CN102809260A - Refrigeration system and control method thereof - Google Patents
Refrigeration system and control method thereof Download PDFInfo
- Publication number
- CN102809260A CN102809260A CN2012102690924A CN201210269092A CN102809260A CN 102809260 A CN102809260 A CN 102809260A CN 2012102690924 A CN2012102690924 A CN 2012102690924A CN 201210269092 A CN201210269092 A CN 201210269092A CN 102809260 A CN102809260 A CN 102809260A
- Authority
- CN
- China
- Prior art keywords
- temperature
- compressor
- magnetic valve
- valve
- air
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000005057 refrigeration Methods 0.000 title claims abstract description 66
- 238000000034 method Methods 0.000 title claims abstract description 31
- 230000000737 periodic effect Effects 0.000 claims abstract description 10
- 238000010438 heat treatment Methods 0.000 claims description 24
- 230000005494 condensation Effects 0.000 claims description 7
- 238000009833 condensation Methods 0.000 claims description 7
- 125000004122 cyclic group Chemical group 0.000 claims description 7
- 238000010257 thawing Methods 0.000 claims description 7
- 239000007788 liquid Substances 0.000 claims description 6
- 238000005516 engineering process Methods 0.000 description 5
- 239000003507 refrigerant Substances 0.000 description 4
- 230000000875 corresponding effect Effects 0.000 description 3
- 238000007710 freezing Methods 0.000 description 3
- 230000008014 freezing Effects 0.000 description 3
- 230000001276 controlling effect Effects 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 235000011464 Pachycereus pringlei Nutrition 0.000 description 1
- 240000006939 Pachycereus weberi Species 0.000 description 1
- 235000011466 Pachycereus weberi Nutrition 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000002596 correlated effect Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000007791 dehumidification Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 238000010304 firing Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000012797 qualification Methods 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000001331 thermoregulatory effect Effects 0.000 description 1
Images
Abstract
The invention provides a refrigeration system and a control method of the refrigeration system. The control method comprises the following steps: setting the temperature set value TS of a refrigeration chamber into at least two values comprising temperature fluctuation minimum value T-min and temperature fluctuation maximum value T-max at different time periods in one work cycle, adjusting the temperature of the refrigeration chamber from the temperature fluctuation minimum value T-min to the temperature fluctuation maximum value T-max, to realize the periodic control over the temperature of the refrigeration chamber, thereby meeting the special requirements on the temperature of the refrigeration system needed by the places such as refrigeration of ham processing techniques.
Description
Technical field
The present invention relates to refrigerating field, belong to a kind of method and cold storage refrigeration system of indoor temperature cyclic fluctuation control, be specifically related to the control method of the refrigeration system in places such as refrigerating, i.e. the control method of cold storage refrigeration system and cold storage refrigeration system.
Background technology
At some industrial site, need carry out special control and adjusting to temperature.For instance; In some delicatessen processing enterprises (for example ham manufacturing enterprise); Often need control the temperature of delicatessen refrigerating chamber, and need the temperature of refrigerating chamber to fluctuate within the specific limits, desirable pattern is that this fluctuation demonstrates periodically and without manual adjustment.
Yet; In cold storage refrigeration system, control commonly used is the control of temperature constant at present, and temperature is controlled in certain scope; Can't performance period and the peak value and the valley (peak-to-valley value) of temperature controlled within the specific limits, can't reach the temperature of setting at corresponding periodic timing node.
In addition, for places such as for example ham processing technology refrigeration can't property performance period variable air rate control, also be unfavorable for the ham processing technology.
Summary of the invention
An object of the present invention is to realize the temperature cycle property control in places such as refrigerating, make place such as refrigeration reach the temperature of setting at corresponding periodic timing node.
Another object of the present invention is that the periodic variable air rate of realizing places such as refrigeration is controlled.
For this reason; The invention provides a kind of control method of cold storage refrigeration system; Control method comprises: the different time in a work period; The desired temperature TS of refrigerating chamber is set at two numerical value that comprise temperature fluctuation minimum of a value Tmin and temperature fluctuation maximum of T max at least, and the adjustment refrigerating chamber temperature from temperature fluctuation minimum of a value Tmin to temperature fluctuation maximum of T max cyclic fluctuation.
Further, the whole working time is set at the integral multiple of work period, when the working time begins, is set at TS=Tmin; When the working time arrives half period, make and the temperature T H=Tmin of said refrigerating chamber simultaneously, TS=Tmin is changed into TS=Tmax; Heating then when the working time reaches one-period, makes the temperature T H=Tmax of refrigerating chamber; Simultaneously, TS=Tmax is changed into TS=Tmin, carry out the periodic cycle of temperature adjustment then.
Further, control method specifically comprises: after the working time begins, use three compressors by platform start refrigeration; Indoor temperature TH≤TS+2 Δ t1 when refrigerating chamber stops No. 1 compressor in three compressors, when indoor temperature TH≤TS+ Δ t1; Stop No. 2 compressors in three compressors again, when indoor temperature TH≤TS+ Δ T1, stop No. 3 compressors in three compressors again; Wherein, Δ t1 is a separate unit compressor temperature adjusted value, and Δ T1 is the inertia adjusted value of Tmin.
Further; Be connected with the heater that adds the thermoelectrical magnetic valve group and utilize No. 1 compressor operating on No. 1 compressor; No. 1 compressor is that heater provides and heats required refrigerant; Adding the thermoelectrical magnetic valve group comprises: be connected in parallel on low capacity between No. 1 compressor and the heater and add thermoelectrical magnetic valve and add thermoelectrical magnetic valve with big capacity, internal diameter of the pipeline size or flow that low capacity adds thermoelectrical magnetic valve add thermoelectrical magnetic valve less than big capacity.When the working time reaches half period, TS=Tmax, No. 1 compressor start heats, and No. 2 compressors and No. 3 compressors are closed; Low capacity adds thermoelectrical magnetic valve and adds thermoelectrical magnetic valve with big capacity and all open, and when TH >=TS-2 Δ t2, low capacity adds thermoelectrical magnetic valve and opens; Big capacity heating closed electromagnetic valve, as TH >=TS-Δ T2, low capacity adds thermoelectrical magnetic valve and adds the thermoelectrical magnetic valve Close All with big capacity; Wherein, Δ t2 is the temperature adjusted value of heater, and Δ T2 is the inertia adjusted value of Tmax.
Further, control method also comprises: respectively there is a dispatch air port on the wall top in the relative both sides of above-mentioned refrigerating chamber, is respectively equipped with the air-valve of a control air quantity on the two dispatch air ports; The air quantity in two dispatch air ports changes just in time opposite; The air-valve in two dispatch air ports, aperture action (aperture is the technical term of valve) is opposite, and air-valve is opened when big; Another air-valve turns down, and the total blast volume addition in two dispatch air ports remains unchanged.
Further, two air-valves are proportional-type air-valve (also claiming proportioning valve), and two proportional-type air-valves are controlled with same control signal, and an air-valve is just established and changeed, and another air-valve is established counter-rotating, and control signal is pressed the triangular wave variation during operation.
Further, control signal is the voltage of 0 ~ 10V, and control signal is changed to Vmin～Vmax～Vmin, and wherein, Vmin is 0.5 ~ 2V, and Vmax is 8 ~ 9.5V.
Further, finish the back in the working time and get into the time of having a rest, the time of having a rest comprises the time of defrosting, and usually, the initial stage of time of having a rest defrosts.After the time of having a rest finishes, get into the next working time, the said working time is an integer work period, preferred 2 ~ 6 work periods, for example 5 work periods, the said time of having a rest is an integer work period, can specifically set as required.In the refrigeration system that is used for producing ham, be preferably 1 ~ 2 work period.
Further, Tmin is 2 ℃, and Tmax is 5 ℃, and Δ t1 is 0.5 ℃.
The present invention also proposes a kind of cold storage refrigeration system, comprising: mechanical system and the electric control system that is electrically connected with mechanical system;
Mechanical system comprises: evaporimeter, expansion valve, filter, condenser, compressor, vapour liquid separator; The output of condenser is connected with reservoir, filter, expansion valve, evaporimeter successively; The output of evaporimeter is connected to the input of compressor through vapour liquid separator; Be connected with the condensation magnetic valve between the output of compressor and the input of condenser; Be connected with the defrosting magnetic valve between the output of compressor and the input of evaporimeter, evaporimeter is provided with the fin temperature sensor, and the connection between each parts realizes through pipeline;
Mechanical system also comprises: heater, first check valve, second check valve; Heater is installed in the back of evaporimeter along airflow direction; First check valve is arranged between the output and reservoir of condenser; Second check valve is arranged between the output and reservoir of heater; Mechanical system also comprises and adds the thermoelectrical magnetic valve group, adds between the input of output and heater that the thermoelectrical magnetic valve group is connected compressor, adds low capacity magnetic valve and big capacity magnetic valve that the thermoelectrical magnetic valve group comprises parallel connection;
Electric control system comprises: programmable logic controller (PLC) that is connected and control module.
Further, compressor comprises: No. 1 compressor, No. 2 compressors and No. 3 compressors of parallel connection, heater is connected with No. 1 compressor.
The present invention is through design temperature fluctuation minimum of a value Tmin and temperature fluctuation maximum of T max a work period intercycle property; Make the temperature property performance period control of refrigerating chamber, thereby can satisfy of the specific (special) requirements of the refrigeration system of place requirements such as ham processing technology refrigeration temperature.
In addition, the present invention realizes that also through the cyclic fluctuation of control air quantity the periodic variable air rate in places such as refrigeration is controlled.
Description of drawings
The accompanying drawing that constitutes the application's a part is used to provide further understanding of the present invention, and the parts of identical function are with same numerical reference among the figure.Illustrative examples of the present invention and explanation thereof are used to explain the present invention, do not constitute improper qualification of the present invention.
Fig. 1 shows the structural representation according to the mechanical system of the cold storage refrigeration system of the embodiment of the invention;
Fig. 2 shows the electric control theory figure according to the cold storage refrigeration system of the embodiment of the invention;
Fig. 3 shows the temperature control flow figure of first according to the embodiment of the invention, i.e. an interior process of refrigerastion of work period;
Fig. 4 shows the second portion temperature control flow figure according to the embodiment of the invention, i.e. an interior heating process of work period; Wherein, Fig. 3 and Fig. 4 are two parts that are connected each other in the work period
Fig. 5 shows the temperature wave cardon according to the embodiment of the invention.
Fig. 6 shows the structure according to the air outlet of the refrigerating chamber of the embodiment of the invention.
The specific embodiment
Except as otherwise noted, used term has implication given below otherwise in the context of the present invention.Other terms that this paper does not specifically provide implication have its common in the art implication.
Control method of the present invention comprises: the different time in a work period; The desired temperature TS of refrigerating chamber is set at two numerical value that comprise temperature fluctuation minimum of a value Tmin and temperature fluctuation maximum of T max at least, and the adjustment refrigerating chamber temperature from temperature fluctuation minimum of a value Tmin to temperature fluctuation maximum of T max cyclic fluctuation.For example, in the process of refrigerastion shown in Figure 3, step s30 is when the working time begins; Desired temperature TS=Tmin, and freeze, in the heating process as shown in Figure 4, step s162; When the working time arrives half period, promptly from refrigeration when adding heat deflection, make the temperature T H=Tmin of refrigerating chamber, simultaneously; TS=Tmin is changed into TS=Tmax, and heating then when the working time reaches one-period, makes the temperature T H=Tmax of refrigerating chamber; Simultaneously, TS=Tmax is changed into TS=Tmin, so carry out the periodic cycle of temperature adjustment.And after setting TS respectively and being peak value (Tmax) and valley (Tmin); Cold storage refrigeration system takes to control stage by stage temperature; Make the temperature of refrigerating chamber from peak value (Tmax) to valley (Tmin), again from valley (Tmin) to peak value (Tmax) circulation change; Or make the temperature of refrigerating chamber from valley (Tmin) to peak value (Tmax), again from peak value (Tmax) to valley (Tmin) circulation change.
Below embodiment be example with a refrigeration system that is used to control the ham refrigerating chamber, specifically illustrate design of the present invention.In other application scenarios, can adjust concrete numerical value.In the present embodiment, this refrigeration system comprises working time and time of having a rest, during the working time, and compressor continuous firing, the operation of freezing or heating; During the time of having a rest, the compressor Close All.For example, as shown in Figure 5, in the moment that the working time begins, promptly the A point is the moment (being that the working time is the time of having a rest before) since the time of having a rest to the entering working time; At this moment, the temperature of refrigerating chamber (rest temperature) is the highest, for example is 5.5 ℃ (inoperative temperature), is set at TS=Tmin this moment, then refrigeration; When the working time arrives half period, i.e. B point makes the temperature T H=Tmin of said refrigerating chamber, and Tmin is 2.5 ℃; Set TS=Tmax then, heating makes the temperature of refrigerating chamber when one-period, and promptly the C point reaches TH=Tmax (operating temperature); Tmax is 4 ℃, freezes then, and in second period, E point when the working time arrives half period; Make the temperature T H=Tmin of said refrigerating chamber, Tmin is 2.5 ℃, sets TS=Tmax then, heating; Make the temperature of refrigerating chamber when second period, promptly the F point reaches TH=Tmax (operating temperature), and Tmax is 4 ℃.Like this loop cycle in the work period, for example, when the twoth half period, i.e. G point, temperature T H=Tmin, Tmin are 2.5 ℃, when the 3rd cycle; Be the H point, TH=Tmax, Tmax are 4 ℃, when the 3rd half period, i.e. and I point, temperature T H=Tmin; Tmin is 2.5 ℃, when the 4th cycle, i.e. and J point, TH=Tmax, Tmax are 4 ℃, when the 4th half period; Be the K point, temperature T H=Tmin, Tmin are 2.5 ℃, when the 5th cycle, i.e. and L point, TH=Tmax; Tmax is 4 ℃, during to the 5th cycle, closes each compressor, stops refrigeration and heating, gets into the time of having a rest, and the length of time of having a rest can be confirmed as required.Time of having a rest finishes the back and gets into the working time automatically through control.So carry out the circulation of working time and time of having a rest, and, also carry out loop cycle in the working time.Certainly, the actual preferable numerical value that uses is: Tmin is 2 ℃, and Tmax is 5 ℃, and Δ t1 is 0.5 ℃, so that sufficient adjustment time and thermograde are arranged, also is fit to the condition that ham is produced.Preferable, can defrost in the time of having a rest, so that follow-up refrigeration.
In addition,, also can not comprised the time of having a rest, only comprised the embodiment of the temperature adjustment process of working time according to Fig. 5.Control method of the present invention is accomplished through cold storage refrigeration system.Cold storage refrigeration system comprises: mechanical system and electric control system.Mechanical system comprises refrigeration or heating function executive system that pipeline is connected to form for be correlated with refrigeration and heater block pass through mechanical connection.Electric control system is the control system that mechanical system is connected and controls through the signal of telecommunication.Mechanical system and electric control system are the relations of carrying out and controlling.
As shown in Figure 1; The mechanical system of cold storage refrigeration system provided by the invention; Comprise evaporimeter 1, expansion valve 13, filter 14, condenser 9, compressor 12, vapour liquid separator 17; The output of condenser 9 is connected with reservoir 16, filter 14, expansion valve 13, evaporimeter 1 successively, and the output of evaporimeter 1 is connected to the input of compressor 12 through vapour liquid separator 17, is connected with condensation magnetic valve 6 between the input of the output of compressor 12 and condenser 9; Be connected with defrosting magnetic valve 3 between the input of the output of compressor 12 and evaporimeter 1, evaporimeter 1 is provided with fin temperature sensor 11.Connection between each parts realizes through pipeline 20.Move in normal range of operation through low-voltage relay 18, high-voltage relay 19 protection refrigeration systems, cold storage refrigeration system is being provided with pressure fan 15 perpendicular to evaporimeter 1 direction.
The mechanical system of cold storage refrigeration system also comprises heater 2, first check valve 7, second check valve 8.Said heater 2 is installed in the back of evaporimeter 1 along airflow direction, and first check valve 7 is arranged between the output and reservoir 16 of condenser 9, and second check valve 8 is arranged between the output and reservoir 16 of heater 2.Heater 2 plays the thermoregulatory effect behind the refrigerated dehumidification, also is through compressor the processing of refrigerant to be realized heating function.Cold storage refrigeration system also comprises and adds the thermoelectrical magnetic valve group, said adding between the input of output and heater 2 that the thermoelectrical magnetic valve group is connected compressor 12.Add low capacity valve 4 (low capacity magnetic valve EVR6) and big capacity valve 5 (big capacity magnetic valve EVR15) that the thermoelectrical magnetic valve group comprises parallel connection.These two magnetic valves can be opened separately respectively, also can all open, with the heating of control heater.
Refrigeration of the present invention, defrosting and heating are all freezed, are defrosted and heat and realize the refrigerant that uses in the cold storage refrigeration system through compressor.Freezing, defrost and heat about compressor can be with reference to prior art.
As shown in Figure 2, each refrigeration or the heater block of above-mentioned mechanical system are connected on the electric control system through the signal of telecommunication.Electric control system is mainly by compositions such as controller (PLC is generally programmable logic controller (PLC)) and control module (AI module) and peripheral detecting elements.Peripheral detecting element (for example comprising sensor) will comprise that signal such as each switching value signal, indoor temperature and each system's evaporating temperature and numerical value are transferred in PLC and the control module thereof; For example, through each switching value signal controlling each refrigeration or energising and outage of heater block.Each refrigeration of mechanical system or the action of heater block wait through gauge tap or control valve, each magnetic valve and air-valve actuator and realize control.Realize action like compressor and blower fan through gauge tap on compressor and the blower fan or control valve.The control principle of electric control system can adopt the control principle of existing cold storage refrigeration system, and realizes the action of setting through the programme-control of PLC and/or control module.For example; Cold storage refrigeration system adopts the operating voltage of 220V, and pressure fan, two condensation fans, three compressors, condensation magnetic valve, low capacity valve 4 (low capacity magnetic valve EVR6) and a big capacity valve 5 (big capacity magnetic valve EVR15), three defrosting magnetic valves and wind valve controller (being called for short air-valve control) are connected to PLC upward and/or on the control module.The unlatching and closure, the start and stop of compressor, the start and stop of blower fan and start and stop of air-valve actuator or the like of PLC and/or each magnetic valve of control module control.
The control of temperature cycle property fluctuation is as shown in Figure 3, and TS is a desired temperature, is an automatic changing value; Start (working time picks up counting) or open state time of having a rest are to getting into the working time; Initial value is Tmin-temperature fluctuation minimum of a value (can set, initial value is 2.0 ℃), and the time reaches 0.5Tz (half period) and becomes Tmax-temperature fluctuation maximum automatically and (can set; Initial value is 5.0 ℃); Time reaches Tz (one-period) and becomes Tmin automatically, by that analogy, and cyclically-varying.Wherein, comprise working time and time of having a rest running time, preferable, the whole working time is the integral multiple of work period, mainly considers because the duration of work temperature is low, and evaporator fin surface can frosting, requires the control that defrosts of initial stage of time of having a rest.So such advantage is to make temperature stop to minimum point when finishing the working time, when treating that the time of having a rest finishes, indoor temperature can not rise De Taigao.
Δ T1 is the inertia adjusted value of Tmin, and when promptly temperature was near Tmin, an inertia temperature surplus of setting in advance when making temperature also have Δ T1 apart from Tmin, stopped refrigeration, and through the inertia of refrigeration, temperature finally reaches Tmin.Because when temperature is reduced near desired value,,, make its control result as far as possible near desired value so Δ T1 is that the valley (minimum of a value) that is used for adjusting temperature fluctuation is Tmin because inertia need stop refrigeration in advance; As a same reason, Δ T2 is the inertia adjusted value of Tmax, is the peak value for the adjustment temperature fluctuation, need stop heating in advance.Be temperature during near Tmax, an inertia temperature surplus of setting in advance when making temperature also have Δ T2 apart from Tmax, stops heating, and through the inertia of heating, temperature finally reaches Tmax.
In exemplary embodiments of the present invention; Adopt the parallel connection of three compressors to form compressor bank, be connected with control assembly on every compressor and be connected on the PLC, (initial value is 0.50 ℃ to separate unit compressor temperature adjustment temperature value Δ t1; Can set); Variations in temperature when separate unit compressor temperature adjustment temperature value Δ t1 is used for adjusting the refrigerating chamber refrigeration is whenever opened one more, just can make temperature of refrigerating chamber decline Δ t1.So, can determine the quantity that compressor is opened according to Δ t1.Because three compressors refrigeration is arranged, therefore, need in the process of cooling, judge, according to parameters such as platform number, time, temperature, stop by platform.Adopt three compressors, can obtain more temperature control node, make temperature curve more level and smooth,, help accuracy control over temperature and classification refrigeration more near sine curve.
As shown in Figure 3, step s30: working time, pressure fan air-supply; Desired value is a valley, i.e. TS=Tmin, compressor bank start; For example, after pressure fan starts 10 seconds, whenever started compressor by platform at a distance from 10 seconds; When temperature reduces gradually, stop No. 1, No. 2 and No. 3 compressors by platform by time condition and temperature conditions.For example, when three operations, along with the operation of three units, the refrigeration indoor temperature descends gradually; When indoor temperature TH≤TS+2 Δ t1, stop compressor No. 1, indoor temperature continues to descend, when time accumulative total reaches 0.3TZ; During indoor temperature TH≤TS+t1, the s100 that takes steps stops compressor No. 2, and indoor temperature continues to descend; When satisfying condition s110, during indoor temperature TH≤TS+ Δ T1, the s120 that takes steps stops compressor No. 3.Through above-mentioned steps, the temperature of refrigerating chamber cyclic fluctuation is similar to sine wave, and the peak-to-valley value of cycle and temperature is adjustable within the specific limits.
As shown in Figure 4, among the step S162, the working time reaches 0.5TZ (half period), converts desired value to peak value T automatically through control module (AI module)
MaxIn the step 150, No. 1 compressor start is for the work of step 160 heater provides refrigerant; In the step 160, refrigerating chamber is heated up by the work that adds the thermoelectrical magnetic valve group, and wherein, heater only is connected with No. 1 compressor, and No. 1 compressor is enough to for heater heating efficiency is provided.In the step 170, condensation magnetic valve EVR20 opens, and low capacity adds thermoelectrical magnetic valve EVR6 and adds thermoelectrical magnetic valve EVR15 with big capacity and open temperature recovery.
Among the S180, return air temperature sensor detects indoor detected temperatures TH >=TS-2 Δ t2 (Δ t2 is the heter temperature adjusted value, can set); Among the step S190, low capacity adds thermoelectrical magnetic valve EVR6 and closes, and big capacity adds thermoelectrical magnetic valve EVR15 to be continued out; Indoor detected temperatures TH continues to rise, when satisfying condition S200, and TH >=TS-Δ t2,, take steps 210: low capacity adds thermoelectrical magnetic valve EVR6 to be opened, and big capacity adds thermoelectrical magnetic valve EVR15 and closes, and indoor detected temperatures TH continues to rise.As TH >=TS-Δ T2; When promptly satisfying condition S220, take steps 230, low capacity adds thermoelectrical magnetic valve and adds the thermoelectrical magnetic valve complete shut-down with big capacity; Condensation magnetic valve EVR20 closes after 5 second time; Accomplish temperature-rise period, synthesize indoor temperature from the peak value to the valley with temperature-fall period in earlier stage, again the one-period from the valley to the peak value.So the sine wave control of temperature has just been formed in circulation.
Among the present invention, it is when considering the heater heating with the switching sequence that big capacity adds thermoelectrical magnetic valve that low capacity adds thermoelectrical magnetic valve, the speed that temperature rises, and the refrigeration cool-down of postorder is to the requirement of temperature.In addition, Tmin is 2 ℃, and Tmax is 5 ℃, and it is in order to make temperature be controlled at low-temperature space that Δ t1 is 0.5 ℃.
Temperature nodes in several timing node above-mentioned (half period and whole cycle) and the rise and fall way; Need just can reach good waveform through field adjustable; The time that equals to heat with the time that guarantees the refrigeration in the one-period; The half period that the half period of promptly freezing equals to heat, the waveform of refrigeration and the waveform of heating want corresponding, for example symmetry.Usually need be according to scope, the refrigerating capacity of compressor of the required refrigerating capacity of refrigerating chamber, heating efficiency is comprehensively considered and repeatedly debug the back and confirm; After in case the temperature nodes in timing node and the rise and fall way is confirmed; The present invention can reach stable periodicity temperature control through the classification regulation and control, realizes that through three compressors three tier structure is cold, when realizing heating through two different magnetic valves of capacity; Two magnetic valves open simultaneously with one open; Three kinds of heated conditions that another is closed have accomplished that the number of the timing node in refrigeration and the heating process equates (for example, being three); Help the smooth of curve on the one hand, help the periodicity and the symmetry of curve on the other hand.
Periodic variable air rate control of the present invention: process is following: as shown in Figure 6, on the wall top of refrigerating chamber 100 relative both sides one dispatch air port is arranged respectively, air outlet 110 and air outlet 120 that being respectively staggers each other is provided with; Every dispatch air port requires air quantity from big to small, and periodic cycle changes from small to large again, and is as shown in Figure 6; Wind 121 directions that wind 111 and the air outlet 120 that air outlet 110 blows out blows out are relative; Form convection current, the air quantity of most of position of refrigerating chamber 100 equals the summation of the air quantity of two air outlets, and the air quantity of two exhaust outlets changes just in time opposite; Thereby realize that the refrigeration room air forms fluctuation, to satisfy the needs of ham processing technology.
Control the air-valve of two air outlets respectively with two air-valve actuators, the aperture action of air-valve is opposite, opens when big for one; Another turns down, and the addition total blast volume is constant basically in theory, and the method for realization is as shown in Figure 2; Two proportional-type air-valves (also claiming proportioning valve) are with same control signal (VM1.2), and an air-valve is just established and changeed during installation, and another air-valve is established counter-rotating; In the time of so just can realizing that a valve area becomes big, another air-valve just in time diminishes.Through the PLC programming; Give two air-valve actuators by control module (AI module) output control signal during operation, signal is pressed triangular wave and is changed, and is voltage (0 ~ 10V) like control signal; The triangle that signal is changed to from Vmin to Vmax Vmin changes; General Vmin is 0.5 ~ 2V, and Vmax is 8 ~ 9.5V, and maximum and minimum of a value are according to the requirement adjustment of actual air volume.For example, total blast volume is 10, at a time, on one side the air quantity of air outlet be 1.5; The air quantity of another side air outlet is 8.5, at another constantly, on one side the air quantity of air outlet be 1; The air quantity of another side air outlet is 9, and at the same position of refrigerating chamber, air quantity is by triangular wave and changes.
The explanation of the specific embodiment of front can disclose general features of the present invention fully; So that other people are easily concrete application by existing knowledge these specific embodiment are adjusted and/or adaptations; These all do not depart from scope of the present invention, so these adjustment and revise and to be regarded as the replacement that is equal to embodiment disclosed in the present invention.
Claims (10)
1. the control method of a cold storage refrigeration system, it is characterized in that: said control method comprises:
Different time in a work period; The desired temperature TS of refrigerating chamber is set at two numerical value that comprise temperature fluctuation minimum of a value Tmin and temperature fluctuation maximum of T max at least, and the adjustment refrigerating chamber temperature from temperature fluctuation minimum of a value Tmin to temperature fluctuation maximum of T max cyclic fluctuation.
2. control method according to claim 1 is characterized in that: the whole working time is set at the integral multiple of work period, when the working time begins; Be set at TS=Tmin, freeze then, when the working time arrives half period; Make and the temperature T H=Tmin of said refrigerating chamber simultaneously, TS=Tmin is changed into TS=Tmax; Heating then when the working time reaches one-period, makes the temperature T H=Tmax of refrigerating chamber; Simultaneously, TS=Tmax is changed into TS=Tmin, repeat the periodic cycle of temperature adjustment then.
3. control method according to claim 2 is characterized in that: said control method specifically comprises: after the working time begins, use three compressors by platform start refrigeration; Indoor temperature TH≤TS+2 Δ t1 when refrigerating chamber stops No. 1 compressor in three compressors, when indoor temperature TH≤TS+ Δ t1; Stop No. 2 compressors in three compressors again; When indoor temperature TH≤TS+ Δ T1, stop No. 3 compressors in three compressors again, wherein; Δ t1 is a separate unit compressor temperature adjusted value, and Δ T1 is the inertia adjusted value of Tmin.
4. control method according to claim 3 is characterized in that: be connected with the heater that adds the thermoelectrical magnetic valve group and utilize No. 1 compressor operating on No. 1 compressor, add the thermoelectrical magnetic valve group and comprise: be connected in parallel on low capacity between said No. 1 compressor and the said heater and add thermoelectrical magnetic valve and add thermoelectrical magnetic valve with big capacity; When the working time reaches half period, TS=Tmax, said No. 1 compressor start heats; No. 2 compressors and No. 3 compressors are closed, and said low capacity adds thermoelectrical magnetic valve and adds thermoelectrical magnetic valve with big capacity and all open, when TH >=TS-2 Δ t2; Said low capacity adds thermoelectrical magnetic valve to be opened, and said big capacity heating closed electromagnetic valve is as TH >=TS-Δ T2; Low capacity adds thermoelectrical magnetic valve and adds the thermoelectrical magnetic valve Close All with big capacity; Wherein, Δ t2 is the temperature adjusted value of said heater, and Δ T2 is the inertia adjusted value of Tmax.
5. control method according to claim 1 is characterized in that: said control method also comprises: respectively there is a dispatch air port on the wall top in the relative both sides of above-mentioned refrigerating chamber, is respectively equipped with the air-valve of a control air quantity on the two dispatch air ports; The air quantity in said two dispatch air ports changes just in time opposite; The air-valve in two dispatch air ports, aperture action is opposite, and air-valve is opened when big; Another air-valve turns down, and the air output sum in two dispatch air ports remains unchanged.
6. control method according to claim 5; It is characterized in that: said two air-valves are the proportional-type air-valve, and said two proportional-type air-valves are controlled with same control signal, and an air-valve is just established and changeed; Another air-valve is established counter-rotating, and control signal is pressed the triangular wave variation during operation.
7. control method according to claim 6 is characterized in that: said control signal is the voltage of 0 ~ 10V, and the triangle that said control signal triangular wave is changed to from Vmin to Vmax Vmin changes, and wherein, Vmin is 0.5 ~ 2V, and Vmax is 8 ~ 9.5V.
8. according to each described control method in the claim 1 to 7; It is characterized in that: finish the back in the working time and get into the time of having a rest; The said time of having a rest comprises the time of defrosting, and after the said time of having a rest finishes, gets into the next working time; The said working time is an integer work period, and the said time of having a rest is 1 work period.
9. a cold storage refrigeration system is characterized in that: comprising: mechanical system and the electric control system that is electrically connected with said mechanical system;
Said mechanical system comprises: through evaporimeter (1), expansion valve (13), filter (14), condenser (9), compressor (12) and the vapour liquid separator (17) of pipeline (20) connection; The output of said condenser (9) is connected with said reservoir (16), said filter (14), said expansion valve (13) and said evaporimeter (1) successively; (17 are connected to the input of said compressor (12) to the output of said evaporimeter (1) through said vapour liquid separator; Condensation magnetic valve (6) is connected between the input of output and said condenser (9) of said compressor (12); Defrosting magnetic valve (3) is connected between the input of output and said evaporimeter (1) of said compressor (12), and said evaporimeter (1) is provided with temperature sensor (11);
Said mechanical system also comprises: heater (2), first check valve (7), second check valve (8); Said heater (2) is installed in the back of said evaporimeter (1) along airflow direction; Said first check valve (7) is arranged between the output and reservoir (16) of said condenser (9); Said second check valve (8) is arranged between the output and reservoir (16) of said heater (2); Said mechanical system also comprises and adds the thermoelectrical magnetic valve group; The said thermoelectrical magnetic valve group that adds is connected compressor ((between 2 the input, the said thermoelectrical magnetic valve group that adds comprises the low capacity magnetic valve (4) of parallel connection and big capacity magnetic valve (5) for 12 output and heater;
Said electric control system comprises: programmable logic controller (PLC) that is connected and/or control module; Said programmable logic controller (PLC) and/or the different time of control module control compressor in a work period; The desired temperature TS of refrigerating chamber is set at two numerical value that comprise temperature fluctuation minimum of a value Tmin and temperature fluctuation maximum of T max at least, and the adjustment refrigerating chamber temperature from temperature fluctuation minimum of a value Tmin to temperature fluctuation maximum of T max cyclic fluctuation.
10. cold storage refrigeration system according to claim 9 is characterized in that: said compressor (12) comprising: No. 1 compressor, No. 2 compressors and No. 3 compressors of parallel connection, said heater is connected with said No. 1 compressor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210269092.4A CN102809260B (en) | 2012-07-31 | 2012-07-31 | Refrigeration system and control method thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210269092.4A CN102809260B (en) | 2012-07-31 | 2012-07-31 | Refrigeration system and control method thereof |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102809260A true CN102809260A (en) | 2012-12-05 |
| CN102809260B CN102809260B (en) | 2015-04-08 |
Family
ID=47233042
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210269092.4A Active CN102809260B (en) | 2012-07-31 | 2012-07-31 | Refrigeration system and control method thereof |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102809260B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113915891A (en) * | 2021-05-08 | 2022-01-11 | 海信（山东）冰箱有限公司 | Refrigerator and temperature control method thereof |
| CN115657759A (en) * | 2022-09-15 | 2023-01-31 | 华中光电技术研究所（中国船舶重工集团公司第七一七研究所） | Composite temperature control quartz flexible accelerometer structure |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06165635A (en) * | 1992-08-19 | 1994-06-14 | Gold Star Co Ltd | Method and apparatus for control of pickle aging |
| JP2705903B2 (en) * | 1993-08-09 | 1998-01-28 | 三星電子株式会社 | Refrigerator temperature control method |
| KR20000038802A (en) * | 1998-12-09 | 2000-07-05 | 구자홍 | System and method for variably changing driving velocity of inverter refrigerator |
| CN1103437C (en) * | 1998-02-16 | 2003-03-19 | 万都空调株式会社 | Method for controlling operation of kimchi refrigerator |
| CN101571339A (en) * | 2008-04-29 | 2009-11-04 | 博西华电器（江苏）有限公司 | Refrigerator defrosting control method and refrigerator applying same |
-
2012
- 2012-07-31 CN CN201210269092.4A patent/CN102809260B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06165635A (en) * | 1992-08-19 | 1994-06-14 | Gold Star Co Ltd | Method and apparatus for control of pickle aging |
| JP2705903B2 (en) * | 1993-08-09 | 1998-01-28 | 三星電子株式会社 | Refrigerator temperature control method |
| CN1103437C (en) * | 1998-02-16 | 2003-03-19 | 万都空调株式会社 | Method for controlling operation of kimchi refrigerator |
| KR20000038802A (en) * | 1998-12-09 | 2000-07-05 | 구자홍 | System and method for variably changing driving velocity of inverter refrigerator |
| CN101571339A (en) * | 2008-04-29 | 2009-11-04 | 博西华电器（江苏）有限公司 | Refrigerator defrosting control method and refrigerator applying same |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113915891A (en) * | 2021-05-08 | 2022-01-11 | 海信（山东）冰箱有限公司 | Refrigerator and temperature control method thereof |
| CN113915891B (en) * | 2021-05-08 | 2022-12-16 | 海信冰箱有限公司 | Refrigerator and temperature control method thereof |
| CN115657759A (en) * | 2022-09-15 | 2023-01-31 | 华中光电技术研究所（中国船舶重工集团公司第七一七研究所） | Composite temperature control quartz flexible accelerometer structure |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102809260B (en) | 2015-04-08 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102878663B (en) | Air conditioning system capable of improving heating effect and defrosting control method for air conditioning system | |
| CA2913664C (en) | Oil return method for multiple air conditioning unit in heating | |
| US20070137238A1 (en) | Multi-range cross defrosting heat pump system and humidity control system | |
| CN104990321B (en) | A kind of air-conditioner and its defrosting method | |
| CN103123147A (en) | Variable refrigerant flow air conditioning system and control method thereof | |
| CN203231415U (en) | Multi-split air conditioning system | |
| US4326387A (en) | Fluidic time delay system | |
| CN102914025A (en) | Method for controlling direct current frequency conversion air-conditioner while operating in refrigeration mode | |
| CN103206750A (en) | Multi-split air conditioning system and status switching control method therefor | |
| US20190203994A1 (en) | Refrigerating and air-conditioning system and system controller | |
| CN110186151B (en) | Operation control method, operation control device, air conditioner, and storage medium | |
| CN103968503A (en) | Air conditioner outdoor unit, and defrosting method and device for air conditioner | |
| CN111795481B (en) | Air conditioning system and control method therefor | |
| Jiang et al. | Research on the control laws of the electronic expansion valve for an air source heat pump water heater | |
| CN104220816A (en) | Air conditioner | |
| CN104344466A (en) | Air conditioner | |
| WO2009023756A2 (en) | Vapor compression system and frost control | |
| WO2014122735A1 (en) | Refrigeration device | |
| KR100712196B1 (en) | Heat pump system and a method for eliminating frost on the outdoor heat exchanger of the heat pump system | |
| CN111059633A (en) | Dehumidification method of air conditioning system | |
| CN111023414B (en) | Air conditioning system and dehumidification control method | |
| CN102809260A (en) | Refrigeration system and control method thereof | |
| CN111121337B (en) | Air conditioner double-condenser defrosting method and air conditioner | |
| JP2016138711A (en) | Air conditioner | |
| CN104246388B (en) | Air conditioner |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20170927 Address after: 811800 Longyangxia Town, Gonghe County, Hainan Tibetan Autonomous Prefecture, Qinghai Patentee after: QINGHAI MINZE LONGYANGXIA ECOLOGICAL WATER HARVEST CO.,LTD. Address before: 311835, Zhejiang City, Zhuji province shop Town Industrial Zone Patentee before: Zhejiang Dunan Electromechanical Technology Co.,Ltd. |
|
| TR01 | Transfer of patent right | ||
| CP03 | Change of name, title or address |
Address after: 811899 North Street, Longyangxia Town, Gonghe County, Hainan Tibetan Autonomous Prefecture, Qinghai Province Patentee after: Longyang Zhixian (Qinghai) Co.,Ltd. Country or region after: China Address before: 811800 North Street, Longyangxia Town, Gonghe County, Hainan Tibetan Autonomous Prefecture, Qinghai Province Patentee before: QINGHAI MINZE LONGYANGXIA ECOLOGICAL WATER HARVEST CO.,LTD. Country or region before: China |
|
| CP03 | Change of name, title or address |