CN102809260B - Refrigeration system and control method thereof - Google Patents
Refrigeration system and control method thereof Download PDFInfo
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- CN102809260B CN102809260B CN201210269092.4A CN201210269092A CN102809260B CN 102809260 B CN102809260 B CN 102809260B CN 201210269092 A CN201210269092 A CN 201210269092A CN 102809260 B CN102809260 B CN 102809260B
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 66
- 238000000034 method Methods 0.000 title claims abstract description 30
- 230000000737 periodic effect Effects 0.000 claims abstract description 9
- 238000010438 heat treatment Methods 0.000 claims description 60
- 238000003860 storage Methods 0.000 claims description 23
- 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
- 239000007788 liquid Substances 0.000 claims description 6
- 238000010257 thawing Methods 0.000 claims description 6
- 238000005516 engineering process Methods 0.000 description 5
- 239000003507 refrigerant Substances 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 238000007710 freezing Methods 0.000 description 3
- 230000008014 freezing Effects 0.000 description 3
- 230000033228 biological regulation Effects 0.000 description 2
- 230000001351 cycling effect Effects 0.000 description 2
- 238000004519 manufacturing process Methods 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
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000001816 cooling Methods 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
- 238000003825 pressing Methods 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 230000001331 thermoregulatory effect Effects 0.000 description 1
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 method and cold storage refrigeration system that a kind of indoor temperature cyclic fluctuation controls, be specifically related to the control method of the refrigeration system in the places such as refrigeration, i.e. the control method of cold storage refrigeration system and cold storage refrigeration system.
Background technology
At some industrial site, need to carry out special control and adjustment to temperature.For example, in some delicatessen processing enterprises (such as ham manufacturing enterprise), often need the temperature controlling delicatessen refrigerating chamber, and need the temperature of refrigerating chamber to fluctuate within the specific limits, desirable pattern is that this fluctuation presents periodically and without manual adjustment.
But, at present in cold storage refrigeration system, conventional control is that temperature constant controls, and temperature controls in certain scope, cannot the peak value of performance period and temperature and valley (peak-to-valley value) controlled within the specific limits, the temperature of setting cannot be reached at corresponding periodically timing node.
In addition, can't the VAV control of property performance period for places such as such as ham processing technology refrigerations, be also unfavorable for ham processing technology.
Summary of the invention
An object of the present invention is the Temperature cycling control realizing the places such as refrigeration, make the places such as refrigeration reach the temperature of setting at corresponding periodically timing node.
Another object of the present invention is the periodic VAV control realizing the places such as refrigeration.
For this reason, the invention provides a kind of control method of cold storage refrigeration system, control method comprises: the different time within a work period, the desired temperature TS of refrigerating chamber is set as two numerical value at least comprising temperature fluctuation minimum of a value Tmin and temperature fluctuation maximum of T max, and adjusts temperature cyclic fluctuation from temperature fluctuation minimum of a value Tmin to temperature fluctuation maximum of T max of refrigerating chamber.
Further, is set as the integral multiple of work period the whole working time, when starting operationally, be set as TS=Tmin, when arriving half period operationally, make the temperature TH=Tmin of described refrigerating chamber, simultaneously, TS=Tmin is changed into TS=Tmax, then heats, when reaching one-period operationally, make the temperature TH=Tmax of refrigerating chamber, meanwhile, TS=Tmax is changed into TS=Tmin, then carry out the periodic cycle of temperature adjustment.
Further, control method specifically comprises: after the working time starts, and uses three compressors by platform start refrigeration, as the indoor temperature TH≤TS+2 Δ t1 of refrigerating chamber, stop No. 1 compressor in three compressors, as indoor temperature TH≤TS+ Δ t1, then stop No. 2 compressors in three compressors, as indoor temperature TH≤TS+ Δ T1, stop No. 3 compressors in three compressors again, wherein, Δ t1 is single compressor temperature adjusted value, and Δ T1 is the inertia adjusted value of Tmin.
Further, No. 1 compressor is connected with heating electromagnetic valve group and the heater utilizing No. 1 compressor operating, No. 1 compressor heats required refrigerant for heater provides, heating electromagnetic valve group comprises: be connected in parallel on No. 1 low capacity heating electromagnetic valve between compressor and heater and Large Copacity heating electromagnetic valve, the internal diameter of the pipeline size of low capacity heating electromagnetic valve or flow are less than Large Copacity heating electromagnetic valve.When reaching half period when operating, TS=Tmax, No. 1 compressor start heats, No. 2 compressors and No. 3 compressors are closed, low capacity heating electromagnetic valve and Large Copacity heating electromagnetic valve are all opened, and as TH >=TS-2 Δ t2, low capacity heating electromagnetic valve is opened, Large Copacity heating electromagnetic valve cuts out, as TH >=TS-Δ T2, low capacity heating electromagnetic valve and Large Copacity heating electromagnetic valve Close All, 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 have a dispatch air port on the wall top of the relative both sides of above-mentioned refrigerating chamber, two dispatch air ports are respectively equipped with the air-valve that controls air quantity, the air quantity change in two dispatch air ports is just in time contrary, the air-valve in two dispatch air ports, aperture action (aperture is the technical term of valve) is contrary, when an air-valve is opened large, another air-valve turns down, and the total blast volume in two dispatch air ports is added and remains unchanged.
Further, two air-valves are proportional-type air-valve (also claiming proportioning valve), and two same control signals of proportional-type air-valve control, and rotating forward established by an air-valve, and reversion established by another air-valve, and during operation, control signal presses triangular wave change.
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, Vmax is 8 ~ 9.5V.
Further, enter the time of having a rest after terminating operationally, the time of having a rest comprises the time of carrying out defrosting, and usually, the initial stage of time of having a rest defrosts.After the time of having a rest terminates, enter the next working time, the described working time is an integer work period, preferably 2 ~ 6 work periods, such as 5 work periods, and the described time of having a rest is an integer work period, can specifically set as required.For the production of in the refrigeration system of ham, be preferably 1 ~ 2 work period.
Further, Tmin is 2 DEG C, and Tmax is 5 DEG C, and Δ t1 is 0.5 DEG C.
The present invention also proposes a kind of cold storage refrigeration system, comprising: mechanical system and the electric control system be electrically connected with mechanical system;
Mechanical system comprises: evaporimeter, expansion valve, filter, condenser, compressor, vapour liquid separator, the output of condenser is connected successively with reservoir, filter, expansion valve, evaporimeter, the output of evaporimeter is connected to the input of compressor by vapour liquid separator, condensation magnetic valve is connected with between the output of compressor and the input of condenser, defrosting magnetic valve is connected with between the output of compressor and the input of evaporimeter, evaporimeter is provided with fin temperature sensor, the connection between each parts is realized by pipeline;
Mechanical system also comprises: heater, the first check valve, the second check valve, heater is arranged on after evaporimeter along airflow direction, first check valve is arranged between the output of condenser and reservoir, second check valve is arranged between the output of heater and reservoir, mechanical system also comprises heating electromagnetic valve group, heating electromagnetic valve group is connected between the output of compressor and the input of heater, and heating electromagnetic valve group comprises low capacity magnetic valve in parallel and Large Copacity magnetic valve;
Electric control system comprises: the programmable logic controller (PLC) be connected and control module.
Further, compressor comprises: No. 1 compressor in parallel, No. 2 compressors and No. 3 compressors, heater is connected with No. 1 compressor.
The present invention is by the design temperature fluctuation minimum of a value Tmin and temperature fluctuation maximum of T max a work period periodically, temperature property performance period of refrigerating chamber is controlled, thus the refrigeration system that can meet the site requirements such as ham processing technology refrigeration is to the particular/special requirement of temperature.
In addition, the present invention also by controlling the cyclic fluctuation of air quantity, realizes the periodic VAV control in the places such as refrigeration.
Accompanying drawing explanation
The accompanying drawing forming a application's part is used to provide a further understanding of the present invention, and in figure, the parts of identical function are with same numerical reference.Schematic description and description of the present invention, for explaining the present invention, does not form inappropriate limitation of the present invention.
Fig. 1 shows the structural representation of the mechanical system of the cold storage refrigeration system according to the embodiment of the present invention;
Fig. 2 shows the electric control theory figure of the cold storage refrigeration system according to the embodiment of the present invention;
Fig. 3 shows the Part I temperature control flow figure according to the embodiment of the present invention, the process of refrigerastion namely in the work period;
Fig. 4 shows the Part II temperature control flow figure according to the embodiment of the present invention, the heating process namely in the work period; Wherein, Fig. 3 and Fig. 4 is two parts be mutually connected in the work period
Fig. 5 shows the temperature wave cardon according to the embodiment of the present invention.
Fig. 6 shows the structure of the air outlet of the refrigerating chamber according to the embodiment of the present invention.
Detailed description of the invention
Unless otherwise stated, term used in context of the present invention has implication given below.Other terms specifically not providing implication herein have its common implication in the art.
Control method of the present invention comprises: the different time within a work period, the desired temperature TS of refrigerating chamber is set as two numerical value at least comprising temperature fluctuation minimum of a value Tmin and temperature fluctuation maximum of T max, and adjusts temperature cyclic fluctuation from temperature fluctuation minimum of a value Tmin to temperature fluctuation maximum of T max of refrigerating chamber.Such as, in process of refrigerastion shown in Fig. 3, step s30, when starting operationally, desired temperature TS=Tmin, and freeze, in heating process as shown in Figure 4, step s162, when arriving half period operationally, namely from refrigeration to when adding heat deflection, make the temperature TH=Tmin of refrigerating chamber, meanwhile, TS=Tmin is changed into TS=Tmax, then heat, when reaching one-period operationally, make the temperature TH=Tmax of refrigerating chamber, simultaneously, TS=Tmax is changed into TS=Tmin, so carries out the periodic cycle of temperature adjustment.And setting after TS is peak value (Tmax) and valley (Tmin) respectively, cold storage refrigeration system takes control by stages temperature, make the temperature of refrigerating chamber from peak value (Tmax) to valley (Tmin), then from valley (Tmin) to peak value (Tmax) circulation change; Or make the temperature of refrigerating chamber from valley (Tmin) to peak value (Tmax), then from peak value (Tmax) to valley (Tmin) circulation change.
The following examples for controlling the refrigeration system of ham refrigerating chamber, specifically illustrate design of the present invention for one.In other application scenarios, can concrete numerical value be adjusted.In the present embodiment, this refrigeration system comprises working time and time of having a rest, and period operationally, compressor continuous firing, carries out the operation of freezing or heating; During the time of having a rest, compressor Close All.Such as, as shown in Figure 5, the moment that working time starts, i.e. A point, from the time of having a rest to the moment (being the time of having a rest before namely the working time) entering the working time, now, the temperature (rest temperature) of refrigerating chamber is the highest, be such as 5.5 DEG C (inoperative temperature), now be set as TS=Tmin, then freeze, when arriving half period operationally, i.e. B point, make the temperature TH=Tmin of described refrigerating chamber, Tmin is 2.5 DEG C, then TS=Tmax is set, heating, make the temperature of refrigerating chamber when one-period, namely C point reaches TH=Tmax(operating temperature), Tmax is 4 DEG C, then freeze, in second period, when arriving half period operationally and E point, make the temperature TH=Tmin of described refrigerating chamber, Tmin is 2.5 DEG C, then TS=Tmax is set, heating, make the temperature of refrigerating chamber when second period, i.e. F point, reach TH=Tmax(operating temperature), Tmax is 4 DEG C.Loop cycle like this within the work period, such as, when the twoth half period, i.e. G point, temperature TH=Tmin, Tmin is 2.5 DEG C, when the 3rd cycle, i.e. H point, TH=Tmax, Tmax is 4 DEG C, when the 3rd half period, i.e. I point, temperature TH=Tmin, Tmin is 2.5 DEG C, when the 4th cycle, i.e. J point, TH=Tmax, Tmax is 4 DEG C, when the 4th half period, i.e. K point, temperature TH=Tmin, Tmin is 2.5 DEG C, when the 5th cycle, i.e. L point, TH=Tmax, Tmax is 4 DEG C, during to the 5th cycle, close each compressor, stop refrigeration and heating, enter the time of having a rest, the length of time of having a rest can be determined as required.By controlling automatically to enter the working time after time of having a rest terminates.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 preferably numerical value used is: Tmin is 2 DEG C, and Tmax is 5 DEG C, and Δ t1 is 0.5 DEG C, to have sufficient regulation time and thermograde, is also applicable to the condition that ham is produced.Preferably, can defrost in the time of having a rest, so that follow-up refrigeration.
In addition, according to Fig. 5, also can not be comprised the time of having a rest, only be comprised the embodiment of the temperature adjustment process of working time.Control method of the present invention has been come by cold storage refrigeration system.Cold storage refrigeration system comprises: mechanical system and electric control system.Mechanical system be associated refrigeration and heater block by mechanical connection, comprise refrigeration or heating function executive system that pipeline is connected to form.Electric control system is the control system being connected by the signal of telecommunication mechanical system and control.Mechanical system and electric control system are the relations performing and control.
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 and reservoir 16, filter 14, expansion valve 13, evaporimeter 1 connects successively, the output of evaporimeter 1 is connected to the input of compressor 12 by vapour liquid separator 17, condensation magnetic valve 6 is connected with between the output of compressor 12 and the input of condenser 9, the magnetic valve 3 that defrosts is connected with between the output of compressor 12 and the input of evaporimeter 1, evaporimeter 1 is provided with fin temperature sensor 11.Connection between each parts is realized by pipeline 20.Protect refrigeration system to run in normal range of operation by low-voltage relay 18, high-voltage relay 19, cold storage refrigeration system is arranging 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.Described heater 2 is arranged on after evaporimeter 1 along airflow direction, and the first check valve 7 is arranged between the output of condenser 9 and reservoir 16, and the second check valve 8 is arranged between the output of heater 2 and reservoir 16.Heater 2 plays the thermoregulatory effect after refrigerated dehumidification, is also to realize heating function by the process of compressor to refrigerant.Cold storage refrigeration system also comprises heating electromagnetic valve group, and described heating electromagnetic valve group is connected between the output of compressor 12 and the input of heater 2.Heating electromagnetic valve group comprises low capacity valve 4(low capacity magnetic valve EVR6 in parallel) and Large Copacity valve 5(Large Copacity magnetic valve EVR15).These two magnetic valves can individually be opened, and also can all open, with the heating of control heater.
Refrigeration of the present invention, defrosting and heating are all freezed by compressor to the refrigerant used in cold storage refrigeration system, defrost and are heated and realize.Carrying out freezing, defrost and heat about compressor can with reference to prior art.
As shown in Figure 2, each refrigeration of above-mentioned mechanical system or heater block are connected in electric control system by the signal of telecommunication.Electric control system is primarily of controller (PLC is generally programmable logic controller (PLC)) and the composition such as control module (AI module) and peripheral detecting element thereof.Peripheral detecting element (such as comprising sensor) will comprise the signals such as each on-off model, indoor temperature and each system evaporating temperature and data transfer in PLC and control module thereof, such as, energising and the power-off of each refrigeration or heater block is controlled by each on-off model.Each refrigeration of mechanical system or the action of heater block realize controlling by gauge tap or control valve, each magnetic valve and fan valve executor etc.As compressor and blower fan realize action by the gauge tap on compressor and blower fan or control valve.The control principle of electric control system can adopt the control principle of existing cold storage refrigeration system, and the programme-control passing through PLC and/or control module realizes the action of setting.Such as, cold storage refrigeration system adopts the operating voltage of 220V, a pressure fan, two condensation fans, three compressors, condensation magnetic valve, a low capacity valve 4(low capacity magnetic valve EVR6) and Large Copacity valve 5(Large Copacity magnetic valve EVR15), three defrosting magnetic valves and wind valve controller (being called for short air-valve control) be connected on PLC and/or in control module.PLC and/or control module control the start and stop etc. of the opening and closing of each magnetic valve, the start and stop of compressor, the start and stop of blower fan and fan valve executor.
As shown in Figure 3, TS is desired temperature in the control of Temperature cycling fluctuation, is an automatic changing value; Start (working time starts timing) or open state time of having a rest are to entering the working time, initial value is that Tmin-temperature fluctuation minimum of a value (can set, initial value is 2.0 DEG C), time reaches 0.5Tz (half period) and automatically becomes Tmax-temperature fluctuation maximum and (can set, initial value is 5.0 DEG C), time reaches Tz (one-period) and automatically becomes Tmin, by that analogy, and cyclically-varying.Wherein, comprise working time and time of having a rest running time, preferably, the whole working time is the integral multiple of work period, mainly considers because duration of work temperature is low, and evaporator fin surface can frosting, requires that the initial stage of time of having a rest carries out defrost control.So make temperature stop to minimum point at the end of such advantage is the working time, at the end for the treatment of the time of having a rest, indoor temperature can not be too high.
Δ T1 is the inertia adjusted value of Tmin, and when namely temperature is close to Tmin, the Inertia Temperature surplus set in advance, when making temperature distance Tmin also have Δ T1, stop refrigeration, through the inertia of refrigeration, temperature finally reaches Tmin.Because when temperature is reduced to close to desired value, due to inertia, need to stop refrigeration in advance, therefore Δ T1 is used to valley (minimum of a value) the i.e. Tmin adjusting temperature fluctuation, makes it control result as far as possible close to desired value; As a same reason, Δ T2 is the inertia adjusted value of Tmax, is the peak value for adjusting temperature fluctuation, needs to stop heating in advance.Namely, when temperature is close to Tmax, the Inertia Temperature surplus set in advance, when making temperature distance Tmax also have Δ T2, stop heating, through the inertia of heating, temperature finally reaches Tmax.
In exemplary embodiments of the present invention, three compressor parallel connections are adopted to form compressor bank, every compressor being connected with control assembly is connected on PLC, single compressor temperature adjustment temperature value Δ t1(initial value is 0.50 DEG C, can set), more the variations in temperature that single compressor temperature adjustment temperature value Δ t1 is used for when adjusting refrigeration chamber, often open one, just can make temperature of refrigerating chamber decline Δ t1.So, can determine according to Δ t1 the quantity that compressor is opened.Because there are three compressor refrigeration, therefore, need to judge in the process of cooling, according to parameters such as number of units, time, temperature, stop by platform.Adopt three compressors, more temperature Controlling vertex can be obtained, make temperature curve more level and smooth, closer to sine curve, be conducive to accurate control and the classification refrigeration of temperature.
As shown in Figure 3, step s30: the working time starts, pressure fan is blown, and desired value is valley, i.e. TS=Tmin, compressor bank is started shooting, such as, after pressure fan starts 10 seconds, started compressor every 10 seconds by platform, when temperature reduces gradually, temporally condition and temperature conditions stop No. 1, No. 2 and No. 3 compressors by platform.Such as, when running for three, along with the operation of three units, temp. in refrigerating chamber declines gradually, as indoor temperature TH≤TS+2 Δ t1, stops No. 1 compressor, indoor temperature continues to decline, when time cumulation reaches 0.3TZ, during indoor temperature TH≤TS+t1, take steps s100, stops No. 2 compressors, and indoor temperature continues to decline, when satisfy condition s110 time, during indoor temperature TH≤TS+ Δ T1, take steps s120, stops No. 3 compressors.By above-mentioned steps, 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, in step S162, the working time reaches 0.5TZ (half period), automatically converts desired value to peak value T by control module (AI module)
max; In step 150, No. 1 compressor start, for the work of step 160 heater provides refrigerant; In step 160, refrigerating chamber is heated up by the work of heating electromagnetic valve group, and wherein, heater is only connected with No. 1 compressor, and No. 1 compressor is enough to for heater provides heating efficiency.In step 170, condensation magnetic valve EVR20 opens, and low capacity heating electromagnetic valve EVR6 and Large Copacity heating electromagnetic valve EVR15 opens, temperature recovery.
In S180, return air temperature sensor detects indoor detected temperatures TH >=TS-2 Δ t2 (Δ t2 is heter temperature adjusted value, can set); In step S190, low capacity heating electromagnetic valve EVR6 closes, and Large Copacity heating electromagnetic valve EVR15 continues out; Indoor detected temperatures TH continues to rise, satisfy condition S200 time, TH >=TS-Δ t2, take steps 210: low capacity heating electromagnetic valve EVR6 opens, Large Copacity heating electromagnetic valve EVR15 closes, and indoor detected temperatures TH continues rising.As TH >=TS-Δ T2, namely satisfy condition S220 time, take steps 230, low capacity heating electromagnetic valve and Large Copacity heating electromagnetic valve complete shut-down, after 5 second time, condensation magnetic valve EVR20 closes, complete temperature-rise period, synthesize indoor temperature from peak value to valley, the one-period again from valley to peak value with the temperature-fall period in early stage.The sine wave that circulation like this just constitutes temperature controls.
In the present invention, the switching sequence of low capacity heating electromagnetic valve and Large Copacity heating electromagnetic valve is when considering that heater heats, the speed that temperature rises, and the refrigeration cool-down of postorder is to the requirement of temperature.In addition, Tmin is 2 DEG C, and Tmax is 5 DEG C, and Δ t1 is 0.5 DEG C is to make temperature control at low-temperature space.
Several timing node above-mentioned (half period and whole cycle) and rise and fall way in temperature nodes, need the waveform that just can have been reached by field adjustable, to ensure the time that the time of the refrigeration in one-period equals to heat, the half period of namely freezing equals the half period heated, refrigeration waveform and heating waveform want corresponding to, such as symmetry.The scope of the refrigerating capacity of usual needs needed for refrigerating chamber, the refrigerating capacity of compressor, heating efficiency is comprehensively carried out considering and is determined after repeatedly debugging, once timing node and rise and fall way in temperature nodes determine after, the present invention can reach stable periodic temperature by classification regulation and control and control, three tier structure is realized cold by three compressors, when realizing heating by two magnetic valves that capacity is different, two magnetic valves are opened simultaneously and are opened with one, another three kinds of heated conditions of closing, accomplish that the number of the timing node in refrigeration and heating process is equal (such as, be three), be conducive to the smooth of curve on the one hand, be conducive to periodicity and the symmetry of curve on the other hand.
Periodic VAV control of the present invention: process is as follows: as shown in Figure 6, a dispatch air port is respectively had on the wall top of the relative both sides of refrigerating chamber 100, be respectively the air outlet 110 and air outlet 120 that mutually stagger and arrange, every dispatch air port requires air quantity from big to small, periodic cycle change from small to large again, as shown in Figure 6, the wind 111 that air outlet 110 blows out is relative with wind 121 direction that air outlet 120 blows out, 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, the air quantity change of two exhaust outlets is just in time contrary, thus realize refrigeration room air formation fluctuation, to meet the needs of ham processing technology.
The air-valve of two air outlets is controlled respectively with two fan valve executors, the aperture action of air-valve is contrary, one another turns down when opening large, is added total blast volume in theory substantially constant, the method realized is as shown in Figure 2, two proportional-type air-valves (also claiming proportioning valve) are with same control signal (VM1.2), and during installation, rotating forward established by an air-valve, and reversion established by another air-valve, so just can realize a valve area change large time, another air-valve just in time diminishes.By PLC programming, control signal is exported to two fan valve executors by control module (AI module) during operation, signal presses triangular wave change, if control signal is voltage (0 ~ 10V), signal intensity is change to the triangle of Vmin from Vmin to Vmax, general Vmin is 0.5 ~ 2V, Vmax is 8 ~ 9.5V, and maximum and minimum of a value adjust according to the requirement of actual air volume.Such as, total blast volume is 10, and at a time, the air quantity of air outlet is 1.5, the air quantity of another side air outlet is 8.5, and in another moment, the air quantity of air outlet is 1, the air quantity of another side air outlet is 9, and at the same position of refrigerating chamber, air quantity is in pressing triangular wave change.
The explanation of detailed description of the invention above can disclose general features of the present invention fully, so that other people are easily embody rule by existing knowledge and adjust and/or adaptations to these detailed description of the invention, these all do not depart from scope of the present invention, and therefore these adjust and revise the equivalent replacement that be considered as embodiment disclosed in the present invention.
Claims (8)
1. a control method for cold storage refrigeration system, is characterized in that: described control method comprises:
Different time within a work period, the desired temperature TS of refrigerating chamber is set as two numerical value at least comprising temperature fluctuation minimum of a value Tmin and temperature fluctuation maximum of T max, and adjust temperature cyclic fluctuation from temperature fluctuation minimum of a value Tmin to temperature fluctuation maximum of T max of refrigerating chamber, is set as the integral multiple of work period the whole working time, when starting operationally, be set as TS=Tmin, then freeze, when arriving half period operationally, make the temperature TH=Tmin of described refrigerating chamber, simultaneously, TS=Tmin is changed into TS=Tmax, then heat, when reaching one-period operationally, make the temperature TH=Tmax of refrigerating chamber, simultaneously, TS=Tmax is changed into TS=Tmin, then the periodic cycle of temperature adjustment is repeated, described control method specifically comprises: after the working time starts, use three compressors by platform start refrigeration, as the indoor temperature TH≤TS+2 Δ t1 of refrigerating chamber, stop No. 1 compressor in three compressors, as indoor temperature TH≤TS+ Δ t1, stop No. 2 compressors in three compressors again, as indoor temperature TH≤TS+ Δ T1, stop No. 3 compressors in three compressors again, wherein, Δ t1 is single compressor temperature adjusted value, Δ T1 is the inertia adjusted value of Tmin.
2. control method according to claim 1, it is characterized in that: No. 1 compressor is connected with heating electromagnetic valve group and the heater utilizing No. 1 compressor operating, heating electromagnetic valve group comprises: be connected in parallel on the low capacity heating electromagnetic valve between described No. 1 compressor and described heater and Large Copacity heating electromagnetic valve, when reaching half period when operating, TS=Tmax, described No. 1 compressor start heats, No. 2 compressors and No. 3 compressors are closed, described low capacity heating electromagnetic valve and Large Copacity heating electromagnetic valve are all opened, when TH >=TS ?2 Δ t2 time, described low capacity heating electromagnetic valve is opened, described Large Copacity heating electromagnetic valve cuts out, when TH >=TS ?Δ T2, low capacity heating electromagnetic valve and Large Copacity heating electromagnetic valve Close All, wherein, Δ t2 is the temperature adjusted value of described heater, Δ T2 is the inertia adjusted value of Tmax.
3. control method according to claim 1, it is characterized in that: described control method also comprises: respectively have a dispatch air port on the wall top of the relative both sides of above-mentioned refrigerating chamber, two dispatch air ports are respectively equipped with the air-valve that controls air quantity, the air quantity change in described two dispatch air ports is just in time contrary, the air-valve in two dispatch air ports, aperture action is contrary, when an air-valve is opened large, another air-valve turns down, and the air output sum in two dispatch air ports remains unchanged.
4. control method according to claim 3, it is characterized in that: described two air-valves are proportional-type air-valve, described two same control signals of proportional-type air-valve control, and rotating forward established by an air-valve, reversion established by another air-valve, and during operation, control signal presses triangular wave change.
5. control method according to claim 4, is characterized in that: described control signal is the voltage of 0 ~ 10V, and described control signal triangular wave is changed to and changes to the triangle of Vmin from Vmin to Vmax, and wherein, Vmin is 0.5 ~ 2V, Vmax is 8 ~ 9.5V.
6. control method according to any one of claim 1 to 5, it is characterized in that: after terminating operationally, enter the time of having a rest, the described time of having a rest comprises the time of carrying out defrosting, after the described time of having a rest terminates, enter the next working time, the described working time is an integer work period, and the described time of having a rest is 1 work period.
7. a cold storage refrigeration system, is characterized in that: comprising: mechanical system and the electric control system be electrically connected with described mechanical system;
Described mechanical system comprises: the evaporimeter (1) connected by pipeline (20), expansion valve (13), filter (14), reservoir (16), condenser (9), compressor (12) and vapour liquid separator (17), the output of described condenser (9) and described reservoir (16), described filter (14), described expansion valve (13) is connected successively with described evaporimeter (1), the output of described evaporimeter (1) is connected to the input of described compressor (12) by described vapour liquid separator (17), condensation magnetic valve (6) is connected between the output of described compressor (12) and the input of described condenser (9), defrosting magnetic valve (3) is connected between the output of described compressor (12) and the input of described evaporimeter (1), described evaporimeter (1) is provided with temperature sensor (11),
Described mechanical system also comprises: heater (2), first check valve (7), second check valve (8), described heater (2) is arranged on after described evaporimeter (1) along airflow direction, described first check valve (7) is arranged between the output of described condenser (9) and reservoir (16), described second check valve (8) is arranged between the output of described heater (2) and reservoir (16), described mechanical system also comprises heating electromagnetic valve group, described heating electromagnetic valve group is connected between the output of compressor (12) and the input of heater (2), described heating electromagnetic valve group comprises low capacity magnetic valve (4) in parallel and Large Copacity magnetic valve (5),
Described electric control system comprises: the programmable logic controller (PLC) be connected and Analog input mModule, described programmable logic controller (PLC) and Analog input mModule control the different time of compressor within a work period, the desired temperature TS of refrigerating chamber is set as two numerical value at least comprising temperature fluctuation minimum of a value Tmin and temperature fluctuation maximum of T max, and adjusts temperature cyclic fluctuation from temperature fluctuation minimum of a value Tmin to temperature fluctuation maximum of T max of refrigerating chamber.
8. cold storage refrigeration system according to claim 7, is characterized in that: described compressor (12) comprising: No. 1 compressor in parallel, No. 2 compressors and No. 3 compressors, described heater is connected with described No. 1 compressor.
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