CN101815911A - The method and apparatus of control cooling system - Google Patents
The method and apparatus of control cooling system Download PDFInfo
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- CN101815911A CN101815911A CN200780100125A CN200780100125A CN101815911A CN 101815911 A CN101815911 A CN 101815911A CN 200780100125 A CN200780100125 A CN 200780100125A CN 200780100125 A CN200780100125 A CN 200780100125A CN 101815911 A CN101815911 A CN 101815911A
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- pressure
- condenser
- condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/027—Condenser control arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
- F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/17—Control issues by controlling the pressure of the condenser
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2116—Temperatures of a condenser
- F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser
Abstract
A kind of vapor compression refrigeration systems comprises control module, and this control module is used to receive working fluid pressure or temperature information, and with control condenser cooling fluid control valve, thereby the flow that minimizes through valve changes.
Description
The cross reference of related application
The application is 11/832,176 the non-temporary patent application of the U.S. based on the sequence number of submitting on August 1st, 2007, and requires its priority.At this, for all purposes in conjunction with this application full content as a reference.
About the research of federal government's subsidy or the statement of exploitation
Inapplicable.
With reference to appendix
Inapplicable.
Technical field
Disclosed herein and the teachings of the present invention relate generally to a kind of cooling system, relate more specifically to the system and method that cooling system is controlled.
Background technology
In conventional vapor compression refrigeration systems, mechanically the raise temperature and pressure of working fluid of compressor is to reach required steam condition.The heat exchanger that is usually designed to condenser is passed to environment or fluid with heat from the working fluid that compressed, thus the condensation working fluid.When condensed working fluid enters second heat exchanger, expansion valve or other expansion gears reduce the pressure of this condensed working fluid, described second heat exchanger is generally evaporimeter, and the heat of environment to be cooled is passed to working fluid in this second heat exchanger.Heated working fluid is back to compressor reducer, and repeats this circulation.
Condenser transmits the heat (that is the heat of environment to be cooled) of working fluid by heat being passed to another environment (as, open air) or cooling fluid (as, cooling water/condenser fluid).Typical cooling water condensation device comprises heat exchanger and fluid regulation valve.The condenser fluid obtains heat from the condensing agent of this condenser of flowing through, and heat is discharged into environment.Then, the condenser fluid fluid regulation valve of flowing through returns condenser.Optionally configuration can be that valve is arranged on after the condenser.
Vapor compression refrigeration systems can be designed to, and makes heat abstraction (or cooling) ability of this system mate with the thermic load that the space that is cooled produces.Yet the thermic load in the space that is cooled changes according to different factors, and described factor comprises season (outdoor temperature) for example, the equipment of working, the number that exists in the described space etc. in described space.In order to provide sufficient cooling in all cases, cooling system must have the suitable ability of maximum heating load with the space that is cooled.Yet it is bigger that the most working condition of this energy force rate that can cause selected cooling system to have requires.If cooling system moves being lower than under its rated capacity situation, cooling system (as, refrigerant compressor reducer) loop start and stopping repeatedly then.
Invention disclosed herein relates to improved cooling system, and the method and apparatus that is used to control cooling system.
Summary of the invention
In one aspect of the invention, provide a kind of method of controlling vapor compression refrigeration systems, this method comprises operation both vapor compression cool cycles, and this circulation comprises condensate and heat exchanger; Determine to leave the pressure and temperature of the fluid of condenser; Determine according to described pressure or described temperature at the timing changing valve position, with the flow through chilled fluid flow of described condenser of control.
Another aspect of the present invention comprises vapor compression refrigeration systems, and this system has: the both vapor compression cool cycles that comprises condenser and working fluid; The condenser cool cycles that comprises control valve for fluids, wherein control valve for fluids is used to change the chilled fluid flow through described condenser; The sensor (transducer) that links to each other with described condenser, described sensor are used for changing the pressure or the temperature of (transduce) described working fluid; With the controller that is used for determining when the position that changes described control valve for fluids in response to the pressure after the conversion or temperature.
Description of drawings
Fig. 1 shows a kind of embodiment in the embodiment of the cooling system that adopts feature of the present invention.
Fig. 2 shows the figure of illustrative embodiments of the band that electrical ball valve moved of steam compression system.
Fig. 3 shows the another kind of embodiment of the steam compression system that adopts feature of the present invention.
The specific embodiment
Above-mentioned accompanying drawing and following description to concrete structure and function do not limit applicant's the scope of invention or the scope of claims.On the contrary, providing these accompanying drawings and written description is in order to instruct those skilled in the art to make and to use this patent claimed invention.It will be understood to those of skill in the art that for the sake of clarity and understand that this paper does not describe or illustrate all features of commercial embodiment of the present invention with being convenient to.Those skilled in the art also will understand, and the exploitation that combines the practical commercial embodiment of each side of the present invention needs numerous decisions relevant with specific implementation, could realize the final goal of developer to commercial embodiment.This decision relevant with specific implementation can comprise, but may be not limited to, obedience and system, commerce, government's relative restrictions and other restriction, and these restrictions can become with the specific embodiment, place and time.Although developer's effort may be complicated and consuming time on absolute sense, but the routine that this effort is the those skilled in the art that made a profit from present disclosure will be carried out.It must be understood that the invention with instruction disclosed herein can be carried out multiple different modification and multiple different replacement form can be arranged.At last, the use such as, but not limited to the term of " one " such expression odd number is not intended to the quantity of restricted articles.Equally, to represent the use of the term of relation such as, but not limited to " on the top ", " bottom ", " left side ", " right side ", " top ", " bottom ", " downwards ", " making progress ", " side " etc., to be in order in specification, with reference to concrete accompanying drawing the time, more clearly being described, and not to be intended to limit the scope of the present invention or claims.
Block diagram and/or operational illustrations below with reference to method are described specific embodiment of the present invention.Should be understood that each square frame in block diagram and/or the operational view, and the combination of the square frame in block diagram and/or the operational view, can be with simulation and/or digital hardware, and/or computer program instructions is realized.This computer program instructions can be provided for the processor of all-purpose computer, special-purpose computer, ASIC and/or other programmable data treatment system.Execution command can produce structure and the function that is used for realizing block diagram and/or operational view required movement.In some alternative embodiments, function/action/structure of mentioning among the figure can be carried out with the order different with the order mentioned in block diagram and/or the operational view.For example, in fact, according to the function/action/structure that relates to, being shown as two operations that take place in order can carry out basically simultaneously, can also carry out with opposite order.
The computer program that uses or used by these embodiment with embodiment disclosed herein can be write with Object-Oriented Programming Language, traditional process type programming language or such as the low level code of assembler language and/or microcode.This program can all be carried out in single processor and/or be carried out between a plurality of processors as software kit independently or as the part of another software kit.
The applicant has invented a kind of system and method that the fluid stream of the fluid cooling heat exchanger in the vapor compression refrigeration systems of flowing through is controlled.By the fluid stream of the fluid cooling heat exchanger of flowing through is controlled, can optimally control the heat energy power of cooling system.Can come the fluid stream of cooling system is carried out optimum control by dual mode at least, and therefore the heat energy power of cooling system be carried out optimum control: (1) controls the heat that removes from condenser by the flow through chilled fluid flow of condenser of control; (2) control the heat that removes from condenser by the heat transfer area of regulating condenser.For example, the chilled fluid flow that increases the condenser of flowing through can increase the cooling capacity of system, because more heat can be passed to cooling fluid from refrigerant.Alternatively, increase area of heat transfer, for example the condensing surface area can increase the heat that is passed to cooling fluid from refrigerant, thus the ability of big cooling system once.Should be understood that the cooling capacity that can reduce system as required in a similar manner.
Fig. 1 shows wherein a kind of illustrative embodiments of the vapor compression refrigeration systems 100 that adopts feature of the present invention.Cooling system 100 comprises both vapor compression cooling circuit 102 substantially, this both vapor compression cooling circuit 102 comprises compressor 120, liquid cools condenser 130, expansion gear (expansiondevice) 150, evaporimeter (that is heat exchanger) 160 and sensor 190.In this specific embodiment, working fluid can be any two-phase refrigerant, such as chlorofluorocarbon (CFCs), hydrogen fluorohydrocarbon (HFCS) or hydrogen fluorochlorohydrocarbon (HCFCs) etc., and R-22 for example, but do not get rid of other optional refrigerant.Second cooling circuit 104 comprises liquid chiller (that is, heat exchanger) 170, fluid valve 140 and liquid cools condenser (that is heat exchanger) 130.Cooling system 100 also comprises control module 180, and this control module 180 is connected with sensor 190 with valve 140.
To the work of cooling system 100 be described below.Refrigerant is compressed in compressor 120, and this compressor 120 can be a reciprocating compressor, and the compressor of screw compressor or other types, and be preferably the electronics screw compressor is for example by compressor that Copeland provided.Refrigerant after the compression arrives liquid cools condenser 130 via discharge pipe 112, in this liquid cools condenser 130 heat of refrigerant is removed.Refrigerant one leaves liquid cools condenser 130, and the temperature of this refrigerant and/or pressure are just changed (transduce) by sensor 190, and this sensor 190 is the pressure or the temperature sensor of any kind well known by persons skilled in the art.Cryogen flow arrives expansion gear 150 through first fluid pipeline 114.Expansion gear 150 can comprise valve, opening or other expansion of liquids devices 150 well known by persons skilled in the art.When refrigerant process expansion mechanism 150, expansion mechanism 150 causes the pressure of refrigerant to descend.
One leaves expansion mechanism, and refrigerant second fluid pipeline 116 of just flowing through arrives evaporimeter 160.Low-pressure refrigerant absorbs heat from environment to be cooled.More specifically, the air in the environment to be cooled is by the coil pipe of evaporimeter, thus heat from transfer of air to refrigerant.By suction channel 118, the refrigerant that will have the heat that absorbs from environment is back to compressor 120, finishes steam compression cycle.Should be understood that the time span and the running frequency of the heat effects compressor 120 required operations of being transmitted in the heat that absorbed in the evaporimeter 160 and the condenser 130.So the heat that transmits in the control liquid cools condenser 130 directly influences the operation of compressor 120.
In second cooling circuit 104, liquid cools condenser 130 is passed to cooling fluid with heat from refrigerant, and this cooling fluid can be the fluid of two-phase refrigerant, ethylene glycol, water or other types.In specific embodiment shown in Figure 1, this cooling fluid is preferably cooling water.This cooling water flow is through the first cooling fluid pipeline 172, with cooling liquid fluid cooler 170, at these liquid fluid cooler 170 places by being expelled in the external environment condition such as the heat of any known devices such as one or more cooling fan with cooling fluid.Then, cooling water flow is to valve 140, and this valve 140 is electricity powered ball valve, solenoid-operated proportional control valve, stop valve, pneumatic, digital, hydraulic pressure perhaps well known by persons skilled in the art, simulation or other convertible fluids restraint devices.Preferably, valve 140 is electrical ball valves.Flow through the 3rd cooling fluid pipeline 176 and be back to fluid cooler condenser 130 of cooling fluid is passed to cooling fluid at these liquid cools condenser 130 place's heats from refrigerant.
Valve 140 can manually be controlled or be controlled by control module 180.Control module 180 receives one or more inputs from sensor 190, and exports one or more control signals to valve 140 or the actuator of controlling described valve 140.Control module 180 can use in a plurality of control programs any to control described valve 140 according to the characteristic that is converted (for example pressure or temperature) of refrigerant.In addition, control module 180 can be used for controlling compressor 120.For example, control module 180 can be indicated compressor 120, for example digital screw compressor, the time that circulation opens and closes.
In embodiment shown in Figure 1, in controller 180, implement control program, preferably to control cooling system 100.Can implement valve position (or flow) control program by control module 180, with the opening and closing of control valve 140.Control module 180 and control software can be designed to implement a kind of control strategy, and this control strategy is used for the shift in position of valve 140 minimums the refrigerant discharge pressure being remained on and can accepting in the limit.Hereinafter will describe preferred valve position control program.This program is used as compressor 120 with variable ability numeral screw compressor.
One of purpose of valve position control program is to avoid valve is arranged to open mode (wherein valve 140 continues to open) or closed condition (wherein valve 140 continues to cut out) as far as possible as far as possible.In order to realize this result, control program is implemented a kind of control strategy, and this control strategy is at discrete time point, the discrete time point when refrigerant pressure sample roughly for example, and the valve position of making (or not making) increment changes.
Another purpose is to avoid producing the startup high-pressure situations by valve 140 being opened to predetermined set-points before compressor 120 starts.Described in present embodiment, preferably set point is made as 50%, and delay in 30 seconds is arranged.
Another purpose of valve position control program is to have the system of can be applicable to (for example with CopelandDigital
The system that compressor is relevant) the effective control strategy in, in this system, refrigerant pressure is not stable basically.And normally increase or reduce, and wherein instantaneous the or almost instantaneous change speed of refrigerant pressure does not provide authentic communication to the overall change direction of refrigerant pressure.For the valve position control program can be moved in such environment, the valve position control program does not use or relies on the change speed of refrigerant discharge pressure or discharge pressure to be increases (or not increasing) or to reduce (or not reducing) and come control valve 140.
Generally speaking, the valve position control program is sampled to the refrigerant discharge pressure on predetermined basis, and described pressure reads by discharging sensor 190, and decision feasible (or not making) valve changing position behind each acquisition refrigerant discharge pressure reading.The optional embodiment of valve position control program can use other readings to determine whether feasible after obtaining each reading (or not making) valve changing position, as using the temperature reading of discharging sensor 190.These optional modes can comprise that use can change the dissimilar refrigerant that pressure is provided with.
Can understand the work of preferred valve Position Control program with reference to figure 2.With reference to figure 2, the valve position control program is mainly used in control refrigerant discharge pressure, makes this pressure remain in " can accept the work zone ".By limiting the different band of the refrigerant discharge pressure detected, and which falls into according to the discharge pressure that is detected and limit in the band and take (or not taking) measure, thereby finish process mentioned above.
First band that the valve position control program is limited is the acceptable operating band.This band has been represented system's plan refrigerant discharge pressure scope of operation therein.In the embodiment of valve position control program, the acceptable operating band is configured to and is fixed to the band between 175 to 210PSIG.In the another kind of form of valve position control program, but user's input pressure of system is regulated deviant, thereby by this deviant indication operation band.
Except can accepting the work zone, the valve position control program defines four bands that are reflected in the discharge pressure more than the upper limit that can accept the work zone.Figure 2 illustrates these bands, wherein with these tape labels be: (i) first high-band in order to discern; (ii) second high-band; (iii) the 3rd high-band; (iv) high-band.In the illustrative embodiments of valve position control program: (i) first high-band is set to the band between 210-220PSIG; (ii) second high-band is set to the band between the 220-230; (iii) the 3rd high-band is set to the band between the 230-350PSIG; And (iv) high-band is set to the band that pressure surpasses 350PSIG.In the another kind of form of valve position control program, but user's input pressure of system is regulated deviant, by this deviant indication except that all bands the (iv) high-band.
The valve position control program also limits three bands of the discharge pressure under the lower limit of expression acceptable operating band.Figure 2 illustrates these bands, with these tape labels be: (i) first low strap in order to discern; (ii) second low strap; (iii) low strap.In the illustrative embodiments of valve position control program: (i) first low strap is set to the band between 160-175PSIG; (ii) second low strap is set to the band between the 100-160PSIG; And (iii) low strap is set to be lower than the band of 100PSIG.In the another kind of form of valve position control program, but user's input pressure of system is regulated deviant, by this deviant indication except that all bands the (iii) low strap.
As its part of work, and the number of times that takes place for the shift in position of limiting valve 140, the hold the record incident of whether occurrence positions change in first high-band, second high-band and/or first low strap of valve position control program.
With high refrigerant pressure is example.The valve position program starts down in " primary condition " at first, and primary condition is not for existing the shift in position incident that takes place that is recorded in first high-band, second high-band and/or first low strap.If detecting detected pressure under the primary condition situation in the acceptable operating band, the valve position control program will be not to the position of valve 140 take action (that is, the position of pressure valve 140 can not change in response to detected pressure).
If when primary condition exists, detected detected pressures is higher or lower than the upper limit that can accept the work zone, and then the valve position control program can change the position of valve 140 or not change the position of valve 140.At first analyzing and testing pressure is higher than the situation that can accept the work zone.
If when primary condition exists, the pressure reading that is provided is higher than the lower limit of first high-band, and then the valve control program can be opened valve 140 5% increment, and writes down the changing position incident of first high-band.If when primary condition existed, the pressure reading that is provided was higher than the lower limit of second high-band, then the valve position control program is opened 5% increment with valve 140, and writes down the changing position incident of second high-band.If carried out shift in position, then be replenishing of any shift in position of making because pressure is higher than the upper limit of first high-band.Therefore, if detected pressure is positioned at the above level of lower limit of second high-band, then have opening of 5% increment, and opening of 5% increment can be arranged again because pressure is higher than the lower limit of second high-band because pressure is higher than the lower limit of first high-band.In these cases, can write down the change in location incident of first high-band and second high-band.
If when primary condition exists, the pressure reading that is provided is higher than the lower limit of the 3rd high-band, and then the valve position control program is opened 10% increment with valve 140, and writes down the shift in position incident of the 3rd high-band.If carry out this shift in position, then this shift in position is replenishing any shift in position of making because pressure is higher than the lower limit of first high-band or second high-band.At last, if when primary condition exists, the pressure reading that is provided is higher than the lower limit of high-band, and then valve 140 opens to fully and opens (100%) position.
In case occurrence positions change incident will make that primary condition no longer exists, the work of valve position control program changes system, makes that being used to make the refrigerant discharge pressure to get back to the number of times that can accept the shift in position in the work zone is restricted.This realizes in the following manner.
In case if occurrence positions change incident, detected pressure is higher than the lower limit of high-band, then valve position control program meeting: (i) valve 140 opened to fully open (100%) position (if valve 140 is not in this position), if perhaps (ii) valve 140 be positioned at 100% open position then do not taked action.
In case if occurrence positions change incident detects pressure between the lower limit and the upper limit of the 3rd high-band, then the valve position control program is opened 10% (as many as 100% open position) again with valve from its original position.No matter before what kind of any shift in position incident is, all can produce the situation of this 10% open position change.
If in case the shift in position incident has taken place, detect pressure between the lower limit and the upper limit of second high-band, then the valve position control program will be taked (or not taking) following measure.If the shift in position incident about second high-band that has not write down when detecting pressure, then system opens 5% again with valve 140, and writes down the second high-band shift in position incident.If the shift in position incident about second high-band that has write down is arranged, then the valve position control program will not taked any action, and allow valve 140 remain on the present position.
If in case the shift in position incident has taken place, detect pressure between the lower limit and the upper limit of first high-band, then the valve position control program can not move and allow valve 140 remain on present position.This is because under these circumstances, has write down the shift in position incident about first high-band.
As mentioned above, in case show that the valve position control program is operated after the occurrence positions change incident, make and avoid valve 140 is placed open mode (valve 140 often leaves in this state).Particularly, in the valve position control program, the detected pressures in the first high-band scope only have single, disposable, 5% open adjusting, the detected pressures in the second high-band scope only have single, disposable, 5% open adjusting.Make described single, disposable open adjusting after, if detected pressures then can not carried out any other adjusting to detected pressure in first high-band or the second high-band scope.
Because the detected pressures in first high-band and second high-band is made the fact of once opening adjustings (based on detected pressures), might rest on a bit (finishing after initial open position changes) in first high-band and the second high-band scope about the valve position control program of refrigerant discharge pressure.For fear of this result, and can accept in the work zone for refrigerant pressure is adjusted to, the valve position control program uses the control strategy based on timer, should be based on the control strategy and the above-mentioned control strategy parallel running based on detected pressures of timer.
According to described control strategy based on timer, when detect that pressure is higher than first high-band following in limited time, the valve position control program is provided with five minutes timer.In case set, then following situation replacement timer taking place: (i) generation of shift in position incident, or (ii) detect the lower limit that pressure is lower than first high-band.If this timer of five minutes is before resetting " to time (time out) ", the valve position control program opens 5% again with valve 140 so.Like this, by utilizing the shift in position of limited quantity, can make the refrigerant discharge pressure be tending towards to accept working range.
Except above-mentioned open position change incident, in some cases, the valve position control program can be carried out the change of " closure " valve position, removes the shift in position record about first high-band or second high-band simultaneously.Particularly, if low 5PSIG of the lower limit of detected pressure ratio second high-band and existence are about the record of the shift in position of second high-band, then the valve position control program will: (i) determine whether valve is regulated, and (ii) remove shift in position record about second high-band.Similarly, if low 5PSIG of the lower limit of detected pressure ratio first high-band and existence are about the record of the shift in position of first high-band, then the valve position control program will: (i) determine whether valve is regulated, and (ii) remove shift in position record about first high-band.In case any shift in position record in second high-band and first high-band all is eliminated, and does not promptly have any shift in position record, has so just rebulid initial condition.
Low refrigerant pressure example.Above-mentioned explanation has considered to be higher than at detected refrigerant pressure the work of the valve 140 under the situation of the upper limit of acceptable operating band.The following operation of system in limited time that is lower than the acceptable operating band at pressure is similar.
From primary condition, whenever being lower than going up of first low strap, detected pressure prescribes a time limit, and the valve position control program closes 4% once with valve 140.The record of this shift in position is saved, to guarantee that this detected pressures is made shift in position one time.If, then no longer carry out the closed position change being lower than the upper limit of first low strap and after carrying out initial 4% close, detecting pressure in the scope of first low strap in response to detecting pressure.
If detect the upper limit that pressure is lower than second low strap, then the valve position control program is closed valve 140 5% (closing to 25% open position at most) again according to detected pressure, and does not consider any shift in position incident before.
If detect the upper limit that pressure is lower than low strap, and valve 140 also is not in 25% open position, and then the valve position control program closes to 25% open position in response to described detection with valve 140.
To the mode similar,, five minutes timer is set then in case detect the upper limit that pressure is lower than first low strap to the explanation of high pressure.Described timer is reset because of following situation: (i) detect the upper limit that pressure is higher than first low strap, or the (ii) shift in position of valve 140.Like this, the shift in position based on timer trends towards in the scope of acceptable work zone refrigerant pressure.
Except above-mentioned closed position change incident, in some cases, the valve position control program can be carried out the change of " opening " valve position, removes the shift in position record about first low strap or second high-band simultaneously.Particularly, if the last limit for height 5PSIG of detected pressure ratio first low strap and existence are about the record of the shift in position of first low strap, then the valve position control program will: (i) determine whether valve is regulated, and (ii) remove shift in position record about first low strap.
Also can take other embodiments of valve position control program.For example, system can use by the discharge temperature of discharging sensor 190 measurements and implement control strategy.In addition, can design the electric time-keeping circuit valve 140 is controlled, to replace or auxiliary valve Position Control program.
Invention disclosed here and instruction has solved the problem and the relevant issues of the fluid pressure rapid fluctuations of the fluid cooling heat exchanger of flowing through.For example, this system and method has used the control strategy that moves of eliminating valve.Because the shift in position of motor and valve is reduced the ILS of valve.Because pressure and temperature is more stable, the performance of cooling system is improved.The life-span of the parts that other response pressures change also obtains increasing.Because valve will not be positioned at complete closed position during system's operation, so reduced the accommodating fluid pressure peak.Service valve need not be opened refrigerant system.
Fig. 3 shows the replacement embodiment of the steam compression system that adopts feature of the present invention.This replacement embodiment is controlled cooling capacity by the heat transfer area of control condenser.Fig. 3 shows the part of traditional vapor compression cooling system 300 (system as shown in Figure 1), wherein uses for example Liebert
Condenser arranged side by side (paradenser) 310 replace condenser 30.Condenser is one group of condenser side by side, is expressed as condenser 310a, 310b and 310c here.To make the as a whole condenser arranged side by side and the efficient of steam compression system in order maximizing,, to make manifold 340 be suitable for guiding cooling fluid one or more through among condenser 310a, 310b in the condenser 310 arranged side by side and the 310c the calibration of system vertical.
As mentioned above, control module 380 can be arranged to manifold 340 is controlled, make as required cooling fluid to be guided to condenser, thus optimization system ability and/or the heat load coupling that produces with the space of cooling off.When not needing condenser 330b and 330c to discharge the heat of refrigerant, the control module 380 bootable cooling fluids first fluid flow duct 302 of flowing through.When not needing condenser 330c to discharge the heat of refrigerant, control module 380 bootable additional cooling fluids second fluid flow conduit 304 of flowing through.At last, when all three condensers that do not need condenser arranged side by side are discharged the heat of refrigerant, the control module 380 bootable cooling fluids first cooling fluid pipeline 306 of flowing through.For example, if system need discharge more heats (according to the temperature that is converted or the pressure of working fluid) from refrigerant, control module 380 will guide cooling fluid through condenser 330c and condenser 330b.Discharge more heat if desired, control module 380 can guide cooling fluid through condenser 330a extraly.The more condenser if more cooling fluid is flowed through then will be discharged more heat from condensing agent.Present embodiment can be independent of or be implemented in conjunction with valve position control program described herein.
Under the situation of the spirit of the invention that does not depart from the applicant, can expect using other or embodiment further of above-mentioned one or more features of the present invention.For example, except using condenser arranged side by side turns to chilled fluid flow, also can use the condenser that is divided into several parts.The condenser that separates can be controlled so as to, and makes fluid be sent to one or more compartments, with the efficient of maximization condenser.In addition, controllable manifold can be used on the workflow side of system, working fluid is guided to one or more condensers.Further embodiment comprises by a plurality of valves in a plurality of cooling systems of single controller control.In addition, the whole bag of tricks and the embodiment of the system and method that the fluid stream of the fluid cooling heat exchanger of flowing through is controlled can be bonded to each other, to produce the version of disclosed method and embodiment.Discussion to discrete component can comprise a plurality of elements, and vice versa.
If there is not opposite special restriction, each step can be carried out according to multiple different order.Each step described herein can be combined with other step, inserts described step, and/or can be split into a plurality of steps.Similarly, the element of describing in function aspects may be implemented as independently parts, also can be combined in the parts with multiple function.
This paper has described the present invention in the context of preferred embodiment and other embodiment, but does not describe each embodiment of the present invention.Those skilled in the art can carry out various modifications and changes to described embodiment.Disclosed and undocumented embodiment is not intended to limit or retrain the scope of invention or the applicability of applicant's conception; but; meeting under the situation of Patent Law, the applicant is intended to protect fully this modification and the improvement within all equivalent scope that drop on following claim or the boundary.
Claims (12)
1. method of controlling vapor compression refrigeration systems comprises:
Operation comprises the both vapor compression cool cycles of condenser;
Determine to leave the pressure or the temperature of the fluid of described condenser; And
According to described pressure or described temperature change valve position, with the stream of control through the cooling fluid of described condenser.
2. the method for claim 1, wherein:
The described step that changes described valve position realizes by using the valve position of increment to change at discrete time point.
3. the method for claim 1, wherein said condenser is a condenser arranged side by side.
4. vapor compression refrigeration systems comprises:
The both vapor compression cool cycles that comprises condenser and working fluid;
The condenser cool cycles that comprises control valve for fluids, described control valve for fluids are used to change the chilled fluid flow through described condenser;
With the sensor that described condenser links to each other, described sensor is used to change the pressure or the temperature of described working fluid; With
Controller, described controller are used to respond the pressure that is converted or the position of the described control valve for fluids of temperature change.
5. vapor compression refrigeration systems as claimed in claim 4, wherein said controller are used to respond the pressure or the temperature that are converted and use the valve position of increment to change the position that changes described control valve for fluids at discrete time point.
6. method of controlling vapor compression refrigeration systems comprises:
Operation comprises the both vapor compression cool cycles of one or more condensers;
Determine to leave the pressure or the temperature of the fluid of described one or more condensers; And
Respond described pressure or the described heat transfer area of described temperature change.
7. method as claimed in claim 6, wherein said one or more condensers are one or more condensers arranged side by side.
8. vapor compression refrigeration systems comprises:
The both vapor compression cool cycles that comprises working fluid and one or more condensers;
The condenser cool cycles that comprises control valve for fluids, described control valve for fluids are used to change the chilled fluid flow through described one or more condensers;
With the sensor that described condenser links to each other, described sensor is used to change the pressure or the temperature of described working fluid;
With the system that described one or more condensers link to each other, described system is used to guide the chilled fluid flow through one or more condensers; With
Controller is used to change the described fluid stream through described one or more condensers, to change heat transfer area.
9. steam compression system as claimed in claim 8, wherein said system is a manifold.
10. method of controlling vapor compression refrigeration systems comprises:
Operation comprises the both vapor compression cool cycles of one or more condensers;
Determine to leave the pressure and temperature of the fluid of described one or more condensers;
According to described pressure or described temperature change valve position, with the chilled fluid flow of control through described one or more condensers; And
Change described heat transfer area according to described pressure and temperature.
11. method as claimed in claim 10, wherein said one or more condensers are one or more condensers arranged side by side.
12. a vapor compression refrigeration systems comprises:
The both vapor compression cool cycles that comprises working fluid and one or more condensers;
The condenser cool cycles that comprises control valve for fluids, described control valve for fluids are used to change the chilled fluid flow through described one or more condensers;
With the sensor that described one or more condensers link to each other, described sensor is used to change the pressure or the temperature of described working fluid; With
Controller, described controller are used for according to the pressure that is converted or the position of the described control valve for fluids of temperature change, and/or the described fluid that changes through described one or more condensers flows to change described heat transfer area.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US11/832,176 | 2007-08-01 | ||
| US11/832,176 US20090031735A1 (en) | 2007-08-01 | 2007-08-01 | System and method of controlling fluid flow through a fluid cooled heat exchanger |
| PCT/US2007/088016 WO2009017517A1 (en) | 2007-08-01 | 2007-12-18 | Method and apparatus for controlling a cooling system. |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101815911A true CN101815911A (en) | 2010-08-25 |
Family
ID=39558708
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200780100125A Pending CN101815911A (en) | 2007-08-01 | 2007-12-18 | The method and apparatus of control cooling system |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20090031735A1 (en) |
| EP (1) | EP2185874A1 (en) |
| CN (1) | CN101815911A (en) |
| WO (1) | WO2009017517A1 (en) |
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|---|---|---|---|---|
| KR100758902B1 (en) * | 2004-11-23 | 2007-09-14 | 엘지전자 주식회사 | multi type air conditioning system and controlling method of the system |
| CN109405367A (en) * | 2018-10-29 | 2019-03-01 | 珠海格力电器股份有限公司 | Water cooler and cooling device |
Family Cites Families (45)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2456386A (en) * | 1946-05-07 | 1948-12-14 | Howell C Cooper | Cascade refrigeration unit with controls therefor |
| US3069867A (en) * | 1961-05-29 | 1962-12-25 | Trane Co | Summer-winter air conditioning system |
| US3357199A (en) * | 1966-04-19 | 1967-12-12 | Westinghouse Electric Corp | Multiple condenser refrigeration systems |
| US3430453A (en) * | 1967-01-24 | 1969-03-04 | American Air Filter Co | Refrigerant condenser arrangement |
| US3481151A (en) * | 1967-12-28 | 1969-12-02 | Frick Co | Refrigerant system employing liquid chilling evaporators |
| US3481152A (en) * | 1968-01-18 | 1969-12-02 | Frick Co | Condenser head pressure control system |
| US3807190A (en) * | 1972-07-26 | 1974-04-30 | Vilter Manufacturing Corp | Refrigeration system with liquid cooled condenser |
| US4014751A (en) * | 1975-06-13 | 1977-03-29 | Mccord James W | Vapor generating and recovering apparatus |
| FR2378242A1 (en) * | 1977-01-19 | 1978-08-18 | Vironneau Pierre | Utilisation of refrigeration plant for heating building - uses heat exchanger between compressor and condenser to supply hot water to heating system |
| US4446774A (en) * | 1980-05-19 | 1984-05-08 | Gershon Meckler | Air conditioning apparatus |
| US4393666A (en) * | 1980-10-14 | 1983-07-19 | Revis Doyle A | Balanced heat exchange assembly |
| US4450690A (en) * | 1983-01-10 | 1984-05-29 | Clark Jr Robert W | Thermally powered, gravitationally assisted heat transfer systems |
| US4982574A (en) * | 1990-03-22 | 1991-01-08 | Morris Jr William F | Reverse cycle type refrigeration system with water cooled condenser and economizer feature |
| JP3312067B2 (en) * | 1993-09-21 | 2002-08-05 | ホシザキ電機株式会社 | Cooling system |
| SE9304264L (en) * | 1993-12-22 | 1995-06-23 | Ericsson Telefon Ab L M | Method and apparatus for cooling in closed rooms |
| US5682754A (en) * | 1996-07-02 | 1997-11-04 | Desert Aire Corp. | Method and apparatus for controlling swimming pool room air and water temperatures |
| US6034873A (en) * | 1998-06-02 | 2000-03-07 | Ericsson Inc | System and method for separating air flows in a cooling system |
| US6161612A (en) * | 1998-06-02 | 2000-12-19 | Ericsson Inc. | Cooling system and method for distributing cooled air |
| US5975114A (en) * | 1998-06-02 | 1999-11-02 | Ericsson Inc. | System, method and apparatus for purging fluid |
| US6202431B1 (en) * | 1999-01-15 | 2001-03-20 | York International Corporation | Adaptive hot gas bypass control for centrifugal chillers |
| AU2001249286A1 (en) * | 2000-03-21 | 2001-10-03 | Liebert Corporation | Method and apparatus for cooling electronic enclosures |
| US6761212B2 (en) * | 2000-05-25 | 2004-07-13 | Liebert Corporation | Spiral copper tube and aluminum fin thermosyphon heat exchanger |
| US6564858B1 (en) * | 2000-07-17 | 2003-05-20 | Liebert Corporation | Overhead cooling system with selectively positioned paths of airflow |
| US6705389B1 (en) * | 2000-07-17 | 2004-03-16 | Emerson Electric Co. | Reconfigurable system and method for cooling heat generating objects |
| US6557624B1 (en) * | 2000-08-09 | 2003-05-06 | Liebert Corporation | Configurable system and method for cooling a room |
| US6637227B2 (en) * | 2000-09-15 | 2003-10-28 | Mile High Equipment Co. | Quiet ice making apparatus |
| US6553778B2 (en) * | 2001-01-16 | 2003-04-29 | Emerson Electric Co. | Multi-stage refrigeration system |
| US6490882B2 (en) * | 2001-03-27 | 2002-12-10 | Liebert Corporation | Method and apparatus for maintaining compressor discharge vapor volume for starting with condensing unit ambient temperatures less than evaporator unit ambient temperatures |
| US6644384B2 (en) * | 2001-09-21 | 2003-11-11 | Liebert Corporation | Modular low profile cooling system |
| US20030196443A1 (en) * | 2002-04-22 | 2003-10-23 | Wei-Ming Chang | Vapor injecting ice and hot water generating device |
| EP1540257B1 (en) * | 2002-05-10 | 2007-01-17 | Chul Soo Lee | Condensing system for a cooling system |
| US6751965B1 (en) * | 2002-12-30 | 2004-06-22 | Steven D. Gottlieb | Refrigeration machine having sequentially charged condensing conduits |
| US6959558B2 (en) * | 2003-03-06 | 2005-11-01 | American Power Conversion Corp. | Systems and methods for head pressure control |
| EP1498683A3 (en) * | 2003-07-18 | 2007-03-07 | Liebert Corporation | Multi-pass parallel-tubes heat exchanger |
| US7028494B2 (en) * | 2003-08-22 | 2006-04-18 | Carrier Corporation | Defrosting methodology for heat pump water heating system |
| RU2249125C1 (en) * | 2003-09-24 | 2005-03-27 | Царев Виктор Владимирович | Self-contained power and heat supply system of rooms in dwelling houses and industrial areas |
| WO2005057097A2 (en) * | 2003-12-05 | 2005-06-23 | Liebert Corporation | Cooling system for high density heat load |
| WO2005075046A1 (en) * | 2004-01-31 | 2005-08-18 | Bailey Richard J | A water production system for making potable water |
| US6862894B1 (en) * | 2004-02-04 | 2005-03-08 | Donald R. Miles | Adaptive auxiliary condensing device and method |
| US20050207116A1 (en) * | 2004-03-22 | 2005-09-22 | Yatskov Alexander I | Systems and methods for inter-cooling computer cabinets |
| CN101044811A (en) * | 2004-11-14 | 2007-09-26 | 利伯特公司 | Integrated heat exchanger(s) in a rack for vertical board style computer systems |
| US7171817B2 (en) * | 2004-12-30 | 2007-02-06 | Birgen Daniel J | Heat exchanger liquid refrigerant defrost system |
| US7511229B2 (en) * | 2005-06-02 | 2009-03-31 | Liebert Corporation | Sensor module, system, and method for sensors in proximity to circuit breakers |
| US7788940B2 (en) * | 2005-08-04 | 2010-09-07 | Liebert Corporation | Electronic equipment cabinet with integrated, high capacity, cooling system, and backup ventilation |
| US8763417B2 (en) * | 2007-11-14 | 2014-07-01 | Hui Jen Szutu | Water cool refrigeration |
-
2007
- 2007-08-01 US US11/832,176 patent/US20090031735A1/en not_active Abandoned
- 2007-12-18 CN CN200780100125A patent/CN101815911A/en active Pending
- 2007-12-18 EP EP07869467A patent/EP2185874A1/en not_active Withdrawn
- 2007-12-18 WO PCT/US2007/088016 patent/WO2009017517A1/en active Application Filing
Also Published As
| Publication number | Publication date |
|---|---|
| EP2185874A1 (en) | 2010-05-19 |
| US20090031735A1 (en) | 2009-02-05 |
| WO2009017517A1 (en) | 2009-02-05 |
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Application publication date: 20100825 |