CN116538718A - Control method of refrigerating system and refrigerating system - Google Patents
Control method of refrigerating system and refrigerating system Download PDFInfo
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- CN116538718A CN116538718A CN202310504457.5A CN202310504457A CN116538718A CN 116538718 A CN116538718 A CN 116538718A CN 202310504457 A CN202310504457 A CN 202310504457A CN 116538718 A CN116538718 A CN 116538718A
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- 238000000034 method Methods 0.000 title claims abstract description 66
- 239000007788 liquid Substances 0.000 claims description 84
- 238000005057 refrigeration Methods 0.000 claims description 63
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 20
- 239000003507 refrigerant Substances 0.000 claims description 19
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 claims description 8
- 229910052757 nitrogen Inorganic materials 0.000 claims description 4
- 230000000694 effects Effects 0.000 abstract description 3
- 238000004134 energy conservation Methods 0.000 abstract description 2
- 230000001276 controlling effect Effects 0.000 description 15
- 238000001816 cooling Methods 0.000 description 5
- 230000008569 process Effects 0.000 description 4
- 230000001105 regulatory effect Effects 0.000 description 4
- 238000009835 boiling Methods 0.000 description 3
- 230000008859 change Effects 0.000 description 3
- 238000001704 evaporation Methods 0.000 description 3
- 230000008020 evaporation Effects 0.000 description 3
- 238000012360 testing method Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 230000009977 dual effect Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000002238 attenuated effect Effects 0.000 description 1
- 238000003763 carbonization Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000001035 drying Methods 0.000 description 1
- 238000005485 electric heating Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 230000004297 night vision Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000008707 rearrangement Effects 0.000 description 1
- 229920006395 saturated elastomer Polymers 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Classifications
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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
- F25B49/022—Compressor 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
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
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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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/07—Details of compressors or related parts
- F25B2400/077—Compressor control units, e.g. terminal boxes, mounted on the compressor casing wall containing for example starter, protection switches or connector contacts
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The embodiment of the invention discloses a control method of a refrigerating system and the refrigerating system, wherein a plurality of compressors share one set of evaporator, condenser and waterway system, and the compressors are controlled to work by adopting double control logic of superheat participation control and control by a proportional-integral-derivative control method by utilizing temperature deviation, so that the technical problems that the large-load high-low temperature refrigerating requirement cannot be met due to the use of a single compressor in the prior art, and the system components are more, the occupied space is larger and the control logic is single due to the use of a direct splicing mode of the double compressors are solved, the refrigerating requirement of the large-load high-low temperature is met, and the technical effects of simple connection structure, small occupied space, high control precision and energy conservation are realized.
Description
Technical Field
The embodiment of the invention relates to the technical field of refrigeration systems, in particular to a control method of a refrigeration system and the refrigeration system.
Background
In a high-load high-low temperature refrigerating unit system, when the refrigerating system performs low-temperature test, particularly when the on-load refrigerating capacity is required to be relatively large, a compressor with high power or even a screw compressor is generally adopted to solve the problem of large refrigerating capacity, or the refrigerating system and the waterway system of two or more sets of compressors are separated to jointly work to solve the problem.
However, a set of high-power compressor system can meet the refrigerating capacity requirement of high refrigerating capacity at normal temperature, such as the refrigerating capacity requirement of more than 40KW, and under the condition of low temperature, for example at-40 ℃, the refrigerating capacity of only about 1KW is usually needed, but the refrigerating capacity of the high-power compressor system at low temperature is also very large, the lowest refrigerating capacity is usually 5-8KW, more electric heating is needed to neutralize the part of the refrigerating capacity to maintain balance, at the moment, the opening degree of a throttle valve is very small, the suction pressure of the compressor is very low, the compressor works under the limit working condition, the suction specific volume is increased, the motor of the compressor is insufficient in cooling, the exhaust temperature is too high, even the compressor has serious problems of overheat protection, low-pressure alarm, carbonization of refrigerating fluid and the like due to long-term working, and the problems of energy conservation and temperature change are not easy to control and stability are avoided.
The two sets of systems are directly spliced, so that the system components are relatively large, the occupied space is relatively large, the action components are also increased, and the refrigeration mode can avoid the influence caused by large load change, but is not economical and energy-saving, and the space utilization rate is not high; and the control logic of a single set of system is simply copied, the control logic is single, and the refrigeration utilization rate of the double set of compressors is not high.
Disclosure of Invention
The embodiment of the invention provides a control method of a refrigerating system and the refrigerating system, which solve the technical problems that a single compressor is used in the prior art, the high-load high-low temperature refrigerating requirement cannot be met, and the system components are more, the occupied space is larger and the control logic is single due to the fact that a double compressor is used in a direct splicing mode.
The embodiment of the invention provides a control method of a refrigerating system, which comprises at least two compressors, an evaporator, a condenser and a waterway system, wherein the power of the at least two compressors is the same, and the at least two compressors share the evaporator, the condenser and the waterway system; the control method comprises the following steps:
acquiring a current temperature value of a target object, and comparing the current temperature value with a preset temperature threshold;
if the current temperature value is higher than the preset temperature threshold value, controlling the compressor to work by using a temperature deviation through a proportional-integral-derivative control method, wherein the temperature deviation is a difference value between the current temperature value and the preset temperature threshold value;
and if the current temperature value is lower than the preset temperature threshold value, controlling the compressor to work by utilizing the temperature deviation and the superheat degree of the refrigerating system.
Further, controlling the operation of the compressor using the temperature deviation and the superheat of the refrigeration system includes:
acquiring the superheat degree of the refrigerant in the refrigeration system, and judging whether the superheat degree is smaller than a preset superheat degree threshold value or not to obtain a first judgment result;
and determining whether to control the operation of the compressor through the valve step adjustment of the electronic expansion valve based on the first judgment result.
Further, determining whether to control the operation of the compressor in combination by the adjustment of the valve step of the electronic expansion valve and the temperature deviation based on the first determination result includes:
if the first judgment result is that the superheat degree is smaller than the preset superheat degree threshold value, reducing the valve step of the electronic expansion valve at a first preset speed, and controlling the compressor to work by using the temperature deviation through a proportional-integral-derivative control method;
and if the first judgment result is that the superheat degree is larger than the preset superheat degree threshold, judging the magnitude relation between the temperature deviation and the preset deviation threshold to obtain a second judgment result, and controlling the compressor to work based on the second judgment result.
Further, controlling the operation of the compressor based on the second determination result includes:
if the second judgment result is that the temperature deviation is smaller than the preset deviation threshold value, the temperature deviation is directly utilized to control the compressor to work through a proportional-integral-derivative control method;
if the second judgment result is that the temperature deviation is larger than the preset deviation threshold, reducing the valve step of the electronic expansion valve at a second preset speed, and controlling the compressor to work by utilizing the temperature deviation through a proportional-integral-derivative control method, wherein the second preset speed is larger than the first preset speed.
Further, controlling the operation of the compressor by a proportional-integral-derivative control method using the temperature deviation includes:
acquiring the current refrigeration requirement of the target object;
and calculating by the proportional-integral-derivative control method based on the current refrigeration requirement and the temperature deviation to obtain the starting quantity of the compressors and the refrigeration capacity of each compressor.
Further, after comparing the current temperature value with a preset temperature threshold, the control method further includes:
and calculating the temperature deviation between the current temperature value and the preset temperature threshold value.
Further, the control method further includes:
acquiring a liquid level value of an expansion water tank in the waterway system, and comparing the liquid level value with a preset liquid level threshold, wherein the preset liquid level threshold comprises a first liquid level threshold, a second liquid level threshold and a third liquid level threshold, the first liquid level threshold is smaller than the second liquid level threshold, and the second liquid level threshold is smaller than the third liquid level threshold;
if the liquid level value is smaller than the first liquid level threshold value, the waterway system automatically feeds liquid to the second liquid level threshold value;
and if the liquid level value is higher than the third liquid level threshold value, the waterway system sends out an alarm prompt.
Further, the control method further includes:
and receiving a pressurizing instruction, and pressurizing the expansion water tank in the waterway system by introducing nitrogen based on the pressurizing instruction.
The embodiment of the invention also provides a refrigerating system, which executes the control method of the refrigerating system in any embodiment; the refrigerating system comprises at least two compressors, an evaporator, a condenser and a waterway system; the power of at least two compressors is the same; at least two compressors share the evaporator, the condenser and the water circuit system.
The embodiment of the invention discloses a control method of a refrigeration system and the refrigeration system, wherein the method comprises the steps of obtaining a current temperature value of a target object, and comparing the current temperature value with a preset temperature threshold; if the current temperature value is higher than the preset temperature threshold value, controlling the compressor to work by utilizing the temperature deviation through a proportional-integral-derivative control method; and if the current temperature value is lower than the preset temperature threshold value, the compressor is controlled to work by utilizing the temperature deviation and the superheat degree of the refrigerating system. The utility model discloses a through a set of evaporimeter of many sets of compressors sharing, condenser and waterway system to adopt the superheat to participate in control and utilize the temperature deviation to carry out the dual control logic control compressor work of control through proportion-integral-differential control method, solved among the prior art and used the unable high low temperature refrigeration demand of satisfying of heavy load that single set of compressor exists, and use the system part more that double set of compressor adopted the mode that directly splice to lead to, occupation space is great and control logic is comparatively single technical problem, not only satisfied the refrigeration demand of heavy load high low temperature, still realized that connection structure is simple, occupation space is few, control accuracy is high and energy-conserving technical effect.
Drawings
Fig. 1 is a block diagram of a refrigeration system according to an embodiment of the present invention;
fig. 2 is a flowchart of a control method of a refrigeration system according to an embodiment of the present invention;
fig. 3 is a flowchart of another control method of a refrigeration system according to an embodiment of the present invention.
Detailed Description
The invention is described in further detail below with reference to the drawings and examples. It is to be understood that the specific embodiments described herein are merely illustrative of the invention and are not limiting thereof. It should be further noted that, for convenience of description, only some, but not all of the structures related to the present invention are shown in the drawings.
It should be noted that the terms "first," "second," and the like in the description and the claims of the present invention and in the drawings are used for distinguishing between different objects and not for limiting a particular order. The following embodiments of the present invention may be implemented individually or in combination with each other, and the embodiments of the present invention are not limited thereto.
Fig. 1 is a block diagram of a refrigeration system according to an embodiment of the present invention. As shown in fig. 1, the refrigeration system includes at least two compressors (as shown in fig. 1, compressor 1# and compressor 2 #), an evaporator, a condenser, and a water path system, the at least two compressors having the same power, the at least two compressors sharing the evaporator, the condenser, and the water path system.
Fig. 2 is a flowchart of a control method of a refrigeration system according to an embodiment of the present invention.
As shown in fig. 2, the control method of the refrigeration system specifically includes the following steps:
s101, acquiring a current temperature value of the target object, and comparing the current temperature value with a preset temperature threshold.
Specifically, in the working process of the refrigeration system, the current temperature value of the target object is required to be acquired first, and then the current temperature value is compared with a preset temperature threshold value, so that whether the target object is in a high-temperature section or a low-temperature section currently is judged, and whether the participation of the superheat degree is required in the working process of the refrigeration system is determined. Typically, the preset temperature threshold is-14.7 ℃.
Optionally, after comparing the current temperature value with the preset temperature threshold in S101, the control method of the refrigeration system further includes: and calculating the temperature deviation between the current temperature value and the preset temperature threshold value.
Specifically, in order to meet the subsequent control requirement of the refrigeration system, after comparing the current temperature value with the preset temperature threshold value, the current temperature value and the preset temperature threshold value need to be subjected to difference to obtain the temperature deviation between the current temperature value and the preset temperature threshold value for standby.
S102, if the current temperature value is higher than a preset temperature threshold value, controlling the operation of the compressor by utilizing a temperature deviation through a proportional-integral-derivative control method, wherein the temperature deviation is the difference value between the current temperature value and the preset temperature threshold value.
Specifically, if the current temperature value is higher than-14.7 ℃, it is indicated that it is in a high temperature section at this time, the compressor is controlled by a PID (proportional-integral-derivative) control method using the temperature deviation. Specifically, the temperature deviation is used as an input amount of PID control, and based on the total cooling demand of the target object, several compressors are required to operate by using the PID control output, and the cooling capacity of each compressor.
Optionally, S102, controlling the operation of the compressor by the proportional-integral-derivative control method using the temperature deviation includes: acquiring the current refrigeration requirement of a target object; and calculating by a proportional-integral-derivative control method based on the current refrigeration requirement and the temperature deviation to obtain the starting quantity of the compressors and the refrigeration capacity of each compressor.
For example, the current refrigeration requirement of the target object is 20%, and the refrigeration system has two compressors, wherein each compressor supports 40% of the refrigeration requirement, and only one compressor is needed at the moment to meet the current refrigeration requirement of the target object; assuming that the current refrigeration requirement of the target object is 60%, one of the two compressors needs to work at full load at the moment, and the other one needs to perform refrigeration output with 20% of refrigeration capacity so as to meet the current refrigeration requirement of the target object.
The compressor is started and stopped at intervals and also has inertia, and the start and stop of the automobile are similar to those of the running automobile, so that the switching of the compressor cannot bring about great influence and severe temperature fluctuation.
And S103, if the current temperature value is lower than the preset temperature threshold value, the compressor is controlled to work by utilizing the temperature deviation and the superheat degree of the refrigerating system.
Specifically, if the current temperature value is lower than-14.7 ℃, the temperature value is indicated to be in a low temperature section at the moment, and the compressor needs to be controlled by utilizing the superheat degree of the refrigeration system besides the temperature deviation and PID control, wherein the superheat degree refers to the difference between the superheat temperature and the saturation temperature of the refrigerant under the same evaporation pressure.
The utility model discloses a through a set of evaporimeter of many sets of compressors sharing, condenser and waterway system to adopt the superheat to participate in control and utilize the temperature deviation to carry out the dual control logic control compressor work of control through proportion-integral-differential control method, solved among the prior art and used the unable high low temperature refrigeration demand of satisfying of heavy load that single set of compressor exists, and use the system part more that double set of compressor adopted the mode that directly splice to lead to, occupation space is great and control logic is comparatively single technical problem, not only satisfied the refrigeration demand of heavy load high low temperature, still realized that connection structure is simple, occupation space is few, control accuracy is high and energy-conserving technical effect.
On the basis of the above technical solutions, fig. 3 is a flowchart of another control method of a refrigeration system according to an embodiment of the present invention, as shown in fig. 3, S103 specifically includes the following steps:
s301, acquiring the superheat degree of the refrigerant in the refrigeration system, and judging whether the superheat degree is smaller than a preset superheat degree threshold value or not to obtain a first judging result.
Specifically, if the current temperature value is lower than-14.7 ℃, it indicates that the temperature is in a low temperature section at this time, and at this time, the superheat degree of the refrigerant in the refrigeration system needs to be obtained, specifically, a pressure fluctuation device exists between the evaporator and the compressor in the refrigeration system, a pressure signal generated by the pressure fluctuation device can be correspondingly converted into the evaporation temperature of the refrigeration system in a saturated state, and a temperature sensor also exists at the outlet of the evaporator, wherein the difference value between the temperature value detected by the temperature sensor and the evaporation temperature is the superheat degree of the refrigerant.
After obtaining the superheat degree of the refrigerant, comparing the superheat degree with a preset superheat degree threshold value to obtain a first judgment result, wherein the preset superheat degree threshold value can be set to be 5 ℃.
S302, determining whether to control the operation of the compressor through the valve step adjustment and the temperature deviation of the electronic expansion valve based on the first judging result.
Optionally, S302 specifically includes: if the first judging result is that the superheat degree is smaller than the preset superheat degree threshold value, reducing the valve step of the electronic expansion valve at a first preset speed, and controlling the compressor to work by using the temperature deviation through a proportional-integral-differential control method; and if the first judgment result is that the superheat degree is larger than the preset superheat degree threshold value, judging the magnitude relation between the temperature deviation and the preset deviation threshold value to obtain a second judgment result, and controlling the compressor to work based on the second judgment result.
Specifically, if the first determination result is that the superheat degree is less than 5 ℃, the valve step of the electronic expansion valve needs to be attenuated slowly, and the valve step of the electronic expansion valve is usually reduced at a first preset speed, wherein the first preset speed can be set to be 3 valve steps per second, 2 valve steps per second or the like as required, and meanwhile, the control of the compressor by the proportional-integral-differential control method through the temperature deviation still plays a role.
If the first judgment result is that the superheat degree is greater than 5 ℃, the magnitude relation between the temperature deviation and the preset deviation threshold value is required to be further judged at the moment, so that the accurate control of the compressor is realized according to the obtained second judgment result.
Optionally, controlling the operation of the compressor based on the second determination result includes: if the second judgment result is that the temperature deviation is smaller than the preset deviation threshold value, the temperature deviation is directly utilized to control the compressor to work through a proportional-integral-differential control method; if the second judgment result is that the temperature deviation is larger than the preset deviation threshold, the valve step of the electronic expansion valve is reduced at a second preset speed, and meanwhile, the operation of the compressor is controlled by utilizing the temperature deviation through a proportional-integral-derivative control method, wherein the second preset speed is larger than the first preset speed.
For example, the preset deviation threshold may be set to 10 ℃ according to needs, and if the second judgment result is that the temperature deviation is less than 10 ℃, the temperature deviation is directly utilized to control the compressor to work through a proportional-integral-differential control method; if the second judgment result is that the temperature deviation is greater than 10 ℃, the valve step of the electronic expansion valve is reduced at a second preset speed, wherein the second preset speed generally selects the maximum valve step set by the electronic expansion valve, and meanwhile, the temperature deviation is utilized to still play a role in controlling the compressor through a proportional-integral-differential control method.
In the embodiment of the invention, the speed of the low temperature Duan Jiangwen can meet corresponding requirements by a double control mode of PID control and superheat control, and the condition that the temperature cannot be stabilized due to unstable valve step attenuation which is easy to occur when single temperature deviation control is adopted can be prevented.
Optionally, the control method of the refrigeration system further includes: acquiring a liquid level value of an expansion water tank in a waterway system, and comparing the liquid level value with a preset liquid level threshold, wherein the preset liquid level threshold comprises a first liquid level threshold, a second liquid level threshold and a third liquid level threshold, the first liquid level threshold is smaller than the second liquid level threshold, and the second liquid level threshold is smaller than the third liquid level threshold; if the liquid level value is smaller than the first liquid level threshold value, the waterway system automatically feeds liquid to the second liquid level threshold value; if the liquid level value is higher than the third liquid level threshold value, the waterway system sends out an alarm prompt.
Specifically, because the volume of the waterway system is large, the traditional manual liquid adding method is time-consuming and labor-consuming, so that referring to fig. 1, a liquid level meter is arranged at the expansion tank of the waterway system, and the liquid level meter can detect the liquid level value in the expansion tank in real time. The refrigeration system is provided with a third-gear liquid level threshold value as required, namely a first liquid level threshold value, a second liquid level threshold value and a third liquid level threshold value. When the liquid level meter detects that the liquid level value of the expansion tank is lower than a liquid level early warning threshold value, namely a first liquid level threshold value, the liquid adding pump can be automatically started, the working circulation liquid (namely the refrigerant) is sucked into the expansion tank from the liquid storage barrel (namely the water storage tank shown in fig. 1), and meanwhile, when the liquid level in the liquid storage barrel is lower than a preset value, an alarm prompt is sent out to prompt a user to add the working liquid, so that dry pumping is prevented.
When the liquid level meter detects that the liquid level value of the expansion water tank is higher than the highest liquid level threshold, namely the third liquid level threshold, an alarm prompt is sent out to prompt a user that the liquid level is too high and to process in time.
Optionally, the control method of the refrigeration system further includes: and receiving a pressurizing instruction, and pressurizing the expansion water tank in the waterway system by introducing nitrogen based on the pressurizing instruction.
Specifically, in general, the boiling point of the working circulation liquid is 110 ℃ or 120 ℃, and in the process of testing the refrigeration system, sometimes the working circulation liquid needs to be tested in a high-temperature environment such as 150 ℃, at this time, the boiling point of the working circulation liquid needs to be increased, a user needs to send a pressurization instruction to the refrigeration system through a man-machine interaction unit, and the refrigeration system automatically pressurizes the expansion tank by introducing nitrogen based on the pressurization instruction, so that the boiling point is increased to perform a higher-temperature test.
The embodiment of the invention also provides a refrigerating system, which executes the control method of the refrigerating system in any embodiment. As shown in fig. 1, the refrigeration system includes at least two compressors (shown as compressor 1# and compressor 2# in fig. 1), an evaporator (i.e., evaporator plate change in fig. 1), a condenser (i.e., double-tube condenser in fig. 1), and a water circuit system (i.e., water storage tank, expansion tank, fill port, level gauge, circulation line thereof, etc. in fig. 1); the power of at least two compressors is the same; at least two compressors share an evaporator, a condenser and a water path system.
Specifically, as shown in fig. 1, in order to distinguish the circulation lines of the two compressors, the corresponding components are distinguished by 1# and 2 #. Referring to fig. 1, taking working engineering of a compressor 1# as an example, a refrigerant enters a 1# oil separator after being compressed by the compressor 1# and then enters a double-sleeve condenser from the 1# oil separator, and is cooled by the double-sleeve condenser to become high-pressure and moderate-temperature refrigerant liquid; after passing through a No. 1 drying filter and a No. 1 night vision goggles, refrigerant liquid enters a No. 1 economizer plate exchanger, the economizer plate exchanger is equivalent to an intercooler device, after cooling through the No. 1 economizer plate exchanger, the refrigerant liquid is divided into two paths, one path enters a main circulation pipeline, namely, absorbs heat after expanding through a No. 1 economizer expansion valve, the refrigerant evaporated into a gaseous state returns to a No. 1 compressor, the other path is divided into two branches, and before one branch returns to a No. 1 gas-liquid separator through a No. 1 cooling electromagnetic valve and a No. 1 expansion valve, the other branch returns to an evaporator plate exchanger through a No. 1 main electromagnetic valve and a No. 1 main electronic expansion valve; after exchanging heat with the waterway system through the evaporator plate, the refrigerant returns to the compressor 1# through the 1# gas-liquid separator.
For the double-tube condenser, there is also a 1# condensing pressure regulating valve for regulating the line pressure of the compressor 1# in the double-tube condenser, and there is a 2# condensing pressure regulating valve for regulating the line pressure of the compressor 2# in the double-tube condenser.
For a waterway system, there are inner and outer circulation, wherein the inner circulation refers to circulation between the inner circulation and the evaporator plate exchange, and the refrigerant stored in the water storage tank enters the evaporator plate exchange through an inner circulation pump and returns to the water storage tank through heat exchange of the refrigerant; the external circulation refers to that the refrigerant subjected to heat exchange treatment in the water storage tank is heated and supplemented by heat through an electric heater and then is output to an external load through an external circulation pump for use. The inside temperature sensor that is provided with of storage water tank for detect expansion tank expend with heat and contract with cold's temperature, the level gauge is used for detecting expansion tank's liquid level value, and the filling opening is used for the liquid feeding in to expansion tank. In addition, the external circulation pump is connected with an external load through a ball valve, and meanwhile, a flowmeter is further arranged at the water storage tank and is also connected with the ball valve.
Similarly, the working principle of the compressor 2# is the same as that of the compressor 1# and will not be described here again.
In the description of embodiments of the present invention, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art.
Finally, it should be noted that the foregoing description is only illustrative of the preferred embodiments of the present invention and the technical principles employed. It will be understood by those skilled in the art that the present invention is not limited to the particular embodiments described herein, but is capable of various obvious changes, rearrangements and substitutions as will now become apparent to those skilled in the art without departing from the scope of the invention. Therefore, while the invention has been described in connection with the above embodiments, the invention is not limited to the embodiments, but may be embodied in many other equivalent forms without departing from the spirit or scope of the invention, which is set forth in the following claims.
Claims (9)
1. The control method of the refrigerating system is characterized in that the refrigerating system comprises at least two compressors, an evaporator, a condenser and a waterway system, the power of the at least two compressors is the same, and the at least two compressors share the evaporator, the condenser and the waterway system; the control method comprises the following steps:
acquiring a current temperature value of a target object, and comparing the current temperature value with a preset temperature threshold;
if the current temperature value is higher than the preset temperature threshold value, controlling the compressor to work by using a temperature deviation through a proportional-integral-derivative control method, wherein the temperature deviation is a difference value between the current temperature value and the preset temperature threshold value;
and if the current temperature value is lower than the preset temperature threshold value, controlling the compressor to work by utilizing the temperature deviation and the superheat degree of the refrigerating system.
2. The method of controlling a refrigerant system as set forth in claim 1, wherein controlling the operation of the compressor using the temperature deviation and the superheat of the refrigerant system together includes:
acquiring the superheat degree of the refrigerant in the refrigeration system, and judging whether the superheat degree is smaller than a preset superheat degree threshold value or not to obtain a first judgment result;
and determining whether to control the operation of the compressor through the valve step adjustment of the electronic expansion valve based on the first judgment result.
3. The control method of a refrigeration system according to claim 2, wherein determining whether to control the operation of the compressor by the adjustment of the valve step of the electronic expansion valve and the temperature deviation together based on the first determination result includes:
if the first judgment result is that the superheat degree is smaller than the preset superheat degree threshold value, reducing the valve step of the electronic expansion valve at a first preset speed, and controlling the compressor to work by using the temperature deviation through a proportional-integral-derivative control method;
and if the first judgment result is that the superheat degree is larger than the preset superheat degree threshold, judging the magnitude relation between the temperature deviation and the preset deviation threshold to obtain a second judgment result, and controlling the compressor to work based on the second judgment result.
4. A control method of a refrigeration system according to claim 3, wherein controlling the operation of the compressor based on the second determination result includes:
if the second judgment result is that the temperature deviation is smaller than the preset deviation threshold value, the temperature deviation is directly utilized to control the compressor to work through a proportional-integral-derivative control method;
if the second judgment result is that the temperature deviation is larger than the preset deviation threshold, reducing the valve step of the electronic expansion valve at a second preset speed, and controlling the compressor to work by utilizing the temperature deviation through a proportional-integral-derivative control method, wherein the second preset speed is larger than the first preset speed.
5. A control method of a refrigeration system according to claim 1, wherein controlling the operation of the compressor by a proportional-integral-derivative control method using a temperature deviation comprises:
acquiring the current refrigeration requirement of the target object;
and calculating by the proportional-integral-derivative control method based on the current refrigeration requirement and the temperature deviation to obtain the starting quantity of the compressors and the refrigeration capacity of each compressor.
6. The control method of a refrigeration system according to claim 1, wherein after comparing the current temperature value with a preset temperature threshold value, the control method further comprises:
and calculating the temperature deviation between the current temperature value and the preset temperature threshold value.
7. The control method of a refrigeration system according to claim 1, characterized in that the control method further comprises:
acquiring a liquid level value of an expansion water tank in the waterway system, and comparing the liquid level value with a preset liquid level threshold, wherein the preset liquid level threshold comprises a first liquid level threshold, a second liquid level threshold and a third liquid level threshold, the first liquid level threshold is smaller than the second liquid level threshold, and the second liquid level threshold is smaller than the third liquid level threshold;
if the liquid level value is smaller than the first liquid level threshold value, the waterway system automatically feeds liquid to the second liquid level threshold value;
and if the liquid level value is higher than the third liquid level threshold value, the waterway system sends out an alarm prompt.
8. The control method of a refrigeration system according to claim 1, characterized in that the control method further comprises:
and receiving a pressurizing instruction, and pressurizing the expansion water tank in the waterway system by introducing nitrogen based on the pressurizing instruction.
9. A refrigeration system, characterized in that it performs the control method of the refrigeration system according to any one of the preceding claims 1 to 8; the refrigerating system comprises at least two compressors, an evaporator, a condenser and a waterway system; the power of at least two compressors is the same; at least two compressors share the evaporator, the condenser and the water circuit system.
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