CN102628627B - Heat pump type heat source machine and heating system - Google Patents
Heat pump type heat source machine and heating system Download PDFInfo
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- CN102628627B CN102628627B CN201210021651.XA CN201210021651A CN102628627B CN 102628627 B CN102628627 B CN 102628627B CN 201210021651 A CN201210021651 A CN 201210021651A CN 102628627 B CN102628627 B CN 102628627B
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Abstract
Provided is a heat pump type heat source machine. In the heat source machine heat source machine, a user can use a manipulator to respectively independently set a stop temperature and a warm water target temperature and can easily perform serial connection arrangement of a plurality of heat pump type heat source machines. The heat pump type heat source machine is provided with a water-cold medium heat exchanger, an inlet temperature sensor for detecting an inlet temperature of the water-cold medium heat exchanger, an outlet temperature sensor for detecting an outlet temperature of the water-cold medium heat exchanger, a running control mechanism for comparing a temperature detected by the inlet temperature sensor with a stop temperature to control the running/ stopping of a refrigeration cycle, a heating capacity control mechanism for comparing a temperature detected by the outlet temperature sensor with a target temperature to control the heating capacity of a refrigeration cycle and an operating mechanism capable of respectively independently setting a stop temperature and a target temperature.
Description
Technical field
The present invention relates to and use heat-pump-type refrigerant cycles produce the heat pump type heat source machine of warm water and use the heating system of this heat source machine.
Background technology
Carry out in the heating system of the heating heated etc. at the load supply warm water to heating equipment, fan-coil component etc. under floor, as the mechanism that water is heated, consider to use the heat pump type heat source machine being thermal source with the air of outdoor air etc.
In such heat pump type heat source machine, the caloric requirement being used for water to heat is more than the heat of load request.Thus, the heat pump type heat source machine of the selected the suitableeest ability (heating heat) according to load is needed.
Heating heat according to arranging the kind etc. of destination and load and different, so must prepare to possess the kind with the heat pump type heat source machine of the heating efficiency of respective load matched.
In addition, also contemplate and to possess multiple refrigerant cycles in order to increase heating efficiency, the water heat exchanger adding thermal output as each refrigerant cycles is connected in series and achieves the heat pump type heat source machine of large ability.(with reference to patent document 1)
Patent document 1: Japanese Unexamined Patent Publication 2008-175476 publication
But when having prepared when corresponding to load the heat pump type heat source machine possessing optimal heating efficiency, machine number becomes many, occur to manufacture and circulate to become inefficent problem.
Summary of the invention
So, the object of the invention is in heat pump type heat source machine, obtain the heat pump type heat source machine being connected in series setting and the heating system that easily can carry out the multiple stage of heat pump type heat source machine.
The heat pump type heat source machine of technical scheme of the present invention, possesses heat pump refrigerant cycles, this heat pump refrigerant cycles has the water-refrigerant heat exchanger for water and refrigerant being carried out heat exchange, the feature of this heat pump type heat source machine is, possess: inlet temperature sensor, detect the water temperature of the entrance side of above-mentioned water-refrigerant heat exchanger; Outlet temperature sensor, detects the water temperature of the outlet side of above-mentioned water-refrigerant heat exchanger; Running controlling organization, compares the inlet water temperature detected by above-mentioned inlet temperature sensor with stopping temperature, controls the running/stopping of above-mentioned heat pump refrigerant cycles; Add heat controlling organization, the outlet water temperature detected by above-mentioned outlet temperature sensor is compared with target temperature, control to add heat by above-mentioned heat pump refrigerant cycles; And operating mechanism, separately can set above-mentioned stopping temperature and above-mentioned target temperature.
Thereby, it is possible to provide a kind of heat pump type heat source machine being connected in series setting easily can carrying out multiple stage.
In addition, the feature of the heating system of technical scheme of the present invention is, be connected in series by each water-refrigerant heat exchanger of water pipe arrangement by above-mentioned to load, pump and multiple stage heat pump type heat source machine, the above-mentioned target temperature of the above-mentioned heat pump type heat source machine of upstream side set lower than the above-mentioned stopping temperature of the above-mentioned heat pump type heat source machine in downstream.
Even if thereby, it is possible to provide a kind of when using when heat pump type heat source machine is connected in series multiple stage, the heating system of running that the overall efficiency that also can carry out mating with the situation of load is higher.
Accompanying drawing explanation
Fig. 1 is the structure chart of the heating system of embodiment for the present invention.
Fig. 2 is refrigerant cycles and the control block diagram of the heat pump type heat source machine used in this heating system.
Fig. 3 is the control flow chart of this heat pump type heat source machine.
Fig. 4 represents the variations in temperature in each portion of this heat pump type heat source machine and the curve map of the operating condition of refrigerant cycles.
Description of symbols
1 heating system, HS (1) ~ HS (n) source heat pump heat machine, 3 pumps, 4 loads, 5 water pipe arrangements, 22 operators, 21 controllers, 23 convertor devices, 24 compressors, 26 water-refrigerant heat exchanger, 28 heat source side heat exchangers, 29 propeller fans, 30 fan motors, 31 outlet temperature sensors, 32 inlet temperature sensors.
Detailed description of the invention
Fig. 1 to Fig. 4 is used to be described embodiments of the present invention.
The structure of the heat pump type heat source machine representing embodiment for the present invention in FIG and the heating system 1 that uses this heat pump type heat source machine.
Heating system 1 makes to lead in the load 4 of heating equipment, fan-coil component etc. floor from the stream of warm water of water pipe arrangement 5 supply.In the load 4, the heat of this warm water is dispelled the heat, and carries out the heating that specifies or heating.Water pipe arrangement 5 is provided with pump 3 in midway, and by this pump 3 action, the current in water pipe arrangement 5 lead to.
In water pipe arrangement 5 midway, be in series provided with multiple heat pump type heat source machine HS (1) ~ HS (n).Water pipe arrangement 5 forms the loop circuit be connected in series by each water-refrigerant heat exchanger (26 in Fig. 2) of load 4 and pump 3, multiple heat pump type heat source machine HS (1) ~ HS (n).By making pump 3 operate, the water in water pipe arrangement 5 is circulation between load 4, multiple heat pump type heat source machine HS (1) ~ HS (n) of being connected in series.The water of such conveying heat becomes loop circuit.
In addition, in FIG, between the heat pump type heat source machine HS (n) and load 4 of most final stage, be configured with pump 3, but the setting position of pump 3 is located at the passable of water pipe arrangement 5 midway everywhere.
Below, in the heat pump type heat source machine HS that water pipe arrangement 5 is connected in series (1) ~ HS (n), arbitrary heat pump type heat source machine is set to heat pump type heat source machine HS (i), will adjacent to this heat pump type heat source machine HS (i), the heat pump type heat source machine in downstream heat pump type heat source machine HS (i+1) be represented for benchmark with the direction of the water of flowing in water pipe arrangement 5.
By the running of pump 3, the water at low temperature flowed out from load 4 in series flows among multiple heat pump type heat source machine HS (1) ~ HS (n).Here, if make heat pump type heat source machine HS (1) ~ HS (n) running, water then in water pipe arrangement 5 is heated by each heat pump type heat source machine HS (1) ~ HS (n) successively until become the temperature of hope, and the water (hot water) after this heating is got back in load 4 again.As a result, warm water is supplied to load 4, this heat is dispelled the heat, carry out heating or heating.
Each heat pump type heat source machine HS (1) ~ HS (n) shown in Fig. 2 is identical structure, is made up of the control device of 1 heat-pump-type refrigerant cycles and this refrigerant cycles of control.Heat-pump-type refrigerant cycles is by with by by the compressor 24 of convertor device 23 variable speed drive, the cross valve 25 of circulating direction changing refrigerant, water-refrigerant heat exchanger 26, expansion valve 27, heat source side heat exchanger 28, again connect to the mode that compressor 24 returns the general refrigerant cycles that coolant piping formed by cross valve 25 successively.
Heat source side heat exchanger 28 is such as the air heat exchanger of fin-and-tube type, and this heat exchanger is provided with the propeller fan 29 for ventilating.
In addition, cross valve 25 is arranged in order to the white defrosting of melting of the attachment condensate moisture in air formed on the surface of heat source side heat exchanger 28 operates, if use heat source side heat exchanger 28 under the atmospheric condition of high temperature not adhering to frost, then do not need cross valve 25.
If make refrigerant cycles operate, then compressed by refrigerant by compressor 24, the HTHP refrigerant of discharge flows in water-refrigerant heat exchanger 26 via cross valve 25.In water-refrigerant heat exchanger 26, the HTHP refrigerant flow through in the water of water pipe arrangement 5 and refrigerant cycles carries out heat exchange, and water is heated.
As the refrigerant of the refrigerant cycles of each heat pump type heat source machine HS (1) ~ HS (n), be used as the R410A of HFC (hydrogen fluorohydrocarbon) refrigerant of the refrigerant do not damaged the ozone layer in the present embodiment, but also can use other suitable refrigerants.
In addition, each heat pump type heat source machine HS (1) ~ HS (n) can be incomplete same, and the heating efficiency of each heat pump type heat source machine HS (1) ~ HS (n) also can be made different.Such as, also can be that the heat pump type heat source machine of 5Kw and the heat pump type heat source machine of 2.5Kw combine by heating efficiency.
Such as, when the maximum heating ability that load 4 needs is 10Kw, both the heat pump type heat source machine of 5Kw can be arranged in series 2 to water pipe arrangement 5, also can be arranged in series the heat pump type heat source machine of water pipe arrangement 5 by the heat pump type heat source machine of 1 5Kw and 2 2.5Kw.
Then, according to Fig. 2, the control device of heat pump type heat source machine HS (i) is described.
The convertor device 23 driving compressor 24 and the fan motor 30 driving propeller fan 29 control by the controller 21 as controlling organization.
Controller 21 is made up of microcomputer and peripheral circuit thereof.In controller 21, the outlet temperature sensor 31 of the temperature (hereinafter referred to as outlet water temperature T out (i)) of the water pipe arrangement 5 of the inlet temperature sensor 32 being transfused to the temperature (hereinafter referred to as inlet water temperature Tin (i)) of the water pipe arrangement 5 of the entrance side of detection water-refrigerant heat exchanger 26 at its input side and the outlet side detecting water-refrigerant heat exchanger 26.And then, on controller 21, be connected to the operator 22 that can carry out the operating mechanism of setting operation as user.
Controller 21 is transfused to these inlet temperature sensors 31, the detected temperatures of outlet temperature sensor 32 and the setting content of operator 22, determines, controls the rotating speed of compressor 24 and fan motor 30 based on these data.
And then, heat source side heat exchanger 28 add heat run time refrigerant exit pipe arrangement near be provided with heat and hand over temperature sensor (Hot hands over temperature セ Application サ) 33, detect refrigerant temperature (Te).In addition, the temperature sensor 34 of the air themperature (To) detecting heat exchange is provided with in the heat exchange air inflow side of heat source side heat exchanger 28.These heat hand over temperature sensor 33, temperature sensor 34 is also connected on controller 21, and the refrigerant temperature Te, the air themperature To that detect read by controller 21.
The detected temperatures of these sensors uses in the detection of the attachment frost state of heat source side heat exchanger 28.The difference (To-Te) of controller 21 based on refrigerant temperature Te, air themperature To and the time variations of this poor (To-Te), detect the white state of attachment, judge that this attachment frost measures the amount whether reached required for defrosting, when being judged as needing defrosting, carry out defrosting running.
The operator 22 playing function as operating mechanism, as represented its outward appearance in Fig. 2, is provided with two kinds of up/down action button 22a, 22b from the teeth outwards and indicates the running/stop button 22c of running/stopping of source heat pump heat machine HS (i).
1st up/down action button 22a is used to the action button of stopping temperature Toff (i) setting source heat pump heat machine HS (i), if inlet water temperature Tin (i) detected by inlet temperature sensor 32 exceedes stop temperature Toff (i), then compressor 24 and fan motor 30 are stopped.
On the top of the 1st up/down action button 22a, be provided with the 1st liquid crystal display part 22d as indication mechanism, stopping temperature Toff (i) set by the 1st up/down action button 22a is shown by digital value.
On the other hand, the 2nd up/down action button 22b is used to the button going out hot water temperature setting source heat pump heat machine HS (i), is used to target temperature Ts (i) setting the warm water exported from source heat pump heat machine HS (i).
Also be provided with the 2nd liquid crystal display part 22e as indication mechanism on the top of the 2nd up/down action button 22b, target temperature Ts (i) set by the 2nd up/down action button 22b is shown by digital value.Like this, operator 22 can independently set stopping temperature Toff (i) of source heat pump heat machine HS (i) and target temperature Ts (i) of warm water by user.
Stopping temperature Toff (i) set by operator 22 and target temperature Ts (i) read in by controller 21, and outlet water temperature T out (i), refrigerant temperature Te, air themperature To that inlet water temperature Tin (i) detected by inlet temperature sensor 32 and outlet temperature sensor 31 detect read in.
Controller 21 has 3 following mechanism (1) ~ (3) to use these data etc. to control source heat pump heat machine HS (i).That is,
(1) inlet water temperature Tin (i) is compared, according to the running controlling organization of the running/stopping of the refrigerant cycles of its output control source heat pump heat machine HS (i) with stopping temperature Toff (i).
(2) in the running of source heat pump heat machine HS (i), according to target temperature Ts (i) and poor Δ T (i) of outlet water temperature T out (i), output frequency f (i) of convertor device 23 is changed, the rotating speed of control compressor 24 and control source heat pump heat machine HS (i) add heat add heat controlling organization.
(3) detect based on the difference (To-Te) of the refrigerant temperature Te of heat source side the heat exchanger 28 and air themperature To of heat exchange and the time variations of this poor (To-Te) and adhere to white state, judge that this attachment frost measures the amount whether reached required for defrosting, at the defrosting works being judged as needing to carry out defrosting running when defrosting.
According to the control flow chart of the controller 21 of Fig. 3, the motion of source heat pump heat machine HS (i) based on the setting content in operator 22 is described.
During controller 21 sets running in running/stop button 22c, by in order to source heat pump heat machine HS (i) that operates, stopping temperature Toff (i), target temperature Ts (i) that operator 22 sets are read in, and the air themperature To of inlet water temperature Tin (i) of the detected value as various temperature sensor, outlet water temperature T out (i), refrigerant temperature Te and heat exchange is read in (step ST0).In addition, if set stopping in running/stop button 22c, then whole the operation of a machine of source heat pump heat machine HS (i) is stopped.
Then step ST0, inlet water temperature Tin (i) is compared (step ST1) with stopping temperature Toff (i), when being (step ST1 is) when Tin (i) > Toff (i), heat radiation in load 4 is less, be judged as not needing heating, so the running of refrigerant cycles is stopped, that is, make compressor 24, fan motor 30 stops (step ST2).After making refrigerant cycles stop in step ST2, again get back to initial step ST1, continue halted state until inlet water temperature Tin (i) drops to less than stopping temperature Toff (i).
On the other hand, in step ST1, drop to less than (step ST1's is no) when stopping temperature Toff (i) at inlet water temperature Tin (i), because the temperature of the water supplied load 4 declines, so be judged as needing heating, refrigerant cycles is operated.That is, make compressor 24, fan motor 30 operates (step ST3 ~ 5).
Specifically, output frequency f (i) of the convertor device 23 that compressor 24 is operated is determined in step ST3,4, this rate-adaptive pacemaker f (i) is exported from convertor device 23 pairs of compressors 24, and operates in the mode making fan motor 30 become the rotating speed of regulation.
First, in step ST3, deduct outlet water temperature T out (i) from target temperature Ts (i) set by operator 22, accounting temperature difference Δ T (i).
Then, in step ST4, based on this temperature difference Δ T (i) and its time variations ratio, output frequency f (i) of convertor device 23 is calculated.The calculating of this output frequency f (i) is in order to by controlling with such as PI, proportional and control output frequency f (i) with temperature difference Δ T (i), controls to add heat to carry out.Further, in step ST5 then, convertor device 23 is controlled, to become output frequency f (i) calculated.
Result, if target temperature Ts (i) is larger with poor Δ T (i) of outlet water temperature T out (i), then output frequency f (i) becomes large, and the rotating speed of compressor 24 increases, and the heating efficiency of source heat pump heat machine HS (i) is increased.
In addition, if difference Δ T (i) is less, then output frequency f (i) diminishes, and the rotating speed of compressor 24 declines, and the heating efficiency of source heat pump heat machine HS (i) is reduced.
Then step ST5, carries out the judgement the need of defrosting running.First, difference (To-Te) and the time variations (step ST6) thereof of refrigerant temperature Te and air themperature To is calculated.Judge the data that calculate whether meet preset need defrosting condition (step ST7).
Here, if be judged as needing defrosting, then defrosting running (step ST8) of refrigerant cycles is performed.In defrosting running, judge whether that defrosting running completes (step ST9), continue defrosting running until complete (step ST9's is no), if completed (step ST9 is), then again get back to step ST1, revert to and add heat run.In addition, the judgement defrosted such as uses the time (7 minutes) of defrosting running or the rising etc. of refrigerant temperature Te.
On the other hand, when being judged as not needing defrosting in step ST7 (step ST7's is no), getting back to step ST0, again repeat each step.
Here, get back to Fig. 2, the action of refrigerant cycles is described.Adding in heat run, refrigerant to be documented in the refrigerant cycles shown in Fig. 2 pipe arrangement horizontal side solid arrow direction flowing.
First, if make compressor 24 operate, then become high temperature by compressing, the refrigerant of high pressure flowed into water-refrigerant heat exchanger 26 by cross valve 25.Water-refrigerant heat exchanger 26 plays function as condenser, by the water supply of the heat of refrigerant to flowing in water pipe arrangement 5, is heated by water, refrigerant self condensation and become liquid refrigerants.
This liquid refrigerants, becoming low pressure, low temperature by expanding during expansion valve 27, flows into the heat source side heat exchanger 28 playing function as evaporimeter.In heat source side heat exchanger 28, refrigerant and the air heat exchange of to be blown by propeller fan 29, taken away the heat in air, evaporation and become gas coolant, returned, repeat this action by cross valve 25 to compressor 24.
When by disposed in the outdoor for heat source side heat exchanger 28, in the winter time, the water condensed on the surface of the heat source side heat exchanger 28 of heat absorption is had to freeze and grow into the situation of frost.If placed by this attachment frost, then heat source side heat exchanger 28 and air no longer can heat exchanges, operate so need suitably to carry out defrosting.
When the difference (To-Te) of the air themperature To based on refrigerant temperature Te and heat exchange and the time variations of this difference be judged as needing to defrost operate, controller 21 makes cross valve 25 reverse, make the flowing of refrigerant to transfer in the other direction, and control output frequency f (i) of convertor device 23, compressor 24 is fixed as the rotating speed of defrosting, the running of fan motor 30 is stopped.
As a result, in defrosting running, the refrigerant of discharging from compressor 24 flows to the direction of dotted arrow Fig. 2, is flowed, here dispel the heat by cross valve 25 thermotropism source heat exchanger 28.The frost be attached on the surface of heat source side heat exchanger 28 is melted by the refrigerant of the high temperature flowed in inside.Then, refrigerant, through expansion valve 27, water-refrigerant heat exchanger 26, returns to compressor 24 via cross valve.
Now, in water-refrigerant heat exchanger 26, can not carry out adding heat run, absorb heat on the contrary, so make the temperature of the water of flowing in water pipe arrangement 5 decline.Therefore, defrosting running preferably completes in short time as far as possible.If defrosting running completes, then controller 21 makes cross valve 25 get back to original position, again re-starts above-mentionedly to add heat run.
In present embodiment, user can operate the operator 22 of heat pump type heat source machine HS (i) and separately set target temperature Ts (i) stopping temperature Toff (i) and warm water.
In the past, heat pump type heat source machine HS (i) does not imagine situation about multiple stage being connected in series, so the target temperature of the warm water preset and stop temperature being fixed and can not to operate or the target temperature of only warm water can set, if the target temperature of setting warm water, then automatically determine the stopping temperature slightly lower than it in controller side.Therefore, even if be connected in series multiple stage heat pump type heat source machine HS (i) to water pipe arrangement, suitable running can not be carried out.
Relative to this, as in the present embodiment, user uses operator 22 independently operate target temperature Ts (i) of stopping temperature Toff (i) and warm water and can set in each heat pump type heat source machine HS (i), thus can carry out the multiple stage of heat pump type heat source machine HS (i) easily be connected in series setting.
As shown in Figure 1, in heating system 1, do not possess multiple stage independently, i.e. the control device of Comprehensive Control, the water-refrigerant heat exchanger 26 of heat pump type heat source machine HS (i) is connected in series relative to load 4 by water pipe arrangement 5.
Here, multiple stage heat pump type heat source machine HS (1) ~ HS (n) selected its add up to maximum heating ability and load 4 to give the maximum heat dissipation capacity thought identical or slightly exceeding its equipment.That is, the total maximum heating ability maximum heating ability of each heat pump type heat source machine added up to of multiple stage heat pump type heat source machine HS (1) ~ HS (n) is more than the maximum heat dissipation capacity of load 4.
Each operator 22 of the heat pump type heat source machine HS (i+1) in the downstream of the flow direction of the water of user's operation setting in heat pump type heat source machine HS (i) and water pipe arrangement 5, sets lower than the stopping temperature Toff (i+1) of the heat pump type heat source machine HS (i+1) in its downstream by the direction relative to the water of flowing in water pipe arrangement 5 at target temperature Ts (i) of the warm water of the heat pump type heat source machine HS (i) of upstream side.That is, Toff (i+1) > Ts (i) is set to.
By carrying out such temperature setting, both heat pump type heat source machine HS (i) can be made to operate expeditiously.Such as, the setting value of each temperature is set to DEG C > Toff (i)=41, Ts (i)=43 DEG C, Ts (i+1)=47 DEG C > Toff (i+1)=45 DEG C.In addition, target temperature is set as Ts (i) < Ts (i+1) certainly.
The action of the heating system 1 when having carried out above-mentioned setting for heat pump type heat source machine HS (i) and heat pump type heat source machine HS (i+1) is described based on Fig. 4.
In addition, in the curve map of the epimere of the variations in temperature in each portion of the expression of Fig. 4, single dotted broken line represents the change of the outlet water temperature T out (i+1) of heat pump type heat source machine HS (i+1), and solid line represents outlet water temperature T out (i) (=Tin (i+1)) of heat pump type heat source machine HS (i) and inlet water temperature Tin (i) of heat pump type heat source machine HS (i).
In the diagram, under the state that the heat dissipation capacity the interval as time t0 ~ t1, in the total heating efficiency of heat pump type heat source machine HS (1) ~ (n) and load 4 roughly balances, inlet water temperature Tin (i) of the heat pump type heat source machine HS (i) of upstream side is DEG C lower than Toff (i)=41, so the heat pump type heat source machine HS (i) of upstream side carries out adding heat run, become target temperature Ts (i)=43 DEG C as far as possible to use saliva temperature Tout (i).
And, even if use saliva temperature Tout (i) by the heat pump type heat source machine HS (i) of upstream side to become target temperature Ts (i)=43 DEG C, the heat pump type heat source machine HS (i+1) in downstream is also inlet water temperature Tin (i+1)=43 DEG C of < Toff (i+1)=45 DEG C, so do not make running stop and carrying out adding heat run.
That is, in this case, carry out the heat pump type heat source machine HS (i) of upstream side and downstream heat pump type heat source machine HS (i+1) both add heat run.As a result, become multiple heat pump type heat source machine HS (i), HS (i+1) dispersion carries out adding the situation of heat run.
In addition, as shown in Figure 4, the outlet pipe arrangement of heat pump type heat source machine HS (i) is directly connected with the entrance pipe arrangement of heat pump type heat source machine HS (i+1), so outlet water temperature T out (i) of heat pump type heat source machine HS (i) is roughly the same with the inlet water temperature Tin (i+1) of heat pump type heat source machine HS (i+1).
On the other hand, in the diagram, if the heat dissipation capacity of load 4 as time t1 ~ t2 is interval reduces, then inlet water temperature Tin (i) of the heat pump type heat source machine HS (i) of upstream side rises, and becomes to exceed to stop temperature Toff (i)=41 DEG C, less than the scope of Toff (i+1)=45 DEG C.If become this state, then the heat pump type heat source machine HS (i) of upstream side will add heat run stopping (OFF), and the heat pump type heat source machine HS (i+1) in downstream continues to add heat run.
Now, heat run will be added by the heat pump type heat source machine HS (i) of upstream side to stop, then add heat to reduce, outlet water temperature T out (i) of the heat pump type heat source machine HS (i) of upstream side drops to inlet water temperature Tin (i).
Therefore, the part as shown in A in Fig. 4, the outlet water temperature T out (i+1) of the heat pump type heat source machine HS (i+1) in downstream also declines.And, in the heat pump type heat source machine HS (i+1) in downstream, become large by temperature difference Δ T (i+1), the output frequency f (i+1) of convertor device 23 is increased, heating efficiency is increased, uses saliva temperature Tout (i+1) and rise to make it close to Ts (i+1)=47 DEG C.
Like this, when the heat dissipation capacity of load 4 is less, if by heat pump type heat source machine HS (1) ~ (n) dispersed-heated of multiple stage, then the heating quantitative change of each heat pump type heat source machine HS (1) ~ (n) obtains too small, and the efficiency of each heat source machine declines.
So, when the heat dissipation capacity of load 4 reduces, by making the stopping of a part of heat pump type heat source machine HS (i), only carrying out adding heat run with the heat pump type heat source machine HS (i+1) of less number of units, the heating quantitative change of every 1 can be made large, the overall efficiency of heating system 1 can be made to improve.
And then, if the heat dissipation capacity of load 4 reduces, then the coolant-temperature gage Tin (i+1) that enters of the heat pump type heat source machine HS (i+1) in downstream exceedes Toff (i+1)=45 DEG C (the time t2 point in Fig. 4) as the stopping temperature of heat pump type heat source machine HS (i+1), the refrigerant cycles running of heat pump type heat source machine HS (i+1) also no longer needs, and the refrigerant cycles of heat pump type heat source machine HS (i+1) also stops.
In this case, which heat pump type heat source machine HS (i), HS (i+1) do not carry out adding heat run, so the inlet water temperature Tin (i+1) of inlet water temperature Tin (i) of heat pump type heat source machine HS (i), outlet water temperature T out (i) and heat pump type heat source machine HS (i+1), outlet water temperature T out (i+1) be all roughly the same temperature (in the diagram, time t2 ~ t3 interval).
Then, if the heat dissipation capacity of load 4 increases, then the coolant-temperature gage Tin (i+1) that enters of the heat pump type heat source machine HS (i+1) in downstream drops to lower than stopping temperature Toff (i+1)=45 DEG C of heat pump type heat source machine HS (i+1) (the time t3 point in Fig. 4), and what start heat pump type heat source machine HS (i+1) adds heat run.
And then, if the heat dissipation capacity of load 4 increases, then coolant-temperature gage Tin (i) that enters of the heat pump type heat source machine HS (i) of upstream side drops to lower than stopping temperature Toff (i+1)=41 DEG C of heat pump type heat source machine HS (i) (the time t4 point in Fig. 4), and what start heat pump type heat source machine HS (i) adds heat run.
Therefore, same with the interval of time t0 ~ t1 in Fig. 4, multiple heat pump type heat source machine HS (i), HS (i+1) dispersion carry out adding heat run, and the outlet water temperature T out (i+1) of the heat pump type heat source machine HS (i+1) in downstream can be maintained more than roughly 45 DEG C.
In addition, in the heating system 1 of present embodiment, even if in multiple stage heat pump type heat source machine HS (1) ~ (n) certain enter into defrosting running, remaining heat pump type heat source machine HS (1) ~ (n) also can continue to add heat run, so can compensate the decline adding heat along with defrosting running.
Such as, when heat pump type heat source machine HS (i) enters into defrosting running, the water-refrigerant heat exchanger 26 of this heat pump type heat source machine HS (i) is by the water cooling in the water pipe arrangement 5 in circulation.
But in such a case, outlet water temperature T out (i) of heat pump type heat source machine HS (i) declines.Thus, inlet water temperature Tin (i) of the water-refrigerant heat exchanger 26 of the heat pump type heat source machine HS (i+1) in the downstream be connected with the outlet pipe arrangement of the water-refrigerant heat exchanger 26 of heat pump type heat source machine HS (i) declines.
The result that inlet water temperature Tin (i) declines is, in the heat pump type heat source machine HS (i+1) in downstream, target temperature Ts (i+1) becomes large with the poor Δ T (i+1) of outlet water temperature T out (i+1), make output frequency f (i+1) become large and the heating efficiency of source heat pump heat machine HS (i+1) is increased, the automatically defrosting of execution compensate for upstream side operates the such running of the water temperature drop that brings.
As described above, according to the present embodiment, when the heat dissipation capacity of the load 4 supplying warm water is larger, perform the dispersed-heated running that multiple stage heat pump type heat source machine HS (i) carries out adding heat run simultaneously, when the heat dissipation capacity of load 4 is less, a part for multiple stage heat pump type heat source machine HS (i) stops, only undertaken adding heat run by remaining heat pump type heat source machine HS (i), can obtain carrying out the heating system 1 of the higher running of the overall efficiency of the situation meeting load.
In addition, when building such heating system 1, the centralized management device of the full detail that Comprehensive Control is detected by each heat pump type heat source machine HS (1) ~ HS (n) is not set, only use the operator 22 of separate each heat pump type heat source machine HS (1) ~ HS (n) and based on setting position (relative to water flowing Cis sequence is set) to carry out the setting of each temperature just passable.
Therefore, if prepare the heat pump type heat source machine HS as standard, for different loads 4, the heat pump type heat source machine HS of standard is connected in series the number of units that the heating efficiency that requires with load 4 is mated, carry out the temperature setting of each heat pump type heat source machine HS (1) ~ HS (n), then can carry out good computer heating control.
In addition, in the heating system 1 of present embodiment, in multiple stage heat pump type heat source machine HS (1) ~ (n), target temperature Ts (i) of the outlet warm water of heat pump type heat source machine HS (i) is set lower than the stopping temperature Toff (i+1) of the heat pump type heat source machine HS (i+1) being arranged on its downstream.
But, larger than the heating efficiency of each heat pump type heat source machine HS in the heat dissipation capacity of load 4, when the number of units being connected in series in heat pump type heat source machine HS (the 1) ~ HS (n) on water pipe arrangement 5 is increased to multiple, also can by its with the direction of water of flowing in water pipe arrangement 5 for benchmark, multiple group (group) is divided at upstream and downstream, the target temperature Ts of the warm water of the heat pump type heat source machine in the group of upstream is made to be identical value, the stopping temperature Toff of the heat pump type heat source machine in the group of downstream is set higher than the target temperature Ts of the warm water of the heat pump type heat source machine of upstream group.
The present invention is not limited to above-mentioned embodiment.And then, can by will disclosed multiple Component units be appropriately combined and form various invention in embodiments of the present invention.Such as, also certain several Component units can be deleted from the whole Component units shown in embodiments of the present invention.In addition, also can be appropriately combined by the Component units crossing over different embodiments.
Claims (3)
1. a heat pump type heat source machine, possesses heat pump refrigerant cycles, and this heat pump refrigerant cycles has the water-refrigerant heat exchanger for water and refrigerant being carried out heat exchange, and the feature of this heat pump type heat source machine is to possess:
Inlet temperature sensor, detects the water temperature of the entrance side of above-mentioned water-refrigerant heat exchanger;
Outlet temperature sensor, detects the water temperature of the outlet side of above-mentioned water-refrigerant heat exchanger;
Running controlling organization, compares the inlet water temperature detected by above-mentioned inlet temperature sensor with stopping temperature, controls the running/stopping of above-mentioned heat pump refrigerant cycles;
Add heat controlling organization, the outlet water temperature detected by above-mentioned outlet temperature sensor is compared with target temperature, control to add heat by above-mentioned heat pump refrigerant cycles; And
Operating mechanism, separately can set above-mentioned stopping temperature and above-mentioned target temperature.
2. a heating system, is characterized in that,
Be connected in series by each water-refrigerant heat exchanger of water pipe arrangement by above-mentioned heat pump type heat source machine according to claim 1 to load, pump and multiple stage, the above-mentioned target temperature of the above-mentioned heat pump type heat source machine of upstream side set lower than the above-mentioned stopping temperature of the above-mentioned heat pump type heat source machine in downstream.
3. heating system as claimed in claim 2, is characterized in that,
The total maximum heating ability of above-mentioned multiple stage heat pump type heat source machine is more than the maximum heat dissipation capacity of load.
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| JP020304/2011 | 2011-02-02 | ||
| JP2011020304A JP2012159255A (en) | 2011-02-02 | 2011-02-02 | Heat pump type heat source device, and heating system |
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| JP5701084B2 (en) * | 2011-02-02 | 2015-04-15 | 東芝キヤリア株式会社 | Heating system |
| JP5818601B2 (en) * | 2011-09-19 | 2015-11-18 | 東芝キヤリア株式会社 | Heat pump heat source machine |
| JP5781060B2 (en) * | 2012-12-25 | 2015-09-16 | 三菱電機株式会社 | Air conditioner |
| JP6152645B2 (en) * | 2013-01-08 | 2017-06-28 | 東京電力ホールディングス株式会社 | Heat supply system |
| TR201816402T4 (en) * | 2013-08-23 | 2018-11-21 | Toshiba Carrier Corp | Hot water heater. |
| CN104819610B (en) * | 2015-04-30 | 2017-11-07 | 广东美的制冷设备有限公司 | air conditioner defrosting control device and method |
| EP3367010B1 (en) * | 2015-10-19 | 2022-06-01 | Mitsubishi Electric Corporation | Heat source system |
| CN107166508B (en) * | 2017-06-21 | 2020-07-21 | 海信（山东）空调有限公司 | Heat pump type floor heating machine control method and heat pump type floor heating machine |
| CN112713129B (en) * | 2021-01-14 | 2022-04-29 | 度亘激光技术（苏州）有限公司 | Semiconductor device heat dissipation device and heat dissipation method |
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