CN116412150A - Centrifugal pump control method and device, equipment, system, air conditioner and storage medium - Google Patents

Centrifugal pump control method and device, equipment, system, air conditioner and storage medium Download PDF

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Publication number
CN116412150A
CN116412150A CN202310392281.9A CN202310392281A CN116412150A CN 116412150 A CN116412150 A CN 116412150A CN 202310392281 A CN202310392281 A CN 202310392281A CN 116412150 A CN116412150 A CN 116412150A
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China
Prior art keywords
centrifugal pump
supercooling degree
parameter
current
cooling liquid
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CN202310392281.9A
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Chinese (zh)
Inventor
高兵
井汤博
王剑
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Beijing Youzhuju Network Technology Co Ltd
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Beijing Youzhuju Network Technology Co Ltd
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Priority to CN202310392281.9A priority Critical patent/CN116412150A/en
Publication of CN116412150A publication Critical patent/CN116412150A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0066—Control, e.g. regulation, of pumps, pumping installations or systems by changing the speed, e.g. of the driving engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/5866—Cooling at last part of the working fluid in a heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid pumps
    • 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
    • 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)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

The present disclosure discloses a centrifugal pump control method and apparatus, a device, a system, an air conditioner and a storage medium, the method comprising: and obtaining the supercooling degree parameter of the cooling liquid at the inlet of the centrifugal pump. And when the supercooling degree parameter of the cooling liquid does not meet the operation requirement of the centrifugal pump, controlling the centrifugal pump to run at a reduced speed. And controlling a heat exchange assembly to adjust the temperature of the cooling liquid at the inlet of the centrifugal pump from the current temperature to a target temperature based on the current supercooling degree determined by the cooling liquid supercooling degree parameter, wherein the target temperature is matched with the operation requirement of the centrifugal pump. The centrifugal pump control method is used for realizing active regulation and control of the cooling liquid at the inlet of the centrifugal pump so as to reduce cavitation risk of the centrifugal pump.

Description

Centrifugal pump control method and device, equipment, system, air conditioner and storage medium
Technical Field
The disclosure relates to the technical field of refrigeration, in particular to a centrifugal pump control method, a centrifugal pump control device, a centrifugal pump control equipment, a centrifugal pump control system, an air conditioner and a storage medium.
Background
In a centrifugal fluorine pump air conditioning system of an internet data center (Internet Data Center, IDC for short), due to the limitation of the working principle of the centrifugal fluorine pump, a necessary cavitation margin needs to be provided at the inlet of the centrifugal fluorine pump to ensure that the centrifugal fluorine pump is not damaged by the impact of bubbles during long-term operation.
The supercooling degree of the inlet of the centrifugal fluorine pump at present mainly depends on the system integration capability of air conditioning equipment manufacturers, the refrigerant state of the inlet of the centrifugal fluorine pump cannot be actively regulated and controlled, and a large cavitation risk exists in the mode switching or the process of severe fluctuation of the load capacity.
Disclosure of Invention
The disclosure aims to provide a centrifugal pump control method, a device, equipment, a system, an air conditioner and a storage medium, which are used for realizing active regulation and control of cooling liquid at an inlet of a centrifugal pump so as to reduce cavitation risk of the centrifugal pump.
In order to achieve the above object, the present disclosure provides a centrifugal pump control method including:
and obtaining the supercooling degree parameter of the cooling liquid at the inlet of the centrifugal pump.
And when the supercooling degree parameter of the cooling liquid does not meet the operation requirement of the centrifugal pump, controlling the centrifugal pump to run at a reduced speed.
And controlling a heat exchange assembly to adjust the temperature of the cooling liquid at the inlet of the centrifugal pump from the current temperature to a target temperature based on the current supercooling degree determined by the cooling liquid supercooling degree parameter, wherein the target temperature is matched with the operation requirement of the centrifugal pump.
Compared with the prior art, in the centrifugal pump control method, the cooling liquid supercooling degree parameter of the centrifugal pump inlet is obtained and is sent to the controller, and after the controller receives the cooling liquid supercooling degree parameter, whether the cooling liquid supercooling degree parameter meets the running requirement of the centrifugal pump can be judged. When the supercooling degree parameter of the cooling liquid does not meet the running requirement of the centrifugal pump, the centrifugal pump is possibly at cavitation risk, and the controller can control the centrifugal pump to run in a decelerating mode, so that the probability of cavitation risk of the centrifugal pump is reduced, and the requirement of the centrifugal pump on cavitation allowance is reduced.
Meanwhile, the controller can also control the heat exchange assembly to adjust the temperature of the cooling liquid at the inlet of the centrifugal pump from the current temperature to the target temperature based on the current supercooling degree of the cooling liquid at the inlet of the centrifugal pump determined by the supercooling degree parameter of the cooling liquid, so that the supercooling degree of the cooling liquid at the inlet of the centrifugal pump is improved, the state of the cooling liquid at the inlet of the centrifugal pump is actively adjusted, the cavitation allowance of the centrifugal pump is increased, the probability of cavitation risk of the centrifugal pump is reduced, and the centrifugal pump is enabled to be far away from the cavitation risk as far as possible.
The present disclosure also provides a centrifugal pump control apparatus including:
and the acquisition module is used for acquiring the supercooling degree parameter of the cooling liquid at the inlet of the centrifugal pump.
And the control module is used for controlling the centrifugal pump to run at a reduced speed when the supercooling degree parameter of the cooling liquid does not meet the running requirement of the centrifugal pump. The control module is also used for controlling the heat exchange assembly to adjust the temperature of the cooling liquid at the inlet of the centrifugal pump from the current temperature to the target temperature based on the current supercooling degree determined by the cooling liquid supercooling degree parameter, and the target temperature is matched with the operation requirement of the centrifugal pump.
Compared with the prior art, the beneficial effects of the centrifugal pump control device provided by the disclosure are the same as those of the centrifugal pump control method according to the technical scheme, and the description is omitted here.
The present disclosure also provides an electronic device, including:
a processor. The method comprises the steps of,
a memory storing a program.
Wherein the program comprises instructions which, when executed by the processor, cause the processor to perform a centrifugal pump control method according to the above.
Compared with the prior art, the beneficial effects of the electronic equipment provided by the disclosure are the same as those of the centrifugal pump control method according to the technical scheme, and the description is omitted here.
The present disclosure also provides a non-transitory computer-readable storage medium storing computer instructions for causing the computer to execute the above-described centrifugal pump control method.
Compared with the prior art, the beneficial effects of the non-transitory computer readable storage medium provided by the disclosure are the same as those of the centrifugal pump control method according to the above technical scheme, and are not repeated here.
The present disclosure also provides a centrifugal pump system comprising: the centrifugal pump comprises a detection assembly, a heat exchange assembly, a centrifugal pump and a controller which is respectively in communication connection with the detection assembly, the heat exchange assembly and the centrifugal pump, wherein the controller is the centrifugal pump control device.
Compared with the prior art, the beneficial effects of the centrifugal pump system provided by the disclosure are the same as those of the centrifugal pump control method according to the technical scheme, and the description is omitted here.
The disclosure also provides an air conditioner comprising the centrifugal pump system.
Compared with the prior art, the beneficial effects of the air conditioner provided by the disclosure are the same as those of the centrifugal pump control method according to the technical scheme, and the description is omitted here.
Drawings
The accompanying drawings, which are included to provide a further understanding of the disclosure, illustrate and explain the present disclosure, and together with the description serve to explain the present disclosure. In the drawings:
fig. 1 is a schematic view of a part of a related art centrifugal fluorine pump air conditioning system;
FIG. 2 is a schematic diagram of an air-conditioning structure in an embodiment of the present disclosure;
FIG. 3A is a schematic diagram of a centrifugal pump system in an embodiment of the present disclosure;
FIG. 3B is another schematic diagram of a centrifugal pump system in an embodiment of the present disclosure;
FIG. 4 is a flow chart of a method of controlling a centrifugal pump in an embodiment of the present disclosure;
FIG. 5 is a block schematic diagram of the modules of a centrifugal pump control apparatus in an embodiment of the present disclosure;
FIG. 6 is a schematic block diagram of a chip in an embodiment of the disclosure;
fig. 7 is a block diagram of an electronic device that can be used to implement embodiments of the present disclosure.
Detailed Description
In order to make the technical problems, technical solutions and advantageous effects to be solved by the present disclosure more clear, the present disclosure is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present disclosure and are not intended to limit the present disclosure.
It will be understood that when an element is referred to as being "mounted" or "disposed" on another element, it can be directly on the other element or be indirectly on the other element. When an element is referred to as being "connected to" another element, it can be directly connected to the other element or be indirectly connected to the other element.
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 one or more such feature. In the description of the present disclosure, the meaning of "a plurality" is two or more, unless explicitly defined otherwise. The meaning of "a number" is one or more than one unless specifically defined otherwise.
In the description of the present disclosure, it should be understood that the directions or positional relationships indicated by the terms "upper", "lower", "front", "rear", "left", "right", etc., are based on the directions or positional relationships shown in the drawings, are merely for convenience in describing the present disclosure and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present disclosure.
In the description of the present disclosure, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communicated with the inside of two elements or the interaction relationship of the two elements. The specific meaning of the terms in this disclosure will be understood by those of ordinary skill in the art as the case may be.
The refrigeration scheme of the internet data center (Internet Data Center, IDC for short) is iteratively updated, and the method is evolved from a Direct expansion (DX) scheme of 1.0 to a concentrated chilled water scheme of 2.0, and then to a current air-cooled energy-saving scheme of a fluorine pump of 3.0. The core device in the air-cooling energy-saving scheme of the fluorine pump is the fluorine pump, and the reliability of the device directly influences the refrigeration stability of the data machine room. However, the fluorine pump is used as a new thing applied in the IDC field, the application time is not long, the application cases are not many, and a certain risk exists in the maturity of the product scheme.
Currently, there are many types of fluorine pumps, including centrifugal type, gear type, vortex type, and vortex type. Centrifugal and gear type are currently used more. Among them, gear type fluorine pumps are more applied as they have potential risks due to engagement wear for long-term operation. The centrifugal fluorine pump is limited by the working principle, the inlet of the centrifugal fluorine pump needs to provide necessary cavitation allowance, otherwise, the inlet of the centrifugal fluorine pump can generate bubbles, in the pressurizing link of the centrifugal fluorine pump, the bubbles are extruded and broken to generate irregular pulse impact on the impeller of the centrifugal fluorine pump, so that irreversible damage is formed, and after long-term operation accumulation, the performance and reliability of the centrifugal fluorine pump can generate great risks.
The supercooling degree of the centrifugal fluorine pump inlet of the centrifugal fluorine pump air conditioning system which is currently applied to IDC mainly depends on the system integration design of air conditioning equipment manufacturers. Fig. 1 is a schematic view showing a part of the structure of a centrifugal fluorine pump air conditioning system in the related art. As shown in fig. 1, the centrifugal fluorine pump air conditioning system 100 includes a liquid reservoir 101, a centrifugal fluorine pump 102, a refrigerant pipe 103, a controller 104, and the like, wherein the refrigerant pipe 103 having a certain height H is generally disposed from an outlet of the liquid reservoir 101 to an inlet of the centrifugal fluorine pump 102, so that the liquid reservoir 101 and the centrifugal fluorine pump 102 are communicated by the refrigerant pipe 103, and a necessary cavitation allowance required for the inlet of the centrifugal fluorine pump 102 is provided by potential energy generated by a height difference of the refrigerant pipe 103, and the controller 104 can regulate an operation state such as an operation speed of the centrifugal fluorine pump 102 based on a refrigerating requirement. The scheme has the advantages of simple system design, low cost and simple operation control, but the refrigerant state of the pump inlet depends on the system integration capability of air conditioner manufacturers, and the supercooling degree of the refrigerant at the inlet of the centrifugal fluorine pump 102 cannot be actively regulated, so that the risk of cavitation is still high when the mode is switched or the load rate is severely fluctuated.
In order to overcome the above problems, fig. 2 is a schematic diagram illustrating a structure of an air conditioner according to an embodiment of the present disclosure. As shown in fig. 2, an air conditioner 200 provided by an embodiment of the present disclosure includes a centrifugal pump system 201, and may further include a compressor 202, a condenser 203, an evaporator 204, a throttle 205, a reservoir 206, a filter 207, and the like of a conventional air conditioner. The throttle member 205 may be an electronic expansion valve, a thermal expansion valve, or a capillary tube.
As shown in fig. 2, the outlet of the compressor 202 is connected to the inlet of the condenser 203, the outlet of the condenser 203 is connected to the inlet of the centrifugal pump system 201 through the reservoir 206, the outlet of the centrifugal pump system 201 is connected to the inlet of the filter 207, the outlet of the filter 207 is connected to the inlet of the evaporator 204 through the throttle 205, and the outlet of the evaporator 204 is connected to the inlet of the compressor 202.
The centrifugal pump system 201 of the exemplary embodiment of the present disclosure can autonomously adjust the state of the centrifugal pump inlet coolant, reducing the occurrence of the centrifugal pump cavitation phenomenon. It should be appreciated that the centrifugal pump system 201 of the exemplary embodiments of the present disclosure may be not only a fluorine pump system, but also other centrifugal pump systems where cavitation risk may occur.
The air conditioner operation principle of the exemplary embodiment of the present disclosure will be described below with reference to the air conditioner illustrated in fig. 2 by taking a fluorine pump system as an example. It should be understood that the fluorine pump system referred to in the following exemplary principles of air conditioning operation is by way of example only and not by way of limitation, and may be replaced with other possible centrifugal pump systems.
As shown in fig. 2, the air conditioner 200 of the exemplary embodiment of the present disclosure is divided into three operation modes, namely, a compressor mode, a natural cooling mode, and a hybrid mode.
As shown in fig. 2, when the air conditioner 200 of the exemplary embodiment of the present disclosure is in the compressor mode, the compressor 202 compresses gaseous freon into high-temperature and high-pressure gaseous freon, and then sends the gaseous freon to the condenser 203 (outdoor unit) to dissipate heat and become normal-temperature and high-pressure liquid freon, so that the outdoor unit blows out hot air. The filtered water directly flows into the filter through the bypass provided with the check valve, and then throttled by the throttle member 205, and then enters the evaporator 204 (indoor unit). Since freon suddenly increases in space after reaching the evaporator 204 from the throttle part 205, the pressure is reduced, the liquid freon is vaporized to become gaseous low-temperature freon, so that a large amount of heat is absorbed, the evaporator 204 is cooled, and the indoor air is blown through the evaporator 204 by the fan of the indoor unit, so that the indoor unit blows out cool air. The water vapor in the air is condensed into water droplets after encountering the cold evaporator 204, and flows out along the water pipe, which is why the air conditioner 200 can produce water. The gaseous freon then returns to the compressor 202 for continued compression and circulation. When heating, there is a component called four-way valve, so that the flow direction of Freon in condenser 203 and evaporator 204 is opposite to that of refrigerating, so that when heating, cold air is blown out from outside, and hot air is blown out from indoor unit.
As shown in fig. 2, when the air conditioner 200 of the exemplary embodiment of the present disclosure is in the natural cooling mode, the air conditioner 200 is switched to the circulation of the fluorine pump system, and the power system at this time is the fluorine pump system, and the compressor 202 is deactivated. The centrifugal pump system 201 (i.e., a fluorine pump system) is connected to an outlet of the condenser 203 through a liquid reservoir 206, and conveys the condensed liquid freon to the evaporator 204 (indoor unit), the condensed liquid freon absorbs heat and evaporates in the evaporator 204 to become high-temperature gaseous freon, and then the gaseous freon directly enters the condenser 203 after flowing through a bypass provided with a one-way valve, indirectly exchanges heat with outdoor cold air, and is condensed into low-temperature liquid freon. This cycle dissipates the indoor heat to the outdoor environment. It can be seen that in the natural cooling mode, the freon forced convection circulation is performed by the fluorine pump, so as to realize continuous refrigeration of the indoor evaporator 204 and continuous heat dissipation of the outdoor condenser 203, obtain the same refrigeration capacity as the compressor 202, and reduce the operation time of the compressor 202, thereby realizing energy saving.
As shown in fig. 2, when the air conditioner 200 of the exemplary embodiment of the present disclosure is in the hybrid mode, the air conditioner 200 may turn on the compressor 202 on the basis of the natural cooling mode, so that the compressor 202 and the centrifugal pump system 201 (i.e., the fluorine pump system) are simultaneously operated, but the compressor 202 is operated at a variable frequency. The compressor 202 compresses gaseous freon into high-temperature and high-pressure gaseous freon, and sends the gaseous freon to the condenser 203 (outdoor unit) to dissipate heat, and then the gaseous freon becomes normal-temperature and high-pressure liquid freon. The normal temperature and high pressure liquid freon is changed into low pressure and low temperature liquid freon through the centrifugal pump system 201 (i.e. the freon pump system) and the throttling part 205, enters the evaporator 204 (the indoor unit), exchanges heat with high temperature air to become low temperature and low pressure gaseous freon agent, and the evaporated low pressure and low temperature gaseous freon returns to the compressor 202 again to form refrigeration cycle.
Fig. 3A shows one structural schematic diagram of a centrifugal pump system of an exemplary embodiment of the present disclosure, and fig. 3B shows another structural schematic diagram of a centrifugal pump system of an exemplary embodiment of the present disclosure. As shown in fig. 3A and 3B, a centrifugal pump system 300 of an exemplary embodiment of the present disclosure may include a detection assembly 301, a heat exchange assembly 302, a centrifugal pump 303, and a controller 304 communicatively coupled to the detection assembly 301, the heat exchange assembly 302, and the centrifugal pump 303, respectively. The communication connection mode can be a wireless communication mode or a wired communication mode. The wireless communication mode can be WIFI, zigBee and other communication modes. The wired communication mode can be a communication mode such as a bus, PLC communication, power line carrier and the like.
As shown in fig. 3A and 3B, the detection assembly 301 is configured to detect a supercooling degree parameter of the cooling fluid at the inlet of the centrifugal pump 303, and send the detection result to the controller 304 in real time, where the supercooling degree parameter of the cooling fluid may include a temperature parameter and a pressure parameter. At this time, the detecting assembly 301 may include a temperature sensor 3011 and a pressure sensor 3012, both of which are located at an inlet of the centrifugal pump 303, the temperature sensor 3011 being used to collect a current temperature, and the pressure sensor 3012 being used to collect a current pressure. The positional relationship between the temperature sensor 3011 and the pressure sensor 3012 is not limited to this, and the pressure sensor 3012 may be provided close to the centrifugal pump, or the temperature sensor 3011 may be provided close to the centrifugal pump. Both the temperature sensor 3011 and the pressure sensor 3012 are commercially available products, and both the temperature sensor 3011 and the pressure sensor 3012 currently commercially available that can meet the detection requirements in the embodiments of the present disclosure are within the selectable scope of the embodiments of the present disclosure.
As shown in fig. 3A and 3B, the controller 304 is configured to control the centrifugal pump 303 to operate at a reduced speed when the supercooling degree parameter of the coolant does not meet the operation requirement of the centrifugal pump 303, and the controller 304 controls the heat exchange assembly 302 to adjust the temperature of the coolant at the inlet of the centrifugal pump 303 from a current temperature to a target temperature, where the target temperature is lower than the current temperature, and the target temperature matches the operation requirement of the centrifugal pump, based on the current supercooling degree determined by the supercooling degree parameter of the coolant. The operational requirements of the centrifugal pump 303 here include: the current supercooling degree is greater than or equal to the first preset supercooling degree, and when the target temperature matches the operation requirement of the centrifugal pump 303, the difference between the saturated temperature of the cooling liquid corresponding to the current pressure and the target temperature is greater than or equal to the first preset supercooling degree. Note that, the first preset supercooling degree may be a point value or a range value.
In practical applications, as shown in fig. 3A and 3B, when the supercooling degree parameter of the coolant does not meet the operation requirement of the centrifugal pump 303, it is indicated that the current coolant may undergo a phase change, and the centrifugal pump 303 may undergo cavitation. At this time, the controller 304 may control the centrifugal pump 303 to perform deceleration operation, and then control the heat exchange assembly 302 to adjust the temperature of the coolant at the inlet of the centrifugal pump 303 from the current temperature to the target temperature based on the current supercooling degree determined by the coolant supercooling degree parameter, or may control the heat exchange assembly 302 to adjust the temperature of the coolant at the inlet of the centrifugal pump 303 from the current temperature to the target temperature based on the current supercooling degree determined by the coolant supercooling degree parameter while controlling the centrifugal pump 303 to perform deceleration operation. After the centrifugal pump 303 is run at a reduced speed by the controller 304, the cavitation margin required for running the centrifugal pump 303 is reduced, and the cavitation risk of the centrifugal pump 303 can be reduced. The controller 304 can reduce the possibility of vaporization of the coolant at the inlet of the centrifugal pump 303 by controlling the heat exchange assembly 302 to adjust the temperature of the coolant at the inlet of the centrifugal pump 303 from the current temperature to the target temperature, thereby reducing the probability of cavitation in the centrifugal pump 303.
For example, as shown in fig. 3A and 3B, the centrifugal pump system 300 according to the exemplary embodiment of the present disclosure may further include a frequency converter 306, and when controlling the centrifugal pump 303 to perform deceleration operation, the controller 304 may actually send a deceleration signal to the frequency converter 306 based on the deceleration operation logic, and the frequency converter 306 controls the centrifugal pump 303 to perform deceleration operation. Here, the deceleration operation logic is determined based on the current rotational speed of the centrifugal pump 303 and the target rotational speed of the centrifugal pump 303. For example, the rotational speed of the centrifugal pump 303 may be gradually reduced in a given unit time until the target rotational speed is reached. The target rotation speed may be obtained according to actual experience, experimental data, or historical statistical data of the staff, and of course, the target rotation speed may also have a mapping relationship with the cavitation margin and the supercooling degree, for example, when the current supercooling degree determined by the controller 304 based on the cooling liquid supercooling degree parameter does not meet the current cavitation demand, the rotation speed of the centrifugal pump 303 under the current supercooling degree may be determined according to the required cavitation margin.
As can be seen from the foregoing, in the centrifugal pump system 300 provided by the present disclosure, the controller 304 is respectively in communication connection with the detecting assembly 301 and the heat exchanging assembly 302, so that the detecting assembly 301 can be used to detect the supercooling degree parameter of the cooling liquid at the inlet of the centrifugal pump 303, and send the cooling liquid supercooling degree parameter to the controller 304, and after receiving the cooling liquid supercooling degree parameter detected by the detecting assembly 301, the controller 304 can determine whether the cooling liquid supercooling degree parameter meets the operation requirement of the centrifugal pump 303. When the cooling liquid supercooling degree parameter does not meet the operation requirement of the centrifugal pump 303, it indicates that there is a risk of cavitation in the centrifugal pump 303, the controller 304 may control the centrifugal pump 303 to operate at a reduced speed, thereby reducing the risk of cavitation, and reducing the requirement of the centrifugal pump 303 for the cavitation margin.
Meanwhile, as shown in fig. 3A and 3B, the controller 304 may further control the heat exchange assembly 302 to adjust the temperature of the cooling liquid at the inlet of the centrifugal pump 303 from the current temperature to the target temperature based on the current supercooling degree of the cooling liquid at the inlet of the centrifugal pump 303 determined by the cooling liquid supercooling degree parameter, so as to increase the supercooling degree of the centrifugal pump 303, actively adjust the cooling liquid state at the inlet of the centrifugal pump 303, increase the cavitation margin of the centrifugal pump 303, reduce the probability of occurrence of cavitation risk of the centrifugal pump 303 under the condition of larger rotation speed, and make the centrifugal pump 303 far away from the cavitation risk as far as possible.
In one possible implementation, as shown in fig. 3A and 3B, the controller 304 of the exemplary embodiments of the present disclosure is further configured to adjust the rotational speed of the centrifugal pump 303 based on the cooling demand when the coolant subcooling parameter meets the operating demand of the centrifugal pump 303. When the coolant supercooling degree parameter satisfies the operation requirement of the centrifugal pump 303, it is indicated that the cavitation margin required for the centrifugal pump 303 is sufficient, and cavitation risk is not generated.
In practical applications, as shown in fig. 3A and 3B, when the supercooling degree parameter of the coolant satisfies the operation requirement of the centrifugal pump 303, the controller 304 adjusts the rotation speed of the centrifugal pump 303 based on the cooling requirement, regardless of the state of the coolant. The cooling requirement here may be selected according to the actual situation, for example, the cooling requirement may be a change in the temperature of the air supply in the room. When the set air supply temperature is 25 ℃, namely the refrigeration requirement is 25 ℃, the monitored air outlet temperature is 28 ℃, the actual air outlet temperature is higher than the refrigeration requirement, and PID (Proportion Integration Differentiation) control logic is required to be used for adjusting the air outlet temperature. For another example, the cooling demand may vary with the load on the data center, and as the load on the air conditioner increases, i.e., as the equipment carried on the data center increases, the heat dissipation increases, requiring more cooling capacity, at which point the cooling capacity of the air conditioner needs to be adjusted using PID (Proportion Integration Differentiation) control logic.
In a possible implementation manner, as shown in fig. 3A and 3B, the controller 304 of the exemplary embodiment of the present disclosure may be further configured to, when it is determined that the cooling liquid supercooling degree parameter does not meet the operation requirement of the centrifugal pump 303, indicate that the centrifugal pump 303 has cavitation risk at this time if the cooling liquid supercooling degree parameter meets the cavitation risk condition, accumulate the working duration of the centrifugal pump 303 at this time by the controller 304, and trigger cavitation risk early warning if the working duration reaches a preset duration, so as to facilitate the operation and maintenance personnel to organize the related maintenance plan in advance. At this time, when the centrifugal pump system 300 of the exemplary embodiment of the present disclosure includes the frequency converter 306, the controller 304 may control the frequency converter 306 to reduce the rotational speed of the centrifugal pump 303, thereby reducing the cavitation demand of the centrifugal pump 303 to reduce the cavitation risk of the centrifugal pump 303. At the same time or thereafter, the controller 304 may control the heat exchange assembly 302 to adjust the temperature of the coolant at the inlet of the centrifugal pump 303 from the current temperature to the target temperature based on the current subcooling degree determined by the coolant subcooling degree parameter. When the supercooling degree parameter of the cooling liquid does not meet the cavitation risk condition, stopping timing, and continuing to regulate and control under the control of the controller 304 until the controller 304 determines that the supercooling degree parameter of the cooling liquid meets the operation requirement of the centrifugal pump 303, and the controller 304 regulates the rotation speed of the centrifugal pump 303 based on the refrigeration requirement.
As a possible implementation manner, as shown in fig. 3A and fig. 3B, the heat exchange assembly 302 is in communication with the coolant line of the inlet of the centrifugal pump, so that when the supercooling degree parameter of the coolant does not meet the operation requirement of the centrifugal pump 303, the controller 304 controls the heat exchange assembly 302 to absorb the heat of the coolant in the coolant line of the inlet of the centrifugal pump 303, reduce the current temperature of the coolant at the inlet of the centrifugal pump 303, increase the supercooling degree of the coolant at the inlet of the centrifugal pump 303, and prevent the risk of cavitation of the centrifugal pump 303. Meanwhile, when the supercooling degree parameter of the cooling liquid meets the operation requirement of the centrifugal pump 303, the controller 304 controls the heat exchange assembly 302 to be not operated, so that the automatic adjustment of the cooling liquid state of the inlet of the centrifugal pump 303 is realized.
In an alternative, as shown in fig. 3A and 3B, the heat exchange assembly 302 may include a heat exchanger 3021, and a controllable valve B in communication with the controller 304, the heat absorbing side of the heat exchanger 3021 being in communication with the coolant inlet line of the centrifugal pump 303, and the heat releasing side of the heat exchanger 3021 being in series with the controllable valve B on the refrigerant line.
The refrigerant line may be in communication with an external refrigerant reservoir, as the refrigerant may be supplied from the outside. At this time, as shown in fig. 3A, the centrifugal pump system 300 further includes a controllable valve a provided on the coolant line. When the controller 304 determines that the cooling liquid supercooling degree parameter does not meet the operation requirement of the centrifugal pump 303, the controller 304 controls the centrifugal pump 303 to operate in a decelerating manner, and simultaneously or later, the controller 304 controls the liquid refrigerant in the refrigerant storage to flow into the heat-absorbing side of the heat exchanger 3021 through the refrigerant pipeline, the controller 304 controls the controllable valve b to be opened, and the controllable valve a to be closed, so that the cooling liquid in the cooling liquid inlet pipeline can flow into the heat-absorbing side of the heat exchanger 3021 entirely, and the gasified gaseous refrigerant absorbs the heat of the cooling liquid flowing into the heat-absorbing side of the heat exchanger 3021 in the heat-absorbing side of the heat exchanger 3021, so that the supercooling degree of the cooling liquid flowing into the heat-absorbing side of the heat exchanger 3021 is increased, thereby ensuring that the centrifugal pump 303 is far away from the cavitation risk. At this time, the gaseous refrigerant flows into the outlet of the evaporator 204 included in the air conditioner 200, which is in communication with the refrigerant outlet of the heat exchange assembly 302, and circulates again.
When the refrigerant can be supplied by a coolant line, i.e., as shown in fig. 3B, the refrigerant is supplied by the accumulator 305, the refrigerant line and the coolant inlet line communicate. In this case, the heat exchanger 3021 may be an economizer, and the controllable valve b may be an expansion valve. A controllable valve b is provided at a portion of the refrigerant line at the heat release side inlet of the heat exchanger 3021 to control the flow of the cooling liquid in the cooling liquid inlet line into the refrigerant line. When the controller 304 determines that the supercooling degree parameter of the cooling liquid does not meet the operation requirement of the centrifugal pump 303, the expansion valve is controlled to be partially opened, part of the high-temperature and high-pressure liquid coolant in the coolant pipeline is introduced into the expansion valve, the high-temperature and high-pressure liquid coolant is throttled into low-temperature and low-pressure wet steam through the expansion valve, and after heat is absorbed in the heat exchanger 3021, the high-temperature and high-pressure liquid coolant flows out from the coolant outlet of the heat exchange assembly 302, so that the supercooling degree effect of the cooling liquid in the coolant pipeline is improved. Here, the opening degree of the controllable valve b is determined by the controller 304 according to the current supercooling degree of the coolant and the first preset supercooling degree. The current temperature and the target temperature of the refrigerant are known, namely deltaT is known, the specific heat capacity C of the refrigerant is known, the heat required to be absorbed by the gasification of the refrigerant is the same as the heat required to be released by the cooling of the cooling liquid, and the cooling liquid is distributed into the cooling liquid pole in the cooling liquid pipeline Is small and can be ignored, so that the heat Q required to be released when the cooling liquid is cooled can be calculated Put and put I.e. the heat Q to be absorbed by the refrigerant vaporising Suction pipe ＝Q Put and put According to the endothermic formula: q=cm Δt, and the mass m of the coolant is obtained, and the opening of the controllable valve b is adjusted according to the mass of the coolant.
The exemplary embodiments of the present disclosure also provide a centrifugal pump control method that may be executed by a controller or may be executed by a chip applied to the controller. Fig. 4 shows a flowchart of a centrifugal pump control method provided by an embodiment of the present disclosure. As shown in fig. 4, a centrifugal pump control method provided by an exemplary embodiment of the present disclosure may include:
step 401: and obtaining the supercooling degree parameter of the cooling liquid at the inlet of the centrifugal pump. The supercooling degree parameters of the cooling liquid comprise: a current temperature parameter of the cooling fluid and a current pressure parameter of the cooling fluid. Taking the centrifugal pump system shown in fig. 3A and 3B as an example, when the detecting component includes a temperature sensor and a pressure sensor, the temperature sensor may be used to collect the current temperature parameter of the cooling liquid, transmit the current temperature parameter of the cooling liquid to the controller, and the pressure sensor may be used to collect the current pressure parameter of the cooling liquid, and transmit the current pressure parameter of the cooling liquid to the controller, so that the controller obtains the current temperature parameter of the cooling liquid and the current pressure parameter of the cooling liquid.
Step 402: and detecting whether the supercooling degree parameter of the cooling liquid meets the operation requirement of the centrifugal pump. If the operational requirements of the centrifugal pump are met, which indicates that the centrifugal pump is not at risk of cavitation, step 403 is performed. If not, step 404 and step 405 may be performed synchronously or asynchronously, indicating that the centrifugal pump is at risk of cavitation. It should be understood that fig. 4 only shows one possible way of performing asynchronously, it is also possible to perform step 405 first, then step 404, or to perform both steps 404 and 405 synchronously. The operating requirements of the centrifugal pump include: the current supercooling degree is larger than or equal to the first preset supercooling degree, and when the target temperature is matched with the operation requirement of the centrifugal pump, the difference value between the saturated temperature of the cooling liquid corresponding to the current pressure and the target temperature is larger than or equal to the first preset supercooling degree. In practical applications, the current subcooling degree may be determined based on a coolant subcooling degree parameter.
For example, a current saturation temperature parameter corresponding to a current pressure parameter may be determined based on the current pressure parameter of the coolant. The current subcooling may be determined based on the current temperature parameter and the current saturation temperature parameter of the cooling fluid. And then comparing the magnitude relation between the current supercooling degree and the first preset supercooling degree. If the current supercooling degree is greater than or equal to the first preset supercooling degree, the operation requirement of the centrifugal pump is met.
For example, when the first preset supercooling degree is Δt Order of (A) Based on the current pressure parameter of the cooling liquid, the saturation temperature parameter T corresponding to the current pressure parameter can be determined Saturation of Then based on the current temperature parameter T of the cooling liquid When (when) And saturation temperature parameter T Saturation of Determining the current supercooling degree DeltaT When (when) . At this time, the current supercooling degree is ΔT When (when) ＝T Saturation of -T When (when) . Under the condition of meeting the operation requirement of the centrifugal pump, delta T When (when) ≥ΔT Order of (A) 。
Step 403: the rotational speed of the centrifugal pump is adjusted based on the refrigeration demand. Taking the centrifugal pump system shown in fig. 3A and 3B as an example, when the centrifugal pump system further includes a frequency converter, in practical application, the refrigeration requirement may be adjusted according to the environmental temperature or the load condition of the data center. And the controller is used for controlling the frequency converter to work according to the refrigerating requirement when the supercooling degree parameter of the cooling liquid meets the running requirement of the centrifugal pump and adjusting the rotating speed of the centrifugal pump.
Step 404: and controlling the centrifugal pump to run at a reduced speed. Taking the centrifugal pump system shown in fig. 2 as an example, when the centrifugal pump system further includes a frequency converter, the controller is configured to determine that when the supercooling degree parameter of the cooling liquid does not satisfy the operation requirement of the centrifugal pump, the controller sends a deceleration signal to the frequency converter based on the deceleration operation logic, and the frequency converter controls the centrifugal pump to perform deceleration operation.
Step 405: and controlling the heat exchange assembly to adjust the temperature of the cooling liquid at the inlet of the centrifugal pump from the current temperature to a target temperature based on the current supercooling degree determined by the cooling liquid supercooling degree parameter, wherein the target temperature is matched with the operation requirement of the centrifugal pump. It should be appreciated that step 404 and step 405 may be performed synchronously or asynchronously herein. In practical application, the controller may determine the heat absorption parameter of the heat exchange assembly based on the current supercooling degree and the target supercooling degree, where the target supercooling degree is greater than or equal to the first preset supercooling degree. Then, the controller controls the heat exchange assembly to adjust the temperature of the cooling liquid at the inlet of the centrifugal pump from the current temperature to the target temperature based on the endothermic parameter of the heat exchange assembly.
Exemplary, the current supercooling degree is set to DeltaT When (when) ＝T Saturation of -T When (when) Target supercooling degree is DeltaT Order of (A) ＝T Saturation of -T Order of (A) The controller may be based on the current subcooling degree DeltaT When (when) And a target supercooling degree DeltaT Order of (A) Determining target heat absorption quantity Q Suction pipe . Then, the controller absorbs the heat Q based on the target Suction pipe And determining the heat absorption parameters of the heat exchange assembly. Since q=cm Δt, in case that the target temperature is determined, the endothermic parameter of the heat exchange assembly may include a refrigerant flow rate parameter, a current temperature parameter of the refrigerant, or a specific heat capacity parameter of the refrigerant, and of course, the endothermic parameter of the heat exchange assembly may also include a refrigerant flow rate parameter and a current temperature parameter of the refrigerant, a specific heat capacity parameter of the refrigerant and a specific heat capacity parameter of the refrigerant, a current temperature parameter of the refrigerant and a specific heat capacity parameter of the refrigerant, and the like.
In an alternative manner, in the step of executing step 404 and step 405 synchronously or asynchronously, the exemplary embodiment of the present disclosure may further detect whether the supercooling degree parameter of the cooling liquid meets the cavitation risk condition, if so, it indicates that the centrifugal pump is most likely to generate cavitation risk, the working time of the centrifugal pump may be longer, and if the working time reaches the preset time, the cavitation risk early warning may be triggered. It should be understood that the preset time period may be designed according to practical situations, for example, 1 month to 3 months, etc., and is not limited thereto.
In practical application, the controller determines that the working time of the centrifugal pump reaches a preset time, and triggers cavitation risk early warning so as to facilitate operation and maintenance personnel to organize related maintenance plans better in advance. When cavitation risk early warning is triggered, the controller can send an alarm instruction to the alarm to control the alarm to early warn, or the controller can send the alarm instruction to a client or a mobile phone of a related person such as an operation and maintenance person.
Illustratively, the cavitation risk condition may include: the current supercooling degree is less than or equal to the second preset supercooling degree. It should be appreciated that the second preset supercooling degree may be a point value or a range value, and is considered as a critical value of the centrifugal pump at risk of cavitation, assuming that the current supercooling degree is Δt When (when) The second preset supercooling degree is delta T Temporary face (L) Current supercooling degree Δt When (when) ≤ΔT Temporary face (L) Centrifugal pumps are considered to be at risk of cavitation.
As can be seen from the foregoing, in the control method of the centrifugal pump according to the exemplary embodiment of the present disclosure, by obtaining the supercooling degree parameter of the cooling liquid at the inlet of the centrifugal pump and sending the supercooling degree parameter of the cooling liquid to the controller, the controller may determine whether the supercooling degree parameter of the cooling liquid meets the operation requirement of the centrifugal pump after receiving the supercooling degree parameter of the cooling liquid detected by the detecting component. When the supercooling degree parameter of the cooling liquid does not meet the running requirement of the centrifugal pump, the centrifugal pump is possibly at cavitation risk, and the controller can control the centrifugal pump to run at a reduced speed, so that the occurrence risk of cavitation risk is reduced, and the requirement of the centrifugal pump on cavitation allowance is reduced.
Meanwhile, the controller can also control the heat exchange assembly to adjust the temperature of the cooling liquid at the inlet of the centrifugal pump from the current temperature to the target temperature based on the current supercooling degree of the cooling liquid at the inlet of the centrifugal pump determined by the supercooling degree parameter of the cooling liquid, so that the supercooling degree of the cooling liquid at the inlet of the centrifugal pump is improved, the state of the cooling liquid at the inlet of the centrifugal pump is actively adjusted, the cavitation allowance of the centrifugal pump is increased, the probability of cavitation risk of the centrifugal pump under the condition of high rotating speed is reduced, and the centrifugal pump is far away from the cavitation risk as far as possible.
The foregoing describes a solution provided by embodiments of the present disclosure. It is to be understood that, in order to achieve the above-described functions, they comprise corresponding hardware structures and/or software modules that perform the respective functions. Those of skill in the art will readily appreciate that the various illustrative elements and algorithm steps described in connection with the embodiments disclosed herein may be implemented as hardware or combinations of hardware and computer software. Whether a function is implemented as hardware or computer software driven hardware depends upon the particular application and design constraints imposed on the solution. Skilled artisans may implement the described functionality in varying ways for each particular application, but such implementation decisions should not be interpreted as causing a departure from the scope of the present disclosure.
The embodiments of the present disclosure may divide functional units of an apparatus according to the above method examples, for example, each functional module may be divided corresponding to each function, or two or more functions may be integrated into one processing module. The integrated modules may be implemented in hardware or in software functional modules. It should be noted that, in the embodiment of the present disclosure, the division of the modules is merely a logic function division, and other division manners may be implemented in actual practice.
In the case where respective functional modules are divided with corresponding respective functions, exemplary embodiments of the present disclosure provide a centrifugal pump control apparatus. Fig. 5 shows a block schematic diagram of a centrifugal pump control apparatus according to an exemplary embodiment of the present disclosure. As shown in fig. 5, the centrifugal pump control apparatus 500 includes:
the obtaining module 501 is configured to obtain a supercooling degree parameter of a cooling liquid at an inlet of the centrifugal pump.
The control module 502 is configured to control the centrifugal pump to perform deceleration operation when the cooling liquid supercooling degree parameter does not meet the operation requirement of the centrifugal pump, and further configured to control the heat exchange assembly to adjust the cooling liquid temperature of the inlet of the centrifugal pump from the current temperature to a target temperature, where the target temperature matches the operation requirement of the centrifugal pump, based on the current supercooling degree determined by the cooling liquid supercooling degree parameter.
In one possible implementation, the coolant subcooling parameter includes: the centrifugal pump control device 500 further includes a determining module 503 configured to determine a current saturation temperature parameter corresponding to the current pressure parameter based on the current pressure parameter of the cooling fluid, and determine a current supercooling degree based on the current temperature parameter of the cooling fluid and the current saturation temperature parameter.
In one possible implementation, the operational requirements of the centrifugal pump include: the current supercooling degree is larger than or equal to the first preset supercooling degree, and when the target temperature is matched with the operation requirement of the centrifugal pump, the difference value between the saturated temperature of the cooling liquid corresponding to the current pressure and the target temperature is larger than or equal to the first preset supercooling degree.
In one possible implementation, the control module 502 is configured to determine an endothermic parameter of the heat exchange assembly based on the current supercooling degree and the target supercooling degree, and control the heat exchange assembly to adjust the temperature of the coolant at the inlet of the centrifugal pump from the current temperature to the target temperature based on the endothermic parameter of the heat exchange assembly, where the target supercooling degree is greater than or equal to the first preset supercooling degree.
In one possible implementation, the control module 502 is configured to determine a target heat absorption amount based on the current subcooling degree and the target subcooling degree, and determine the heat absorption parameter of the heat exchange assembly based on the target heat absorption amount.
In one possible implementation, the heat absorption parameter of the heat exchange assembly includes at least one of a refrigerant flow parameter, a current temperature parameter of the refrigerant, and a specific heat capacity parameter of the refrigerant.
In one possible implementation, the control module 502 is further configured to adjust the rotational speed of the centrifugal pump based on the cooling demand when the coolant subcooling parameter meets the operating demand of the centrifugal pump.
In one possible implementation, the control module 502 is further configured to accumulate the working time of the centrifugal pump if the coolant supercooling degree parameter satisfies the cavitation risk condition when the coolant supercooling degree parameter does not satisfy the operation requirement of the centrifugal pump. And if the working time length reaches the preset time length, triggering cavitation risk early warning.
In one possible implementation, the cavitation risk condition includes: the current supercooling degree is less than or equal to the second preset supercooling degree.
Fig. 6 shows a schematic block diagram of a chip of an exemplary embodiment of the present disclosure. As shown in fig. 6, the chip 600 includes one or more (including two) processors 601 and a communication interface 602. The communication interface 602 may support a server to perform the data transceiving steps of the method described above, and the processor 601 may support the server to perform the data processing steps of the method described above.
Optionally, as shown in fig. 6, the chip 600 further includes a memory 603, and the memory 603 may include a read only memory and a random access memory, and provides operation instructions and data to the processor. A portion of the memory may also include non-volatile random access memory (non-volatile random access memory, NVRAM).
In some embodiments, as shown in FIG. 6, the processor 601 performs the corresponding operation by invoking a memory-stored operating instruction (which may be stored in an operating system). The processor 601 controls the processing operations of any one of the terminal devices, which may also be referred to as a central processing unit (central processing unit, CPU). Memory 603 may include read only memory and random access memory and provide instructions and data to processor 601. A portion of the memory 603 may also include NVRAM. Such as an in-application memory 603, a communication interface 602, and a processor 601 are coupled together by a bus system 604, which may include a power bus, a control bus, a status signal bus, etc., in addition to a data bus. But for clarity of illustration, the various buses are labeled as bus system 604 in fig. 6.
The method disclosed by the embodiment of the disclosure can be applied to a processor or implemented by the processor. The processor may be an integrated circuit chip having signal processing capabilities. In implementation, the steps of the above method may be performed by integrated logic circuits of hardware in a processor or by instructions in the form of software. The processor may be a general purpose processor, a digital signal processor (digital signal processing, DSP), an ASIC, an off-the-shelf programmable gate array (field-programmable gate array, FPGA) or other programmable logic device, discrete gate or transistor logic device, discrete hardware components. The various methods, steps and logic blocks of the disclosure in the embodiments of the disclosure may be implemented or performed. A general purpose processor may be a microprocessor or the processor may be any conventional processor or the like. The steps of a method disclosed in connection with the embodiments of the present disclosure may be embodied directly in hardware, in a decoded processor, or in a combination of hardware and software modules in a decoded processor. The software modules may be located in a random access memory, flash memory, read only memory, programmable read only memory, or electrically erasable programmable memory, registers, etc. as well known in the art. The storage medium is located in a memory, and the processor reads the information in the memory and, in combination with its hardware, performs the steps of the above method.
The exemplary embodiments of the present disclosure also provide an electronic device including: a processor; and a memory storing a program. The memory stores a computer program executable by the processor for causing the electronic device to perform a method according to an embodiment of the present disclosure when executed by the processor.
The present disclosure also provides a non-transitory computer-readable storage medium storing a computer program, wherein the computer program, when executed by a processor of a computer, is for causing the computer to perform a method according to an embodiment of the present disclosure.
The present disclosure also provides a computer program product comprising a computer program, wherein the computer program, when executed by a processor of a computer, is for causing the computer to perform a method according to embodiments of the disclosure.
Referring to fig. 7, a block diagram of an electronic device 700 that may be a server or a client of the present disclosure, which is an example of a hardware device that may be applied to aspects of the present disclosure, will now be described. Electronic devices are intended to represent various forms of digital electronic computer devices, such as laptops, desktops, workstations, personal digital assistants, servers, blade servers, mainframes, and other suitable computers. The electronic device may also represent various forms of mobile devices, such as personal digital processing, cellular telephones, smartphones, wearable devices, and other similar computing devices. The components shown herein, their connections and relationships, and their functions, are meant to be exemplary only, and are not meant to limit implementations of the disclosure described and/or claimed herein.
As shown in fig. 7, the electronic device 700 includes a computing unit 701 that can perform various appropriate actions and processes according to a computer program stored in a Read Only Memory (ROM) 702 or a computer program loaded from a storage unit 708 into a Random Access Memory (RAM) 703. In the RAM 703, various programs and data required for the operation of the device 700 may also be stored. The computing unit 701, the ROM 702, and the RAM 703 are connected to each other through a bus 704. An input/output (I/O) interface 705 is also connected to bus 704.
As shown in fig. 7, various components in the electronic device 700 are connected to the I/O interface 705, including: an input unit 706, an output unit 707, a storage unit 708, and a communication unit 709. The input unit 706 may be any type of device capable of inputting information to the electronic device 700, and the input unit 706 may receive input numeric or character information and generate key signal inputs related to user settings and/or function controls of the electronic device. The output unit 707 may be any type of device capable of presenting information and may include, but is not limited to, a display, speakers, video/audio output terminals, vibrators, and/or printers. Storage unit 708 may include, but is not limited to, magnetic disks, optical disks. The communication unit 709 allows the electronic device 700 to exchange information/data with other devices through computer networks, such as the internet, and/or various telecommunications networks, and may include, but is not limited to, modems, network cards, infrared communication devices, wireless communication transceivers and/or chipsets, such as bluetooth (TM) devices, wiFi devices, wiMax devices, cellular communication devices, and/or the like.
As shown in fig. 7, the computing unit 701 may be a variety of general and/or special purpose processing components having processing and computing capabilities. Some examples of computing unit 701 include, but are not limited to, a Central Processing Unit (CPU), a Graphics Processing Unit (GPU), various specialized Artificial Intelligence (AI) computing chips, various computing units running machine learning model algorithms, a Digital Signal Processor (DSP), and any suitable processor, controller, microcontroller, etc. The computing unit 701 performs the various methods and processes described above. For example, in some embodiments, the methods of the exemplary embodiments of the present disclosure may be implemented as a computer software program tangibly embodied on a machine-readable medium, such as the storage unit 708. In some embodiments, part or all of the computer program may be loaded and/or installed onto the electronic device 700 via the ROM 702 and/or the communication unit 709. In some embodiments, the computing unit 701 may be configured to perform the method by any other suitable means (e.g., by means of firmware).
Program code for carrying out methods of the present disclosure may be written in any combination of one or more programming languages. These program code may be provided to a processor or controller of a general purpose computer, special purpose computer, or other programmable data processing apparatus such that the program code, when executed by the processor or controller, causes the functions/operations specified in the flowchart and/or block diagram to be implemented. The program code may execute entirely on the machine, partly on the machine, as a stand-alone software package, partly on the machine and partly on a remote machine or entirely on the remote machine or server.
In the context of this disclosure, a machine-readable medium may be a tangible medium that can contain, or store a program for use by or in connection with an instruction execution system, apparatus, or device. The machine-readable medium may be a machine-readable signal medium or a machine-readable storage medium. The machine-readable medium may include, but is not limited to, an electronic, magnetic, optical, electromagnetic, infrared, or semiconductor system, apparatus, or device, or any suitable combination of the foregoing. More specific examples of a machine-readable storage medium would include an electrical connection based on one or more wires, a portable computer diskette, a hard disk, a Random Access Memory (RAM), a read-only memory (ROM), an erasable programmable read-only memory (EPROM or flash memory), an optical fiber, a portable compact disc read-only memory (CD-ROM), an optical storage device, a magnetic storage device, or any suitable combination of the foregoing.
As used in this disclosure, the terms "machine-readable medium" and "computer-readable medium" refer to any computer program product, apparatus, and/or device (e.g., magnetic discs, optical disks, memory, programmable Logic Devices (PLDs)) used to provide machine instructions and/or data to a programmable processor, including a machine-readable medium that receives machine instructions as a machine-readable signal. The term "machine-readable signal" refers to any signal used to provide machine instructions and/or data to a programmable processor.
To provide for interaction with a user, the systems and techniques described here can be implemented on a computer having: a display device (e.g., a CRT (cathode ray tube) or LCD (liquid crystal display) monitor) for displaying information to a user; and a keyboard and pointing device (e.g., a mouse or trackball) by which a user can provide input to the computer. Other kinds of devices may also be used to provide for interaction with a user; for example, feedback provided to the user may be any form of sensory feedback (e.g., visual feedback, auditory feedback, or tactile feedback); and input from the user may be received in any form, including acoustic input, speech input, or tactile input.
The systems and techniques described here can be implemented in a computing system that includes a background component (e.g., as a data server), or that includes a middleware component (e.g., an application server), or that includes a front-end component (e.g., a user computer having a graphical user interface or a web browser through which a user can interact with an implementation of the systems and techniques described here), or any combination of such background, middleware, or front-end components. The components of the system can be interconnected by any form or medium of digital data communication (e.g., a communication network). Examples of communication networks include: local Area Networks (LANs), wide Area Networks (WANs), and the internet.
The computer system may include a client and a server. The client and server are typically remote from each other and typically interact through a communication network. The relationship of client and server arises by virtue of computer programs running on the respective computers and having a client-server relationship to each other.
In the above embodiments, it may be implemented in whole or in part by software, hardware, firmware, or any combination thereof. When implemented in software, may be implemented in whole or in part in the form of a computer program product. The computer program product includes one or more computer programs or instructions. When the computer program or instructions are loaded and executed on a computer, the processes or functions described by the embodiments of the present disclosure are performed in whole or in part. The computer may be a general purpose computer, a special purpose computer, a computer network, a terminal, a user equipment, or other programmable apparatus. The computer program or instructions may be stored in a computer readable storage medium or transmitted from one computer readable storage medium to another computer readable storage medium, for example, the computer program or instructions may be transmitted from one website site, computer, server, or data center to another website site, computer, server, or data center by wired or wireless means. The computer readable storage medium may be any available medium that can be accessed by a computer or a data storage device such as a server, data center, etc. that integrates one or more available media. The usable medium may be a magnetic medium, e.g., floppy disk, hard disk, tape; optical media, such as digital video discs (digital video disc, DVD); but also semiconductor media such as solid state disks (solid state drive, SSD).
Although the present disclosure has been described in connection with specific features and embodiments thereof, it will be apparent that various modifications and combinations thereof can be made without departing from the spirit and scope of the disclosure. Accordingly, the specification and drawings are merely exemplary illustrations of the present disclosure as defined in the appended claims and are considered to cover any and all modifications, variations, combinations, or equivalents within the scope of the disclosure. It will be apparent to those skilled in the art that various modifications and variations can be made to the present disclosure without departing from the spirit or scope of the disclosure. Thus, the present disclosure is intended to include such modifications and alterations insofar as they come within the scope of the appended claims or the equivalents thereof.

Claims (19)

1. A centrifugal pump control method, characterized by comprising:
acquiring a supercooling degree parameter of a cooling liquid at an inlet of a centrifugal pump;
when the supercooling degree parameter of the cooling liquid does not meet the operation requirement of the centrifugal pump, controlling the centrifugal pump to run at a reduced speed;
and controlling a heat exchange assembly to adjust the temperature of the cooling liquid at the inlet of the centrifugal pump from the current temperature to a target temperature based on the current supercooling degree determined by the cooling liquid supercooling degree parameter, wherein the target temperature is matched with the operation requirement of the centrifugal pump.
2. The method of controlling a centrifugal pump according to claim 1, wherein the coolant supercooling degree parameter includes: the control method of the centrifugal pump further comprises the following steps of:
determining a current saturation temperature parameter corresponding to the current pressure parameter based on the current pressure parameter of the cooling liquid;
the current subcooling degree is determined based on the current temperature parameter of the cooling liquid and the current saturation temperature parameter.
3. The method of controlling a centrifugal pump according to claim 2, wherein the operation requirement of the centrifugal pump includes: the current supercooling degree is larger than or equal to a first preset supercooling degree, and when the target temperature is matched with the running requirement of the centrifugal pump, the difference value between the cooling liquid saturation temperature corresponding to the current pressure and the target temperature is larger than or equal to the first preset supercooling degree.
4. The method of claim 1, wherein controlling the heat exchange assembly to adjust the temperature of the coolant at the centrifugal pump inlet from a current temperature to a target temperature based on the determined current subcooling degree of the coolant subcooling degree parameter, comprises:
Determining an endothermic parameter of the heat exchange assembly based on the current supercooling degree and a target supercooling degree, wherein the target supercooling degree is greater than or equal to a first preset supercooling degree;
and controlling the heat exchange assembly to adjust the temperature of the cooling liquid at the inlet of the centrifugal pump from the current temperature to the target temperature based on the heat absorption parameter of the heat exchange assembly.
5. The method of controlling a centrifugal pump according to claim 4, wherein said determining an endothermic parameter of a heat exchange assembly based on the current subcooling degree and a target subcooling degree comprises:
determining a target heat absorption amount based on the current supercooling degree and the target supercooling degree;
and determining an endothermic parameter of the heat exchange assembly based on the target endothermic amount.
6. The method of claim 4, wherein the heat absorption parameter of the heat exchange assembly comprises at least one of a refrigerant flow parameter, a current temperature parameter of the refrigerant, and a specific heat capacity parameter of the refrigerant.
7. The control method of a centrifugal pump according to any one of claims 1 to 6, characterized in that the control method of a centrifugal pump further comprises:
and when the supercooling degree parameter of the cooling liquid meets the operation requirement of the centrifugal pump, adjusting the rotating speed of the centrifugal pump based on the refrigeration requirement.
8. The control method of a centrifugal pump according to any one of claims 1 to 6, characterized in that the control method of a centrifugal pump further comprises:
when the supercooling degree parameter of the cooling liquid does not meet the running requirement of the centrifugal pump, if the supercooling degree parameter of the cooling liquid meets the cavitation risk condition, accumulating the working time of the centrifugal pump;
and if the working time length reaches the preset time length, triggering cavitation risk early warning.
9. The method of controlling a centrifugal pump according to claim 8, wherein the cavitation risk condition includes: the current supercooling degree is smaller than or equal to a second preset supercooling degree.
10. A centrifugal pump control apparatus, comprising:
the acquisition module is used for acquiring the supercooling degree parameter of the cooling liquid at the inlet of the centrifugal pump;
and the control module is used for controlling the centrifugal pump to run in a decelerating mode when the supercooling degree parameter of the cooling liquid does not meet the running requirement of the centrifugal pump, and is also used for controlling the heat exchange assembly to adjust the temperature of the cooling liquid at the inlet of the centrifugal pump from the current temperature to the target temperature based on the current supercooling degree determined by the supercooling degree parameter of the cooling liquid, and the target temperature is matched with the running requirement of the centrifugal pump.
11. An electronic device, comprising:
a processor; the method comprises the steps of,
a memory storing a program;
wherein the program comprises instructions which, when executed by the processor, cause the processor to perform the centrifugal pump control method according to any one of claims 1 to 9.
12. A non-transitory computer-readable storage medium storing computer instructions for causing the computer to execute the centrifugal pump control method according to any one of claims 1 to 9.
13. A centrifugal pump system, comprising: the centrifugal pump control device comprises a detection assembly, a heat exchange assembly, a centrifugal pump and a controller which is in communication connection with the detection assembly, the heat exchange assembly and the centrifugal pump respectively, wherein the controller is the centrifugal pump control device according to claim 10.
14. The centrifugal pump system of claim 13, wherein the detection assembly comprises a temperature sensor and a pressure sensor, the temperature sensor and the pressure sensor both located at the centrifugal pump inlet, the temperature sensor for acquiring a current temperature and the pressure sensor for acquiring a current pressure.
15. The centrifugal pump system of claim 13, wherein the heat exchange assembly is in communication with a coolant line of the centrifugal pump inlet.
16. The centrifugal pump system of claim 15, wherein the heat exchange assembly comprises a heat exchanger, and a controllable valve in communication with the controller, the heat absorbing side of the heat exchanger being in communication with the coolant inlet line of the centrifugal pump, the heat releasing side of the heat exchanger being in series with the controllable valve on a refrigerant line.
17. The centrifugal pump system according to claim 16, wherein said coolant inlet line and said refrigerant line are in communication, said controllable valve being provided at a location of said refrigerant line at an inlet of a heat release side of said heat exchanger, said controllable valve being an expansion valve.
18. An air conditioner comprising the centrifugal pump system according to any one of claims 13 to 17.
19. An air conditioner according to claim 18 wherein the air conditioner includes an evaporator outlet in communication with a refrigerant outlet of the heat exchange assembly.
CN202310392281.9A 2023-04-13 2023-04-13 Centrifugal pump control method and device, equipment, system, air conditioner and storage medium Pending CN116412150A (en)

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CN202310392281.9A CN116412150A (en) 2023-04-13 2023-04-13 Centrifugal pump control method and device, equipment, system, air conditioner and storage medium

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116951800A (en) * 2023-09-15 2023-10-27 广东美的暖通设备有限公司 Control method, control device, dual-cycle refrigeration system and storage medium

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116951800A (en) * 2023-09-15 2023-10-27 广东美的暖通设备有限公司 Control method, control device, dual-cycle refrigeration system and storage medium
CN116951800B (en) * 2023-09-15 2024-01-02 广东美的暖通设备有限公司 Control method, control device, dual-cycle refrigeration system and storage medium

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