of the hot water storage tank 27 located below the first hot-water-storage-tank water temperature sensor 212;
(3) a third hot-water-storage-tank water temperature sensor 214 that is provided on a side surface of the hot water storage tank 27, and detects the hot water temperature of the side surface of a portion of the hot water storage tank 27 located below the second hot-water-storage-tank water temperature sensor 213;
(4) a fourth hot-water-storage-tank water temperature sensor 215 that is provided on a side surface of the hot water storage tank 27, and detects the hot water temperature of the side surface of a portion of the hot water storage tank 27 located below the third hot-water-storage-tank water temperature sensor 214;
(5) a hot-water-storage-tank exiting water temperature sensor 216 that is provided in the water exit part of the hot water storage tank 27, and detects the temperature of water exiting the hot water storage tank 27;
(6) a hot-water-storage-tank entering water temperature sensor 217 that is provided in the water supply part of the hot water storage tank 27, and detects the temperature of water entering the hot water storage tank 27; and
(7) a tank water flow meter 218 that is provided in the water exit part of the hot water storage tank 27, and detects the flow rate of water exiting the hot water storage tank 27.

The heat source unit 301 is installed outside a building, for example. The heat source unit 301 is connected to the use units 303 a and 303 b via the liquid extension pipe 7, the gas extension pipe 13, and the branch unit 302. The heat source unit 301 is also connected to the hot water supply unit 304 via the hot water supply gas extension pipe 16, the liquid extension pipe 7, and the branch unit 302. The heat source unit 301 constitutes a part of the refrigerant circuit in the combined air-conditioning and hot water supply system 100.
The heat source unit 301 includes an outdoor-side refrigerant circuit that constitutes a part of the refrigerant circuit. This outdoor-side refrigerant circuit has, as its constituent devices, a compressor 1 that compresses the refrigerant, a four-way valve 3 for switching the direction of flow of the refrigerant in accordance with the outdoor operation mode, three solenoid valves (a first discharge solenoid valve 2, a second discharge solenoid valve 15, and a low-pressure equalizing solenoid valve 21), an outdoor heat exchanger 4 as a heat source-side heat exchanger, and an accumulator 14 for storing excess refrigerant. The heat source unit 301 also includes an outdoor air-sending device 5 for supplying air to the outdoor heat exchanger 4, and an outdoor pressure-reducing mechanism 6 serving as a heat source-side pressure-reducing mechanism for controlling the flow rate of the refrigerant to be distributed.
The compressor 1 sucks a refrigerant, and compresses the refrigerant into a high temperature/high pressure state. The compressor 1 that is equipped in Embodiment 1 is capable of varying operation capacity, and is configured by, for example, a positive displacement compressor that is driven by a motor (not illustrated) controlled by an inverter. While Embodiment 1 is directed to a case where there is only one compressor 1, the present invention is not limited to this. Depending on the number of use units 303 a and 303 b and hot water supply units 304 that are connected, or the like, two or more compressors 1 may be connected in parallel. Further, the discharge-side pipe connected to the compressor 1 divides into branches at a point, one of which is connected to the gas extension pipe 13 via the four-way valve 2, and the other is connected to the hot water supply gas extension pipe 16 via the second discharge solenoid valve 15.
The four-way valve 3, the first discharge solenoid valve 2, the second discharge solenoid valve 15, and the low-pressure equalizing solenoid valve 21 each function as a flow switching device that switches the direction of flow of the refrigerant in accordance with the operation mode of the heat source unit 301.
FIG. 4 illustrates details of the operations of the four-way valve and solenoid valves with respect to operation modes. The “solid line” and “broken line” indicated in FIG. 4 mean the “solid line” and “broken line” representing the switching states of the four-way valve 3 illustrated in FIG. 1, respectively.
The four-way valve 3 is switched into the state of “solid line” in the cooling operation mode A and the simultaneous cooling and hot water supply operation mode E. That is, in the cooling operation mode A and the simultaneous cooling and hot water supply operation mode E, the four-way valve 3 is switched so as to connect the suction side of the compressor 1 and the gas side of the indoor heat exchangers 10 a and 10 b, in order to make each of the indoor heat exchangers 10 a and 10 b function as an evaporator for the refrigerant that is compressed in the compressor 1. In the heating operation mode B, the hot water supply operation mode C, and the simultaneous heating and hot water supply operation mode D, the four-way valve 3 is switched into the state of “broken line”. That is, in the heating operation mode B, the hot water supply operation mode C, and the simultaneous heating and hot water supply operation mode D, the four-way valve 3 is switched so as to connect the suction side of the compressor 1 and the gas side of the outdoor heat exchanger 4, in order to make the outdoor heat exchanger 4 function as an evaporator for the refrigerant that is compressed in the compressor 1.
The first discharge solenoid valve 2 is switched so as to be “open” in the cooling operation mode A, the heating operation mode B, and the simultaneous cooling and hot water supply operation mode E. That is, in the cooling operation mode A, the first discharge solenoid valve 2 is switched so as to connect the discharge side of the compressor 1 and the gas side of the outdoor heat exchanger 4, in order to make the outdoor heat exchanger 4 function as a condenser for the refrigerant that is compressed in the compressor 1, and in the heating operation mode B and the simultaneous heating and hot water supply operation mode D, the first discharge solenoid valve 2 is switched so as to connect the discharge side of the compressor 1 and the gas side of the indoor heat exchangers 10 a and 10 b, in order to make each of the indoor heat exchangers 10 a and 10 b function as a condenser for the refrigerant that is compressed in the compressor 1. In addition, in the hot water supply operation mode C and the simultaneous heating and hot water supply operation mode D, the first discharge solenoid valve 2 is switched so as to be “closed”.
The second discharge solenoid valve 15 is switched so as to be “open” in the hot water supply operation mode C, the simultaneous heating and hot water supply operation mode D, and the simultaneous cooling and hot water supply operation mode E. That is, in the hot water supply operation mode C, the simultaneous heating and hot water supply operation mode D, and the simultaneous cooling and hot water supply operation mode E, the second discharge solenoid valve 15 connects the discharge side of the compressor 1 and the gas side of the plate water-heat exchanger 17, in order to make the plate water-heat exchanger 17 function as a condenser for the refrigerant that is compressed in the compressor 1. Moreover, in the cooling operation mode A and the heating operation mode B, the second discharge solenoid valve 15 is switched so as to be “closed”.
The low-pressure equalizing solenoid valve 21 is switched so as to be “open” in the simultaneous cooling and hot water supply operation mode E. That is, in the simultaneous cooling and hot water supply operation mode E, the low-pressure equalizing solenoid valve 21 connects the suction side of the compressor 1 and the gas side of the outdoor heat exchanger 4, in order to turn the outdoor heat exchanger 4 into a low pressure state. In addition, in the cooling operation mode A, the heating operation mode B, the hot water supply operation mode C, and the simultaneous heating and hot water supply operation mode D, the low-pressure equalizing solenoid valve 21 is switched so as to be “closed”.
The gas side of the outdoor heat exchanger 4 is connected to the four-way valve 3, and the liquid side of the outdoor heat exchanger 4 is connected to the outdoor pressure-reducing mechanism 6. The outdoor heat exchanger 4 can be configured by, for example, a cross-fin type fin-and-tube heat exchanger including a heat-transfer tube and a number of fins. Alternatively, the outdoor heat exchanger 4 may be configured as a micro-channel heat exchanger, a shell-and-tube heat exchanger, a heat-pipe heat exchanger, or a double-pipe heat exchanger. The outdoor heat exchanger 4 functions as a condenser for the refrigerant to cool the refrigerant in the cooling operation mode A, and functions as an evaporator for the refrigerant to heat the refrigerant in the heating operation mode B, the hot water supply operation mode C, the simultaneous heating and hot water supply operation mode D, and the simultaneous cooling and hot water supply operation mode E.
The outdoor air-sending device 5 has the function of sucking the outdoor air into the heat source unit 301, causing the outdoor air to exchange heat in the outdoor heat exchanger 4, and thereafter emitting the air outdoors. That is, in the heat source unit 301, heat can be exchanged between the outside air introduced by the outdoor air-sending device 5, and the refrigerant flowing through the outdoor heat exchanger 4. The outdoor air-sending device 5 is configured to be able to vary the flow rate of air supplied to the outdoor heat exchanger 4. The outdoor air-sending device 5 includes a fan such as a propeller fan, and a motor that drives this fan, for example, a DC fan motor.
The accumulator 14 is provided on the suction side of the compressor 1. The accumulator 14 has the function of storing a liquid refrigerant to prevent liquid backflow to the compressor 1 when an abnormality occurs in the combined air-conditioning and hot water supply system 100 or during the transient response of the operational state caused by a change in operation control.

(Sensors)

The heat source unit 301 is also provided with various sensors described below:
(1) a high-pressure sensor 201 that is provided on the discharge side of the compressor 1, and detects high-pressure side pressure;
(2) a discharge temperature sensor 202 that is provided on the discharge side of the compressor 1, and detects discharge temperature;
(3) an outdoor gas temperature sensor 203 that is provided on the gas side of the outdoor heat exchanger 4, and detects gas refrigerant temperature;
(4) an outdoor liquid temperature sensor 204 that is provided on the liquid side of the outdoor heat exchanger 4, and detects the temperature of a liquid refrigerant; and
(5) an outside air temperature sensor 205 that is provided on the suction port side of the outside air of the heat source unit 301, and detects the temperature of the outside air entering the unit.
The operations of the compressor 1, first discharge solenoid valve 2, four-way valve 3, outdoor air-sending device 5, outdoor pressure-reducing mechanism 6, second discharge solenoid valve 15, and low-pressure equalizing solenoid valve 21 are controlled by the controlling section 103 that functions as normal operation control means for performing normal operation including the cooling operation mode A, the heating operation mode B, the hot water supply operation mode C, the simultaneous heating and hot water supply operation mode D, and the simultaneous cooling and hot water supply operation mode E.

The branch unit 302 is installed inside a building, for example. The branch unit 302 is connected to the heat source unit 301 via the liquid extension pipe 7 and the gas extension pipe 13, is connected to the use units 303 a and 303 b via the indoor liquid pipes 9 a and 9 b and the indoor gas pipes 12 a and 12 b, respectively, and is connected to the hot water supply unit 304 via the hot water supply liquid pipe 19. The branch unit 302 constitutes a part of the refrigerant circuit in the combined air-conditioning and hot water supply system 100. The branch unit 302 has the function of controlling the flow of the refrigerant in accordance with the operation that is being required for each of the use units 303 a and 303 b and the hot water supply unit 304.
The branch unit 302 includes a branch refrigerant circuit that constitutes a part of the refrigerant circuit. This branch refrigerant circuit has, as its constituent devices, indoor pressure-reducing mechanisms 8 a and 8 b each serving as use-side pressure-reducing mechanism for controlling the flow rate of the refrigerant to be distributed, and a hot water supply pressure-reducing mechanism 20 for controlling the flow rate of the refrigerant to be distributed.
The indoor pressure-reducing mechanisms 8 a and 8 b are provided in the indoor liquid pipes 9 a and 9 b, respectively. The hot water supply pressure-reducing mechanism 20 is provided in the hot water supply liquid pipe 19 within the branch unit 302. The indoor pressure-reducing mechanisms 8 a and 8 b each function as a pressure reducing valve or an expansion valve. In the cooling operation mode A, the indoor pressure-reducing mechanisms 8 a and 8 b reduce the pressure of the refrigerant flowing through the liquid extension pipe 7, and in the simultaneous cooling and hot water supply operation mode E, the indoor pressure-reducing mechanisms 8 a and 8 b reduce the pressure of the refrigerant flowing through the hot water supply pressure-reducing mechanism 20, thereby causing the refrigerant to expand. In the heating operation mode B and the simultaneous heating and hot water supply operation mode D, the indoor pressure-reducing mechanisms 8 a and 8 b reduce the pressures of refrigerant flowing through the indoor liquid pipes 9 a and 9 b, respectively, thereby causing the refrigerant to expand. The hot water supply pressure-reducing mechanism 20 functions as a pressure reducing valve or an expansion valve. In the hot water supply operation mode C and the simultaneous heating and hot water supply operation mode D, the hot water supply pressure-reducing mechanism 20 reduces the pressure of the refrigerant flowing through the hot water supply liquid pipe 19 to thereby cause the refrigerant to expand. The indoor pressure-reducing mechanisms 8 a and 8 b and the hot water supply pressure-reducing mechanism 20 are each preferably configured so that its opening degree can be variably controlled, for example, precision flow control means formed by an electronic expansion valve, or inexpensive refrigerant flow control means such as a capillary.
As illustrated in FIG. 3, the operation of the hot water supply pressure-reducing mechanism 20 is controlled by the controlling section 103 of the controller 110 that functions as normal operation control means for performing normal operation of the hot water supply unit 304 including the hot water supply operation (see FIG. 3). In addition, the operations of the indoor pressure-reducing mechanisms 8 a and 8 b are controlled by the controlling section 103 that functions as normal operation control means for performing normal operation of the use units 303 a and 303 b including the cooling operation and the heating operation.
As illustrated in FIG. 3, various quantities detected by various temperature sensors and pressure sensors are inputted to the measuring section 101, and processed in the computing section 102. Then, on the basis of the processing results in the computing section 102, the controlling section 103 controls the compressor 1, the first discharge solenoid valve 2, the four-way valve 3, the outdoor air-sending device 5, the outdoor pressure-reducing mechanism 6, the indoor pressure-reducing mechanisms 8 a and 8 b, the indoor air-sending devices 11 and 11 b, the second discharge solenoid valve 15, the water supply pump 18, and the hot water supply pressure-reducing mechanism 20. That is, the operation of the combined air-conditioning and hot water supply system 100 is controlled in an integrated manner by the controller 110 including the measuring section 101, the computing section 102, and the controlling section 103. The controller 110 can be configured by a microcomputer. Computational expressions in the following description of Embodiment 1 are computed by the computing section 102, and the controlling section 103 controls various devices such as the compressor 1 in accordance with the computation results. Data used in the computing section 102, computation results, and the like are stored in the memory section 104. The clock section 105 outputs the current time.
Specifically, on the basis of the operation mode inputted via a remote control (for example, a cooling request signal that requests the cooling operation of the use units 303 a or 303 b), a hot water supply request signal described later, designation of a set temperature or the like, and information detected by various sensors, the controlling section 103 executes various operation modes by controlling:
the driving frequency of the compressor 1;
switching of the first discharge solenoid valve 2;
switching of the four-way valve 3;
the rotation speed (including ON/OFF) of the outdoor air-sending device 5;
the opening degree of the outdoor pressure-reducing mechanism 6;
the opening degrees of the indoor pressure-reducing mechanisms 8 a and 8 b;
the rotation speeds (including ON/OFF) of the indoor air-sending devices 11 a and 11 b;
switching of the second discharge solenoid valve 15;
the rotation speed (including ON/OFF) of the water supply pump 18;
the opening degree of the hot water supply pressure-reducing mechanism 20; and
switching of the low-pressure equalizing solenoid valve 21.
The measuring section 101, the computing section 102, the controlling section 103, the memory section 104, and the clock section 105 may be provided integrally, or may be provided separately. Alternatively, the measuring section 101, the computing section 102, the controlling section 103, the memory section 104, and the clock section 105 may be provided in one of the units. Further, the measuring section 101, the computing section 102, the controlling section 103, the memory section 104, and the clock section 105 may be provided in each unit.

The combined air-conditioning and hot water supply system 100 executes the cooling operation mode A, the heating operation mode B, the hot water supply operation mode C, the simultaneous heating and hot water supply operation mode D, and the simultaneous cooling and hot water supply operation mode E by controlling various devices equipped to the heat source unit 301, the branch unit 302, the use units 303 a and 303 b, and the hot water supply unit 304 in accordance with an air conditioning load required for each of the use units 303 a and 303 b, and a hot water supply request made to the hot water supply unit 304.

Specific refrigerant flow methods and normal control methods for individual devices in the cooling operation mode A, the heating operation mode B, the hot water supply operation mode C, the simultaneous heating and hot water supply operation mode D, and the simultaneous cooling and hot water supply operation mode E executed by the combined air-conditioning and hot water supply system 100 will be described. The operations of the four-way valve 3 in individual operation modes are as illustrated in FIG. 4.

[Cooling Operation Mode A]

In the cooling operation mode A, the four-way valve 3 is in the state indicated by the solid line, that is, a state in which the discharge side of the compressor 1 is connected to the gas side of the outdoor heat exchanger 4. Further, the first discharge solenoid valve 2 is open, the second discharge solenoid valve 15 is closed, and the low-pressure equalizing solenoid valve 21 is closed. Further, the opening degree of the hot water supply pressure-reducing mechanism 20 is at the minimum (fully closed).
In this state of the refrigerant circuit, the compressor 1, the outdoor air-sending device 5, and the indoor air-sending devices 11 a and 11 b are activated. Then, a low-pressure gas refrigerant is sucked into the compressor 1, where the refrigerant is compressed into a high temperature/high pressure gas refrigerant. Thereafter, the high temperature/high pressure gas refrigerant enters the outdoor heat exchanger 4 via the first discharge solenoid valve 2 and the four-way valve 3, where the gas refrigerant is condensed by exchanging heat with the outdoor air supplied by the outdoor air-sending device 5, and turns into a high-pressure liquid refrigerant. After exiting the outdoor heat exchanger 4, the refrigerant flows to the outdoor pressure-reducing mechanism 6, where its pressure is reduced. Thereafter, the refrigerant enters the branch unit 302 via the liquid extension pipe 7. At this time, the outdoor pressure-reducing mechanism 6 is being controlled to the maximum opening degree (fully open). The refrigerant that has entered the branch unit 302 is reduced in pressure in the indoor pressure-reducing mechanisms 8 a and 8 b, and turns into a two-phase gas-liquid refrigerant at low pressure. Thereafter, the refrigerant exits the branch unit 302, and enters the use units 303 a and 303 b via the indoor liquid pipes 9 a and 9 b.
The refrigerant that has entered the use units 303 a and 303 b enters the indoor heat exchangers 10 a and 10 b, and is evaporated and turns into a low-pressure gas refrigerant by exchanging heat with the indoor air supplied by the indoor air-sending devices 11 a and 11 b. Here, each of the indoor pressure-reducing mechanisms 8 a and 8 b is controlled so that there is no temperature difference (cooled indoor temperature difference) in the use unit 303 a or 303 b, which is calculated by subtracting a set temperature from the indoor suction temperature detected by the indoor suction temperature sensor 208 a or 208 b. Accordingly, refrigerant flows through each of the indoor heat exchangers 10 a and 10 b at a flow rate suited to the cooling load required for the air-conditioned space where the use unit 303 a or 303 b is installed.
The refrigerant that has exited the indoor heat exchangers 10 a and 10 b exits the use units 303 a and 303 b, and flows to the gas extension pipe 13 after passing through the indoor gas pipes 12 a and 12 b and the branch unit 302. The refrigerant then passes through the accumulator 14 via the four-way valve 3, and is sucked into the compressor 1 again.
The operating frequency of the compressor 1 is controlled by the controlling section 103 so that the evaporating temperature becomes a predetermined value in accordance with the maximum cooled indoor temperature difference. Here, the evaporating temperature is the temperature detected by the indoor liquid temperature sensor 206 a or 206 b. The maximum cooled indoor temperature difference is the temperature difference in either one of the use units 303 a and 303 b in which the temperature difference (cooled indoor temperature difference) calculated by subtracting a set temperature from the indoor suction temperature detected by the indoor suction temperature sensor 208 a or 208 b is maximum. Specifically, the operating frequency of the compressor 1 is controlled by the controlling section 103 so that the evaporating temperature becomes a predetermined value in accordance with the maximum cooled indoor temperature difference. In addition, the air flow of the outdoor air-sending device 5 is controlled by the controlling section 103 so that the condensing temperature becomes a predetermined value in accordance with the outside air temperature detected by the outside air temperature sensor 205. Here, the condensing temperature is the saturation temperature computed from the pressure detected by the high-pressure sensor 201.

[Heating Operation Mode B]

In the heating operation mode B, the four-way valve 3 is in the state indicated by the broken line, that is, a state in which the discharge side of the compressor 1 is connected to the gas side of the indoor heat exchangers 10 a and 10 b, and the suction side of the compressor 1 is connected to the gas side of the outdoor heat exchanger 4. In addition, the first discharge solenoid valve 2 is open, the second discharge solenoid valve 15 is closed, and the low-pressure equalizing solenoid valve 21 is closed. Further, the hot water supply pressure-reducing mechanism 20 is fully closed.
In this state of the refrigerant circuit, the compressor 1, the outdoor air-sending device 5, the indoor air-sending devices 11 a and 11 b, and the water supply pump 18 are activated. Then, a low-pressure gas refrigerant is sucked into the compressor 1, where the refrigerant is compressed into a high temperature/high pressure gas refrigerant. Thereafter, the high temperature/high pressure gas refrigerant flows through the first discharge solenoid valve 2 and the four-way valve 3.
The refrigerant that has entered the four-way valve 3 exits the heat source unit 301, and flows to the branch unit 302 via the gas extension pipe 13. Thereafter, the refrigerant enters the use units 303 a and 303 b via the indoor gas pipes 12 a and 12 b. The refrigerant that has entered the use units 303 a and 303 b enters the indoor heat exchangers 10 a and 10 b, where the refrigerant is condensed by exchanging heat with the indoor air supplied by the indoor air-sending devices 11 a and 11 b and turns into a high-pressure liquid refrigerant, and exits the indoor heat exchangers 10 a and 10 b. The refrigerant that has heated the indoor air in the indoor heat exchangers 10 a and 10 b exits the use units 303 a and 303 b, and enters the branch unit 302 via the indoor liquid pipes 9 a and 9 b. Then, the refrigerant is reduced in pressure by the indoor pressure-reducing mechanisms 8 a and 8 b, and turns into a two-phase gas-liquid or liquid-phase refrigerant. Thereafter, the refrigerant exits the branch unit 302.
Each of the indoor pressure-reducing mechanisms 8 a and 8 b is controlled so that there is no temperature difference (heated indoor temperature difference) in the use unit 303 a or 303 b, which is calculated by subtracting an indoor set temperature from the indoor suction temperature detected by the indoor suction temperature sensor 208 a or 208 b. Accordingly, refrigerant flows through each of the indoor heat exchangers 10 a and 10 b at a flow rate suited to the heating load required for the air-conditioned space where the use unit 303 a or 303 b is installed.
The refrigerant that has exited the branch unit 302 enters the heat source unit 301 via the liquid extension pipe 7, and after passing through the outdoor pressure-reducing mechanism 6, the refrigerant enters the outdoor heat exchanger 4. The opening degree of the outdoor pressure-reducing mechanism 6 is being controlled to the full opening. The refrigerant that has entered the outdoor pressure-reducing mechanism 6 is evaporated by exchanging heat with the outside air supplied by the outdoor air-sending device 5, and turns into a low-pressure gas refrigerant. After exiting the outdoor heat exchanger 4, this refrigerant passes through the accumulator 14 via the four-way valve 3, and is thereafter sucked into the compressor 1 again.
The operating frequency of the compressor 1 is controlled by the controlling section 103 so that the condensing temperature becomes a predetermined value in accordance with the maximum heated indoor temperature difference. The method of calculating the condensing temperature is the same as that in the case of the cooling operation. In addition, the maximum heated indoor temperature difference is the temperature difference in either one of the use units 303 a and 303 b in which the temperature difference (heated indoor temperature difference) calculated by subtracting an indoor set temperature from the indoor suction temperature detected by the indoor suction temperature sensor 208 a or 208 b is maximum. Further, the air flow of the outdoor air-sending device 5 is controlled by the controlling section 103 so that the evaporating temperature becomes a predetermined value in accordance with the outside air temperature detected by the outside air temperature sensor 205. Here, the evaporating temperature is calculated from the temperature detected by the outdoor liquid temperature sensor 204.

[Hot Water Supply Operation Mode C]

In the hot water supply operation mode C, the four-way valve 3 is in the state indicated by the broken line, that is, a state in which the discharge side of the compressor 1 is connected to the gas side of the plate water-heat exchanger 17, and the suction side of the compressor 1 is connected to the gas side of the outdoor heat exchanger 4. In addition, the first discharge solenoid valve 2 is closed, the second discharge solenoid valve 15 is open, and the low-pressure equalizing solenoid valve 21 is closed. Further, the indoor pressure-reducing mechanisms 8 a and 8 b are fully closed.
In this state of the refrigerant circuit, the compressor 1, the outdoor air-sending device 5, the indoor air-sending devices 11 a and 11 b, and the water supply pump 18 are activated. Then, a low-pressure gas refrigerant is sucked into the compressor 1, where the refrigerant is compressed into a high temperature/high pressure gas refrigerant. Thereafter, the high temperature/high pressure gas refrigerant enters the second discharge solenoid valve 15.
The refrigerant that has entered the second discharge solenoid valve 15 exits the heat source unit 301, and enters the hot water supply unit 304 via the hot water supply gas extension pipe 16. The refrigerant that has entered the hot water supply unit 304 enters the plate water-heat exchanger 17, where the refrigerant is condensed by exchanging heat with the water supplied by the water supply pump 18 and turns into a high-pressure liquid refrigerant, and exits the plate water-heat exchanger 17 (first radiator). After the refrigerant that has heated the water in the plate water-heat exchanger 17 exits the hot water supply unit 304, the refrigerant enters the branch unit 302 via the hot water supply liquid pipe 19, and is reduced in pressure by the hot water supply pressure-reducing mechanism 20 (first pressure-reducing mechanism) and turns into a two-phase gas-liquid refrigerant at low pressure. Thereafter, the refrigerant exits the branch unit 302, and enters the heat source unit 301 via the liquid extension pipe 7.
The hot water supply pressure-reducing mechanism 20 is controlled by the controlling section 103 to such an opening degree that the degree of subcooling on the liquid side of the plate water-heat exchanger 17 becomes a predetermined value. The degree of subcooling on the liquid side of the plate water-heat exchanger 17 is calculated by computing the saturation temperature (condensing temperature) from the pressure detected by the high-pressure sensor 201, and subtracting the temperature detected by the hot water supply liquid temperature sensor 209 from the saturation temperature. The hot water supply pressure-reducing mechanism 20 controls the flow rate of refrigerant flowing through the plate water-heat exchanger 17 so that the degree of subcooling of the refrigerant on the liquid side of the plate water-heat exchanger 17 becomes a predetermined value. Consequently, the high-pressure liquid refrigerant that has been condensed in the plate water-heat exchanger 17 has a predetermined degree of subcooling. In this way, in the plate water-heat exchanger 17, refrigerant flows at a flow rate suited to the hot water supply request made in accordance with the usage condition of hot water in the facility where the hot water supply unit 304 is installed.
The refrigerant that has exited the branch unit 302 enters the heat source unit 301 via the liquid extension pipe 7, and after passing through the outdoor pressure-reducing mechanism 6, the refrigerant enters the outdoor heat exchanger 4 (first evaporator). The opening degree of the outdoor pressure-reducing mechanism 6 is being controlled to the full opening. The refrigerant that has entered the outdoor heat exchanger 4 is evaporated by exchanging heat with the outside air supplied by the outdoor air-sending device 5, and turns into a low-pressure gas refrigerant. After exiting the outdoor heat exchanger 4, this refrigerant passes through the accumulator 14 via the four-way valve 3, and is thereafter sucked into the compressor 1 again.
Here, the air flow of the outdoor air-sending device 5 is controlled by the controlling section 103 so that the evaporating temperature becomes a predetermined value in accordance with the outside air temperature detected by the outside air temperature sensor 205. Here, the evaporating temperature is the temperature detected by the outdoor liquid temperature sensor 204.
In the hot water supply operation mode according to related art, the operating frequency of the compressor 1 is controlled by the controlling section 103 to a high frequency in order to avoid running out of hot water. Consequently, high hot water supply capacity can be secured, and the water temperature within the hot water storage tank 27 can be raised to a set hot water supply temperature in the shortest possible time.
However, operation efficiency deteriorates in that case. Accordingly, in order to achieve high operation efficiency while avoiding running out of hot water, the operating frequency of the compressor 1 is controlled to a low frequency by using a record of past hot water usage. The control of the operating frequency of the compressor executed on the basis of Equations (1) to (7) below will be referred to as “hot water supply operation control”.
First, a hot water supply operation time Δt_start[sec] (control period information) is stored into the memory section 104 in advance (for example, 7200 sec). Next, the usage of hot water on the previous day, that is, the maximum heat consumption L_m(outgoing heat supply) of the tank unit 305 and the corresponding point in time t_mare stored into the memory section 104. Specifically, the computing section 102 computes the heat consumption of the tank unit 305 in a day every hour, calculates the time t_m[h: mm] at which the heat consumption is maximum and the maximum heat consumption L_m[kJ] at the corresponding time, and stores the computed values into the memory section 104 as learned values (the computing section acting as hot water supply load storing means). In this regard, “learning” means a process in which the controller 110 (the computing section 102) stores at least the heat consumption to be learned, and the occurrence time of the heat consumption into the memory section 104. Here, the time is set on the basis of time measurement by the clock section 105.
As illustrated in FIG. 5, the computing section 102 computes the power consumption of the hot water storage tank 27 at various times of a day every hour by using Equation (1) (outgoing heat supply calculation rule) (the computing section acting as hot water supply load computing means).
L _m=ρ_w ×C _{p, w} ×V _wo ×t _w×(T _tankwo −T _tankwi) (1)
where
C_{p, w}: specific heat of water [kJ/(kgK)],
L_m: maximum heat consumption (target hot-water heat storage) [kJ],
T_tankwi: supply water temperature [degrees C],
T_tankwo: exiting water temperature [degrees C],
V_wo: volume flow rate of exiting water [m³/s],
Δt_w: water exiting time [s], and
ρ_w: density of water [kg/m³].
T_tankwiis the smallest value of temperature detected in the past (for example, the smallest value of temperature detected in the past three days), among temperatures detected by the inlet water temperature sensor 210.
T_tankwois the temperature detected by the outlet water temperature sensor 211, and is the temperature detected at the time when water exits the hot water storage tank 27.
V_wois the volume flow rate detected by the tank water flow meter 218.
The largest one of the heat consumptions computed from Equation (1) is the maximum heat consumption L_m, and the corresponding point in time is the maximum consumption time t_m. The maximum heat consumption L_mand the maximum consumption time t_mrepresent information related to the hot water supply load.
After elapse of one day, the controlling section 103 starts the hot water supply operation mode C when the time (hot water supply start time) that precedes the time t_mat which the maximum heat consumption L_mwas recorded on the previous day by Δt_startis reached as illustrated in FIG. 6. That is, the controlling section 103 controls the compressor 1 at the operating frequency described below. The operating frequency (target operating frequency F_m) of the compressor 1 in this case is determined by Equations (2) to (6).
Li=ρ _w ×C _{p, w} ×[V ₁×(T _tank1 −T _tankwi)+(V ₂ −V ₁)×(T _tank2 ×T _tankwi)+(V ₃ −V ₂)×(T _tank3 −T _tankwi)+(V ₄ −V ₃)×(T _tank4 −T _tankwi)] (2)
Q _wm=(L _m −L _i)/Δt _start (3)
T _wom =T _wi +Q _wm/(ρ_w ×C _{p, w} ×V _w) (4)
ΔF=f(T _wom −T _wo) (5)
F _m =F+ΔF (6)
where
C_{p, w}: specific heat of water [kJ/(kgK)],
F: operating frequency of the compressor 1 prior to control [Hz],
F_m: target operating frequency of the compressor 1 [Hz],
Δ_F: amount by which to change the operating frequency of the compressor 1 [Hz],
L_i: hot-water heat stored in the hot water storage tank 27 at the start of hot water supply [kJ],
L_m: maximum heat consumption (target hot-water heat storage) [kJ],
Q_wm: hot water supply capacity target [kW],
T_tank1temperature of hot water stored from the uppermost part to a first upper part of the hot water storage tank 27 [degrees C],
T_tank2: temperature of hot water stored from the first upper part to a second upper part of the hot water storage tank 27 [degrees C],
T_tank3: temperature of hot water stored from the second upper part to a third upper part of the hot water storage tank 27 [degrees C],
T_tank4: temperature of hot water stored from the third upper part to the lowermost part of the hot water storage tank 27 [degrees C],
T_tankwi: supply water temperature [degrees C] (which is detected by the sensor 217),
T_wi: inlet water temperature [degrees C] (which is detected by the sensor 210),
T_wo: outlet water temperature [degrees C] (which is detected by the sensor 211),
T_wom: outlet water temperature target [degrees C] (target temperature of T_wo),
Δt_start: hot water supply operation time [sec]
V₁: internal volume from the uppermost part to the first upper part of the hot water storage tank 27 [m³],
V₂: internal volume from the uppermost part to the second upper part of the hot water storage tank 27 [m³],
V₃: internal volume from the uppermost part to the third upper part of the hot water storage tank 27 [m³],
V₄: internal volume from the uppermost part to the lowermost part of the hot water storage tank 27 [m³],
V_w: volume flow rate of intermediate water [m³/s] (intermediate water flow meter 219), and
ρ_w: density of water [kg/m³].
FIG. 7 schematically illustrates a method of computing the heat stored in the hot water storage tank 27.
The expression “at the start of hot water supply” means the time corresponding to Δt_start.
Equation (2) is derived from the definitions as illustrated in FIG. 7.
T_widenotes the temperature of water entering the hot water supply unit 304 from the tank unit 305 (which is detected by the sensor 210),
T_wodenotes the temperature of water exiting the hot water supply unit 304 toward the tank unit 305 (which is detected by the sensor 211),
T_tank1denotes the temperature detected by the first hot-water-storage-tank water temperature sensor 212,
T_tank2denotes the temperature detected by the second hot-water-storage-tank water temperature sensor 213,
T_tank3denotes the temperature detected by the third hot-water-storage-tank water temperature sensor 214,
T_tank4denotes the temperature detected by the fourth hot-water-storage-tank water temperature sensor 215, and
V_wdenotes the volume flow rate detected by the intermediate water flow meter 219 (water flow meter).
As a specific procedure, the computing section 102 computes the hot-water heat storage Li in the hot water storage tank 27 at the start of hot water supply by Equation (2) (heat storage calculation rule) (the computing section 102 acting as heat storage computing means). Next, the computing section 102 computes the hot water supply capacity target Q_wmby using Equation (3) from the maximum heat consumption L_mand the hot water supply operation time Δt_startthat are obtained as a result of learning on the previous day. That is, the target value of the hot water supply capacity (heat rejection capacity) of the plate water-heat exchanger 17 (first radiator) is set. Next, by using the inlet water temperature T_wi, the computing section 102 computes the outlet water temperature target T_womfor the case where the hot water supply capacity target Q_wmis set, by Equation (4) (the computing section 102 acting as outlet water temperature target computing means). The outlet water temperature target T_womrefers to the target temperature of a water flow detected by the outlet water temperature sensor 211. Then, from the deviation between the outlet water temperature target T_womand the outlet water temperature T_wo, the computing section 102 computes the amount ΔF by which to change the operating frequency of the compressor 1 on the basis of Equation (5). Lastly, the computing section 102 computes the target operating frequency F_mof the compressor 1 by Equation (6). By determining the operating frequency of the compressor 1 through this procedure (hereinafter, sometimes referred to as compressor control procedure), running out of hot water can be avoided even when the operating frequency of the compressor 1 is set to a low value. Consequently, it is possible for the controlling section 103 to perform a hot water supply operation with high operation efficiency (the controlling section acting as heating control means).
(With Regard to Learning of L_mand t_m)
When a day is over, the maximum heat consumption L_mand the maximum consumption time t_mof the day are updated as learning results, and are applied to the next day. In this way, changes in the usage of hot water by the user can be reflected.
While the maximum heat consumption L_mand the maximum consumption time t_mare updated every day in the above example, the present invention is not limited to this. The maximum heat consumption L_mand the maximum consumption time t_mmay be learned from the usage of hot water over two days or one week. When these values are to be learned over a plurality of days equal to or more than two days, the maximum heat consumption L_mmay be calculated as the average of the plurality of days, and the maximum consumption time t_mmay be determined to be the time that has been learned the most. When the maximum heat consumption Lm and the maximum consumption time tm are to be learned over one week or more, these values may be calculated for each day of the week (Monday through Sunday). Increasing the number of days to be referenced in this way makes it possible to avoid running out of hot water with precision and ensure high operation efficiency. While learning is performed by dividing time in one-hour intervals, the present invention is not limited to this. Time may be divided in thirty-minute intervals or two-hour intervals.

(Inlet Water Temperature Sensor 210)

The inlet water temperature T_wiis set as the temperature detected by the inlet water temperature sensor 210. However, the present invention is not limited to this. The inlet water temperature T_wimay be set as the water temperature of the hot water storage tank by regarding the inlet water temperature as being equal to the water temperature of the hot water storage tank. Specifically, as illustrated in FIG. 2, the heat exchange part between intermediate water and the hot water stored in the hot water storage tank 27 is located in a lower part of the hot water storage tank 27, and the intermediate water outlet is located near the lowermost part of the tank. Accordingly, the inlet water temperature may be set as the temperature detected by the fourth hot-water-storage-tank water temperature sensor 215. In this way, it is possible to acquire the inlet water temperature T_wieven in the absence of the inlet water temperature sensor 210.

(Outlet Water Temperature Sensor 211)

The outlet water temperature T_wois set as the temperature detected by the outlet water temperature sensor 211. However, the present invention is not limited to this. For example, by regarding the condensing temperature of the plate water-heat exchanger 17 and the temperature detected by the outlet water temperature sensor 211 as being equal, the condensing temperature of the plate water-heat exchanger 17 (first radiator) may be computed from the saturation temperature of the pressure detected by the high-pressure sensor 201, and the computed condensing temperature may be used as the outlet water temperature T_wo. In this way, it is possible to acquire the outlet water temperature T_woeven in the absence of the outlet water temperature sensor 211.

(Rotation Speed Control for Water Supply Pump 18)

By lowering the rotation speed of the water supply pump 18 to reduce the flow rate V_wof intermediate water (first radiator inflow water), the outlet water temperature target T_wombecomes higher, and the temperature difference between the inlet water temperature and the outlet water temperature target becomes greater. Accordingly, by controlling the rotation speed of the water supply pump 18 so that the temperature difference between the inlet water temperature and the outlet water temperature target becomes a predetermined value or more (for example, 5 degrees C. or more), it is possible to prevent deterioration of controllability due to a sensor error. Therefore, the control section 103 can control the operating frequency of the compressor 1 with precision (the controlling section acting as water flow control means).
(Hot Water Supply Operation Time Δt_start)
In the foregoing description, the hot water supply operation time Δt_startis inputted in advance, and thereafter handled as a constant value without being updated. However, as is apparent from FIG. 6, the hot water supply capacity target Q_wmvaries with the hot water supply operation time Δt_start, and so does the operating frequency of the compressor 1. For this reason, depending on the usage condition of hot water by the user, the deviation between the maximum heat consumption L_mand the hot-water heat storage L_iin the hot water storage tank 27 at the start of hot water supply becomes large. Consequently, the hot water supply capacity target Q_wmcomputed by Equation (3) becomes large, and the operating frequency of the compressor 1 becomes high, resulting in a decrease in operation efficiency. Therefore, in order to ensure a constant operation efficiency, it is desirable to vary also the hot water supply operation time Δt_startin accordance with the usage condition of hot water by the user.
As a method to achieve this, a standard target hot water supply capacity Q_std(standard heat supply) is stored into the memory section 104 in advance, and the hot water supply operation time Δt_startis updated on the basis of the standard target hot water supply capacity Q_stdand the hot water supply capacity target Q_wm. Specifically, after the end of the hot water supply operation mode C, by regarding from Equation (3) that the reciprocals of the hot water supply capacity and hot water supply time are proportional, the computing section 102 computes the hot water supply operation time Δt_startby Equation (7) from the hot water supply capacity target Q_wmdetermined by Equation (3) and the standard hot water supply capacity Q_std(the computing section 102 acting as hot water supply time computing means).
Δt _start=(Q _wm /Q _std)×Δt _old=(L _m −L _i)/ΔQ _std (7)
where
Q_std: standard hot water supply capacity [kW], and
Δt_old: previous hot water supply time [sec].
The computing section 102 updates the hot water supply operation time Δt_startto the hot water supply operation time Δt_startdetermined by computation of Equation (7), from the previous hot water supply time Δt_old(past hot water supply time), and applies the updated hot water supply operation time Δt_startto the hot water supply operation from the next day onward. Because there is a possibility that the usage condition of hot water by the user may change, the hot water supply operation time Δt_startis learned again and updated at the end of a day. Determining the hot water supply operation time Δt_startin this way makes it possible for any user to control the hot water supply capacity to a predetermined value, thereby ensuring high operation efficiency.
Embodiment 1 is directed to the case where the compressor 1 is controlled only with respect to the maximum heat consumption L_min the usage of hot water by the user. However, the present invention is not limited to this. This control (hot water supply operation control) may be applied to the case of another heat consumption L_kby storing the heat consumption L_kand the corresponding point in time t_kinto the memory section 104. In this way, the hot water supply operation can be performed with high operation efficiency for any kind of load.

(Control for Plurality of Heat Consumptions)

In Embodiment 1, the load stored in the memory section 104 is only the maximum heat consumption L_m. However, the present invention is not limited to this. A plurality of (for example, two or three) kinds of loads (plurality of heat consumptions) may be stored in the memory section 104, and this control (hot water supply operation control) may be applied to each kind of load. At this time, since the target hot-water heat storage L_mvaries with the heat consumption, in order to obtain a predetermined hot water supply target Q_wmirrespective of the heat consumption, that is, irrespective of the target hot-water heat storage, the hot water supply time Δt_startneeds to be stored individually for each kind of load. In this way, it is possible to apply this control a plurality of times in a day, thereby achieving improved energy saving. Specifically, this is performed by the following procedure in a case where this control is to be applied for two kinds of loads, the maximum heat consumption and a second heat consumption (the maximum heat consumption>the second heat consumption).
(a) First, the maximum heat consumption in a day and the maximum consumption time that is the corresponding point in time are stored into the memory section 104, and a second heat consumption and a second consumption time that is the corresponding point in time are stored into the memory section 104.
(b) Then, after elapse of a day, the hot water supply operation mode C is started when the time that precedes the maximum consumption time by a maximum hot water supply time stored in the memory section 104 in advance is reached. The operating frequency of the compressor 1 in this case is determined by Equations (2) to (6).
(c) After the end of the hot water supply operation mode C, the maximum hot water supply time that is to be applied to the next day is computed from Equation (7).
(d) The hot water supply operation mode C is started when the time that precedes the second consumption time by a second hot water supply time stored in the memory section 104 in advance is reached. The operating frequency of the compressor 1 in this case is determined by Equations (2) to (6). After the end of the hot water supply operation mode C, the second hot water supply time that is to be applied to the next day is computed from Equation (7).
(e) Then, a hot water supply operation is executed on the next day in the same manner as the previous day.
While Embodiment 1 is directed to the case of the combined air-conditioning and hot water supply system 100, the present invention is not limited to this. The present technique can be applied also to the hot water supply operation of a hot water supply system in which the heat source unit 301 and the hot water supply unit 304 are connected by a refrigerant communication pipe, that is, a hot water supply system that does not have an air-conditioning function and is capable of only hot water supply operation.

[Simultaneous Heating and Hot Water Supply Operation Mode D]

In the simultaneous heating and hot water supply operation mode D (parallel heat rejection operation), the four-way valve 3 is in the state indicated by the broken line in FIG. 4, that is, the discharge side of the compressor 1 is connected to the gas side of the plate water-heat exchanger 17, and the suction side of the compressor 1 is connected to the gas side of the outdoor heat exchanger 4. Further, the first discharge solenoid valve 2 is open, the second discharge solenoid valve 15 is open, and the low-pressure equalizing solenoid valve 21 is closed.
In this state of the refrigerant circuit, the compressor 1, the outdoor air-sending device 5, the indoor air-sending devices 11 a and 11 b, and the water supply pump 18 are activated. Then, a low-pressure gas refrigerant is sucked into the compressor 1, where the gas refrigerant is compressed into a high temperature/high pressure gas refrigerant. Thereafter, the high temperature/high pressure gas refrigerant is distributed so as to flow through the first discharge solenoid valve 2 or the second discharge solenoid valve 15.
The refrigerant that has entered the second discharge solenoid valve 15 exits the heat source unit 301, and enters the hot water supply unit 304 via the hot water supply gas extension pipe 16. The refrigerant that has entered the hot water supply unit 304 enters the plate water-heat exchanger 17, where the refrigerant is condensed by exchanging heat with the water supplied by the water supply pump 18 and turns into a high-pressure liquid refrigerant, and exits the plate water-heat exchanger 17. After the refrigerant that has heated the water in the plate water-heat exchanger 17 exits the hot water supply unit 304, the refrigerant enters the branch unit 302 via the hot water supply liquid pipe 19, and is reduced in pressure by the hot water supply pressure-reducing mechanism 20 and turns into a two-phase gas-liquid refrigerant at low pressure. Thereafter, the refrigerant merges with the refrigerant that has flown through each of the indoor pressure-reducing mechanisms 8 a and 8 b at a branch part 26, and exits the branch unit 302. The flow path that branches out from the discharge side of the compressor 1 and leads to the first discharge solenoid valve 2, the four-way valve 3, the indoor heat exchangers 10 a and 10 b, and the indoor pressure-reducing mechanisms 8 a and 8 b is a branch flow path with respect to the flow path of the hot water supply operation (heat rejection branch flow path).
The hot water supply pressure-reducing mechanism 20 is controlled by the controlling section 103 to such an opening degree that the degree of subcooling on the liquid side of the plate water-heat exchanger 17 becomes a predetermined value. The degree of subcooling on the liquid side of the plate water-heat exchanger 17 is the same as in the case of the hot water supply operation. The hot water supply pressure-reducing mechanism 20 controls the flow rate of refrigerant flowing through the plate water-heat exchanger 17 so that the degree of subcooling of the refrigerant on the liquid side of the plate water-heat exchanger 17 becomes a predetermined value. Consequently, the high-pressure liquid refrigerant that has been condensed in the plate water-heat exchanger 17 has a predetermined degree of subcooling. In this way, in the plate water-heat exchanger 17, refrigerant flows at a flow rate suited to the hot water supply request made in accordance with the usage condition of hot water in the facility where the hot water supply unit 304 is installed.
Meanwhile, the refrigerant that has entered the first discharge solenoid valve 2 passes through the four-way valve 3, and thereafter, the refrigerant exits the heat source unit 301, and flows to the branch unit 302 via the gas extension pipe 13. Thereafter, the refrigerant enters the use units 303 a and 303 b via the indoor gas pipes 12 a and 12 b. The refrigerant that has entered the use units 303 a and 303 b enters the indoor heat exchangers 10 a and 10 b (second radiator), where the refrigerant exchanges heat with the indoor air supplied by the indoor air-sending devices 11 a and 11 b and turns into a high-pressure liquid refrigerant, and exits the indoor heat exchangers 10 a and 10 b. The refrigerant that has heated the indoor air in the indoor heat exchangers 10 a and 10 b exits the use units 303 a and 303 b, enters the branch unit 302 via the indoor liquid pipes 9 a and 9 b, and is reduced in pressure by the indoor pressure-reducing mechanisms 8 a and 8 b (second pressure-reducing mechanism) and turns into a two-phase gas-liquid or liquid-phase refrigerant at low pressure. Thereafter, the refrigerant that has exited the indoor pressure-reducing mechanisms 8 a and 8 b merges with the refrigerant that has flown through the hot water supply pressure-reducing mechanism 20 at the branch part 26, and exits the branch unit 302.
Each of the indoor pressure-reducing mechanisms 8 a and 8 b is controlled so that there is no temperature difference (heated indoor temperature difference) in the use unit 303 a or 303 b, which is calculated by subtracting an indoor set temperature from the indoor suction temperature detected by the indoor suction temperature sensor 208 a or 208 b. Accordingly, refrigerant flows through each of the indoor heat exchangers 10 a and 10 b at a flow rate suited to the heating load required for the air-conditioned space where the use unit 303 a or 303 b is installed.
The refrigerant that has exited the branch unit 302 enters the heat source unit 301 via the liquid extension pipe 7, and after passing through the outdoor pressure-reducing mechanism 6, the refrigerant enters the outdoor heat exchanger 4. The opening degree of the outdoor pressure-reducing mechanism 6 is being controlled to the full opening. The refrigerant that has entered the outdoor heat exchanger 4 evaporates by exchanging heat with the outside air supplied by the outdoor air-sending device 5, and turns into a low-pressure gas refrigerant. After exiting the outdoor heat exchanger 4, this refrigerant passes through the accumulator 14 via the four-way valve 3, and is thereafter sucked into the compressor 1 again.
The air flow of the outdoor air-sending device 5 is controlled by the controlling section 103 so that the evaporating temperature becomes a predetermined value in accordance with the outside air temperature detected by the outside air temperature sensor 205. Here, the evaporating temperature is calculated from the temperature detected by the outdoor liquid temperature sensor 204.
In the simultaneous heating and hot water supply operation mode D, it is necessary to output a heating capacity suited to a heating load while supplying hot water. In related art, in order to avoid running out of hot water while a hot water supply operation is performed, it is necessary to control the frequency of the compressor to a high frequency in an attempt to provide a large hot water supply capacity. By applying the hot water supply operation control, it is possible to grasp the minimum required hot water supply capacity, and control the operating frequency of the compressor 1 accordingly. Consequently, it is possible to achieve high operation efficiency that outputs a heating capacity suited to a heating load while performing a hot water supply operation simultaneously.
FIG. 8 is a flowchart illustrating control of the compressor in the simultaneous heating and hot water supply operation mode D. After the simultaneous heating and hot water supply operation mode D is started in step S11, in step S12, the operating frequency of the compressor 1 is controlled in accordance with a heating load in the same manner as in the heating operation mode B. That is, in Embodiment 1, the operating frequency of the compressor 1 is controlled by the controlling section 103 so that the condensing temperature becomes a predetermined value in accordance with the maximum heated indoor temperature difference. The method of calculating the condensing temperature is the same as in the case of the cooling operation. In this operation, a heating capacity suited to a heating load is secured. Next, in step S13, the outlet water temperature target T_womis computed in the same manner as in the case of the hot water supply operation mode C. That is, the hot water supply capacity target Q_wm(the minimum required hot water supply capacity) is computed by Equation (3) by using the maximum heat capacity consumption L_mand the maximum consumption time t_mthat have been learned through a hot water supply operation, and the outlet water temperature target T_womis computed by Equation (4). Next, in step S14, the outlet water temperature T_woand the outlet water temperature target T_womare compared with each other. Here, it is determined whether the hot water supply capacity determined by the operating frequency of the compressor 1 controlled in step S12 is sufficient for storing the quantity of heat equal to the maximum heat consumption L_min the hot water storage tank 27 by the maximum consumption time t_m. That is, it is determined whether the hot water supply capacity is larger than the hot water supply capacity target Q_wm. If the outlet water temperature T_wois higher than the outlet water temperature target T_wom, it is determined that a sufficient hot water supply capacity is secured, and the processing proceeds to step S15 and the operating frequency of the compressor 1 is maintained as it is. If the outlet water temperature T_wois lower than the outlet water temperature target T_wom, it is determined that the hot water supply capacity is insufficient, that is, the hot water supply capacity is smaller than the hot water supply capacity target, and the processing proceeds to step S16 where the operating frequency of the compressor 1 is raised until the outlet water temperature T_wobecomes equal to the outlet water temperature target T_wom.
Through this operation, in a case where the hot water supply capacity is larger than the hot water supply capacity target Q_wm, the minimum required hot water supply capacity can be determined in accordance with the actual usage of hot water by the user in the past while outputting a heating capacity suited to a heating load, and the operating frequency of the compressor 1 can be set accordingly. Therefore, as compared with a case where the usage of hot water by the user is not used as in related art, it is possible to perform the simultaneous heating and hot water supply operation while controlling the operating frequency of the compressor 1 to a low frequency.
As in the case of the hot water supply operation mode C, by computing the hot water supply operation time target Δt_mby Equation (7), and updating the hot water supply operation time Δt_start, it is possible for any user to make the hot water supply capacity target Q_wmconstant with respect to the standard hot water supply capacity Q_std, thereby achieving high operation efficiency.

[Simultaneous Cooling and Hot Water Supply Operation Mode E]

In the simultaneous cooling and hot water supply operation mode E (parallel heat removal and condensation operation), the use units 303 a and 303 b are in cooling operation, and the hot water supply unit 304 is in hot water supply operation. In the simultaneous cooling and hot water supply operation mode E, the four-way valve 3 is in the state indicated by the broken line. That is, the discharge side of the compressor 1 is connected to the plate water-heat exchanger 17 via the hot water supply gas extension pipe 16, and the suction side of the compressor 1 is connected to the gas side of the outdoor heat exchanger 4. The first discharge solenoid valve 2 is closed, the second discharge solenoid valve 15 is open, and the low-pressure equalizing solenoid valve 21 is open.
In this state of the refrigerant circuit, the compressor 1, the outdoor air-sending device 5, the indoor air-sending devices 11 a and 11 b, and the water supply pump 18 are activated. Then, a low-pressure gas refrigerant is sucked into the compressor 1, where the refrigerant is compressed into a high temperature/high pressure gas refrigerant. Thereafter, the high temperature/high pressure gas refrigerant enters the second discharge solenoid valve 15.
The refrigerant that has entered the second discharge solenoid valve 15 exits the heat source unit 301, and enters the hot water supply unit 304 via the hot water supply gas extension pipe 16. The refrigerant that has entered the hot water supply unit 304 enters the plate water-heat exchanger 17, where the refrigerant condenses by exchanging heat with the water supplied by the water supply pump 18 and turns into a high-pressure liquid refrigerant, and exits the plate water-heat exchanger 17. The refrigerant that has heated the water in the plate water-heat exchanger 17 exits the hot water supply unit 304, and enters the branch unit 302 via the hot water supply liquid pipe 19.
The refrigerant that has entered the branch unit 302 is reduced in pressure by the hot water supply pressure-reducing mechanism 20, and turns into a two-phase gas-liquid or liquid-phase refrigerant at intermediate pressure. Here, the hot water supply pressure-reducing mechanism 20 is controlled to the maximum opening degree. Thereafter, the refrigerant is divided into a flow of refrigerant that enters the liquid extension pipe 7, and a flow of refrigerant that enters the indoor pressure-reducing mechanisms 8 a and 8 b. As illustrated in FIG. 1, the refrigerant that flows toward the indoor unit divides into branches at the branch part 26. In FIG. 1, the flow path along the indoor pressure-reducing mechanisms 8 a and 8 b (second pressure-reducing mechanism), the indoor heat exchangers 10 a and 10 b (second evaporator), and the four-way valve 3 constitutes a heat removal branch flow path.
The refrigerant that has entered the indoor pressure-reducing mechanisms 8 a and 8 b is reduced in pressure into a two-phase gas-liquid state at low pressure, and enters the use units 303 a and 303 b via the indoor liquid pipes 9 a and 9 b. The refrigerant that has entered the use units 303 a and 303 b enters the indoor heat exchangers 10 a and 10 b, where the refrigerant is evaporated by exchanging heat with the indoor air supplied by the indoor air-sending devices 11 a and 11 b and turns into a low-pressure gas refrigerant.
Here, each of the indoor pressure-reducing mechanisms 8 a and 8 b is controlled so that there is no temperature difference (cooled indoor temperature difference) in the use unit 303 a or 303 b, which is calculated by subtracting a set temperature from the indoor suction temperature detected by the indoor suction temperature sensor 208 a or 208 b. Accordingly, refrigerant flows through each of the indoor heat exchangers 10 a and 10 b at a flow rate suited to the cooling load required for the air-conditioned space where the use unit 303 a or 303 b is installed.
The refrigerant that has flown through the indoor heat exchangers 10 a and 10 b thereafter exits the use units 303 a and 303 b, and enters the heat source unit 301 via the indoor gas pipes 12 a and 12 b, the branch unit 302, and the gas extension pipe 13. The refrigerant that has entered the heat source unit 301 passes through the four-way valve 3, and thereafter merges with the refrigerant that has passed through the outdoor heat exchanger 4.
Meanwhile, the refrigerant that has entered the liquid extension pipe 7 thereafter enters the heat source unit 301, and after being reduced in pressure into a two-phase gas-liquid refrigerant at low pressure by the outdoor pressure-reducing mechanism 6, the refrigerant enters the outdoor heat exchanger 4, where the refrigerant evaporates by exchanging heat with the outdoor air supplied by the outdoor air-sending device 5. Thereafter, the refrigerant passes through the low-pressure equalizing solenoid valve 21, and merges with the refrigerant that has passed through each of the indoor heat exchangers 10 a and 10 b. Thereafter, the refrigerant passes through the accumulator 14 and is sucked into the compressor 1 again.
Since the low-pressure equalizing solenoid valve 21 is installed for the purpose of lowering the pressure in the outdoor heat exchanger 4, its diameter is small. Therefore, it is not possible to remove excess heat of cooling. Therefore, the air flow of the outdoor air-sending device 5 is controlled to the minimum value required to cool the radiator plate, and the opening degree of the outdoor pressure-reducing mechanism 6 is controlled to a small opening.
In the simultaneous cooling and hot water supply operation mode E, it is necessary to output a cooling capacity suited to a cooling load while supplying hot water. In related art, in order to avoid running out of hot water while a hot water supply operation is performed, it is necessary to control the frequency of the compressor to a high frequency in an attempt to provide a large hot water supply capacity. Consequently, the cooling capacity becomes excessive, and it is necessary to switch between the hot water supply operation mode C and the simultaneous cooling and hot water supply operation mode E alternately, resulting in poor operation efficiency. By applying the present technique, it is possible to grasp the minimum required hot water supply capacity, and control the operating frequency of the compressor 1 accordingly. Consequently, by employing the present technique, it is possible to achieve an operation that outputs a cooling capacity suited to a cooling load while performing a hot water supply operation simultaneously, thereby obtaining high operation efficiency.
FIG. 9 is a flowchart illustrating control of the compressor in the simultaneous cooling and hot water supply operation mode E. After the simultaneous cooling and hot water supply operation mode E is started in step S21, in step S22, the operating frequency of the compressor 1 is controlled in accordance with a cooling load in the same manner as in the cooling operation mode A. That is, in Embodiment 1, the operating frequency of the compressor 1 is controlled by the controlling section 103 so that the evaporating temperature becomes a predetermined value in accordance with the maximum cooled indoor temperature difference. The method of calculating the evaporating temperature is the same as in the case of the cooling operation. In this operation, a cooling capacity suited to a cooling load is secured. Next, in step S23, the outlet water temperature target T_womis computed in the same manner as in the case of the hot water supply operation mode C. That is, the hot water supply target Q_wm(the minimum required hot water supply capacity) is computed by Equation (3) by using the maximum heat capacity consumption L_mand the maximum consumption time t_mthat have been learned through a hot water supply operation, and the outlet water temperature target T_womis computed by Equation (4). Next, in step S24, the outlet water temperature T_woand the outlet water temperature target T_womare compared with each other. Here, it is determined whether the hot water supply capacity determined by the operating frequency of the compressor 1 controlled in step S22 is sufficient for storing the quantity of heat equal to the maximum heat consumption L_min the hot water storage tank 27 by the maximum consumption time t_m. That is, it is determined whether the hot water supply capacity is larger than the hot water supply capacity target Q_wm. If the outlet water temperature T_wois higher than the outlet water temperature target T_wom, it is determined that a sufficient hot water supply capacity is secured, and the processing proceeds to step S25 and the operating frequency of the compressor 1 is maintained as it is. If the outlet water temperature T_wois lower than the outlet water temperature target T_wom, it is determined that the hot water supply capacity is insufficient, that is, the hot water supply capacity is smaller than the hot water supply capacity target, and the processing proceeds to step S26 where the operating frequency of the compressor 1 is raised until the outlet water temperature T_wobecomes equal to the outlet water temperature target T_wom.
Through this operation, in a case where the hot water supply capacity is larger than the hot water supply capacity target Q_wm, the minimum required hot water supply capacity can be determined in accordance with the actual usage of hot water by the user in the past while outputting a cooling capacity suited to a cooling load, and the operating frequency of the compressor 1 can be set accordingly. Therefore, as compared with a case where the usage of hot water by the user is not used as in related art, it is possible to perform the simultaneous cooling and hot water supply operation while controlling the operating frequency of the compressor 1 to a low frequency. In related art, even in a case where the cooling load is small, the hot water supply capacity is set to a large value in order to prevent running out of hot water, resulting in an increase in cooling capacity. According to the present invention, however, operation can be performed while making the hot water supply capacity small, which makes it possible to perform operation while setting the cooling capacity small in a case where the cooling load is small, thereby achieving high operation efficiency. Moreover, it is also possible to avoid running out of hot water when supplying hot water.
As in the case of the hot water supply operation mode C, by computing the hot water supply operation time target Δt_mby Equation (7), and updating the hot water supply operation time Δt_start, it is possible for any user to keep the hot water supply capacity target Q_wmconstant, thereby achieving high operation efficiency.
As described in the foregoing, the combined air-conditioning and hot water supply system 100 according to Embodiment 1 makes it possible to perform a hot water supply operation with high operation efficiency, and also avoid running out of hot water.
While Embodiment 1 described above is directed to the combined air-conditioning and hot water supply system 100 (refrigeration cycle apparatus), it is also possible to grasp the operation of the combined air-conditioning and hot water supply system 100 as a refrigeration cycle control method.

REFERENCE SIGNS LIST

1 compressor, 2 first discharge solenoid valve, 3 four-way valve, 4 outdoor heat exchanger, 5 outdoor air-sending device, 6 outdoor pressure-reducing mechanism, 7 liquid extension pipe, 8 a, 8 b indoor pressure-reducing mechanism, 9 a, 9 b indoor liquid pipe, 10 a, 10 b indoor heat exchanger, 11 a, 11 b indoor air-sending device, 12 a, 12 b indoor gas pipe, 13 gas extension pipe, 14 accumulator, 15 second discharge solenoid valve, 16 hot water supply gas extension pipe, 17 plate water-heat exchanger, 18 water supply pump, 19 hot water supply liquid pipe, 20 hot water supply pressure-reducing mechanism, 21 low-pressure equalizing solenoid valve, 22 upstream water pipe, 23 downstream water pipe, 24 water inflow pipe connecting part, 25 water downstream pipe connecting part, 26 branch part, 27 hot water storage tank, 100 combined air-conditioning and hot water supply system, 110 controller, 102 computing section, 103 controlling section, 104 memory section, 105 clock section, 201 high-pressure sensor, 202 discharge temperature sensor, 203 outdoor gas temperature sensor, 204 outdoor liquid temperature sensor, 205 outside air temperature sensor, 206 a, 206 b indoor liquid temperature sensor, 207 a, 207 b indoor gas temperature sensor, 208 a, 208 b indoor suction temperature sensor, 209 hot water supply liquid temperature sensor, 210 inlet water temperature sensor, 211 outlet water temperature sensor, 212 first hot-water-storage-tank water temperature sensor, 213 second hot-water-storage-tank water temperature sensor, 214 third hot-water-storage-tank water temperature sensor, 215 fourth hot-water-storage-tank water temperature sensor, 216 hot-water-storage-tank exiting water temperature sensor, 217 hot-water-storage-tank entering water temperature sensor, 218 tank flow meter, 219 intermediate water flow meter, 301 heat source unit, 302 branch unit, 303 a, 303 b use unit, 304 hot water supply unit, 305 tank unit

Claims

1-10. (canceled)

11. A refrigeration cycle apparatus in which a refrigerant is circulated, comprising:

a refrigeration cycle mechanism that has a compressor whose operating frequency can be controlled, a first radiator that supplies heat by means of the refrigerant to tank water that is water stored in a hot water storage tank, a first pressure-reducing mechanism, and a first evaporator, the refrigerant circulating in an order of the compressor, the first radiator, the first pressure-reducing mechanism, and the first evaporator; and

a controller,

wherein the controller includes,

a memory section configured to store control period information indicating a preset control period, and be capable of storing other information,

a computing section configured to calculate a heat consumption on a time period basis, the heat consumption indicating a quantity of heat that has been supplied to an outside by the tank water within the time period, the time period being one of divided predetermined time period of a day, store the calculated heat consumption and a corresponding point in time into the memory section, and compute current heat storage in the tank water, and

a controlling section configured to control the operating frequency of the compressor,

wherein the computing section,

from the heat consumptions of at least past one day stored in the memory section, calculates a maximum heat consumption that is to be the largest among other heat consumptions to be generated on a current day and a maximum consumption time that is a corresponding point in time to the maximum heat consumption,

at a time that precedes the maximum consumption time by the control period, computes the heat storage in the tank water, and on a basis of the heat storage and the maximum heat consumption of the current day, computes a hot water supply capacity target and the operating frequency of the compressor, the hot water supply capacity target serving as a heat rejection target value necessary for the first radiator to bring the heat storage in the tank water into the maximum heat consumption at the maximum consumption time,

wherein the controlling section controls the compressor at the operating frequency computed by the computing section, and

wherein the computing section updates the control period stored in the memory section on a basis of the hot water supply capacity target, and uses the updated control period for computing the operating frequency of the compressor in accordance with the maximum heat consumption on a following day.

12. The refrigeration cycle apparatus of claim 11, further comprising:

an outlet temperature sensor configured to detect a temperature of outflow water exiting from an outlet of the first radiator in a water flow path, the water flow path being a flow path of water that enters the first radiator from the hot water storage tank, passes through the first radiator, and returns to the hot water storage tank,

wherein the computing section,

at the time that precedes the maximum consumption time by the control period, computes the heat storage in the tank water, and on the basis of the heat storage and the maximum heat consumption of the current day, calculates a target temperature indicating a target temperature of the outflow water, to bring the heat storage in the tank water into the maximum heat consumption at the maximum consumption time, and

computes the operating frequency of the compressor that brings the temperature of the outflow water detected by the outlet temperature sensor into the target temperature.

13. The refrigeration cycle apparatus of claim 11,

wherein the memory section stores standard heat supply that indicates a standard value of heat to be supplied to the tank water per unit time, and

wherein the computing section, after elapse of the maximum consumption time of the current day, updates the control period stored in the memory section into a new control period in accordance with a proportion of the standard heat supply to the hot water supply capacity target, and stores the updated new control period into the memory section.

14. The refrigeration cycle apparatus of claim 11, further comprising:

a tank water sensor that detects a temperature of the tank water,

wherein the computing section calculates the current heat storage in the tank water by using the temperature of the tank water detected by the tank water sensor.

15. The refrigeration cycle apparatus of claim 11, further comprising:

an inlet temperature sensor that detects a temperature of inflow water entering an inlet of the first radiator in a water flow path, the water flow path being a flow path of water that enters the first radiator from the hot water storage tank, passes through the first radiator, and returns to the hot water storage tank; and

a high-pressure sensor that detects a high pressure from a discharge side of the compressor to a liquid side of the first pressure-reducing mechanism,

wherein the computing section computes a condensing temperature of the first radiator on a basis of the high pressure detected by the high-pressure sensor; and

wherein the controlling section controls the operating frequency of the compressor by further using the condensing temperature calculated by the computing section and the temperature of the inflow water detected by the inlet temperature sensor.

16. The refrigeration cycle apparatus of claim 12, further comprising:

a water supply pump that causes the water to flow through the water flow path; and

an inlet temperature sensor that detects a temperature of inflow water entering an inlet of the first radiator in the water flow path,

wherein the controlling section keeps a temperature difference between the temperature of the inflow water detected by the inlet temperature sensor and the target temperature indicating the target temperature of the outflow water, at a predetermined value or more by controlling a flow rate of the inflow water entering the first radiator through control of the water supply pump, while controlling the operating frequency of the compressor.

17. The refrigeration cycle apparatus of claim 12, further comprising:

a heat rejection branch flow path that is a branch flow path that branches out from a discharge side of the compressor, the heat rejection branch flow path having a second radiator and a second pressure-reducing mechanism, the heat rejection flow path being connected in an order of the second radiator and the second pressure-reducing mechanism from the discharge side of the compressor and merging with a portion between the first pressure-reducing mechanism and the first radiator,

wherein upon executing a parallel heat rejection operation that causes a discharged refrigerant discharged from the compressor to enter and circulate through the first radiator and the second radiator, the controlling section controls the operating frequency of the compressor on a basis of a heating load indicating a load required for the second radiator,

wherein the computing section compares the temperature of the outflow water when the operating frequency of the compressor is being controlled on a basis of the heating load with the target temperature,

when the temperature of the outflow water is lower than the target temperature,

the controlling section changes the operating frequency of the compressor to an operating frequency that brings the temperature of the outflow water into the target temperature.

18. The refrigeration cycle apparatus of claim 12, further comprising:

a heat removal branch flow path that branches out from a branch part between the first pressure-reducing mechanism and the first evaporator, the heat removal branch flow path having a second pressure-reducing mechanism and a second evaporator, the heat removal branch flow path being connected in an order of the second pressure-reducing mechanism and the second evaporator from the branch part and merging with a suction side of the compressor,

wherein the controlling section, upon executing a parallel heat removal and heat rejection operation that is a parallel operation of a heat rejection operation of the first radiator and a heat removal operation of the second evaporator, the heat rejection operation causing the discharged refrigerant discharged from the compressor to be sucked into the compressor from the suction side via the first radiator, the first pressure-reducing mechanism, the branch part, and the first evaporator, the heat removal operation causing the discharged refrigerant to be sucked into the compressor from the suction side via the first radiator, the first pressure-reducing mechanism, the branch part, the second pressure-reducing mechanism, and the second evaporator, controls the operating frequency of the compressor on a basis of a cooling load indicating a load required for the second evaporator,

wherein the computing section compares the temperature of the outflow water when the operating frequency of the compressor is being controlled on a basis of the heating load with the target temperature, and

when the temperature of the outflow water is lower than the target temperature,

19. A refrigeration cycle control method for a refrigeration cycle apparatus through which a refrigerant is circulated, the refrigeration cycle apparatus including

a refrigeration cycle mechanism that has a compressor whose operating frequency can be controlled, a first radiator that supplies heat by means of the refrigerant to tank water that is water stored in a hot water storage tank, a first pressure-reducing mechanism, and a first evaporator, the refrigerant circulating in an order of the compressor, the first radiator, the first pressure-reducing mechanism, and the first evaporator,

a controlling section configured to control the operating frequency of the compressor, the refrigeration cycle control method comprising:

from the heat consumptions of at least past one day stored in the memory section, calculating a maximum heat consumption that is to be the largest among other heat consumptions to be generated on a current day and a maximum consumption time that is a corresponding point in time to the maximum heat consumption, by the computing section;

at a time that precedes the maximum consumption time by the control period, computing the heat storage in the tank water, and on a basis of the heat storage and the maximum heat consumption of the current day, computes a hot water supply capacity target and the operating frequency of the compressor, the hot water supply capacity target being a hot water supply capacity target serving as a heat rejection target value necessary for the first radiator to bring the heat storage in the tank water into the maximum heat consumption at the maximum consumption time, by the computing section;

controlling the compressor at the operating frequency computed by the computing section, by the controlling section; and

updating the control period stored in the memory section on a basis of the hot water supply capacity target, and using the updated control period for computing the operating frequency of the compressor in accordance with the maximum heat consumption on the following day, by the computing section.