CN116149392A - Temperature control method and system - Google Patents
Temperature control method and system Download PDFInfo
- Publication number
- CN116149392A CN116149392A CN202310091467.0A CN202310091467A CN116149392A CN 116149392 A CN116149392 A CN 116149392A CN 202310091467 A CN202310091467 A CN 202310091467A CN 116149392 A CN116149392 A CN 116149392A
- Authority
- CN
- China
- Prior art keywords
- temperature
- variable frequency
- compressor
- cooling
- throttle valve
- 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.)
- Pending
Links
Images
Classifications
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D23/00—Control of temperature
- G05D23/19—Control of temperature characterised by the use of electric means
- G05D23/20—Control of temperature characterised by the use of electric means with sensing elements having variation of electric or magnetic properties with change of temperature
-
- 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
Landscapes
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The application relates to a temperature control method and a temperature control system, comprising the following steps: acquiring the actual temperature of the cooling liquid in the cooling liquid system; when the absolute value of the difference between the actual temperature and the target temperature is larger than a first preset temperature difference, controlling the opening degree of the throttling mechanism to be unchanged and adjusting the frequency of the variable-frequency compressor; when the absolute value is smaller than a first preset temperature difference, controlling the frequency of the variable-frequency compressor to be unchanged and adjusting the opening of the throttling mechanism; the cooling liquid system can exchange heat with the refrigerating system and can circularly supply cooling liquid to the load end, and the refrigerating system comprises a variable frequency compressor and a throttling mechanism. The refrigeration system is subjected to cold energy adjustment through the cooperative cooperation of the variable frequency compressor and the throttling mechanism, so that the actual temperature finally approaches to or is equal to the target temperature, and compared with temperature control equipment without a cold energy adjustment function by adopting the fixed frequency compressor in the prior art, the energy consumption is reduced, and the accurate control of the temperature of the cooling liquid is realized.
Description
Technical Field
The present disclosure relates to the field of temperature control technologies, and in particular, to a temperature control method and system.
Background
With the development and innovation of technology, a chip (integrated circuit, abbreviated as IC) is widely used as an important electronic component in various fields of consumer electronics, high-end manufacturing, network communication, household appliances, internet of things and the like, and has become one of important marks for measuring the national industrial competitiveness and comprehensive national force.
Before shipment, the chip needs to be subjected to multiple links such as design, manufacture and test. In general, a temperature control device is required to provide stable temperature conditions for an end load during testing of a chip, so as to ensure production process accuracy or accuracy of test data.
At present, the temperature control equipment comprises a fixed-frequency compressor and an electric heater, and the self cooling capacity adjustment precision of the temperature control equipment is low. And because the cold quantity adjusting precision of the temperature control equipment is lower, the power consumption of the compressor is high, and an electric heater is needed to counteract the redundant cold quantity, so that the energy consumption is higher.
Disclosure of Invention
Based on this, it is necessary to provide a temperature control method and system capable of reducing energy consumption, aiming at the problem of higher energy consumption of the conventional temperature control device.
A temperature control method comprising the steps of:
acquiring the actual temperature of the cooling liquid in the cooling liquid system;
when the absolute value of the difference value between the actual temperature and the target temperature is larger than a first preset temperature difference, controlling the opening degree of the throttling mechanism to be unchanged and adjusting the frequency of the variable frequency compressor;
when the absolute value is smaller than the first preset temperature difference, controlling the frequency of the variable frequency compressor to be unchanged and adjusting the opening of the throttling mechanism;
the cooling liquid system can exchange heat with the refrigerating system and can provide cooling liquid for a load end, the refrigerating system comprises the variable frequency compressor and the throttling mechanism, and the throttling mechanism is used for adjusting the temperature of a refrigerant which is input into a heat exchange part which exchanges heat with the cooling liquid system in the refrigerating system.
In one embodiment, before controlling the opening degree of the throttling mechanism to be unchanged and adjusting the frequency of the variable frequency compressor when the absolute value of the difference between the actual temperature and the target temperature is greater than a first preset temperature difference, the method further comprises the steps of:
acquiring the magnitude relation between the actual temperature and the target temperature;
when the actual temperature is smaller than the target temperature, controlling the refrigerating system to enter a heating mode; when the actual temperature is greater than the target temperature, controlling the refrigerating system to enter a cooling mode;
when the refrigerating system is in the heating mode, the first preset temperature difference is a first heating preset temperature difference; when the refrigeration system is in the cooling mode, the first preset temperature difference is a first cooling preset temperature difference.
In one embodiment, when the refrigeration system is in the heating mode and the absolute value of the difference between the actual temperature and the target temperature is greater than the first heating preset temperature difference, controlling the opening degree of a second throttle valve to be unchanged and increasing the frequency of the variable frequency compressor;
when the refrigerating system is in the heating mode and the absolute value is smaller than the first heating preset temperature difference, controlling the frequency of the variable frequency compressor to be unchanged and adjusting the opening of the second throttle valve;
The throttling mechanism comprises a second throttling valve, and the second throttling valve is arranged on a bypass pipeline which is used for communicating the outlet end of the variable frequency compressor with the input end of the evaporator.
In one embodiment, the throttling mechanism further comprises a first throttling valve, the variable frequency compressor, the condenser, the first throttling valve and the evaporator are sequentially communicated to form a closed loop of the refrigerating system, and the refrigerating system exchanges heat with the cooling liquid system through the evaporator;
and when the refrigerating system is in the heating mode, controlling the opening degree of the first throttle valve to be unchanged.
In one embodiment, when the refrigeration system is in the cooling mode and the absolute value of the difference between the actual temperature and the target temperature is greater than the first cooling preset temperature difference, controlling the opening of the first throttle valve to be unchanged and increasing the frequency of the variable frequency compressor;
when the refrigerating system is in the cooling mode and the absolute value is smaller than the first cooling preset temperature difference, controlling the frequency of the variable frequency compressor to be unchanged and adjusting the opening of the first throttle valve;
the throttling mechanism comprises a first throttling valve, the variable frequency compressor, the condenser, the first throttling valve and the evaporator are sequentially communicated to form a closed loop of the refrigerating system, and the refrigerating system exchanges heat with the cooling liquid system through the evaporator.
In one embodiment, when the refrigeration system is in the cooling mode and the absolute value is smaller than the first cooling preset temperature difference, controlling the frequency of the variable frequency compressor to be unchanged and adjusting the opening of the first throttle valve includes the steps of:
when the absolute value is larger than a second preset temperature difference, controlling the frequency of the variable frequency compressor to be unchanged and adjusting the opening of the first throttle valve according to the suction superheat degree and/or the actual temperature of the variable frequency compressor;
when the absolute value is smaller than or equal to the second preset temperature difference, controlling the frequency of the variable frequency compressor to be unchanged and controlling the opening of the first throttle valve to be unchanged;
the second preset temperature difference is smaller than the first preset temperature difference.
In one embodiment, when the refrigeration system is in the cooling mode, the second throttle valve is controlled to be closed;
the throttling mechanism further comprises a second throttling valve, and the second throttling valve is arranged on a bypass pipeline which is used for communicating the outlet end of the variable frequency compressor with the input end of the evaporator.
In one embodiment, when the absolute value is less than or equal to a second preset temperature difference, the refrigeration system is in a temperature control mode;
When in the temperature control mode, controlling the frequency of the variable frequency compressor to be unchanged, enabling the first throttle valve to be in a set opening degree to be unchanged, and adjusting the opening degree of the second throttle valve to enable the actual temperature to be in a preset temperature range;
the variable-frequency compressor, the condenser, the first throttle valve and the evaporator are sequentially communicated to form a closed loop of the refrigerating system, the refrigerating system exchanges heat with the cooling liquid system through the evaporator, and the second throttle valve is arranged on a bypass pipeline which is used for communicating an air outlet end of the variable-frequency compressor with an input end of the evaporator; the second preset temperature difference is smaller than the first preset temperature difference.
In one embodiment, the method further comprises the steps of:
according to the change trend of the actual condensing pressure of the condenser, controlling the rotating speed of the variable frequency fan so that the actual condensing pressure is in the range of the preset condensing pressure;
the refrigerating system further comprises a condenser and a variable frequency fan, wherein the variable frequency fan is used for radiating heat of the condenser.
In one embodiment, the method further comprises the steps of:
controlling the rotating speed of the variable frequency pump according to the parameters of the cooling liquid required by the load end;
Wherein the coolant system includes a variable frequency pump for providing a driving force for flowing a coolant in the coolant system.
A temperature control system for use in the temperature control method of any one of the preceding claims, comprising:
the refrigerating system comprises a variable-frequency compressor, an evaporator, a condenser and a throttling mechanism, wherein the throttling mechanism comprises a first throttling valve and a second throttling valve, the variable-frequency compressor, the condenser, the first throttling valve and the evaporator are sequentially communicated to form a closed loop of the refrigerating system, the variable-frequency compressor is provided with an air outlet end communicated with the condenser, the second throttling valve is arranged on a bypass pipeline, and the bypass pipeline connects the air outlet end of the variable-frequency compressor with the input end of the evaporator;
and the cooling liquid system is used for performing heat exchange with the evaporator and can circularly supply cooling liquid to the load end.
According to the temperature control method and the temperature control system, the refrigeration system is subjected to cold energy adjustment through the cooperative cooperation of the variable frequency compressor and the throttling mechanism, so that the actual temperature finally approaches to or is equal to the target temperature, and compared with temperature control equipment adopting a fixed frequency compressor without a cold energy adjustment function in the prior art, the energy consumption is reduced, and the accurate control of the temperature of the cooling liquid is realized.
Drawings
FIG. 1 is a flow chart of a temperature control method according to an embodiment of the present application;
FIG. 2 is a schematic diagram of a temperature control system according to an embodiment of the present application;
fig. 3 is a flowchart of a temperature control method according to another embodiment of the present application.
Reference numerals illustrate:
100. a temperature control system; 10. a cooling fluid system; 11. a first pipeline; 12. a second pipeline; 13. a variable frequency pump; 14. a liquid storage tank; 141. a fluid supplementing port; 15. a first temperature sensor; 16. a first pressure sensor; 17. a second temperature sensor; 18. a liquid outlet; 19. a liquid inlet; 20. a refrigeration system; 21. a variable frequency compressor; 22. a condenser; 23. a first throttle valve; 24. a second throttle valve; 25. an evaporator; 26. a variable frequency fan; 27. drying the filter; 28. a third temperature sensor; 29. a fourth temperature sensor; 210. a second pressure sensor; 220. a third pressure sensor; 230. a fourth pressure sensor; 200. and a load end.
Detailed Description
In order to make the above objects, features and advantages of the present application more comprehensible, embodiments accompanied with figures are described in detail below. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present application. This application is, however, susceptible of embodiment in many other forms than those described herein and similar modifications can be made by those skilled in the art without departing from the spirit of the application, and therefore the application is not to be limited to the specific embodiments disclosed below.
In the description of the present application, it should be understood that the terms "center," "longitudinal," "transverse," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," etc. indicate orientations or positional relationships based on the orientation or positional relationships shown in the drawings, are merely for convenience in describing the present application and simplifying the description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be configured and operated in a particular orientation, and therefore should not be construed as limiting the present application.
Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In the description of the present application, the meaning of "plurality" is at least two, such as two, three, etc., unless explicitly defined otherwise.
In this application, unless specifically stated and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; either directly or indirectly, through intermediaries, or both, may be in communication with each other or in interaction with each other, unless expressly defined otherwise. The specific meaning of the terms in this application will be understood by those of ordinary skill in the art as the case may be.
In this application, unless expressly stated or limited otherwise, a first feature "up" or "down" a second feature may be the first and second features in direct contact, or the first and second features in indirect contact via an intervening medium. Moreover, a first feature being "above," "over" and "on" a second feature may be a first feature being directly above or obliquely above the second feature, or simply indicating that the first feature is level higher than the second feature. The first feature being "under", "below" and "beneath" the second feature may be the first feature being directly under or obliquely below the second feature, or simply indicating that the first feature is less level than the second feature.
It will be understood that when an element is referred to as being "fixed" or "disposed" on another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and the like are used herein for illustrative purposes only and are not meant to be the only embodiment.
As described in the background: conventional temperature control devices result in higher energy consumption. The applicant has found that the root cause of the above problems is: the traditional temperature control equipment comprises a fixed-frequency compressor and an electric heater, and the self cold quantity adjusting precision of the temperature control equipment is low. The temperature control equipment has low self cooling capacity adjustment precision, the cooling capacity is not adjusted during partial load, the power consumption of the compressor is high, and the cooling capacity is wasted. The electric heater is adopted to offset redundant cold energy, and the consumption of electric power is increased, so that high energy consumption is caused.
Meanwhile, the temperature control equipment adopting the electric heater and the compressor is used for adjusting the refrigerating capacity according to the heating power of the electric heater. In practical application, the amount of change of the end load is several watts, tens of watts or even hundreds of watts, and the power adjustment of the electric heater cannot meet the requirement, so that the refrigerating capacity adjustment capability cannot meet the requirement, and the temperature control precision is low.
Referring to fig. 1, an embodiment of the present application provides a temperature control method, including the steps of:
s110: acquiring an actual temperature of the cooling fluid in the cooling fluid system 10 (see fig. 2);
the coolant system 10 is a system capable of supplying coolant to the load side 200, the load side 200 is a use side for loading the electronic component under test, and the actual temperature is the temperature of the coolant flowing in the coolant system 10. Specifically, the electronic component is a chip, and the coolant system 10 provides a circulating coolant to the load side 200 to provide a constant or approximately constant cooling temperature to the chip. It should be understood that a non-flowing medium may be used in the cooling liquid system 10, so long as the temperature control effect on the chip can be achieved, and no detailed description is provided herein.
S120: when the absolute value of the difference between the actual temperature and the target temperature is larger than a first preset temperature difference, controlling the opening degree of the throttling mechanism to be unchanged and adjusting the frequency of the variable frequency compressor 21;
the target temperature is a preset temperature, namely the temperature reached by the expected cooling liquid preset by a user. In some embodiments, the actual temperature is the temperature of the liquid outlet 18 of the cooling liquid system 10, that is, the temperature of the cooling liquid provided at the load end 200 by the cooling liquid system 10, and when the cooling liquid does not exchange heat with the electronic components loaded at the load end 200, the set target temperature corresponds to the temperature of the liquid outlet 18 of the cooling liquid. The actual temperature is obtained by a first temperature sensor 15 arranged on a cooling line of the cooling liquid system 10 with a liquid outlet 18. In other embodiments, the actual temperature is the temperature of the inlet 19 of the cooling fluid system 10, that is, the temperature of the cooling fluid flowing back to the cooling fluid system 10 after heat exchange with the load end 200, and the set target temperature corresponds to the temperature of the inlet 19 of the cooling fluid. The actual temperature is obtained by means of a second temperature sensor 17 arranged on a cooling line of the cooling liquid system 10 with a liquid inlet 19.
Here, the target temperature is not limited to a specific one, and may be set as needed. The first preset temperature difference is a preset temperature difference, and in a specific embodiment, the first preset temperature difference is 3 °. Of course, in other embodiments, the first preset temperature difference may be selected according to needs, which is not limited herein.
The inverter compressor 21 is a compressor whose relative rotational speed is constant, and whose rotational speed is continuously adjusted within a certain range by a control means or means, and which can continuously change the output energy. The inverter compressor 21 includes two parts, one part being an inverter controller and the other part being a compressor. The principle of the variable frequency controller is that alternating current in a power grid is converted into square wave pulse to be output, and the rotating speed of a motor driving the compressor can be controlled by adjusting the frequency (namely, the duty ratio) of the square wave pulse. The higher the frequency, the higher the rotational speed.
Controlling the opening degree of the throttle mechanism to be unchanged means that: the throttle mechanism is controlled to keep the initial opening unchanged. Adjusting the frequency of the inverter compressor 21 means: the inverter compressor 21 enters a PID automatic control state.
S130: when the absolute value is smaller than the first preset temperature difference, the frequency of the variable frequency compressor 21 is controlled to be unchanged and the opening degree of the throttling mechanism is adjusted.
The frequency of the inverter compressor 21 is unchanged means that: the inverter compressor 21 is operated at a constant frequency. Adjusting the opening degree of the throttle means: changing the opening degree of the throttling mechanism, the throttling mechanism enters a PID automatic control state, such as adjusting the opening degree of the throttling mechanism or adjusting the opening degree of the throttling mechanism.
Here, the refrigeration system 20 includes the inverter compressor 21 and the throttle mechanism described above, and the coolant system 10 is capable of exchanging heat with the refrigeration system 20, and the throttle mechanism is used to adjust the temperature of the refrigerant in the refrigeration system 20 that is input to the heat exchange portion that exchanges heat with the coolant system 20.
It should be noted that, when the absolute value of the difference between the actual temperature and the target temperature is equal to the first preset temperature difference, neither the throttle mechanism nor the inverter compressor 21 is adjusted.
According to the temperature control method, the refrigerating system 20 is subjected to cold energy adjustment through the cooperative cooperation of the variable frequency compressor 21 and the throttling mechanism, so that the actual temperature finally approaches to or is equal to the target temperature, and compared with temperature control equipment without a cold energy adjustment function by adopting a fixed frequency compressor in the prior art, the energy consumption is reduced, and the accurate control of the temperature of cooling liquid is realized.
In one embodiment, before step S110, the method further includes the steps of:
acquiring the magnitude relation between the actual temperature and the target temperature;
when the actual temperature is less than the target temperature, controlling the refrigeration system 20 to enter a warm-up mode; when the actual temperature is greater than the target temperature, the refrigeration system 20 is controlled to enter a cooling mode.
When the actual temperature is less than the target temperature, the temperature of the coolant is proved to be low, and the refrigeration system 20 is controlled to enter the warm-up mode. When the actual temperature is greater than the target temperature, the temperature of the cooling fluid is proved to be higher, and the refrigeration system 20 is controlled to enter the cooling mode.
Wherein, when the refrigeration system 20 is in the heating mode, the first preset temperature difference is a first heating preset temperature difference; when the refrigeration system 20 is in the cooling mode, the first preset temperature difference is a first cooling preset temperature difference. In one embodiment, the first temperature increase preset temperature difference is equal to the first temperature decrease preset temperature difference. It is contemplated that in other embodiments, the first temperature increase preset temperature difference and the first temperature decrease preset temperature difference may be different.
In one embodiment, when the refrigeration system 20 is in the warm-up mode and the absolute value of the difference between the actual temperature and the target temperature is greater than the first warm-up preset temperature difference, the opening of the second throttle 24 is controlled to be unchanged and the frequency of the inverter compressor 21 is increased.
Further, when the refrigeration system 20 is in the warm-up mode and the absolute value of the difference between the actual temperature and the target temperature is greater than the first warm-up preset temperature difference, the opening degree of the first throttle valve 23 is controlled to be unchanged. Of course, in other embodiments, when the refrigeration system 20 is in the heating mode and the absolute value of the difference between the actual temperature and the target temperature is greater than the first heating preset temperature difference, the opening of the first throttle valve 23 may also be adjusted, which is not limited herein. Specifically, when the refrigeration system 20 is in the warm-up mode and when the absolute value of the difference between the actual temperature and the target temperature is greater than the first warm-up preset temperature difference, the first throttle valve 23 is controlled to be fixed at a default opening (the default opening is the opening when the first throttle valve 23 is in a natural state, at this time, no control is performed on the first throttle valve 23, the first throttle valve 23 is naturally maintained at the opening), the second throttle valve 24 is in an initial opening and the inverter compressor 21 enters the PID automatic control state, the inverter compressor 21 is controlled to be increased in frequency, the heating amount increases as the frequency of the inverter compressor 21 increases, and the coolant temperature increases.
When the refrigeration system 20 is in the warm-up mode and when the absolute value is less than the first warm-up preset temperature difference, the frequency of the inverter compressor 21 is controlled to be unchanged and the opening degree of the second throttle valve 24 is adjusted.
Further, when the refrigeration system 20 is in the warm-up mode and the absolute value of the difference between the actual temperature and the target temperature is smaller than the first warm-up preset temperature difference, the opening degree of the first throttle valve 23 is controlled to be unchanged at the same time. Of course, in other embodiments, when the refrigeration system 20 is in the heating mode and the absolute value of the difference between the actual temperature and the target temperature is less than the first heating preset temperature difference, the opening of the first throttle valve 23 may also be adjusted, which is not limited herein.
Specifically, when the refrigeration system 20 is in the warm-up mode and when the absolute value is smaller than the first warm-up preset temperature difference, the first throttle valve 23 is controlled to be fixed at the default opening, the frequency of the inverter compressor 21 is unchanged, and the second throttle valve 24 is brought into the PID automatic control state.
The throttle mechanism includes a first throttle valve 23 and a second throttle valve 24, the inverter compressor 21, the condenser 22, the first throttle valve 23, and the evaporator 25 are sequentially connected to form a closed circuit of the refrigeration system 20, the refrigeration system 20 exchanges heat with the coolant system 10 through the evaporator 25, and the second throttle valve 24 is provided on a bypass line connecting an outlet end of the inverter compressor 21 and an input end of the evaporator 25.
In one embodiment, when the refrigeration system 20 is in the cooling mode and the absolute value of the difference between the actual temperature and the target temperature is greater than the first cooling preset temperature difference, the opening of the first throttle 23 is controlled to be unchanged and the frequency of the inverter compressor 21 is increased.
Specifically, when the refrigeration system 20 is in the cooling mode and the absolute value of the difference between the actual temperature and the target temperature is greater than the first cooling preset temperature difference, the first throttle valve 23 is controlled to be fixed at an initial opening (the initial opening is different from the default opening, the default opening is the opening of the first throttle valve 23 in the natural uncontrolled state, and the initial opening is the opening of the first throttle valve 23 which is manually controlled to be set) and the inverter compressor 21 enters the PID automatic control state. If the inverter compressor 21 is controlled to increase in frequency according to the absolute value of the difference between the actual temperature and the target temperature, the cooling capacity increases and the cooling liquid temperature decreases as the frequency of the inverter compressor 21 increases.
When the refrigeration system 20 is in the cooling mode and the absolute value is smaller than the first cooling preset temperature difference, the frequency of the inverter compressor 21 is controlled to be unchanged and the opening of the first throttle valve 23 is adjusted.
Specifically, when the refrigeration system 20 is in the cooling mode and when the absolute value is smaller than the first cooling preset temperature difference, the frequency of the inverter compressor 21 is controlled to be unchanged and the first throttle valve 23 is brought into the PID automatic control state.
Further, when the refrigeration system 20 is in the cooling mode and the absolute value is greater than the second preset temperature difference, the frequency of the variable frequency compressor 21 is controlled to be unchanged and the opening of the first throttle valve 23 is adjusted according to the suction superheat degree and/or the actual temperature of the variable frequency compressor 21. When the refrigeration system 20 is in the cooling mode, the frequency of the inverter compressor 21 is controlled to be unchanged and the opening of the first throttle valve 23 is controlled to be unchanged when the absolute value is less than or equal to the second preset temperature difference.
Here, the opening degree of the first throttle valve 23 is controlled in accordance with the suction superheat degree in the refrigeration system 20. The suction superheat degree increases, the opening degree of the first throttle valve 23 increases, the refrigerant flow rate increases, and the refrigerating capacity increases. The suction superheat degree decreases, the opening degree of the first throttle valve 23 decreases, and the refrigerating capacity decreases. When the actual temperature of the coolant supplied to the load side 200 by the coolant system 10 increases, which corresponds to the increase in the suction temperature of the refrigeration system 20 and the increase in the suction superheat, the opening degree of the first throttle valve 23 is increased, so that the cooling capacity is increased, and the actual temperature of the coolant is reduced. The suction superheat degree is preferably adopted for judgment, because the degree of suction superheat degree can directly reflect the opening degree of the first throttle valve 23 in the mode, if the suction superheat degree is higher, the refrigeration capacity provided by the first throttle valve 23 to the evaporator 25 is insufficient, the opening degree of the first throttle valve 23 is smaller, and the opening degree of the first throttle valve 23 needs to be increased to reduce the suction superheat degree.
It should be further noted that the second preset temperature difference is a preset temperature difference, and in a specific embodiment, the second preset temperature difference is 2 °. Of course, in other embodiments, the second preset temperature difference may be selected according to the need, which is not limited herein.
Further, when the refrigeration system 20 is in the cooling mode, the second throttle 24 is controlled to be closed.
In one embodiment, the refrigeration system 20 is in the temperature control mode when the absolute value is less than or equal to the second predetermined temperature difference. In the temperature control mode, the frequency of the inverter compressor 21 is controlled to be unchanged, the first throttle valve 23 is set at a set opening degree, and the opening degree of the second throttle valve 24 is adjusted so that the actual temperature is within a preset temperature range.
In one embodiment, when the target temperature is set to 30 ℃, the cooling mode or the heating mode is used to make the absolute value of the actual temperature and 30 ℃ be less than or equal to the second preset temperature difference, and the refrigeration system 20 will enter the temperature control mode.
Specifically, when the refrigeration system 20 is in the temperature control mode, the variable frequency compressor 21 is controlled to have a constant frequency, the first throttle valve 23 is at a set opening degree, and the second throttle valve 24 is brought into a PID automatic control state. When the suction superheat of the inverter compressor 21 increases and/or the actual temperature of the coolant increases, for example, the opening degree of the second throttle valve 24 is controlled to decrease, the amount of hot gas to the evaporator 25 is decreased, and the cooling amount is increased for decreasing the temperature of the coolant. When the suction superheat of the inverter compressor 21 decreases and/or the actual temperature of the cooling liquid decreases, the opening degree of the second throttle valve 24 is controlled to increase, the amount of hot gas to the evaporator 25 is increased, and the cooling amount is decreased for increasing the temperature of the cooling liquid.
It should be noted that the actual temperature being within the preset temperature range means that: the actual temperature is fluctuated within a certain temperature range, so that the absolute value of the difference value between the actual temperature and the target temperature is smaller than or equal to a second preset temperature difference.
In the temperature control mode, the opening degree of the first throttle valve 23 is different from the opening degrees of the temperature increasing mode and the temperature decreasing mode. When switching from the temperature increasing mode to the temperature controlling mode, the opening degree of the first throttle valve 23 needs to be adjusted from the default opening degree to the set opening degree corresponding to the temperature controlling mode, and then the first throttle valve 23 is kept at the set opening degree. When switching from the cooling mode to the temperature control mode, it is also necessary to adjust the opening degree of the first throttle valve 23 from the opening degree in the cooling mode to a set opening degree, and then to keep the first throttle valve 23 at the set opening degree. In the case of the temperature control mode from the temperature increasing mode, the amount of the first throttle valve 23 is adjusted to the set opening, or the amount of the first throttle valve 23 is adjusted to the set opening from the temperature decreasing mode, and the amount of the first throttle valve 23 is determined according to the target temperature to be reached by the coolant. When the cooling liquid needs to reach a lower temperature control temperature, the required set opening degree is larger; when the coolant is required to reach a higher target temperature, the required set opening degree is smaller.
In the above-described configuration, when the refrigeration system 20 is in the temperature control mode, the opening degree of the first throttle valve 23 is controlled to be constant, and the actual temperature is set within the preset temperature range by adjusting the opening degree of the second throttle valve 24. Compared with the mode that the first throttling valve 23 and the second throttling valve 24 are adjusted simultaneously (the opening degree of the first throttling valve 23 is controlled by the refrigerating system 20 according to the change of the suction superheat degree and/or the actual temperature), if the actual temperature of the cooling liquid is increased, the opening degree of the first throttling valve 23 is increased at the moment, the refrigerating capacity is increased for reducing the temperature of the cooling liquid, when the actual temperature of the cooling liquid is reduced, the opening degree of the first throttling valve 23 is reduced, the refrigerating capacity is reduced, so that the temperature of the cooling liquid is reduced, meanwhile, the second throttling valve 24 controls the hot gas to the evaporator 25, the suction superheat degree of the refrigerating system 20 is increased while the refrigerating capacity is counteracted, the opening degree of the first throttling valve 23 is also increased, the refrigerating capacity is increased, and when the opening degree of the first throttling valve 23 and the second throttling valve 24 are adjusted simultaneously, so that the refrigerating system 20 fluctuates, and the temperature control stability is improved, and when the load is changed, the opening degree of the second throttling valve 24 is controlled, namely the opening degree of the second throttling valve 24 is controlled, so that the refrigerating capacity is matched with the refrigerating capacity is provided by the second throttling valve 24, and the refrigerating capacity 200 is matched with the refrigerating capacity, and the working end 200 is obtained.
In some embodiments, the temperature control method further comprises the steps of:
according to the trend of the actual condensing pressure of the condenser 22, the rotation speed of the variable frequency fan 26 is controlled so that the actual condensing pressure is within the range of the preset condensing pressure.
The compressor of the refrigeration system 20 is the variable frequency compressor 21, the condensation load varies with the frequency of the variable frequency compressor 21, but the heat exchange area of the condenser 22 is fixed, if the rotation speed of the fan is fixed, the actual condensation pressure in the condenser 22 will fluctuate greatly, and the heat exchange amount is not matched with the condensation load. The variable frequency fan 26 is adopted by the refrigeration system 20, the rotation speed of the variable frequency fan 26 changes along with the change of the actual condensing pressure, for example, when the actual condensing pressure increases, the heat exchange amount required by the refrigeration system 20 increases, the variable frequency fan 26 is controlled to increase in frequency, and the rotation speed of the variable frequency fan 26 increases, so that the actual condensing pressure of the condenser 22 is kept within the up-and-down fluctuation range of the preset condensing pressure. Specifically, the variable frequency fan 26 enters a PID automatic control state according to a preset condensing pressure. In the above cooling mode, when the frequency of the inverter compressor 21 increases, the exhaust pressure of the inverter compressor will correspondingly increase, and the actual condensing pressure of the condenser 22 will also increase, at this time, the PID controller controls the inverter fan 26 to increase in frequency, so as to satisfy the heat exchange amount required by the refrigeration system 20 and ensure that the actual condensing pressure is maintained within the preset condensing pressure range, so that the macroscopic appearance is that the rotational speed of the inverter fan 26 increases with the increase of the frequency of the inverter compressor 21. In the foregoing heating mode, when the frequency of the inverter compressor 21 increases, the exhaust pressure will correspondingly increase, but since the bypass line where the second throttle valve 24 is located will lead part of the exhaust split flow to the evaporator 25, the actual condensing pressure will not fluctuate too much at this time, and therefore the rotational speed of the inverter fan 26 will not change too much. When the actual condensing pressure of the condenser 22 is smaller than the minimum value of the preset condensing pressure, the variable frequency fan 26 is turned off, and otherwise, turned on.
Here, the condensing pressure is a pressure value generated in the condenser 22 during the flow of the refrigerant. Typically, this actual condensing pressure is detected by a fourth pressure sensor 230 provided at the outlet end of the condenser 22. The variable frequency fan 26 adopts a variable frequency speed control device, and changes the air quantity by changing the rotating speed of the fan so as to adapt to the requirements of the production process.
In one embodiment, the temperature control method further comprises the steps of:
the rotation speed of the variable frequency pump 13 is controlled according to the parameters of the cooling liquid required by the load end 200. Wherein the coolant system 10 comprises a variable frequency pump 13, the variable frequency pump 13 being adapted to provide a driving force for the flow of coolant in the coolant system 10.
Here, the parameters of the coolant required by the load end 200 include the flow rate and the pressure of the coolant. The variable frequency pump 13 is capable of varying the rotational speed relative to a circulating pump with a constant rotational speed to accommodate different production processes. Specifically, the pressure of the cooling liquid is obtained by the first pressure sensor 16 provided on the cooling line thereof.
Since the load end 200 is different according to the electronic components, the required parameters of the cooling liquid are different. By the above arrangement, the rotation speed of the variable frequency pump 13 is controlled according to the parameters of the cooling liquid required by the load end 200, so that the parameters of the cooling liquid can meet the requirements of cooling different electronic components.
Referring to fig. 3, the temperature control method of the present application will be described with reference to a specific example, in which the first preset temperature difference is set to 3 ℃, and the second preset temperature difference is set to 2 ℃:
the target temperature, pressure, and flow rate of the coolant required for the load side 200 are set.
The variable frequency pump 13 is turned on for circulation, the variable frequency compressor 21 is turned on after the time delay is 60S, and the mode judgment is entered.
When the actual temperature of the cooling fluid is less than the target temperature, the refrigeration system 20 enters a warm-up mode. In the warm-up mode, the first throttle valve 23 is at a default opening degree, and the second throttle valve 24 is at an initial opening degree. When the absolute value of the actual temperature and the target temperature is greater than 3 ℃, the first throttle valve 23 is at a default opening, the inverter compressor 21 is in a PID automatic control state, and the second throttle valve 24 is at an initial opening. When the absolute value of the actual temperature and the target temperature is less than 3 ℃, the variable frequency compressor 21 is fixed in frequency, the first throttle valve 23 is in a default opening degree, and the second throttle valve 24 is in a PID automatic control state.
When the actual temperature of the cooling fluid is greater than the target temperature, the refrigeration system 20 enters a cooling mode. In the cooling mode, the second throttle valve 24 is closed. When the absolute value of the actual temperature and the target temperature is greater than 3 ℃, the inverter compressor 21 is in the PID automatic control state, and the first throttle valve 23 is in the initial opening. When the absolute value of the actual temperature and the target temperature is less than 3 ℃, the variable frequency compressor 21 is fixed in frequency, and the first throttle valve 23 is in a PID automatic control state according to the suction superheat degree and/or the actual temperature of the variable frequency compressor 21.
When the absolute value is 2 ℃ or less, the refrigeration system 20 switches to the temperature control mode. In the temperature control mode, the variable frequency compressor 21 is fixed in frequency, the opening of the first throttle valve 23 is controlled to be unchanged, and the actual temperature is in a preset temperature range by adjusting the opening of the second throttle valve 24. Specifically, in the temperature control mode, the opening degree of the second throttle valve 24 is adjusted to be small when the actual temperature rises, and the opening degree of the second throttle valve 24 is adjusted to be large when the actual temperature falls.
Referring to fig. 2, an embodiment of the present application provides a temperature control system 100 for the above temperature control method, which includes a refrigeration system 20 and a cooling liquid system 10, wherein the cooling liquid system 10 can exchange heat with the refrigeration system 20 and can circulate and provide cooling liquid to a load terminal 200, so that electronic components located at the load terminal 200 meet a test temperature requirement.
Specifically, the temperature control system 100 further includes an electronic control system that is capable of controlling the refrigeration system 20 to cooperate with the coolant system 10.
The refrigeration system 20 includes a variable frequency compressor 21, a condenser 22, a throttling mechanism including a first throttling valve 23 and a second throttling valve 24, and an evaporator 25. Specifically, the first throttle valve 23 and the second throttle valve 24 are both electronic expansion valves. The inverter compressor 21, the condenser 22, the first throttle valve 23 and the evaporator 25 are sequentially connected to form a closed circuit of the refrigeration system 20. The inverter compressor 21 has a return air end and an outlet air end that are in communication with each other, and the evaporator 25 includes a first refrigerant passage that is part of the closed circuit of the refrigeration system 20 and a second refrigerant passage that is part of the closed circuit of the coolant system 10, wherein the first refrigerant passage has an input end and an output end that are in communication with each other. The second throttle valve 24 is provided on a bypass line connecting the outlet end of the inverter compressor 21 with the input end of the evaporator 25. The coolant system 10 exchanges heat with the evaporator 25 for supplying coolant to the load side 200.
During refrigeration, the inverter compressor 21 sucks high-temperature low-pressure refrigerant gas at the output end of the evaporator 25, compresses the refrigerant into high-temperature high-pressure refrigerant gas through compression work, and discharges the high-temperature high-pressure refrigerant gas to the condenser 22 through the gas outlet end. When passing through the condenser 22, the refrigerant is condensed into medium-temperature high-pressure refrigerant liquid by the condenser 22, throttled and depressurized into low-temperature low-pressure refrigerant liquid by the first throttle valve 23, and finally enters the evaporator 25 again from the input end of the evaporator 25. As the cooling liquid system 10 exchanges heat with the evaporator 25, the low-temperature low-pressure refrigerant absorbs heat of the cooling liquid in the cooling liquid system 10 in the evaporator 25, evaporates itself into a high-temperature low-pressure refrigerant gas, and enters the inverter compressor 21 again from the return air end of the inverter compressor 21. The cooling liquid in the cooling liquid system 10 flows to the load end 200 through the self-cooling pipeline after the temperature of the cooling liquid is reduced, and then flows from the load end 200 to the cooling liquid system 10 to exchange heat with the evaporator 25, so that the circulation is repeated.
During heating, the high-temperature and high-pressure refrigerant gas discharged by the variable-frequency compressor 21 passes through the second throttle valve 24, is throttled and depressurized to be high-temperature and low-pressure refrigerant gas, enters the evaporator 25, the high-temperature and low-pressure refrigerant gas in the evaporator 25 transfers heat to cooling liquid, the temperature of the cooling liquid is increased, the refrigerant is cooled to be low-temperature and low-pressure gas and then is sucked by the variable-frequency compressor 21, the variable-frequency compressor 21 does work, and the refrigerant is circulated repeatedly and continuously to finish heating.
The temperature control system 100 can perform cold energy adjustment on the refrigerating system 20 through the cooperative cooperation of the variable frequency compressor 21 and the throttling mechanism, and finally enables the actual temperature to approach the target temperature or be equal to the target temperature.
Further, the refrigeration system 20 further includes a variable frequency fan 26, where the variable frequency fan 26 is used for heat dissipation of the condenser 22, and is capable of changing the rotational speed according to the trend of the actual condensing pressure, so that the actual condensing pressure of the condenser 22 is within the preset condensing pressure range.
In one embodiment, the refrigeration system 20 further includes a dry filter 27, the dry filter 27 being disposed between the condenser 22 and the first throttle valve 23 for absorbing moisture in the refrigerant and filtering impurities in the refrigerant. That is, the high-pressure refrigerant liquid formed by condensation in the condenser 22 is first dried by the dry filter 27 to remove moisture and filtered impurities, and then enters the first throttle valve 23 to be throttled.
Still further, the refrigeration system 20 also includes a third temperature sensor 28, a fourth temperature sensor 29, a second pressure sensor 210, and a third pressure sensor 220. The third temperature sensor 28 and the second pressure sensor 210 are disposed on the refrigeration pipeline between the inverter compressor 21 and the condenser 22, and are used for detecting the temperature and the pressure of the high-pressure refrigerant gas compressed by the inverter compressor 21. The fourth temperature sensor 29 and the third pressure sensor 220 are disposed on the refrigerating pipeline between the evaporator 25 and the inverter compressor 21, for detecting the temperature and pressure of the high-temperature low-pressure refrigerant gas flowing to the inverter compressor 21 through the evaporator 25, respectively.
In some embodiments, refrigeration system 20 further includes a fourth pressure sensor 230, fourth pressure sensor 230 being disposed on the refrigeration circuit between condenser 22 and dry filter 27 for detecting the pressure of the high pressure refrigerant liquid condensed by condenser 22.
In one embodiment, the cooling fluid system 10 includes a cooling pipeline and a variable frequency pump 13, the cooling pipeline can exchange heat with the refrigerating system 20, and the variable frequency pump 13 is disposed on the cooling pipeline to provide driving force for circulating the cooling fluid in the cooling pipeline. In this way, the rotation speed of the variable frequency pump 13 can be controlled according to the parameters of the cooling liquid required by the load end 200, so that the parameters of the cooling liquid can meet the requirements of cooling different electronic components.
Further, the coolant system 10 further includes a tank 14, and the tank 14 has a fluid replenishment port 141, and the coolant can be replenished into the tank 14 through the fluid replenishment port 141. The cooling pipeline comprises a first pipeline 11 and a second pipeline 12, the first pipeline 11 is communicated with a second refrigerant channel of the evaporator 25 to exchange heat with the first refrigerant channel, the second pipeline 12 is connected with the liquid storage tank 14 and the first pipeline 11, and the variable frequency pump 13 is arranged on the first pipeline 11. In this way, a part of the cooling liquid after heat exchange with the evaporator 25 flows to the liquid storage tank 14, flows to the first pipeline 11 through the liquid storage tank 14, and flows to the load end 200 through the first pipeline 11 for heat exchange, and the other part directly flows to the load end 200 through the first pipeline 11 for heat exchange.
The coolant system 10 further comprises a first temperature sensor 15, a first pressure sensor 16 and a second temperature sensor 17. The coolant system 10 has a liquid outlet 18 for the coolant to flow to the load port 200, and a liquid inlet 19 for the coolant to flow back from the load port 200. The first temperature sensor 15 and the first pressure sensor 16 are provided on a cooling line having a liquid outlet 18, and the second temperature sensor 17 is provided on a cooling line having a liquid inlet 19. The first temperature sensor 15 and the first pressure sensor 16 are used for detecting the temperature and the pressure of the coolant flowing to the load end 200, respectively, and the second temperature sensor 17 is used for detecting the temperature of the coolant flowing back to the coolant system 10 from the load end 200.
In some embodiments, the temperature control system 100 further includes a housing, and the refrigeration system 20 and the coolant system 10 are disposed in the housing. Specifically, the casing is hollow cuboid structure. The casing includes bottom plate, first curb plate, second curb plate, third curb plate, fourth curb plate and roof, and first curb plate, second curb plate, third curb plate and fourth curb plate all are located the same side of bottom plate and extend towards same direction mutually bottom plate, and the roof lid is located first curb plate, second curb plate, third curb plate and fourth curb plate, and bottom plate, first curb plate, second curb plate, third curb plate, fourth curb plate and roof enclose jointly and establish formation accommodation space. The housing further includes a partition plate disposed in the accommodating space to divide the accommodating space into a plurality of subspaces, thereby facilitating the arrangement of the components of the refrigeration system 20 and the coolant system 10.
In one embodiment, the first side plate and the third side plate are disposed opposite to each other and located at two sides of the housing in the length direction, and the second side plate, the fourth side plate and the top plate are detachably mounted on the first side plate and the third side plate, so that maintenance of the internal structure is facilitated.
The temperature control method and the temperature control system 100 provided by the application have the following beneficial effects:
1. the refrigeration system 20 is subjected to cold energy adjustment through the cooperative cooperation of the variable frequency compressor 21 and the throttling mechanism, so that the actual temperature finally approaches to or is equal to the target temperature, and compared with temperature control equipment without a cold energy adjustment function by adopting a fixed frequency compressor in the prior art, the temperature control device realizes accurate control of the temperature of cooling liquid.
2. In the temperature control mode, the first throttle valve 23 is set at a set opening degree, the variable frequency compressor 21 is fixed in frequency, and the opening degree of the second throttle valve 24 is controlled to provide matched refrigerant, namely the refrigerating system 20 can provide matched refrigerating capacity with a load by controlling the opening degree of the second throttle valve 24, so that the load end 200 obtains stable working temperature.
3. The variable frequency compressor 21, the variable frequency pump 13, the variable frequency fan 26 and the like adopt a variable frequency design, so that partial load operation can be performed according to actual demands, energy waste is avoided, and in addition, when the variable frequency system runs at full load, the operation power consumption can be reduced by the variable frequency system, so that energy conservation is realized.
The technical features of the above-described embodiments may be arbitrarily combined, and all possible combinations of the technical features in the above-described embodiments are not described for brevity of description, however, as long as there is no contradiction between the combinations of the technical features, they should be considered as the scope of the description.
The above examples merely represent a few embodiments of the present application, which are described in more detail and are not to be construed as limiting the scope of the invention. It should be noted that it would be apparent to those skilled in the art that various modifications and improvements could be made without departing from the spirit of the present application, which would be within the scope of the present application. Accordingly, the scope of protection of the present application is to be determined by the claims appended hereto.
Claims (11)
1. A method of temperature control comprising the steps of:
acquiring an actual temperature of the cooling fluid in the cooling fluid system (10);
when the absolute value of the difference between the actual temperature and the target temperature is larger than a first preset temperature difference, controlling the opening degree of the throttling mechanism to be unchanged and adjusting the frequency of the variable frequency compressor (21);
when the absolute value is smaller than the first preset temperature difference, controlling the frequency of the variable frequency compressor (21) to be unchanged and adjusting the opening of the throttling mechanism;
The cooling liquid system (10) can exchange heat with the cooling liquid system (20) and can provide cooling liquid for a load end (200), the cooling liquid system (20) comprises the variable frequency compressor (21) and the throttling mechanism, and the throttling mechanism is used for adjusting the temperature of a refrigerant input to a heat exchange part which exchanges heat with the cooling liquid system (10) in the cooling liquid system (20).
2. The temperature control method according to claim 1, characterized by further comprising the step of, before controlling the opening degree of the throttle mechanism and adjusting the frequency of the inverter compressor (21) when the absolute value of the difference between the actual temperature and the target temperature is greater than a first preset temperature difference:
acquiring the magnitude relation between the actual temperature and the target temperature;
controlling the refrigeration system (20) to enter a warm-up mode when the actual temperature is less than the target temperature; controlling the refrigeration system (20) to enter a cooling mode when the actual temperature is greater than the target temperature;
wherein, when the refrigeration system (20) is in the warm-up mode, the first preset temperature difference is a first warm-up preset temperature difference; when the refrigeration system (20) is in the cooling mode, the first preset temperature difference is a first cooling preset temperature difference.
3. A temperature control method according to claim 2, characterized by controlling the opening degree of a second throttle valve (24) unchanged and increasing the frequency of the inverter compressor (21) when the refrigeration system (20) is in the warm-up mode and when the absolute value of the difference of the actual temperature and the target temperature is greater than the first warm-up preset temperature difference;
when the refrigerating system (20) is in the heating mode and the absolute value is smaller than the first heating preset temperature difference, controlling the frequency of the variable frequency compressor (21) to be unchanged and adjusting the opening of the second throttle valve (24);
the throttling mechanism comprises a second throttling valve (24), and the second throttling valve (24) is arranged on a bypass pipeline which is used for communicating the air outlet end of the variable frequency compressor (21) with the input end of the evaporator (25).
4. A temperature control method according to claim 3, characterized in that the throttle mechanism further comprises a first throttle valve (23), the inverter compressor (21), the condenser (22), the first throttle valve (23) and the evaporator (25) are sequentially communicated to form a closed loop of the refrigeration system (20), and the refrigeration system (20) exchanges heat with the coolant system (10) through the evaporator (25);
When the refrigerating system (20) is in the heating mode, the opening degree of the first throttle valve (23) is controlled to be unchanged.
5. A temperature control method according to claim 2, characterized by controlling the opening degree of a first throttle valve (23) unchanged and increasing the frequency of the inverter compressor (21) when the refrigeration system (20) is in the cooling mode and when the absolute value of the difference between the actual temperature and the target temperature is greater than the first cooling preset temperature difference;
when the refrigerating system (20) is in the cooling mode and the absolute value is smaller than the first cooling preset temperature difference, controlling the frequency of the variable frequency compressor (21) to be unchanged and adjusting the opening of the first throttle valve (23);
the throttling mechanism comprises a first throttling valve (23), the variable frequency compressor (21), a condenser (22), the first throttling valve (23) and an evaporator (25) are sequentially communicated to form a closed loop of the refrigerating system (20), and the refrigerating system (20) exchanges heat with the cooling liquid system (10) through the evaporator (25).
6. The temperature control method according to claim 5, wherein when the refrigeration system (20) is in the cooling mode and when the absolute value is smaller than the first cooling preset temperature difference, controlling the frequency of the inverter compressor (21) to be constant and adjusting the opening degree of the first throttle valve (23) includes the steps of:
When the absolute value is larger than a second preset temperature difference, controlling the frequency of the variable frequency compressor (21) to be unchanged and adjusting the opening of the first throttle valve (23) according to the suction superheat degree of the variable frequency compressor (21) and/or the actual temperature;
when the absolute value is smaller than or equal to the second preset temperature difference, controlling the frequency of the variable frequency compressor (21) to be unchanged and controlling the opening of the first throttle valve (23) to be unchanged;
the second preset temperature difference is smaller than the first preset temperature difference.
7. The temperature control method according to claim 5, characterized by controlling a second throttle valve (24) to be closed when the refrigeration system (20) is in the cooling mode;
the throttling mechanism further comprises a second throttling valve (24), and the second throttling valve (24) is arranged on a bypass pipeline which is used for communicating the air outlet end of the variable frequency compressor (21) with the input end of the evaporator (25).
8. The temperature control method according to any one of claims 1 to 7, wherein the refrigeration system (20) is in a temperature control mode when the absolute value is equal to or less than a second preset temperature difference;
in the temperature control mode, controlling the frequency of the variable frequency compressor (21) to be unchanged, controlling the first throttle valve (23) to be in a set opening degree to be unchanged, and adjusting the opening degree of the second throttle valve (24) so as to enable the actual temperature to be in a preset temperature range;
The throttling mechanism comprises a first throttling valve (23) and a second throttling valve (24), the variable frequency compressor (21), a condenser (22), the first throttling valve (23) and an evaporator (25) are sequentially communicated to form a closed loop of the refrigerating system (20), the refrigerating system (20) exchanges heat with the cooling liquid system (10) through the evaporator (25), and the second throttling valve (24) is arranged on a bypass pipeline which communicates an air outlet end of the variable frequency compressor (21) with an input end of the evaporator (25); the second preset temperature difference is smaller than the first preset temperature difference.
9. The temperature control method according to claim 1, characterized by further comprising the step of:
according to the change trend of the actual condensing pressure of the condenser (22), controlling the rotating speed of the variable frequency fan (26) so that the actual condensing pressure is in the range of the preset condensing pressure;
the refrigeration system (20) further comprises a condenser (22) and a variable frequency fan (26), and the variable frequency fan (26) is used for radiating heat of the condenser (22).
10. The temperature control method according to claim 1, characterized by further comprising the step of:
controlling the rotating speed of the variable frequency pump (13) according to the parameters of the cooling liquid required by the load end (200);
Wherein the cooling fluid system (10) comprises a variable frequency pump (13), the variable frequency pump (13) being adapted to provide a driving force for flowing a cooling fluid in the cooling fluid system (10).
11. A temperature control system for use in the temperature control method according to any one of claims 1 to 10, comprising:
the refrigerating system (20) comprises a variable-frequency compressor (21), an evaporator (25), a condenser (22) and a throttling mechanism, wherein the throttling mechanism comprises a first throttling valve (23) and a second throttling valve (24), the variable-frequency compressor (21), the condenser (22), the first throttling valve (23) and the evaporator (25) are sequentially communicated to form a closed loop of the refrigerating system (20), the second throttling valve (24) is arranged on a bypass pipeline, and the bypass pipeline connects an air outlet end of the variable-frequency compressor (21) with an input end of the evaporator (25);
and the cooling liquid system (10) is used for exchanging heat with the evaporator (25) and can circularly supply cooling liquid to the load end (200).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310091467.0A CN116149392A (en) | 2023-01-17 | 2023-01-17 | Temperature control method and system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310091467.0A CN116149392A (en) | 2023-01-17 | 2023-01-17 | Temperature control method and system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN116149392A true CN116149392A (en) | 2023-05-23 |
Family
ID=86338531
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202310091467.0A Pending CN116149392A (en) | 2023-01-17 | 2023-01-17 | Temperature control method and system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN116149392A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117053448A (en) * | 2023-10-12 | 2023-11-14 | 哲弗智能系统（上海）有限公司 | Method, device and equipment for controlling temperature of cooling liquid of liquid cooling unit |
| CN117219904A (en) * | 2023-08-31 | 2023-12-12 | 南方电网调峰调频(广东)储能科技有限公司 | Refrigeration control method, device and system of liquid cooling system and storage medium |
-
2023
- 2023-01-17 CN CN202310091467.0A patent/CN116149392A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117219904A (en) * | 2023-08-31 | 2023-12-12 | 南方电网调峰调频(广东)储能科技有限公司 | Refrigeration control method, device and system of liquid cooling system and storage medium |
| CN117219904B (en) * | 2023-08-31 | 2024-04-30 | 南方电网调峰调频(广东)储能科技有限公司 | Refrigeration control method, device and system of liquid cooling system and storage medium |
| CN117053448A (en) * | 2023-10-12 | 2023-11-14 | 哲弗智能系统（上海）有限公司 | Method, device and equipment for controlling temperature of cooling liquid of liquid cooling unit |
| CN117053448B (en) * | 2023-10-12 | 2024-02-20 | 哲弗智能系统（上海）有限公司 | Method, device and equipment for controlling temperature of cooling liquid of liquid cooling unit |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN116149392A (en) | Temperature control method and system | |
| CN108700359B (en) | Compressor capacity modulation system for multiple compressors | |
| US7600390B2 (en) | Method and apparatus for control of carbon dioxide gas cooler pressure by use of a two-stage compressor | |
| CN101970953B (en) | Carbon dioxide refrigerant vapor compression system | |
| CN110906477B (en) | Efficient and stable magnetic suspension water chilling unit, control method and device | |
| JP5707621B2 (en) | Constant temperature liquid circulation device and operation method thereof | |
| KR101513768B1 (en) | Air conditioning apparatus | |
| CN103380334B (en) | Freezing cycle device | |
| CN104653444B (en) | Method and device for controlling starting of variable-frequency air conditioner | |
| AU2017291682B2 (en) | Vector drive for vapor compression systems | |
| EP2616749A2 (en) | System and method for controlling an economizer circuit | |
| JP2009139014A (en) | Air conditioner and operation control method for it | |
| CN114576817B (en) | Air conditioner control method | |
| CN111637086A (en) | Centrifugal compressor air supply system for gas bearing support | |
| WO2014196662A1 (en) | Constant-temperature liquid circulation device and method for adjusting temperature of constant-temperature liquid | |
| KR101166385B1 (en) | A air conditioning system by water source and control method thereof | |
| CN201047687Y (en) | Hot gas bypass back-out concurrent heating defrost constant temperature hot-water system | |
| KR101409740B1 (en) | Chiller for semiconductor manufacturing device | |
| CN115309056A (en) | Control method of multiple water chilling units | |
| RU2488750C2 (en) | Refrigerator with control of specified settings | |
| CN219531250U (en) | Variable air volume high-low temperature control device | |
| CN219392531U (en) | Temperature control device of temperature verification box | |
| EP1508752A1 (en) | Thermohygrostat-type air conditioner with means for controlling evaporation temperature | |
| CN114508808B (en) | Magnetic suspension variable frequency water chilling unit | |
| JP7255708B2 (en) | Air conditioner outdoor unit, air conditioner, and control method for air conditioner outdoor unit |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |