CN102016439B - Heat pump water heater - Google Patents
Heat pump water heater Download PDFInfo
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- CN102016439B CN102016439B CN2008801287228A CN200880128722A CN102016439B CN 102016439 B CN102016439 B CN 102016439B CN 2008801287228 A CN2008801287228 A CN 2008801287228A CN 200880128722 A CN200880128722 A CN 200880128722A CN 102016439 B CN102016439 B CN 102016439B
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- bathtub
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D17/00—Domestic hot-water supply systems
- F24D17/0078—Recirculation systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D17/00—Domestic hot-water supply systems
- F24D17/02—Domestic hot-water supply systems using heat pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
- F24H1/54—Water heaters for bathtubs or pools; Water heaters for reheating the water in bathtubs or pools
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- Engineering & Computer Science (AREA)
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- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
Abstract
A heat pump water heater includes, to secure heating ability, improve heating efficiency and save energy for totally optimum operation control for a period including a winter defrosting time, a heat pump refrigerant circuit (30) having a compressor, a water refrigerant heat exchanger, an expansion valve and an air refrigerant heat exchanger, a hot water supply circuit (40) having a hot water reservoir tank, an internal circulation pump, a hot water supply mixing valve, a bath heat exchanger, a bath circulation pump and a hot water and water mixing valve for performing hot water storage in a tank, direct supply of hot water from the water refrigerant heat exchanger, hot water supply from the tank, filling a bathtub and additional heating of the bath and an operation control part (50) for performing an operation of hot water storage, an operation of directly supplying hot water, an operation of supplying hot water from the tank, an operation of filling the bathtub and an operation of additionally heating the bath by the operation setting of a hot water outlet remote controller (51) and a bathroom remote controller (52). The operation control part performs the optimum operation control for selecting one of three kinds of operating means including a heating efficiency prioritized operation, a heating ability prioritized operation and an intermediate defrosting operation based on an ambient temperature, an air refrigerant heat exchanger temperature and a hot water supply and storage mode as determination standard.
Description
Technical field
The present invention relates to Teat pump boiler, relate in particular to comprise the frosting phase during in the optimum operation of heat pump control.
Background technology
Existing Teat pump boiler, generally similarly to be provided with jumbo hot-water storage tank with the electrical heat hydrophone, the cheap electric power of discounted cost carries out the heat pump running with night, at midnight, hot water is boiled, be stored in the hot-water storage tank, use by day the Teat pump boiler of the hot-water storage type of the hot water of storing.
On the other hand, develop in recent years on the daytime that main supplying hot water uses and also carry out the heat pump running, directly supply with the warm water after heating, realized thus the moment formula Teat pump boiler of the significantly miniaturization of hot-water storage tank.For example there is disclosed example in patent documentation 1 in conventional example as this formula Teat pump boiler moment.
According to this patent documentation 1, carry out in advance the hot-water storage running, stored hot water in the small-sized hot water hold-up tank of 60～100L, when using hot water, the running that does not arrive proper temperature in the heating-up temperature of heat pump is initial, sneak into the high-temperature water from the hot-water storage tank in the heating water of heat pump, reach proper temperature and come supplying hot water, when making heating-up temperature reach proper temperature when turning round by heat pump, stop the hot water supply from the hot-water storage tank, directly supply with by the turn round water of the proper temperature after heating of heat pump and use.
In addition, the moment running of formula Teat pump boiler is controlled, corresponding to water pot hot-water storage or kitchen/washroom hot water supply, the rotating speed that changes compressor is adjusted heating efficiency, the defrosting of air refrigerant heat exchanger (evaporimeter) is according to the temperature detection frosting degree of air refrigerant heat exchanger, after the heating properties of a large amount of frostings, heat pump reduces, opening the defrosting by-passing valve and defrost, is all fairly simple structure.
Patent documentation 1:JP JP 2003-279133 communique
As disclosed in above-mentioned patent documentation 1, in existing Teat pump boiler, substantially change the rotating speed of compressor corresponding to the hot water supply purposes, adjust heating efficiency.But along with Teat pump boiler is universal, use expands to a plurality of branches in recent years, and it is complicated that the hot water supply temperature also becomes.For example about bathtub hot water implantation temperature, in the past at balneation supplying hot water not long ago, therefore the hot water supply temperature is approximately constant is 42 ℃, and the function of additional prior pre-set hot water injection length, just need to supply with 45 ℃ of slightly high hot water, appended function simultaneously so that can be according to 38 ℃～48 ℃ hot water supply temperature of Season select.
In addition, also obtained variation about water pot hot-water storage temperature, corresponding to the seasonal variations of hot water supply use amount, carried out intergrade in summer, spring and autumn with approximately 65 ℃ store hot water, store hot water with 70～75 ℃ in the winter time, store the settings such as hot water with 85～90 ℃ during low temperature in the winter time.
For these diversified hot water supply behaviours in service, the running of heat pump controls to guarantee that the hot water supply amount attaches most importance to, and controls in the preferential mode of heating efficiency corresponding to each hot water supply temperature, may not become optimum operation from energy-conservation viewpoint and control.For example bathtub hot water being injected running when carrying out time reservation, even the elongated efficiency of heating surface that also can make of hot water injection length is preferential, but in the situation that shower needs larger hot water supply amount like that, compares with efficient and must make heating efficiency preferential.In addition, in the winter time, when making continuous operation preferential, the heating efficiency that is caused by frosting when long-time supplying hot water reduces and becomes problem, when detection air refrigerant heat exchanger temperature enters the defrosting running, existence begins to defrost in kitchen hot water supply process or in the process that washes one's face and stops the problem of supplying hot water, requires for these diversified service conditions at present, the necessity of the optimum operation control mode of considered heating efficiency, energy-conservation, defrosting is controlled etc.
Summary of the invention
The object of the invention is to address these problems, provide a kind of when comprising winter frost removing during in realize the raising of the guaranteeing of heating efficiency, the efficiency of heating surface and energy-conservation, synthetically carry out the Teat pump boiler that optimum operation is controlled.
In order to solve described problem, the present invention mainly adopts following structure.
a kind of Teat pump boiler possesses: heat pump refrigerant loop, air refrigerant heat exchanger and coolant piping that it has the compressor of compression refrigerant, the cool water media heat exchanger that carries out the heat exchange of water and refrigerant, expansion valve, carries out the heat exchange of air and refrigerant, the hot water supply loop, it has the hot-water storage tank that has by the warm water after described cool water media heat exchanger heats, the machine internal circulation pump, the hot water supply mixing valve, carry out the bathtub heat exchanger with heat exchange by the warm water after described cool water media heat exchanger heats, bathtub circulation pump, water mixing valve, sparge pipe, this hot water supply loop formation: the hot-water storage loop of storing high-temperature water in described hot-water storage tank, to going out the direct direct hot water supply circuit of supplying with by the warm water after described cool water media heat exchanger heats in hot water position, supply with water pot hot water supply loop from the warm water of described hot-water storage tank to going out the hot water position, use pump to the bathtub hot water infusion circuit of bathtub supply by the warm water after described cool water media heat exchanger heats by described bathtub circulation, supply with from described bathtub with the bathtub of the warm water of heat exchanger heating circuit again to bathtub with pump by the circulation of described bathtub, and operation control section, it is by going out the operating and setting of hot water position remote controller and bathtub remote controller, control each inscape and carry out the hot-water storage running, direct hot water supplying operation, water pot hot water supply running, bathtub hot water injects running, bathtub adds heat run again, in described Teat pump boiler, described operation control section, environment temperature with Teat pump boiler, the temperature of described air refrigerant heat exchanger, and comprise to water pot storage hot water, to going out hot water position supplying hot water, bathtub hot water injects, hot water supply in running more than the scheduled time is carried out optimum operation in interior hot water supply/hot-water storage pattern as determinating reference and is controlled, this optimum operation is controlled and is used for judging that the efficiency of heating surface preferentially turns round, heating efficiency preferentially turns round, some in middle these 3 kinds of drive manners of defrosting running.
In addition, in described Teat pump boiler, described operation control section, reach maximum compressor rotary speed running with the efficiency of heating surface when being judged to be the described efficiency of heating surface and preferentially turning round, reach maximum compressor rotary speed running with heating efficiency when being judged to be described heating efficiency and preferentially turning round, when being judged to be the running that defrosts after reaching maximum compressor rotary speed running with heating efficiency during the defrosting running in the middle of described and passing through approximately time of 1/2 of heat pump duration of runs of being inferred.And described operation control section, as described determinating reference, be divided into described environment temperature more than approximately+7 ℃ or below approximately-7 ℃, peace treaty-7 ℃～+ 7 ℃ at least more than two parts.
In addition, in described Teat pump boiler, described operation control section as described determinating reference, is divided into described air refrigerant heat exchanger temperature approximately more than 0 ℃ and less than about 0 ℃ of these two parts.And described operation control section as described determinating reference, for each hot water supply pattern learning heat pump duration of runs, is the about hot water supply pattern more than 60 minutes in the situation that infer the duration of runs, and in the middle of judging, the defrosting running is controlled as optimum operation.And described operation control section is judged in the frosting of carrying out described air refrigerant heat exchanger after heat run finishes that adds of heat pump running, when being judged to be frosting, then the running that defrosts stops the heat pump running, when being judged to be not frosting, do not stop the heat pump running with not defrosting running.
According to the present invention, can judge the optimum operation of the service condition that has taken into full account Teat pump boiler, realize the raising of the guaranteeing of heating efficiency, the efficiency of heating surface and energy-conservation in the time of can comprising winter frost removing, synthetically select best drive manner.
In addition, by more specifically determinating reference and the efficiency of heating surface of specified in more detail optimum operation mode preferentially turn round, heating efficiency preferentially turns round, middle these 3 kinds of drive manners of defrosting running, can be further when realizing optimum operation mode selected, easily carry out commercialization.
In addition, frosting when detecting the running end, then the running that only defrosts when frosting is arranged shuts down, therefore, when beginning, the running next time can there is no entry into service under the state of frosting, the raising of the heat temperature raising characteristic in the time of can realizing turning round beginning, and, externally can prevent that the frosting of turning round when finishing from increasing under the condition such as the low or snowfall of air themperature in stopping period.
According to the record of the following embodiments of the invention relevant to accompanying drawing, can understand other purpose of the present invention, feature and advantage.
Description of drawings
Fig. 1 means the inscape of Teat pump boiler of embodiments of the present invention and the overall structure figure of access path.
Fig. 2 means the flow chart of Teat pump boiler, the flow process running of the hot water supply when opening kitchen faucet and using hot water of embodiments of the present invention.
Fig. 3 means the chart of the relation of heating efficiency in general Teat pump boiler and the efficiency of heating surface.
Fig. 4 means the decision condition of the optimum operation mode in the Teat pump boiler that determines present embodiment and the table of determinating reference.
Fig. 5 mean in general Teat pump boiler winter continuous operation situation under the chart that changes of time of heating efficiency.
Fig. 6 means in the Teat pump boiler of present embodiment, infers in the winter time the key diagram of the comparison that adds heat of continuous operation in the situation of hot water supply time long (for example 70 minutes) and middle defrosting running.
Fig. 7 means in the Teat pump boiler of present embodiment, infers in the winter time the key diagram of the comparison that adds heat of continuous operation in the situation of hot water supply time short (for example 50 minutes) and middle defrosting running.
The specific embodiment
Below, describe the Teat pump boiler of embodiments of the present invention in detail with reference to Fig. 1～Fig. 7.Fig. 1 means the inscape of Teat pump boiler of embodiments of the present invention and the overall structure figure of access path.In Fig. 1, the Teat pump boiler of present embodiment is made of heat pump refrigerant loop 30, hot water supply loop 40 and running control module 50 as a whole.
Heat pump refrigerant loop 30 consists of with two endless form of the first refrigerant loop 30a and the second refrigerant loop 30b, connect successively and consist of via medium side heat-transfer pipe 2a, 2b, expansion valve 3a, 3b, air refrigerant heat exchanger 4a, the 4b of coolant piping with compressor 1a, 1b, configuration in cool water media heat exchanger 2 respectively, enclosed therein refrigerant.
Compressor 1a, 1b can carry out volume controlled, when supplying with a large amount of hot water, turn round with large capacity.At this, compressor 1a, 1b by PWM control, Control of Voltage (for example PAM control) and their combination control, and can carry out rotating speed control from low speed (for example 700 rev/mins) to (for example 7000 rev/mins) at a high speed.Cool water media heat exchanger 2 possesses medium side heat-transfer pipe 2a, 2b and water supply side heat-transfer pipe 2c, 2d, carries out heat exchange between medium side heat-transfer pipe 2a, 2b and water supply side heat-transfer pipe 2c, 2d.
The fast electric expansion valve of response when generally using aperture to adjust as expansion valve 3a, 3b reduces pressure to the middle temperature high pressure refrigerant that transports via cool water media heat exchanger 2, carries to air refrigerant heat exchanger 4a, 4b as holding evaporable low pressure refrigerant.In addition, expansion valve 3a, 3b play the effect that the aperture that changes coolant path is come the refrigerant circulation in adjusting heat pump refrigerant loop, also carry out to increase aperture, to air refrigerant heat exchanger 4a, 4b are a large amount of carry in the warm refrigerant task of dissolving white defroster.
Air refrigerant heat exchanger 4a, 4b are taken into extraneous air by the rotation of Air Blast fan 5a, 5b, carry out the heat exchange of air and refrigerant, carry out the task of absorbing heat from extraneous air.Hot water supply loop 40 possesses be used to the water-flow circuit that carries out following action: (1) hot-water storage, (2) directly hot water supply, (3) water pot hot water supply, (4) bathtub hot water inject, (5) bathtub heats again.
Hot-water storage loop (1) is for the running of seething with excitement by water pot, store the water loop of high-temperature water in hot-water storage tank 16, via sparge pipe, hot-water storage tank 16, machine internal circulation pump 17, hydro-thermal of ac sensor 10, water supply side heat-transfer pipe 2c, 2d, hot water supply mixing valve 11, hot-water storage tank 16 are connected successively and consist of.
Directly hot water supply circuit (2), go out hot water metal parts 14 via sparge pipe with water supply metal parts 6, pressure-reducing valve 7, water-supply quantity sensor 8, water supply side check-valves 9, hydro-thermal of ac sensor 10, water supply side heat-transfer pipe 2c, 2d, hot water supply mixing valve 11, water mixing valve 12, flow rate regulating valve 13, kitchen and connect successively and consist of.Water supply metal parts 6 is connected with waterings such as water pipes, and the kitchen goes out hot water metal parts 14 and is connected with kitchen faucet 15 grades.
Water pot hot water supply loop (3) goes out hot water metal parts 14 via sparge pipe with water supply metal parts 6, pressure-reducing valve 7, water-supply quantity sensor 8, water supply side check-valves 9, hot-water storage tank 16, hot water supply mixing valve 11, water mixing valve 12, flow rate regulating valve 13, kitchen and connects successively and consist of.
Bathtub hot water infusion circuit (4) connects water supply metal parts 6, pressure-reducing valve 7, water-supply quantity sensor 8, water supply side check-valves 9, hydro-thermal of ac sensor 10, water supply side heat-transfer pipe 2c, 2d, hot water supply mixing valve 11, water mixing valve 12, flow rate regulating valve 13, bathtub hot water injection valve 18, flow switch 19, bathtub circulating pump 20, level sensor 21, bathtub hot water input and output metal parts 22, bathtub loop adapter 23, bathtub 24 successively and consists of via sparge pipe.In addition, be connected with bathtub 24 from bathtub hot water input and output metal parts 22, also be connected with bathtub tap 25 or shower (not shown) simultaneously, to its supplying hot water.When bathtub hot water injected, in the time of with the direct hot water supply of bathtub hot water infusion circuit, the hot water amount in hot-water storage tank 16 did not reach and carries out from hot-water storage tank 16 to bathtub 24 water pot hot water supply in scope below minimum necessary amount yet.
Bathtub is heating circuit (5) again, via sparge pipe, bathtub 24, bathtub loop adapter 23, bathtub hot water input and output metal parts 22, level sensor 21, bathtub circulating pump 20, flow switch 19, bathtub is gone out hot water metal parts 26, bathtub loop adapter 23, bathtub 24 with bathtub heat transfer water pipe 27b, the bathtub of heat exchanger 27 and connects successively and consist of.When bathtub heats again, with bathtub again when the water circulation of the bathtub water of heating circuit (5), the running of running heat pump and machine internal circulation pump 17, and open warm water open and close valve 28, make by the warm water after 2 heating of cool water media heat exchanger and circulate in the warm water heat-transfer pipe 27a of bathtub with heat exchanger 27 interior settings, carry out heat exchange between warm water heat-transfer pipe 27a and bathtub heat transfer water pipe 27b, carry out bathtub and heat again.
then, running control module 50, (be not limited to the kitchen by kitchen remote controller 51, washroom etc. go out the remote controller at hot water place) and the operating and setting of bathtub remote controller 52, carry out the running in heat pump refrigerant loop 30/stop and compressor 1a, the rotating speed of 1b is controlled, simultaneously by controlling expansion valve 3a, the refrigerant aperture of 3b is adjusted, machine internal circulation pump 17, the running of bathtub circulating pump 20/stop and hot water supply mixing valve 11, water mixing valve 12, flow rate regulating valve 13, bathtub hot water injection valve 18, warm water open and close valve 28, carry out the hot-water storage running, direct hot water supplying operation, water pot hot water supply running, bathtub hot water injects running, bathtub adds heat run again.
In addition, running control module 50 is controlled the rotating speed of compressor 1a, 1b, slowly increase rotating speed when the running beginning, in order to shorten the heat temperature raising time with predetermined high rotation speed operation, but in the situation that the such common load of washroom, kitchen hot water supply (approximately 42 ℃), return to the middling speed running after running is stable, and is controlled to be running relatively at a high speed when the large hot-water storage of thermic load turns round (approximately 65～90 ℃).
and, be provided with in Teat pump boiler: for detection of the water pot thermistor 16a～16e of hot-water storage temperature or the hot-water storage amount of hot-water storage tank 16, detect the environment temperature thermistor (not shown) of environment temperature, detecting the air heat of the temperature of air refrigerant heat exchanger hands over thermistor and detects the thermistor (not shown) of the temperature of each one or detect compressor 1a, the pressure sensor of the discharge pressure of 1b (not shown), detect the level sensor 21 of the water level in bathtub 24 etc., each detection signal is input to running control module 50.Running control module 50 is according to each equipment of these signal controlling.
In addition, hot water supply mixing valve 11, initial in the hot water supply running, open simultaneously between cool water media heat exchanger 2 sides and water mixing valve 12 sides and between hot-water storage tank 16 sides and water mixing valve 12 sides, from cool water media heat exchanger 2 and hot-water storage tank 16 both sides' supplying hot waters, when the heating-up temperature of the cool water media heat exchanger 2 by heat pump reaches hot water supply temperature (approximately 42 ℃), to close between hot-water storage tank 16 sides and water mixing valve 12 sides, only from cool water media heat exchanger 2 supplying hot waters.
In addition, warm water open and close valve 28 is arranged on cool water media heat exchanger 2 and bathtub is used between heat exchanger 27, when heating again, opens by bathtub, carry out bathtub and add again heat run, close water loop in the time in addition, be used for preventing from using from cool water media heat exchanger 2 to bathtub the leakage of the heat of heat exchanger 27.In addition, water supply side check-valves 9 only flows through water in a direction, anti-backflow.
Then, with reference to the heat pump refrigerant loop 30 of Fig. 1 and hot water supply loop 40, according to the running action of the Teat pump boiler of the hot water supply run chart explanation present embodiment of Fig. 2.Fig. 2 means the flow chart of flow process in the Teat pump boiler of embodiments of the present invention, the hot water supply running when opening kitchen faucet and using hot water.
when opening kitchen faucet 15 and bring into use hot water (step 61), detection by water-supply quantity sensor 8, running control module 50 makes compressor 1a, the 1b running, the running in the refrigerant loop 30 of beginning heat pump, simultaneously by water supply metal parts 6, pressure-reducing valve 7, water-supply quantity sensor 8, water supply side check-valves 9, hydro-thermal of ac sensor 10, water supply side heat-transfer pipe 2c, 2d, hot water supply mixing valve 11, water mixing valve 12, flow rate regulating valve 13, the kitchen goes out hot water metal parts 14, the direct hot water supply circuit of kitchen faucet 15 begins direct hot water supplying operation (step 62).Simultaneously, go out the water pot hot water supply loop of hot water metal parts 14, kitchen faucet 15 by water supply metal parts 6, pressure-reducing valve 7, water-supply quantity sensor 8, water supply side check-valves 9, hot-water storage tank 16, hot water supply mixing valve 11, water mixing valve 12, flow rate regulating valve 13, kitchen, beginning water pot hot water supply running (step 63).
at this, heat pump refrigerant loop 30 is passing through compressor 1a, 1b compression and the HTHP refrigerant send into the medium side heat-transfer pipe 2a of cool water media heat exchanger 2, 2b, heating is at water supply side heat-transfer pipe 2c, after the water that flows in 2d, make it to the 11 side circulations of hot water supply mixing valve, but after running during soon intensification, the refrigerant that is sent to cool water media heat exchanger 2 high pressure that do not reach a high temperature fully, temperature is lower, and cool water media heat exchanger 2 is whole cooling, therefore the heating efficiency that water is heated is inadequate, therefore need to supply with the water pot hot water supply (step 63) from the high-temperature water of hot-water storage tank 16.Along with the process of time, refrigerant becomes HTHP, and therefore, the increasing from the thermal discharge of refrigerant of generation constantly increases the heating efficiency of water.
Before reaching the proper temperature state, the heating efficiency of heat pump running needs several minutes, therefore, running control module 50 from running beginning until reach the proper temperature state during when making the rotating ratio of compressor 1a, 1b normal at a high speed, carry out concurrently simultaneously supplying with from hot-water storage tank 16 the water pot hot water supply running (step 63) of high-temperature water, supply with the water of proper temperature from kitchen faucet 15.In addition, carry out the heating-up temperature of heat pump running and judge (step 64), if do not arrive set point of temperature, continue the parallel running of direct hot water supply and water pot hot water supply, if more than reaching set point of temperature, stop water pot hot water and supply water (step 65), continue to come supplying hot water (step 66) by the individual operation of direct hot water supply.
In addition, running control module 50, when the mixed hot water temperature after hot water supply mixing valve 11 is more much lower than proper temperature, increase water pot hot water supply amount, and make 11 actions of hot water supply mixing valve, so that along with roughly reducing water pot hot water supply amount near proper temperature, adjust flow proportional and reach proper temperature.And then, when, also can by adjusting the output from water mixing valve 12, adjusting to the hot water supply temperature of using terminal during higher than proper temperature by the mixed hot water temperature after hot water supply mixing valve 11.
Therefore, the task of hot-water storage tank 16 is, auxiliary when making intensification before the hot water supply temperature reaches enough temperature as the heating efficiency of heat pump running, the ability in heat pump refrigerant loop 30, the particularly output of compressor 1a, 1b are larger, more can shorten the heating-up time, reduce the capacity of hot-water storage tank 16.In addition, to carry out bathtub hot water injection etc. use when many places like that in the hot water supply of kitchen in order only to deal with by direct hot water supply, the capacity of compressor 1a, 1b, with respect to general 5kW left and right of using in existing hot-water storage type, wish to increase to the 20kW left and right, but not only need to develop new compressor, each parts in heat pump refrigerant loop 30 also need new research, and are extremely difficult.
Therefore, in embodiments of the present invention, make double-circulating heat pump mode 30a, the 30b of the compressor about the twice of having used two existing compressors, utilization and the actual reliability of prior art have been guaranteed, as long as the capacity of compressor is enough, even application/effect of the present invention does not have difference yet in the single circulating heat pump mode.
Then, when when the running warm and when becoming the individual operation of direct hot water supply when (step 66), according to the temperature of environment temperature (external air temperature), air refrigerant heat exchanger 4a, 4b and hot water supply pattern (in Fig. 2, the kitchen hot water supply) as the determinating reference of critical item (step 67), carry out the judgement (step 68) of optimum operation mode.
Judgement (step 68) by the optimum operation mode, when being judged to be mode A, be made as the efficiency of heating surface preferentially turn round (step 69), when being judged to be mode B, be made as heating efficiency preferentially turn round (step 70), when being judged to be mode C, defrosting running in the middle of being made as (narration in the back, running defrosts in the process of hot water supply running) continues direct hot water supplying operation (step 71).
After this, when hot water uses end (step 72), stop direct hot water supply (step 73), carry out simultaneously the frosting of air refrigerant heat exchanger 4a, 4b and judge (step 74), when being judged to be frosting (for example temperature is judged to be frosting in time below 0 ℃ around) running (step 75) defrosts, then stop heat pump running (step 76), when being judged to be not frosting, do not stop heat pump running (step 76) with not defrosting running.
The content of the determinating reference of optimum operation control mode of Teat pump boiler of present embodiment and optimum operation mode A, B, C then, is described with reference to Fig. 3 and Fig. 4.Fig. 3 means the chart of the relation of the heating efficiency of general Teat pump boiler and the efficiency of heating surface.Fig. 4 means the decision condition of optimum operation mode of the Teat pump boiler that determines present embodiment and the table of determinating reference.
Heating efficiency when Fig. 3 represents the heat pump running and the relation of the efficiency of heating surface, line chart A represents the situation of kitchen hot water supply (approximately 42 ℃), line chart B represents that the water pot hot-water storage is (to the water pot supplying hot water, described hot-water storage loop (1)) situation of (approximately 65 ℃), be illustrated at certain hot water supply temperature, heating efficiency is higher, and the efficiency of heating surface is lower.This is due in order to increase heating efficiency, and the rotating speed that improves compressor carries out High Rotation Speed, so the mechanical loss of compressor increases and cause, with in automobile with respect to common speed, the fuel utilization Efficiency Decreasing of gasoline is same when running at high speed.
The line chart A of Fig. 3, in certain condition, for example when 17 ℃ of 16 ℃ of environment temperatures, supply water temperature, in order to be heated to kitchen hot water supply temperature (approximately 42 ℃) more than certain flow (for example 5L/ minute), minimum heating efficiency Amin is necessary.Then, when increasing heating efficiency from heating efficiency Amin, the efficiency of heating surface reduces gradually, reaches heating efficiency maximum point Amax.Line chart B and line chart A are under identical conditions, when carrying out water pot hot-water storage running (running in described hot-water storage loop (1)), in order to be heated to water pot hot-water storage temperature (approximately 65 ℃), minimum heating efficiency Bmin is necessary, when increasing heating efficiency from heating efficiency Bmin, the efficiency of heating surface reduces gradually, reaches heating efficiency maximum point Bmax.In addition, heating efficiency maximum point Amax, Bmax are also different according to the heating efficiency of heat pump and hot water supply temperature, hot water supply flow etc.
By line chart A and line chart B as can be known, under identical conditions, the heating efficiency that the higher needs of hot water supply temperature are larger, therefore when improving heating efficiency similarly, the efficiency of heating surface reduces when the hot water supply temperature is high.
Then, an example of expression optimum operation mode determinating reference in Fig. 4.As operating condition, these three projects of environment temperature (external air temperature), air refrigerant heat exchanger temperature and hot water supply pattern are set.Environment temperature is divided into high due to temperature or absolute humidity is low, therefore hardly frosting+more than 7 ℃ or below-7 ℃, with-7 ℃～+ 7 ℃ of easy frosting, air refrigerant heat exchanger temperature is divided into more than 0 ℃ and less than 0 ℃ (if heat exchanger temperature more than 0 ℃, frost is difficult to adhere to).On the other hand, hot water supply mode division is: the hot water supply pattern more than 60 minutes that water pot hot-water storage, the hot water supply of washroom, kitchen, the injection of bathtub hot water, shower and each pattern are common.For each hot water supply pattern of dividing, division corresponding to environment temperature and air refrigerant heat exchanger temperature, stipulated the optimum operation mode, by using these conditions, as the optimum operation mode, judge A (efficiency of heating surface preferentially turns round), B (heating efficiency preferentially turns round), C (middle defrosting running).
Environment temperature is divided into two stages of temperature province with the temperature province of easy frosting of frost-free, but be not limited to this, also can be further divided into two stages to the zone of easy frosting-7 ℃～+ 7 ℃, for example be divided into the temperature province in-2 ℃～+ 3 ℃ of the easiest frosting and-7 ℃～+ 7 ℃ scopes except this zone,-2 ℃～+ 3 ℃ altogether are divided into 3 zones, in the situation that may be controlled to the aperture of further opening expansion valve and defrost.
In example shown in Figure 4, divide water pot hot-water storage running with 150L, the difference when having inferred high-boiling (approximately 80 ℃～90 ℃) in the winter time before and after 60 minutes, according to the heating efficiency of heat pump etc., the division capacity is different.In addition, hot water inject, shower is made as the preferential B of heating efficiency, in order to shorten the stand-by period before balneation, and the hot water supply quantity not sufficient when avoiding shower, but inject, when particularly not needing the shower of the strong flow of water, also can be judged to be the preferential A of running efficiency at the automatic hot-water of inferring based on subscription time.
At this, the A of optimum operation mode mainly makes the preferential running of the efficiency of heating surface control, and therefore, carries out the efficiency of heating surface transport maximum as target the Amin in Fig. 3 or Bmin.The B of optimum operation mode mainly makes the preferential running of heating efficiency control, and therefore, carries out the heating efficiency transport maximum as target the Amax in Fig. 3 or Bmax.In addition, defrosting running in the middle of the C of optimum operation mode carries out (the defrosting running in the process of hot water supply running), but it is the frosting phase optimum operation mode that the efficiency of heating surface that caused by frosting when having considered winter low temperature reduces, and uses Fig. 5～Fig. 7 to carry out following explanation.
Fig. 5 mean in general Teat pump boiler winter continuous operation situation under the chart that changes of time of heating efficiency.The duration of runs when line A of Fig. 5 is illustrated in winter low temperature in the situation of (approximately-7 ℃～+ 7 ℃ of environment temperatures) continuous operation and the variation of heating efficiency.Along with the process of the duration of runs, in the surperficial frosting of air refrigerant heat exchanger 4a, 4b, approximately after 30 minutes, the heat exchange performance of air refrigerant heat exchanger reduces process, and heating efficiency reduces.When the heating efficiency of start of run is made as 100%, through approximately being reduced to sometimes below 50% after 1 hour, need the defrosting running.
If defrost running in the process of hot water supply running, again return to initial heating efficiency, but the defrosting running stops hot water supply, therefore under being zero state, the hot water supply amount needs power consumption, cause the reduction of the efficiency of heating surface, therefore in the situation that the continuous hot water supplying operation more than 30 minutes, judgement still the not defrosting running and continue the hot water supply running under the state that heating efficiency reduces of running that on the way defrosts is a difficult problem relevant to intricatelys such as service condition or hot water supply durations of runs.
Present embodiment, as the optimum operation control method for this problem, control determinating reference according to optimum operation shown in Figure 4, control to judge during water pot hot-water storage more than 150L and by service condition or study and infer the hot water supply time more than 1 hour the time, defrosting running C in the middle of selecting, running defrosts when process is inferred approximately hot water supply in the 1/2 hour running of hot water supply time.At this, infer the duration of runs and be the hot water supply pattern more than 60 minutes, for example according to the empirical learning of every day when certain hot water supply pattern is made decision the situation of 6 pm supplying hot water more than 60 minutes, when beginning this certain hot water supply pattern to 6 pm on the same day, because results of learning are estimated as hot water supply pattern more than 60 minutes.
Fig. 6 means in the Teat pump boiler of present embodiment, infers in the winter time continuous operation in long situation of hot water supply time and the key diagram of the comparison that adds heat in middle defrosting running.In Fig. 6, it is that approximately the heating efficiency 70 minutes the time changes that the hot water supply time is inferred in expression, therefore, becomes line A1 such when having carried out the continuous hot water supplying operation, and the total that line A1 below area became during 70 minutes adds heat.
In the present embodiment, infer the hot water supply time more than 60 minutes, therefore defrosting running in the middle of being judged to be, as shown in the dotted line of line B1 and line B2, surpass approximately through the runnings that defrost in 30 minutes of 1/2 hour, the total that the below area of line B1 and line B2 became during 70 minutes adds heat.At this, when the total during to 70 minutes adds heat and compares, can be clear and definite according to Fig. 6, the heat reduction amount that the adds E that frosting during with the continuous hot water supplying operation causes (deduct from the dotted line of B2 the solid line part of A1 after amount) compares, the heat reduction amount that the adds D that defrosting running causes (through adding the amount that heat disappears in the defrosting running after 30 minutes) is less, therefore, it is many that middle defrosting running (B1 and B2) adds heat than continuous operation (A1), whole as running, the efficiency of heating surface is good.
Fig. 7 means in the Teat pump boiler of present embodiment, infers in the winter time continuous operation in short situation of hot water supply time and the key diagram of the comparison that adds heat in middle defrosting running.In Fig. 7, as inferring the example of hot water supply time less than 60 minutes, the situation of 50 minutes has been described.In the situation that carried out the continuous hot water supplying operation, as line A2, corresponding to short amount of time, heating efficiency reduction amount E reduces, and becomes to have carried out than the centre heat reduction amount that the adds D that the defrosting in the situation of defrosting running causes and lack.Therefore, the total of the continuous operation that the downside area of line A2 is represented adds heat, adds heat than the total of defrosting running in the middle of the downside product representation of line C1, C2 many, and continuous operation is better than the efficiency of heating surface of centre defrosting running.
As mentioned above, being characterized as of embodiments of the present invention, judge the optimum operation mode with environment temperature, air refrigerant heat exchanger temperature, hot water supply pattern as determinating reference, according to described judgement select that the efficiency of heating surface preferentially turns round, heating efficiency preferentially turns round, optimum operation mode in middle defrosting running, generally carry out optimum operation and control, realize the raising of the guaranteeing of necessary heating efficiency, the efficiency of heating surface and energy-conservation.The concrete structure of this feature possesses: via coolant piping with compressor, carry out water be connected with refrigerant heat exchange cool water media heat exchanger, expansion valve, carry out that air is connected with refrigerant that the air refrigerant heat exchanger of heat exchange connects successively and heat pump refrigerant loop; By described cool water media heat exchanger, hot water supply mixing valve, be used for storing hot-water storage tank, the machine internal circulation pump by the warm water after the cool water media heat exchanger heats and hot-water storage loop that the sparge pipe that connects consists of between these parts; By supplying with metal parts, described hot-water storage tank, hot water supply mixing valve, water mixing valve, flow rate regulating valve, go out the hot water metal parts and hot water supply loop that the sparge pipe that connects consists of between these parts; And the running control module of controlling the action of described compressor, expansion valve, hot water supply mixing valve, machine internal circulation pump, water mixing valve, flow rate regulating valve etc., described running control module has: according to the determinating reference of the optimum operation mode that adopts in environment temperature or air refrigerant heat exchanger temperature and hot water supply pattern, judge the optimum operation mode, as described optimum operation mode, be provided with at least that the efficiency of heating surface preferentially turns round, heating efficiency preferentially turns round and the optimum operation control module of middle these 3 kinds of drive manners of defrosting running.
So, the running control module of present embodiment, one of concrete feature is, and is by inferring the hot water supply time, long in the hot water supply time, in the good situation of the words efficient of middle defrosting running, carry out centre defrosting running, short in the hot water supply time, in the good situation of the words efficient of continuous operation, carry out continuous operation, therefore can carry out the interim optimum operation of frosting.and, the running control module of present embodiment, by environment temperature (external air temperature), air refrigerant heat exchanger temperature, and the determinating reference of the optimum operation mode that adopts in the hot water supply pattern, judge that the efficiency of heating surface preferentially turns round, heating efficiency preferentially turns round, and the optimum operation mode is selected in middle defrosting running, in the present embodiment, illustrated be applied to carry out direct hot water supplying operation moment the formula Teat pump boiler situation, but in the hot-water storage type Teat pump boiler, capacity by the hot-water storage tank is large, be controlled at by study and change the hot-water storage amount every day and use etc. in situation and use present embodiment, also can obtain the same effect of moment formula.
Above-mentioned record is to make for embodiment, but the present invention is not limited to this, it should be understood by those skilled in the art that in the scope of purport of the present invention and the request patent protection that adds to carry out various changes and correction.
Claims (6)
1. Teat pump boiler possesses:
Heat pump refrigerant loop, air refrigerant heat exchanger and coolant piping that it has the compressor of compression refrigerant, the cool water media heat exchanger that carries out the heat exchange of water and refrigerant, expansion valve, carries out the heat exchange of air and refrigerant;
the hot water supply loop, it has the hot-water storage tank that has by the warm water after described cool water media heat exchanger heats, the machine internal circulation pump, the hot water supply mixing valve, carry out the bathtub heat exchanger with heat exchange by the warm water after described cool water media heat exchanger heats, bathtub circulation pump, water mixing valve, sparge pipe, this hot water supply loop formation: the hot-water storage loop of storing high-temperature water in described hot-water storage tank, to going out the direct direct hot water supply circuit of supplying with by the warm water after described cool water media heat exchanger heats in hot water position, supply with water pot hot water supply loop from the warm water of described hot-water storage tank to going out the hot water position, use pump to the bathtub hot water infusion circuit of bathtub supply by the warm water after described cool water media heat exchanger heats by described bathtub circulation, supply with from described bathtub with the bathtub of the warm water of heat exchanger heating circuit again to bathtub with pump by the circulation of described bathtub, and
Operation control section, it is by going out the operating and setting of hot water position remote controller and bathtub remote controller, controls that each inscape is carried out the hot-water storage running, directly hot water supplying operation, water pot hot water supply running, bathtub hot water inject running, bathtub adds heat run again,
Described Teat pump boiler is characterised in that,
Described operation control section is carried out following optimum operation and is controlled: with the temperature of the environment temperature of Teat pump boiler, described air refrigerant heat exchanger and comprise to water pot store hot water, hot water position supplying hot water, bathtub hot water inject to going out, the hot water supply of running more than the scheduled time interior hot water supply/hot-water storage pattern as determinating reference judge that the efficiency of heating surface preferentially turns round, heating efficiency preferentially turns round, middle these 3 kinds of drive manners of defrosting running some
Described operation control section, reach maximum compressor rotary speed running with the efficiency of heating surface when being judged to be the described efficiency of heating surface and preferentially turning round, reach maximum compressor rotary speed running with heating efficiency when being judged to be described heating efficiency and preferentially turning round, when being judged to be the running that defrosts after reaching maximum compressor rotary speed running with heating efficiency during the defrosting running in the middle of described and passing through time of 1/2 of heat pump duration of runs of being inferred.
2. Teat pump boiler possesses:
Heat pump refrigerant loop, air refrigerant heat exchanger and coolant piping that it has the compressor of compression refrigerant, the cool water media heat exchanger that carries out the heat exchange of water and refrigerant, expansion valve, carries out the heat exchange of air and refrigerant;
the hot water supply loop, it has the hot-water storage tank that has by the warm water after described cool water media heat exchanger heats, the machine internal circulation pump, the hot water supply mixing valve, carry out the bathtub heat exchanger with heat exchange by the warm water after described cool water media heat exchanger heats, bathtub circulation pump, water mixing valve, sparge pipe, this hot water supply loop formation: the hot-water storage loop of storing high-temperature water in described hot-water storage tank, to going out the direct direct hot water supply circuit of supplying with by the warm water after described cool water media heat exchanger heats in hot water position, supply with water pot hot water supply loop from the warm water of described hot-water storage tank to going out the hot water position, use pump to the bathtub hot water infusion circuit of bathtub supply by the warm water after described cool water media heat exchanger heats by described bathtub circulation, supply with from described bathtub with the bathtub of the warm water of heat exchanger heating circuit again to bathtub with pump by the circulation of described bathtub, and
Operation control section, it is by going out the operating and setting of hot water position remote controller and bathtub remote controller, controls that each inscape is carried out the hot-water storage running, directly hot water supplying operation, water pot hot water supply running, bathtub hot water inject running, bathtub adds heat run again,
Described Teat pump boiler is characterised in that,
Described operation control section is carried out following optimum operation and is controlled: with the temperature of the environment temperature of Teat pump boiler, described air refrigerant heat exchanger and comprise to water pot store hot water, hot water position supplying hot water, bathtub hot water inject to going out, the hot water supply of running more than the scheduled time interior hot water supply/hot-water storage pattern as determinating reference judge that the efficiency of heating surface preferentially turns round, heating efficiency preferentially turns round, middle these 3 kinds of drive manners of defrosting running some
Described operation control section as described determinating reference, for each hot water supply pattern learning heat pump duration of runs, is hot water supply pattern more than 60 minutes in the situation that infer the duration of runs, and in the middle of judging, the defrosting running is controlled as optimum operation.
3. the described Teat pump boiler of any one according to claim 1 to 2, is characterized in that,
Described operation control section, as described determinating reference, described environment temperature is divided into+more than 7 ℃ or below-7 ℃ and-7 ℃～+ 7 ℃ at least more than two parts.
4. the described Teat pump boiler of any one according to claim 1 to 2, is characterized in that,
Described operation control section as described determinating reference, is divided into described air refrigerant heat exchanger temperature more than 0 ℃ and less than 0 ℃ of these two parts.
5. the described Teat pump boiler of any one according to claim 1 to 2, is characterized in that,
Described operation control section is judged in the frosting of carrying out described air refrigerant heat exchanger after heat run finishes that adds of heat pump running,
When being judged to be frosting, then the running that defrosts stops the heat pump running, when being judged to be not frosting, does not stop the heat pump running with not defrosting running.
6. the described Teat pump boiler of any one according to claim 1 to 2, is characterized in that,
Described heat pump refrigerant loop is the double-circulating heat pump refrigerant loop of using respectively two described compressors, two described cool water media heat exchangers, two described expansion valves, two described air refrigerant heat exchangers, two described coolant pipings.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2008-110292 | 2008-04-21 | ||
| JP2008110292A JP5081050B2 (en) | 2008-04-21 | 2008-04-21 | Heat pump water heater |
| PCT/JP2008/064649 WO2009130804A1 (en) | 2008-04-21 | 2008-08-15 | Heat pump water heater |
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| CN102016439A CN102016439A (en) | 2011-04-13 |
| CN102016439B true CN102016439B (en) | 2013-11-06 |
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| CN2008801287228A Expired - Fee Related CN102016439B (en) | 2008-04-21 | 2008-08-15 | Heat pump water heater |
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| JP (1) | JP5081050B2 (en) |
| KR (1) | KR101222300B1 (en) |
| CN (1) | CN102016439B (en) |
| WO (1) | WO2009130804A1 (en) |
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| CN101852494A (en) * | 2010-05-31 | 2010-10-06 | 宁波海诚电器有限公司 | Air energy water heater and control method thereof |
| US9863680B2 (en) * | 2013-06-20 | 2018-01-09 | Mitsubishi Electric Corporation | Heat pump apparatus |
| CN105650855B (en) * | 2016-03-26 | 2019-06-07 | 广东万家乐燃气具有限公司 | A kind of gas heater and its control method with reservation function |
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| JP2003222392A (en) * | 2002-01-29 | 2003-08-08 | Daikin Ind Ltd | Heat pump type water heater |
| CN1548864A (en) * | 2003-05-20 | 2004-11-24 | 乐金电子(天津)电器有限公司 | Defrosting control method for air conditioner |
| JP2005121283A (en) * | 2003-10-16 | 2005-05-12 | Matsushita Electric Ind Co Ltd | Heat pump water heater |
| JP2005127588A (en) * | 2003-10-23 | 2005-05-19 | Matsushita Electric Ind Co Ltd | Heat pump hot-water supply device |
| JP2006266591A (en) * | 2005-03-24 | 2006-10-05 | Hitachi Home & Life Solutions Inc | Heat pump water heater |
| CN2935006Y (en) * | 2006-04-30 | 2007-08-15 | 谢坤 | Automatic defrost heat pump water heater |
| JP2008008507A (en) * | 2006-06-27 | 2008-01-17 | Mitsubishi Electric Corp | Hot water storage type water supply system |
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2008
- 2008-04-21 JP JP2008110292A patent/JP5081050B2/en not_active Expired - Fee Related
- 2008-08-15 KR KR1020107023388A patent/KR101222300B1/en not_active IP Right Cessation
- 2008-08-15 WO PCT/JP2008/064649 patent/WO2009130804A1/en active Application Filing
- 2008-08-15 CN CN2008801287228A patent/CN102016439B/en not_active Expired - Fee Related
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003222392A (en) * | 2002-01-29 | 2003-08-08 | Daikin Ind Ltd | Heat pump type water heater |
| CN1548864A (en) * | 2003-05-20 | 2004-11-24 | 乐金电子(天津)电器有限公司 | Defrosting control method for air conditioner |
| JP2005121283A (en) * | 2003-10-16 | 2005-05-12 | Matsushita Electric Ind Co Ltd | Heat pump water heater |
| JP2005127588A (en) * | 2003-10-23 | 2005-05-19 | Matsushita Electric Ind Co Ltd | Heat pump hot-water supply device |
| JP2006266591A (en) * | 2005-03-24 | 2006-10-05 | Hitachi Home & Life Solutions Inc | Heat pump water heater |
| CN2935006Y (en) * | 2006-04-30 | 2007-08-15 | 谢坤 | Automatic defrost heat pump water heater |
| JP2008008507A (en) * | 2006-06-27 | 2008-01-17 | Mitsubishi Electric Corp | Hot water storage type water supply system |
Also Published As
| Publication number | Publication date |
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| KR20100128332A (en) | 2010-12-07 |
| JP5081050B2 (en) | 2012-11-21 |
| WO2009130804A1 (en) | 2009-10-29 |
| CN102016439A (en) | 2011-04-13 |
| KR101222300B1 (en) | 2013-01-16 |
| JP2009257717A (en) | 2009-11-05 |
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