CN205090526U - Control system and water chilling unit using same - Google Patents
Control system and water chilling unit using same Download PDFInfo
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- CN205090526U CN205090526U CN201520805278.6U CN201520805278U CN205090526U CN 205090526 U CN205090526 U CN 205090526U CN 201520805278 U CN201520805278 U CN 201520805278U CN 205090526 U CN205090526 U CN 205090526U
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- water
- heat exchanger
- temperature
- compressor
- temperature difference
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 226
- 239000000498 cooling water Substances 0.000 claims abstract description 24
- 230000008859 change Effects 0.000 claims description 27
- 238000001704 evaporation Methods 0.000 claims description 9
- 239000003507 refrigerant Substances 0.000 description 6
- 239000007788 liquid Substances 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000002452 interceptive effect Effects 0.000 description 3
- 238000004891 communication Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 230000009466 transformation Effects 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
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- Air Conditioning Control Device (AREA)
Abstract
The utility model discloses a control system and use its cooling water set, through the temperature of intaking that detects the cooling water set heat exchanger, go out the water temperature and be used for calculating the heat transfer heat exchanger parameter of the average difference in temperature to based on these parameter coordination control water pump frequency and compressor load, can keep the cooling water set to be in whole energy-conserving running state under any operating mode.
Description
Technical field
The utility model relates to air-conditioning technical, is specifically related to a kind of control system and applies its handpiece Water Chilling Units.
Background technology
Handpiece Water Chilling Units can be used as the main frame of central air conditioner system, and current handpiece Water Chilling Units carries out frequency conversion to realize Energy Saving Control by the water pump controlling driving cooling water usually, but, the compressor operating of handpiece Water Chilling Units may be caused after pump variable frequency in non-energy-conservation interval.
Utility model content
In view of this, the utility model provides a kind of control system, control method and application its handpiece Water Chilling Units, and to make under any operating mode, water pump and compressor unison control, and whole unit is in the running status of whole energy.
First aspect, provides a kind of control system of handpiece Water Chilling Units, comprising:
Inflow temperature sensor, is arranged at the evaporimeter water inlet of described handpiece Water Chilling Units, for detecting the inflow temperature of described handpiece Water Chilling Units heat exchanger;
Leaving water temperature sensors, is arranged at the evaporimeter delivery port of described handpiece Water Chilling Units, for detecting the leaving water temperature of described heat exchanger;
Heat exchanger parameter obtaining device, for detecting the heat exchanger parameter for Numerical heat transfer mean temperature difference;
Controller, for the frequency of water pump and the load of compressor of handpiece Water Chilling Units according to described inflow temperature, leaving water temperature and described heat exchanger state modulator.
Preferably, described heat exchanger parameter obtaining device is pressure sensor, for obtaining the tracheal pressure of heat exchanger.
Preferably, described controller is used for obtaining corresponding evaporating temperature according to described tracheal pressure, and calculate the Inlet and outlet water temperature difference according to described inflow temperature, leaving water temperature, calculate heat transfer mean temperature difference according to described inflow temperature, leaving water temperature and described evaporating temperature, control the frequency of described water pump and the load of described compressor remains in each self-corresponding preset range to make described leaving water temperature, the described Inlet and outlet water temperature difference and described heat transfer mean temperature difference.
Preferably, described controller also for obtaining water pump frequency change rate and compressor load rate of change, and controls the frequency of described water pump and the load of described compressor remains in each self-corresponding preset range to make described water pump frequency change rate and compressor load rate of change.
Second aspect, provides a kind of handpiece Water Chilling Units, comprising:
Heat exchanger, for utilizing cold-producing medium and cooling water heat exchange;
Compressor, for compressing cold-producing medium;
Water pump, is connected in cooling water recirculation system, circulates between terminating machine and heat exchanger for driving cooling water; And
Control system as above.
The utility model is by detecting the inflow temperature of handpiece Water Chilling Units heat exchanger, leaving water temperature and the heat exchanger parameter for Numerical heat transfer mean temperature difference, and control water pump frequency and compressor load based on these parameter coordinations, can under any operating mode, keep handpiece Water Chilling Units to be in the running status of whole energy.
Accompanying drawing explanation
By referring to the description of accompanying drawing to the utility model embodiment, above-mentioned and other objects, features and advantages of the present utility model will be more clear, in the accompanying drawings:
Fig. 1 is the structural representation of the handpiece Water Chilling Units of the utility model embodiment;
Fig. 2 is the schematic diagram of the control system of the handpiece Water Chilling Units of the utility model embodiment;
Fig. 3 is the schematic diagram of the control system of the handpiece Water Chilling Units of another embodiment of the utility model.
Detailed description of the invention
Based on embodiment, the utility model is described below, but the utility model is not restricted to these embodiments.In hereafter details of the present utility model being described, detailedly describe some specific detail sections.Do not have the description of these detail sections can understand the utility model completely for a person skilled in the art yet.In order to avoid obscuring essence of the present utility model, known method, process, flow process, element and circuit do not describe in detail.
In addition, it should be understood by one skilled in the art that the accompanying drawing provided at this is all for illustrative purposes, and accompanying drawing is not necessarily drawn in proportion.
Unless the context clearly requires otherwise, similar words such as " comprising ", " comprising " otherwise in whole description and claims should be interpreted as the implication that comprises instead of exclusive or exhaustive implication; That is, be the implication of " including but not limited to ".
In description of the present utility model, it is to be appreciated that term " first ", " second " etc. are only for describing object, and instruction or hint relative importance can not be interpreted as.In addition, in description of the present utility model, except as otherwise noted, the implication of " multiple " is two or more.
Fig. 1 is the structural representation of the handpiece Water Chilling Units of the utility model embodiment.The present embodiment is described for air-cooled liquid chillers, but it will be understood by those skilled in the art that the utility model embodiment also can be applied to the handpiece Water Chilling Units of other type.As shown in Figure 1, described handpiece Water Chilling Units comprises heat exchanger 1, condenser 2, fan 3, compressor 4, expansion valve 7, water pump 5 and control system 6.
Wherein, heat exchanger 1 is connected with refrigerant circulation line and cooling water circulation pipeline, and in heat exchanger 1, cold-producing medium and cooling water carry out heat exchange.In the present embodiment, heat exchanger 1 is evaporimeter.In evaporimeter 1, cold-producing medium is evaporated thus is freezed to cooling water.Preferably, evaporimeter 1 can be shell and tube evaporator.
Compressor 4 carries out for the gaseous refrigerant sucking the low-temp low-pressure after heat exchange the gaseous refrigerant that compressed shape becomes HTHP.Be recycled to condenser 2 by the cold-producing medium after compressor compresses along refrigerant circulation line and carry out condensation.Fan 3, for dispelling the heat to condenser 2, is condensed into liquid state to make cold-producing medium and enters evaporimeter 1 along refrigerant circulation line via expansion valve 7 in condenser 2.
Again carry out heat exchange.Heat exchanger 1, compressor 4, condenser 2 and expansion valve 7 constitute the closed circuit of cold-producing medium.
Should be understood that and to be described as heat exchanger for evaporimeter above, the handpiece Water Chilling Units of the utility model embodiment also can adopt the heat exchanger of non-phase-change heat-exchange, under the prerequisite adopting this kind of heat exchanger, can not comprise condenser in refrigeration cycle.
Water pump 5 is connected in cooling water circulation loop, circulates between terminating machine a and heat exchanger 1 for driving cooling water.
Should be understood that in cooling water circulation pipeline, all right setting example is if the multiple instrument such as stop valve, automatic exhaust steam valve, drainpipe, expansion tank, check-valves, filter or device are with regulation and control cooling water circulation pipeline.
Control system 6 runs on power save mode for the load of the frequency and compressor 4 that control water pump 5 to make whole handpiece Water Chilling Units.
Fig. 2 is the schematic diagram of the control system of the handpiece Water Chilling Units of the utility model embodiment.As shown in Figure 2, control system 6 comprises inflow temperature sensor 61, leaving water temperature sensors 62, heat exchanger parameter obtaining device 63 and controller 64.
Inflow temperature sensor 61 is arranged at the evaporimeter water inlet of handpiece Water Chilling Units, for detecting the inflow temperature T of heat exchanger 1
i.
Leaving water temperature sensors 62 is arranged at the evaporimeter delivery port of handpiece Water Chilling Units, for detecting the leaving water temperature T of heat exchanger 1
o.
Heat exchanger parameter obtaining device 63 is for detecting the heat exchanger parameter for Numerical heat transfer mean temperature difference.Preferably, be under the prerequisite of evaporimeter at heat exchanger, because evaporimeter adopts phase transformation mode to conduct heat, cold-producing medium remains saturation temperature (also referred to as evaporating temperature) in evaporimeter.Now, heat exchanger parameter is the tracheal pressure of evaporimeter, can acquire in evaporimeter the temperature of the cold-producing medium being in vapor liquid equilibrium state according to this tracheal pressure, thus can calculate the heat transfer mean temperature difference of heat exchanger further.In this case, heat exchanger parameter obtaining device 63 is pressure sensor, and it is for detecting the tracheal pressure of evaporimeter.
Be that under the prerequisite of non-phase-change type heat exchanger, cold-producing medium carries out heat exchange with cooling water in liquid form in heat exchanger at heat exchanger.Now, heat exchanger parameter for the feed liquor temperature of cold-producing medium and can go out liquid temp, can calculate the heat transfer mean temperature difference of heat exchanger based on the inflow temperature of above-mentioned two temperature and cooling water and leaving water temperature further.In this case, heat exchanger parameter obtaining device 63 comprises and is arranged at feed liquor temperature sensor in the refrigerant circulation line of heat exchanger and fluid temperature sensor.
Controller 64 is connected with inflow temperature sensor 61, leaving water temperature sensors 62 and heat exchanger parameter obtaining device 63, receives the inflow temperature T that three detects
i, leaving water temperature T
oand heat exchanger parameter.Controller 64 is also connected with water pump 5 and compressor 4 simultaneously, controls to send instruction respectively to water pump 5 and compressor 4.
Controller 64 is for according to inflow temperature T
i, leaving water temperature T
o(tracheal pressure P is preferably with heat exchanger parameter
i) control the frequency of water pump 5 of handpiece Water Chilling Units and the load of compressor 4.
Particularly, controller 64 is according to tracheal pressure P
iobtain corresponding evaporating temperature T
e, and according to inflow temperature T
i, leaving water temperature T
ocalculate Inlet and outlet water temperature difference T (also namely, Δ T=T
i-T
o), then according to inflow temperature T
i, leaving water temperature T
owith evaporating temperature T
enumerical heat transfer mean temperature difference Δ T
d, and then control the frequency of water pump 5 and the load of compressor 4 to make leaving water temperature T
o, Inlet and outlet water temperature difference T and heat transfer mean temperature difference Δ T
dremain in each self-corresponding preset range.Wherein, conduct heat mean temperature difference Δ T
dvarious existing mode can be adopted to calculate acquisition, such as, logarithmic mean temperature difference (LMTD) account form can be adopted calculate, also can adopt arithmetic mean account form to calculate.In the present embodiment, arithmetic mean account form is adopted to carry out Numerical heat transfer mean temperature difference Δ T
d, that is: Δ T
d=(T
o+ T
i)/2-T
e.
Leaving water temperature T
ocan represent whether the refrigeration of handpiece Water Chilling Units can reach user's requirement, Inlet and outlet water temperature difference T and heat transfer mean temperature difference Δ T
dthe efficient state of water pump and compressor collaborative work can be represented.On the whole, conduct heat mean temperature difference Δ T
dthe operating efficiency of larger explanation compressor is higher, but, heat transfer mean temperature difference Δ T
dthe excessive efficiency of water pump that may also can cause declines.Therefore, above-mentioned parameter being controlled in the preset range of correspondence, handpiece Water Chilling Units overall operation can be showed in power save mode meeting reality while user requires.
In the present embodiment, controller 64 controls compressor in the following manner and carries out load or unload, also, meets the following conditions time control compressor 4 at the same time and loads:
(1), leaving water temperature T
obe greater than target leaving water temperature T
swith the first control deviation a and, that is, T
o>T
s+ a.Wherein, target leaving water temperature T
sfor the value preset, it can be undertaken arranging and revising by the man-machine interactive system (such as control panel) of handpiece Water Chilling Units by user.The value of the first control deviation a also for pre-setting, it is preferably 0.5 degree Celsius.
(2), conduct heat mean temperature difference Δ T
dbe less than heat transfer temperature difference lower threshold b, or water pump 4 is in peak frequency.Wherein, heat transfer temperature difference lower threshold b is the value preset.
When meeting the following conditions at the same time, controller 64 controls compressor 4 and unloads:
(1), leaving water temperature T
obe less than target leaving water temperature T
swith the difference of the first control deviation a, that is, T
o<T
s-a.
(2), conduct heat mean temperature difference Δ T
dbe greater than heat transfer temperature difference upper limit threshold c, or water pump is in minimum running frequency, or water pump does not carry out frequency reducing.Wherein, heat transfer temperature difference upper limit threshold c is the value preset.
Control compressor 5 in other cases and keep current state.
First control deviation a defines leaving water temperature T
otarget leaving water temperature T can be departed from
sscope, i.e. (T
s-a, T
s+ a), once leaving water temperature T
odepart from target leaving water temperature T
sexceed the scope that the first control deviation a limits, then likely trigger and compressor load is intervened, to ensure leaving water temperature T
ostable.
Meanwhile, heat transfer temperature difference lower threshold b and heat transfer temperature difference upper limit threshold c defines the optimum interval of system heat exchange mean temperature difference, and i.e. (b, c), in this interval, compressor 4 and water pump 5 cooperation make entire system efficiency higher.Heat transfer mean temperature difference Δ T
ddepart from system heat transfer temperature difference when not being in optimum interval, entire system efficiency is lower.
At leaving water temperature T
oexceed target leaving water temperature T
smore, and when system heat transfer temperature difference is not in optimum interval, reduce leaving water temperature T by controlling compressor 4 loading
o, heat transfer mean temperature difference Δ T can be increased simultaneously
dto make entire system improved efficiency.
At leaving water temperature T
oexceed target leaving water temperature T
smore, and water pump has been in peak frequency state, when cannot reduce leaving water temperature further by quickening water circulation, needs to ensure leaving water temperature T by loading compressor 4
ostable.
At leaving water temperature T
olower than target leaving water temperature T
smore, and when system heat transfer temperature difference is not in optimum interval, improve leaving water temperature T by controlling compressor 4 unloading
o, heat transfer mean temperature difference Δ T can be reduced simultaneously
dto make entire system improved efficiency.
At leaving water temperature T
olower than target leaving water temperature T
smore, and water pump 5 is in minimum frequency or water pump 5 when not carrying out frequency reducing according to the control of controller, the state of water pump can not change, now, must by ensure leaving water temperature T to compressor 4 unloading
ostable.
In the utility model is implemented, control water pump raising frequency and refer to the rotating speed improving water pump driving motor, frequency reducing refers to the rotating speed reducing water pump driving motor, after water pump carries out frequency control, cooling water circulation speed/flow in cooling water circulation loop can change to make cooling water in heat exchanger 1, carry out the time variations of heat exchange, the Inlet and outlet water temperature difference can increase (water pump raising frequency) or reduce (water pump frequency reducing), and then affects the operation of whole system.In the present embodiment, controller 64 controls water pump 5 in the following manner and carries out raising frequency or frequency reducing.
Water pump 5 raising frequency is controlled when meeting the following conditions at the same time:
(1), Inlet and outlet water temperature difference T is greater than target Inlet and outlet water temperature difference T
swith the second control deviation A and, that is, Δ T> Δ T
s+ A.Wherein, target Inlet and outlet water temperature difference T
sfor the value preset, user can be undertaken arranging and revising by man-machine interactive system.And, the value of the second control deviation A also for presetting.
(2), conduct heat mean temperature difference Δ T
dbe greater than heat transfer temperature difference upper limit threshold c, or compressor is in full load condition.
When meeting the following conditions at the same time, control water pump 5 frequency reducing:
(1), Inlet and outlet water temperature difference T is less than target Inlet and outlet water temperature difference T
swith the difference of the second control deviation A, that is, Δ T< Δ T
s-A.
(2), conduct heat mean temperature difference Δ T
dbe less than heat transfer temperature difference lower threshold b, or compressor 4 is in minimum load state or compressor 4 does not unload.
Control water pump 5 in other cases and keep current state.
Second control deviation A defines Inlet and outlet water temperature difference T can depart from target Inlet and outlet water temperature difference T
sscope, i.e. (Δ T
s-A, Δ T
s+ A), once Inlet and outlet water temperature difference T departs from target leaving water temperature Δ T
sexceed the scope that the second control deviation A limits, then likely trigger and water pump frequency is intervened, to ensure that Inlet and outlet water temperature difference T's is stable.Inlet and outlet water temperature difference T keeps stable can ensure that water pump is in energy-saving run state.
Meanwhile, heat transfer temperature difference lower threshold b and heat transfer temperature difference upper limit threshold c defines the optimum interval of system heat exchange mean temperature difference, and i.e. (b, c), in this interval, compressor 4 and water pump 5 cooperation make entire system efficiency higher.Heat transfer mean temperature difference Δ T
ddepart from system heat transfer temperature difference when not being in optimum interval, entire system efficiency is lower.
Target Inlet and outlet water temperature difference T is exceeded at Inlet and outlet water temperature difference T
smore, and when system heat transfer temperature difference is not in optimum interval, by controlling water pump 5 raising frequency, improve the circulation rate of cooling water, reduce its time of staying in heat exchanger, to reduce Inlet and outlet water temperature difference T, this can reduce heat transfer mean temperature difference Δ T simultaneously
dto make entire system improved efficiency.
Target Inlet and outlet water temperature difference T is exceeded at Inlet and outlet water temperature difference T
smore, and compressor 4 is in full load condition, when cannot reduce the Inlet and outlet water temperature difference further by increase compressor load, must by ensureing that to water pump 5 raising frequency Inlet and outlet water temperature difference T stablizes.
At Inlet and outlet water temperature difference T lower than target Inlet and outlet water temperature difference T
smore, and when system heat transfer temperature difference is not in optimum interval, by controlling water pump 5 frequency reducing, lowering the circulation rate of cooling water, reducing its time of staying in heat exchanger, to improve Inlet and outlet water temperature difference T, heat transfer mean temperature difference Δ T can be increased simultaneously
dto make entire system improved efficiency.
At Inlet and outlet water temperature difference T lower than target Inlet and outlet water temperature difference T
smore, and compressor 4 is in minimum load state or compressor 4 when not unloading according to the control of controller, the state of compressor 4 can not change, now, must by ensureing that to water pump 5 frequency reducing Inlet and outlet water temperature difference T stablizes.
Thus, by detecting the inflow temperature of handpiece Water Chilling Units heat exchanger, leaving water temperature and the heat exchanger parameter for Numerical heat transfer mean temperature difference, and control water pump frequency and compressor load based on these parameter coordinations, can under any operating mode, keep handpiece Water Chilling Units to be in the running status of whole energy.
And, for original handpiece Water Chilling Units with pump variable frequency power saving function, owing to being provided with inflow temperature sensor, leaving water temperature sensors and heat exchanger parameter obtaining device, therefore, the handpiece Water Chilling Units being transform as the present embodiment need not increase new sensing element, keep handpiece Water Chilling Units to be in the running status of whole energy under just can be implemented in any operating mode, transformation and upgrade cost is lower.
Fig. 3 is the schematic diagram of the control system of the handpiece Water Chilling Units of another embodiment of the utility model.As shown in Figure 3, control system 6 comprises inflow temperature sensor 61, leaving water temperature sensors 62, heat exchanger parameter obtaining device 63 and controller 64.
Wherein, inflow temperature sensor 61, leaving water temperature sensors 62 are identical with a upper embodiment with the setting of heat exchanger parameter obtaining device 63, do not repeat them here.
Controller 64 is connected with inflow temperature sensor 61, leaving water temperature sensors 62 and heat exchanger parameter obtaining device 63, receives the inflow temperature T that three detects
i, leaving water temperature T
oand heat exchanger parameter.Controller 64 is also connected with water pump 5 and compressor 4 simultaneously, obtain (can with water pump 5, compressor 4 two-way communication) according to the communication with water pump 5 and compressor 4 or the instruction that sends according to self obtains water pump frequency change rate and compressor load rate of change, and send instruction respectively to water pump 5 and compressor 4 and control.
Wherein, water pump frequency change rate is the change of frequency of water pump in the unit time, and also, [H (t)-H (t-Δ t)]/Δ t, wherein, the water pump frequency that H (t) is t, Δ t is the scheduled time.Compressor load rate of change is the load change of unit time inner compressor, and also, [L (t)-L (t-Δ t)]/Δ t, wherein, the compressor load that L (t) is t, Δ t is the scheduled time.Both can embody the intensity of water pump and compressor adjustment respectively.
Controller 64 is for according to inflow temperature T
i, leaving water temperature T
o(package tracheal pressure P is preferably with heat exchanger parameter
i) and water pump frequency change rate and compressor load rate of change control the frequency of the water pump of described handpiece Water Chilling Units and the load of compressor.
Particularly, controller 64 is according to tracheal pressure P
iobtain corresponding evaporating temperature T
e, and according to inflow temperature T
i, leaving water temperature T
ocalculate Inlet and outlet water temperature difference T; Then according to inflow temperature T
i, leaving water temperature T
owith evaporating temperature T
enumerical heat transfer mean temperature difference Δ T
d, the control frequency of water pump 5 and the load of compressor 4 are to make leaving water temperature T
o, Inlet and outlet water temperature difference T and heat transfer mean temperature difference Δ T
dand water pump frequency change rate and keep compressor load rate of change in each self-corresponding preset range.
In the present embodiment, controller 64 controls compressor in the following manner and carries out load or unload, also, when meeting the following conditions at the same time, controls compressor 4 and loads:
(1), leaving water temperature T
obe greater than target leaving water temperature T
swith the first control deviation a and, that is, T
o>T
s+ a.Wherein, target leaving water temperature T
sfor the value preset, it can be undertaken arranging and revising by the man-machine interactive system of handpiece Water Chilling Units by user.The value of the first control deviation a also for pre-setting, it is preferably 0.5 degree Celsius.
(2), conduct heat mean temperature difference Δ T
dbe less than heat transfer temperature difference lower threshold b, or water pump is in peak frequency.Heat transfer temperature difference lower threshold b is the value preset.
(3), water pump frequency change rate is less than first threshold d.Wherein, first threshold d is the value preset.
Meanwhile, when meeting the following conditions at the same time, control compressor 4 and unload:
(1), leaving water temperature T
obe less than target leaving water temperature T
swith the difference of the first control deviation a, that is, T
o<T
s-a.
(2), conduct heat mean temperature difference Δ T
dbe greater than heat transfer temperature difference upper limit threshold c, or water pump is in minimum running frequency, or water pump does not carry out frequency reducing.Wherein, heat transfer temperature difference upper limit threshold c is preset value.
Control compressor 4 in other cases and keep current state.
By increasing the consideration for water pump frequency change rate when controlling compressor 4 and loading, avoid the adjustment due to compressor 4 to cause the frequent raising frequency of water pump, thus keeping system is stablized, the service life of extension device.
In the present embodiment, controller 64 controls water pump 5 in the following manner and carries out raising frequency or frequency reducing.
When meeting the following conditions at the same time, control water pump 5 raising frequency:
(1), Inlet and outlet water temperature difference T is greater than target Inlet and outlet water temperature difference T
swith the second control deviation A and, that is, Δ T> Δ T
s+ A.Wherein, target Inlet and outlet water temperature difference T
sfor the value preset, user can be undertaken arranging and revising by human-computer interaction interface.The value of the second control deviation A also for presetting.
(2), conduct heat mean temperature difference Δ T
dbe greater than heat transfer temperature difference upper limit threshold c, or compressor is in full load condition.
(3), compressor load rate of change is less than Second Threshold D.Wherein, Second Threshold D is the value preset.
When meeting the following conditions at the same time, control water pump 5 frequency reducing:
(1), Inlet and outlet water temperature difference T is less than target Inlet and outlet water temperature difference T
swith the difference of the second control deviation A, that is, Δ T< Δ T
s-A.
(2), conduct heat mean temperature difference Δ T
dbe less than heat transfer temperature difference lower threshold b, or compressor is in minimum load state or described compressor state remains unchanged.
Control water pump 5 in other cases and keep current state.
By increasing the consideration for compressor frequency rate of change when controlling water pump 5 raising frequency, avoid the adjustment due to water pump 5 to cause compressor 4 and frequently load, thus keeping system being stablized, the service life of extension device.
The foregoing is only preferred embodiment of the present utility model, be not limited to the utility model, to those skilled in the art, the utility model can have various change and change.All do within spirit of the present utility model and principle any amendment, equivalent replacement, improvement etc., all should be included within protection domain of the present utility model.
Claims (5)
1. a control system for handpiece Water Chilling Units, comprising:
Inflow temperature sensor, is arranged at the evaporimeter water inlet of described handpiece Water Chilling Units, for detecting the inflow temperature of described handpiece Water Chilling Units heat exchanger;
Leaving water temperature sensors, is arranged at the evaporimeter delivery port of described handpiece Water Chilling Units, for detecting the leaving water temperature of described heat exchanger;
Heat exchanger parameter obtaining device, for detecting the heat exchanger parameter for Numerical heat transfer mean temperature difference;
Controller, for the frequency of water pump and the load of compressor of handpiece Water Chilling Units according to described inflow temperature, leaving water temperature and described heat exchanger state modulator.
2. control system according to claim 1, is characterized in that, described heat exchanger parameter obtaining device is pressure sensor, for obtaining the tracheal pressure of heat exchanger.
3. control system according to claim 2, it is characterized in that, described controller is used for obtaining corresponding evaporating temperature according to described tracheal pressure, and calculate the Inlet and outlet water temperature difference according to described inflow temperature, leaving water temperature, calculate heat transfer mean temperature difference according to described inflow temperature, leaving water temperature and described evaporating temperature, control the frequency of described water pump and the load of described compressor remains in each self-corresponding preset range to make described leaving water temperature, the described Inlet and outlet water temperature difference and described heat transfer mean temperature difference.
4. control system according to claim 3, it is characterized in that, described controller also for obtaining water pump frequency change rate and compressor load rate of change, and controls the frequency of described water pump and the load of described compressor remains in each self-corresponding preset range to make described water pump frequency change rate and compressor load rate of change.
5. a handpiece Water Chilling Units, comprising:
Heat exchanger, for utilizing cold-producing medium and cooling water heat exchange;
Compressor, for compressing cold-producing medium;
Water pump, is connected in cooling water recirculation system, circulates between terminating machine and heat exchanger for driving cooling water; And
Control system according to any one of claim 1-4.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520805278.6U CN205090526U (en) | 2015-10-15 | 2015-10-15 | Control system and water chilling unit using same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520805278.6U CN205090526U (en) | 2015-10-15 | 2015-10-15 | Control system and water chilling unit using same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205090526U true CN205090526U (en) | 2016-03-16 |
Family
ID=55481207
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520805278.6U Withdrawn - After Issue CN205090526U (en) | 2015-10-15 | 2015-10-15 | Control system and water chilling unit using same |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN205090526U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105318460A (en) * | 2015-10-15 | 2016-02-10 | 珠海格力电器股份有限公司 | Control system, control method and water chilling unit applying control system and control method |
-
2015
- 2015-10-15 CN CN201520805278.6U patent/CN205090526U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105318460A (en) * | 2015-10-15 | 2016-02-10 | 珠海格力电器股份有限公司 | Control system, control method and water chilling unit applying control system and control method |
| CN105318460B (en) * | 2015-10-15 | 2018-01-23 | 珠海格力电器股份有限公司 | Control system, control method and water chilling unit applying control system and control method |
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Inventor after: Cheng Qi Inventor after: Li Jian Inventor after: Liu Mingquan Inventor after: Zou Yingnan Inventor after: Chen Peisheng Inventor after: Chen Xibao Inventor after: Wang Xiuchuan Inventor after: Shi Jiangang Inventor after: Wang Jiankai Inventor after: Zhong Hailing Inventor after: Chen Fabin Inventor before: Cheng Qi Inventor before: Chen Peisheng Inventor before: Chen Xibao Inventor before: Wang Jiankai Inventor before: Zhong Hailing |
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Effective date of registration: 20170125 Address after: 519070 Guangdong city of Zhuhai Province Qianshan Patentee after: GREE ELECTRIC APPLIANCES,Inc.OF ZHUHAI Patentee after: STATE NUCLEAR POWER ENGINEERING Co. Address before: 519070 Guangdong city of Zhuhai Province Qianshan Patentee before: GREE ELECTRIC APPLIANCES,Inc.OF ZHUHAI |
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