WO2024217147A1 - 一种双机头机组的控制方法、装置和存储介质 - Google Patents

一种双机头机组的控制方法、装置和存储介质 Download PDF

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Publication number
WO2024217147A1
WO2024217147A1 PCT/CN2024/078404 CN2024078404W WO2024217147A1 WO 2024217147 A1 WO2024217147 A1 WO 2024217147A1 CN 2024078404 W CN2024078404 W CN 2024078404W WO 2024217147 A1 WO2024217147 A1 WO 2024217147A1
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WO
WIPO (PCT)
Prior art keywords
dual
head
head unit
efficiency
cooling capacity
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Ceased
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PCT/CN2024/078404
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English (en)
French (fr)
Inventor
岳宝
祝用华
袁永莉
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Shanghai Kong Intelligent Building Co Ltd
GD Midea Heating and Ventilating Equipment Co Ltd
Original Assignee
Shanghai Kong Intelligent Building Co Ltd
GD Midea Heating and Ventilating Equipment Co Ltd
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Publication of WO2024217147A1 publication Critical patent/WO2024217147A1/zh
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Ceased legal-status Critical Current

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Classifications

    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/02—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating liquids, e.g. brine
    • 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

Definitions

  • the present invention relates to air conditioning technology, and more particularly to a control method, device and storage medium for a dual-head air conditioner.
  • Centrifugal chillers are widely used in air-conditioning systems of large and medium-sized buildings due to their large capacity and high efficiency.
  • the capacity of a single unit can reach more than 1,000 tons of cooling, and the unit may be powered by two or more compressors. Due to the high power consumption during operation, energy saving is of great significance for dual (multi) head chillers.
  • the optimization control of air-conditioning water systems often controls the units by starting and stopping the units, and the attention to the operating energy efficiency of the units themselves is not high, and there are not many targeted optimization control schemes.
  • the same increase and decrease of the heads is often used to solve the pressure-flow balance problem between different pressure heads, so the unit energy efficiency is low under some load conditions.
  • the operation strategy of conventional multi-head variable frequency centrifugal chillers is mainly optimized from the reliability aspects such as reducing the pressure ratio when the variable frequency centrifugal compressor is started and shut down, and the control strategy is not optimized based on the efficiency curve of the variable frequency centrifugal compressor under variable working conditions and loads, with the optimal energy efficiency of the unit as the goal.
  • chillers are in partial load operation most of the time. Therefore, there is an urgent need for an operation control method that improves the operation of multi-head variable frequency centrifugal chillers to effectively improve the partial load energy efficiency of the unit, thereby reducing the unit's operating energy consumption and operating costs.
  • the present disclosure provides a control method for a dual-head unit, the method comprising:
  • the horizontal axis of the dual-head unit efficiency map is the cooling capacity ratio and the vertical axis is the pressure ratio; determining the boundary pressure ratio corresponding to the cooling capacity ratio according to the cooling capacity ratio and the information of the single-head and dual-head dividing line in the dual-head unit efficiency map;
  • the minimum pressure ratio is the ratio of the theoretical minimum condensing pressure to the theoretical maximum evaporating pressure.
  • the efficiency map of the dual-head unit includes a first efficiency contour line when the single-head unit is in operation and a second efficiency contour line when the dual-head unit is in operation;
  • the dividing line between the single and double heads is determined by the following method:
  • the dividing line between the single and double heads is determined according to the maximum flow rate and the highest pressure ratio point, and the intersection point of the contour lines.
  • the same efficiency value is the highest or second highest efficiency value on the map.
  • the dual-head unit efficiency map is determined by the following steps:
  • the abscissa of the data in the first efficiency spectrum is multiplied by 50%, and the ordinate remains unchanged, to obtain a second efficiency spectrum of the dual-head unit in the single-head operation mode;
  • the first efficiency map and the second efficiency map are superimposed to obtain the efficiency map of the dual-head unit when the dual-head unit is in single-head operation and dual-head operation.
  • determining the maximum flow rate and the highest pressure ratio point when a single head is running in the efficiency spectrum of the dual-head unit includes:
  • the maximum flow rate and the highest pressure ratio point when a single head is running in the efficiency map of the dual-head unit are determined according to the determined maximum cooling capacity proportion and the determined highest pressure ratio.
  • determining the boundary pressure ratio corresponding to the cooling capacity ratio includes:
  • the corresponding boundary pressure ratio is determined according to the cooling capacity ratio.
  • determining the number of heads of the dual-head unit in operation in the next cycle according to the minimum pressure ratio and the boundary pressure ratio includes:
  • the dual-head unit starts one head in the next cycle and enters the single-head operation mode
  • the dual-head unit starts two heads in the next cycle and enters the dual-head operation mode.
  • the method further includes:
  • the dual-head operation mode is switched to the dual-head operation mode when the switching time interval is met;
  • the single-head operation mode is switched to the single-head operation mode when the switching time interval is met.
  • the disclosed embodiment also provides a control method for a dual-head unit, which is applied to a centrifugal chiller, and the method includes:
  • the dual-head unit efficiency map includes a first efficiency contour line when a single head is running and a second efficiency contour line when a dual head is running;
  • the single-head and double-head dividing line is determined by the following method: determine the maximum flow and the highest pressure ratio point when the single head is running in the efficiency map of the double-head unit; determine the contour intersection point of the first efficiency contour line and the second efficiency contour line with the same efficiency value on the side of the small cooling capacity proportion in the efficiency map of the double-head unit; determine the single-head and double-head dividing line according to the maximum flow and the highest pressure ratio point, and the contour intersection point;
  • the dual-head unit When the cooling capacity ratio is less than or equal to the first horizontal coordinate value, the dual-head unit starts one head in the next cycle; when the cooling capacity ratio is greater than or equal to the second horizontal coordinate value, the dual-head unit starts two heads in the next cycle.
  • determining the maximum flow rate and the highest pressure ratio point when a single head is running in the efficiency spectrum of the dual-head unit includes:
  • the maximum flow rate and the highest pressure ratio point when a single head is running in the efficiency map of the dual-head unit are determined according to the determined maximum cooling capacity ratio and the determined highest pressure ratio.
  • the disclosed embodiment also provides a control device for a dual-head unit, including a memory and a processor; the memory is used to store a control program for the dual-head unit, and the processor is used to read and execute the control program for the dual-head unit, and execute any of the methods described in the above embodiments.
  • the embodiments of the present disclosure further provide a computer-readable storage medium storing computer-executable instructions, which, when executed by a processor, can perform any of the methods described in the above embodiments.
  • FIG1 is a flow chart of a control method for a dual-head unit according to an embodiment of the present disclosure
  • FIG2 is a flow chart of another control method of a dual-head unit according to an embodiment of the present disclosure.
  • FIG3 is a schematic diagram of a control device for a dual-head unit according to an embodiment of the present disclosure
  • FIG4 is a graph of centrifugal compressor efficiency in some embodiments.
  • FIG5 is a schematic diagram of the efficiency spectrum and switching boundary line of a dual-head unit in some exemplary embodiments
  • FIG6 is a schematic diagram of determining the maximum flow rate and the highest pressure ratio point when a single head is running in a dual-head unit efficiency spectrum in some exemplary embodiments;
  • FIG7 is a schematic diagram of a dual-head unit control method in some exemplary embodiments.
  • FIG8 is a flow chart of a dual-head unit control method in some exemplary embodiments.
  • the disclosed embodiments include and contemplate combinations of features and elements known to those of ordinary skill in the art.
  • the disclosed embodiments, features, and elements of the disclosed embodiments may also be combined with any conventional features or elements to form a unique invention scheme defined by the claims.
  • Any features or elements of any embodiment may also be combined with features or elements from other invention schemes to form another unique invention scheme defined by the claims. Therefore, it should be understood that any feature shown and/or discussed in the disclosed embodiments may be implemented individually or in any appropriate combination. Therefore, except for the limitations made according to the attached claims and their equivalents, the embodiments are not subject to other limitations.
  • various modifications and changes may be made within the scope of protection of the attached claims.
  • the specification may have presented the method and/or process as a specific sequence of steps. However, to the extent that the method or process does not rely on the specific order of the steps described herein, the method or process should not be limited to the steps in the specific order described. As will be appreciated by those of ordinary skill in the art, other orders of steps are also possible. Therefore, the specific order of the steps set forth in the specification should not be interpreted as a limitation to the claims. In addition, the claims for the method and/or process should not be limited to the steps performed in the order written, and those skilled in the art can easily understand that these orders can be changed and still remain within the spirit and scope of the disclosed embodiments.
  • the present disclosure provides a control method for a dual-head unit, as shown in FIG1 , the method includes the following steps 100-130:
  • Step 100 Determine the required cooling capacity according to the operating data and temperature value of the dual-head unit in the current cycle
  • Step 110 determining the cooling capacity ratio according to the ratio of the determined required cooling capacity to the nominal cooling capacity
  • Step 120 Obtain the efficiency map of the dual-head unit, and determine the boundary pressure ratio corresponding to the cooling capacity ratio according to the cooling capacity ratio and the information of the single-head and dual-head dividing line in the dual-head unit efficiency map;
  • Step 130 Determine the minimum pressure ratio, and determine the number of heads of the dual-head unit in operation in the next cycle based on the minimum pressure ratio and the boundary pressure ratio.
  • the temperature values include an evaporator inlet water temperature value, an evaporator outlet water temperature value, a condenser inlet water temperature value, and a condenser outlet water temperature value.
  • the cooling water flow rate and the chilled water flow rate can be calculated by jointly solving the following four equations:
  • Qe represents the cooling capacity
  • P represents the power consumption of the compressor
  • Qc represents the condensation heat rejection
  • CP represents the specific heat capacity of water
  • EWTe represents the evaporator inlet water temperature value
  • LWTe represents the evaporator outlet water temperature value
  • EWTc represents the condenser inlet water temperature value
  • LWTc represents the condenser outlet water temperature value
  • m_flow_c represents the cooling water flow rate
  • m_flow_e represents the chilled water flow rate
  • ⁇ represents the error coefficient
  • ⁇ is theoretically a number close to 0
  • ⁇ Tc EWTc- LWTc
  • ⁇ Te EWTe - LWTe
  • ⁇ Tc represents the difference between the condenser inlet water and outlet water temperatures
  • ⁇ Te represents the difference between the evaporator inlet water and outlet water temperatures.
  • the formula is used according to the condensation inlet water temperature value, the condensation outlet water temperature value, the cooling water flow rate and the specific heat capacity of water:
  • the formula is used according to the evaporator inlet water temperature value, evaporator outlet water temperature value, chilled water flow rate and specific heat capacity of water:
  • the horizontal axis represents the flow factor and the vertical axis represents the pressure head factor.
  • the flow factor on the horizontal axis is the ratio of the compressor operating refrigerant flow divided by the rated refrigerant flow, and the flow factor is dimensionless;
  • the pressure head factor on the vertical axis is the compressor operating pressure ratio divided by the maximum pressure ratio (the maximum pressure ratio is the maximum value that the compressor equipment can reach).
  • the compressor efficiency spectrum is technical data obtained by the compressor manufacturer through experimental measurement or other methods, which characterizes the efficiency of the compressor under different refrigerant flow rates (corresponding to cooling capacity) and different pressure ratios.
  • the compressor efficiency can be characterized by the cooling capacity ratio and the pressure ratio value.
  • Step 1 Calculate the required cooling capacity based on the user set temperature, inlet water temperature and chilled water flow rate:
  • Q e_set is the required cooling capacity
  • m_flow_e is the chilled water flow rate
  • C P is the specific heat capacity of water
  • EWT e is the evaporator inlet water temperature
  • LWT e_set is the set evaporator outlet water temperature.
  • Step 2 Divide the calculated required cooling capacity by the nominal cooling capacity to determine the cooling capacity ratio:
  • f Q is the cooling capacity ratio
  • Q e_set is the required cooling capacity
  • Q _nom is the nominal cooling capacity, which is the value of the compressor and is a known quantity.
  • the efficiency spectrum of the dual-head unit includes the first efficiency contour line when the single-head unit is running and the second efficiency contour line when the dual-head unit is running; the dotted line in Figure 5 represents the first efficiency contour line when the dual-head unit is running, and the solid line represents the second efficiency contour line when the single-head unit is running.
  • a critical point is determined to switch to the single-head unit to achieve energy saving. For example, point A and point C are critical points, and line segment AC is the boundary line.
  • the efficiency map of the dual-head unit is determined by the following steps:
  • Step 1 Obtaining a first efficiency spectrum of the dual-head unit in a dual-head operation mode
  • the first efficiency spectrum of the twin-head unit in the twin-head operation mode is the same as the efficiency spectrum of the single-head unit;
  • Step 2 Multiply the abscissa of the data in the first efficiency map by 50%, and keep the ordinate unchanged, to obtain a second efficiency map of the dual-head unit in the single-head operation mode;
  • the implementation process of this step is equivalent to scaling the first efficiency map, with the horizontal axis reduced to half of the original value, and the vertical axis unchanged.
  • the reason for this is that the cooling capacity ratio is equal to the required cooling capacity divided by the nominal cooling capacity (fixed value).
  • the cooling capacity ratio is calculated based on the nominal cooling capacity in the dual-head operation mode, and the required cooling capacity when the dual-head unit is operating in single-head mode is 50% of that when it is operating in dual-head mode. Therefore, the second efficiency map of the dual-head unit in single-head operation mode can be obtained by performing the above transformation on the first efficiency map of the dual-head unit in dual-head operation mode.
  • Step 3 Superimpose the first efficiency spectrum and the second efficiency spectrum to obtain the efficiency spectrum of the dual-head unit when the dual-head unit is in single-head operation and dual-head operation.
  • the first efficiency spectrum (the first efficiency spectrum of the dual-head unit in the dual-head operation mode) is a dotted line
  • the second efficiency spectrum is a solid line
  • the efficiency curve of the single head (solid line) and the efficiency curve of the dual head (dotted line) are superimposed in the same coordinate system to form the efficiency spectrum of the dual-head unit shown in Figure 5.
  • the process of determining the maximum flow rate and the highest pressure ratio point (i.e., point A in FIG. 5 ) when a single head is running in the efficiency spectrum of the dual-head unit is as follows:
  • the first step is to determine the maximum cooling capacity proportion of a single head in the efficiency spectrum of a dual-head unit
  • the maximum value of the cooling capacity ratio on the horizontal axis of the efficiency spectrum is determined by dividing the maximum cooling capacity by the rated cooling capacity.
  • the rated cooling capacity is a product parameter of the compressor and is a known value.
  • the maximum cooling capacity ratio when a single head is running is half of the horizontal axis on the efficiency spectrum.
  • the second step is to determine the maximum pressure ratio when the single-head unit is in operation in the efficiency spectrum of the dual-head unit;
  • the maximum pressure ratio can be determined by the value on the efficiency map. For example, in FIG6 , the maximum pressure ratio is 5.
  • Step 3 The intersection of the determined maximum cooling capacity share line (line 1 in FIG6 ) and the determined maximum pressure ratio line (line 2 in FIG6 ) is taken as the maximum flow rate and the maximum pressure ratio point (point A) when a single head is running in the efficiency spectrum of the dual-head unit.
  • the dividing line between the single and double heads is determined by:
  • the first step is to determine the maximum flow rate and the highest pressure ratio point when a single head is running in the efficiency spectrum of the dual-head unit;
  • the second step is to determine the intersection point of the first efficiency contour line and the second efficiency contour line with the same efficiency value on the side of small cooling capacity ratio in the efficiency spectrum of the dual-head unit;
  • the third step is to determine the single-head and double-head dividing line according to the maximum flow rate and the highest pressure ratio point, and the intersection point of the contour lines.
  • the same efficiency value is the highest or second highest efficiency value on the efficiency spectrum of the double-head unit.
  • the specific implementation process of the single-head and double-head dividing line is as follows: As shown in Figure 5, the single-head and double-head dividing line is determined by two points. The first point is the maximum flow rate and the highest pressure ratio point when the single head is running, that is, point A; the second point is the intersection point of the contour lines on the small cooling capacity ratio side, that is, point B. After determining point A and point B, the single-head and double-head dividing line can be obtained through the straight line formula based on the two points, as follows:
  • P r represents the dividing pressure ratio
  • f Q represents the cooling capacity ratio
  • a and b are the slope and intercept of the dividing line between the single head and the double head, respectively.
  • determining the number of heads of a dual-head unit in operation according to the minimum pressure ratio and the boundary pressure ratio includes:
  • one head of the dual-head unit When the minimum pressure ratio is greater than or equal to the cut-off pressure ratio, one head of the dual-head unit is turned on;
  • the two heads of the dual-head unit are turned on.
  • the specific calculation process of the minimum pressure ratio is as follows:
  • the evaporation temperature is lower than the chilled water outlet temperature, so the theoretical maximum evaporation pressure can be calculated by the chilled water outlet temperature set value LWT e_set :
  • Pe_max is the theoretical maximum evaporation pressure
  • LWT e_set is the chilled water outlet temperature setting value
  • the unit is °C
  • Pe_max is in kPa.
  • the condensation pressure is higher than the refrigerant saturation pressure corresponding to the cooling water outlet temperature, so the theoretical minimum condensation pressure can be calculated by the cooling water outlet temperature (LWT c ):
  • Pc_min is the theoretical minimum condensing pressure
  • LWT c is the condensing outlet water temperature value
  • the unit is °C, which can be replaced by the condensing temperature, or the condensing inlet water temperature plus the design water temperature difference
  • Pc_min unit is kPa.
  • the minimum pressure ratio is:
  • Pr_min Pc_min/Pe_max
  • Pr_min is the minimum pressure ratio
  • Pc_min is the theoretical minimum condensing pressure
  • Pe_max is the theoretical maximum evaporating pressure
  • the number of heads of a dual-head unit is determined based on the minimum pressure ratio and the boundary pressure ratio, and the method also includes: when the current operation is a single-head operation mode, and it is determined that the dual-head operation mode will be turned on in the next cycle, when the switching time interval is met, switching to the dual-head operation mode; when the current operation is a dual-head operation mode, and it is determined that the single-head operation mode will be turned on in the next cycle, when the switching time interval is met, switching to the single-head operation mode.
  • the current operating status is obtained from the unit operating data, and the switching boundary value is determined by the dual-head efficiency map; the water flow rate is input or calculated from the unit operating data, and the required cooling capacity is further calculated; the number of operating heads is determined based on the determined switching boundary value and the required cooling capacity; after the number of operating heads is determined based on the required cooling capacity and the dual-head switching boundary value, adjustments are made based on the speed-guide vane coupling control method.
  • the speed-guide vane coupling control is to open the guide vane to the maximum when loading and then adjust the speed. When unloading, adjust the speed first (until the surge speed limit) and then adjust the guide vane opening. For example: after determining the operation mode of the next cycle of the dual-head unit switching, adjust according to the speed-guide vane coupling control method, as follows:
  • the first step is to determine the surge speed and the blocking speed according to the pressure ratio and the inlet guide vane opening of the current cycle
  • Step 2 When the die is loaded, the guide vane opening is set to the maximum opening, and the rotation speed of the die is adjusted to the blocking speed;
  • Step 3 When the engine head is unloading, the engine head speed is set to the surge speed and the guide vane opening is adjusted.
  • the surge speed and the blocking speed can be calculated in real time according to the pressure ratio and the guide vane opening of the current cycle by the following formula:
  • Pr represents the pressure ratio
  • IGV represents the inlet guide vane opening
  • a ⁇ f represent fitting coefficients, which are coefficients determined according to the compressor model and are pre-written into the control program.
  • the present disclosure provides another control method for a dual-head unit, as shown in FIG2 , the method includes the following steps 200-230:
  • Step 200 Determine the required cooling capacity according to the operating data and temperature value of the dual-head unit in the current cycle
  • Step 210 determining the cooling capacity ratio according to the ratio of the determined required cooling capacity to the nominal cooling capacity
  • Step 220 Obtain the efficiency map of the dual-head unit, and determine the first abscissa value of the intersection of the single-head and dual-head dividing line and the abscissa axis in the efficiency map of the dual-head unit and the second abscissa value of the maximum flow and the highest pressure ratio point according to the cooling capacity proportion and the information of the single-head and dual-head dividing line in the efficiency map of the dual-head unit;
  • Step 230 When the cooling capacity ratio is less than or equal to the first horizontal coordinate value, the dual-head unit starts one head in the next cycle; when the cooling capacity ratio is greater than or equal to the second horizontal coordinate value, the dual-head unit starts two heads in the next cycle.
  • step 200 and step 210 are respectively the same as the methods of step 100 and step 110.
  • the efficiency spectrum of the dual-head unit in step 220 is the same as the efficiency spectrum of the dual-head unit in step 120.
  • step 220 the first abscissa of the intersection of the single-head and double-head dividing line and the abscissa axis in the double-head unit efficiency spectrum is shown as point C in FIG5, and the second abscissa of the maximum flow rate and the highest pressure ratio point is shown as point A in FIG5;
  • the corresponding boundary pressure ratio is determined according to the cooling capacity ratio.
  • the cooling capacity ratio is less than or equal to the first horizontal coordinate point C, the dual-head unit starts one head; when the cooling capacity ratio is greater than or equal to the second horizontal coordinate point A, the dual-head unit starts two heads.
  • the disclosed embodiment provides a control device for a dual-head machine set, as shown in FIG3 , the device includes: a memory 310 and a processor 320;
  • the memory 310 is used to store the control program for the dual-head unit
  • the processor 320 is used to read and execute the control program for the dual-head unit, and execute the control method for the dual-head unit of any of the above embodiments.
  • the disclosed embodiment provides a computer-readable storage medium storing computer-executable instructions.
  • the control method of the centrifugal chiller of any of the above embodiments is performed.
  • the disclosed embodiment provides another control method for a dual-head unit.
  • the flow chart of the control method is shown in FIG8 .
  • the specific implementation process is as follows:
  • Step 701. Obtain the operation data and temperature value of the dual-head unit to determine the cooling capacity ratio
  • Step 702 Calculate the corresponding boundary pressure ratio according to the determined cooling capacity ratio
  • Step 703. Determine the minimum pressure ratio, and determine the number of heads of the dual-head unit in operation based on the minimum pressure ratio and the boundary pressure ratio.
  • Step 704. Control the operating parameters according to the speed-guide vane coupling PID according to the number of heads opened;
  • Step 705 Send the operating parameters to the actuator, and control the operating parameters of the unit through the actuator.
  • a control method for a dual-head unit proposed in an embodiment of the present disclosure is based on physical characteristics and combined with PID control. It has strong theoretical explanatory power, stable control effect, and is easy to implement without changing/adding any hardware.
  • the unit is controlled according to the compressor speed and inlet guide vanes for optimal operating efficiency.
  • the unit control method is simpler and can achieve high-efficiency operation under low-load conditions.
  • Such software may be distributed on a computer-readable medium, which may include a computer storage medium (or non-transitory medium) and a communication medium (or temporary medium).
  • a computer storage medium includes volatile and non-volatile, removable and non-removable media implemented in any method or technology for storing information (such as computer-readable instructions, data structures, program modules, or other data).
  • Computer storage media include, but are not limited to, RAM, ROM, EEPROM, flash memory or other memory technology, CD-ROM, digital versatile disks (DVD) or other optical disk storage, magnetic cassettes, magnetic tapes, magnetic disk storage or other magnetic storage devices, or any other medium that can be used to store the desired information and can be accessed by a computer.
  • communication media typically includes computer Machine-readable instructions, data structures, program modules, or other data in a modulated data signal such as a carrier wave or other transport mechanism, and may include any information delivery media.

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Abstract

一种双机头机组的控制方法、装置和存储介质，所述方法包括：获取当前周期双机头机组的运行数据及温度值确定需求冷量，根据所确定的需求冷量和名义冷量之比确定冷量占比；获取双机头机组效率图谱，其中，所述双机头机组效率图谱中横坐标为冷量占比，纵坐标为压比；根据所述冷量占比和所述双机头机组效率图谱中的单、双机头分界线的信息确定所述冷量占比对应的分界压比；确定最小压比，并根据所述最小压比和所述分界压比确定所述双机头机组运行的机头数。

Description

一种双机头机组的控制方法、装置和存储介质
本申请要求于2023年04月21日提交中国专利局、申请号为202310432817.5、发明名称为“一种双机头机组的控制方法和装置”的中国专利申请的优先权，其内容应理解为通过引用的方式并入本申请中。
技术领域
本文涉及空调技术，尤指一种双机头机组的控制方法、装置和存储介质。
背景技术
离心式冷水机组以其容量大、效率高在大中型建筑空调系统中得到广泛应用，在一些应用场景中，单机组容量可达1000冷吨以上，机组可能由2台或多台压缩机提供循环动力。由于运行时功耗较高，对于双(多)机头的冷水机组，其运行节能具有重要的意义。一些技术中，对于空调水系统的优化控制常以机组启停等方式对机组进行控制，对于机组本身的运行能效关注度不高，针对性的优化控制方案不多。对于双(多)机头机组常采用机头同增同减的方式以解决不同压头间压-流平衡问题，故在一些负荷工况下机组能效较低。另一方面，常规的多机头变频离心式冷水机组运行策略主要从降低变频离心式压缩机启动和关闭时的压比等可靠性方面进行优化，并未根据变频离心式压缩机在变工况变负载时的效率曲线，以机组最优能效为目标进行控制策略优化。在实际使用中，冷水机组大部分时间处于部分负荷运行，因此，亟待需要一种通过改善多机头变频离心式冷水机组的运行控制方法，以有效提高机组的部分负荷能效，从而降低机组运行能耗和运行费用。
发明内容
以下是对本文详细描述的主题的概述。本概述并非是为了限制权利要求的保护范围。
本公开实施例提供了一种双机头机组的控制方法，所述方法包括：
根据当前周期双机头机组的运行数据及温度值确定需求冷量；根据所确定的需求冷量和名义冷量之比确定冷量占比；
获取双机头机组效率图谱，其中，所述双机头机组效率图谱中横坐标为冷量占比，纵坐标为压比；根据所述冷量占比和所述双机头机组效率图谱中的单、双机头分界线的信息，确定所述冷量占比对应的分界压比；
确定最小压比，并根据所述最小压比和所述分界压比确定下一个周期所述双机头机组运行的机头数；其中，所述最小压比为理论最低冷凝压力和理论最高蒸发压力的比值。
一种示例性的实施例中，所述双机头机组效率图谱包括单机头运行时的第一效率等高线和双机头运行时的第二效率等高线；
所述单、双机头分界线通过以下方式确定：
确定所述双机头机组效率图谱中单机头运行时的最大流量与最高压比点；
确定所述双机头机组效率图谱中，相同效率值的第一效率等高线和第二效率等高线在小冷量比例侧的等高线交界点；
根据所述最大流量与最高压比点，及所述等高线交界点，确定所述单、双机头分界线。
一种示例性的实施例中，所述相同效率值是图谱上效率最高或次高的效率值。
一种示例性的实施例中，所述双机头机组效率图谱通过以下步骤确定：
获取所述双机头机组在双机头运行模式下的第一效率图谱；
将所述第一效率图谱中数据的横坐标乘以50％，纵坐标不变，得到所述双机头机组在单机头运行模式下的第二效率图谱；
将所述第一效率图谱和第二效率图谱叠加，得到所述双机头机组在单机头运行和双机头运行时的双机头机组效率图谱。
一种示例性的实施例中，所述确定所述双机头机组效率图谱中单机头运行时的最大流量与最高压比点，包括：
确定所述双机头机组效率图谱中单机头运行时的最大冷量占比；
确定所述双机头机组效率图谱中单机头运行时的最高压比；
根据所确定的最大冷量占比与所确定的最高压比确定所述双机头机组效率图谱中单机头运行时的最大流量与最高压比点。
一种示例性的实施例中，所述确定所述冷量占比对应的分界压比，包括：
确定所述双机头机组效率图谱中所述单、双机头分界线与横坐标轴的交点的第一横坐标值，以及所述最大流量与最高压比点的第二横坐标值；
在所述冷量占比大于所述第一横坐标值且小于所述第二横坐标值的情况下，再根据所述冷量占比确定相应的分界压比。
下一个周期下一个周期一种示例性的实施例中，所述根据所述最小压比和分界压比确定下一个周期所述双机头机组运行的机头数，包括：
在所述最小压比大于或等于分界压比的情况下，下一个周期所述双机头机组开启一个机头，进入单机头运行模式；
在所述最小压比小于分界压比的情况下，下一个周期所述双机头机组开启两个机头，进入双机头运行模式。
一种示例性的实施例中，所述方法还包括：
在当前所述双机头机组运行的是单机头运行模式，确定出下一个周期开启双机头运行模式的情况下，在满足切换的时间间隔时，切换为双机头运行模式；
在当前运行的是双机头运行模式，确定出下一个周期开启单机头运行模式的情况下，在满足切换的时间间隔时，切换为单机头运行模式。
本公开实施例还提供了一种双机头机组的控制方法，应用于离心式冷水机组，所述方法包括：
根据双机头机组的运行数据及温度值确定需求冷量；根据所确定的需求冷量和名义冷量之比确定冷量占比；
获取双机头机组效率图谱，其中，所述双机头机组效率图谱中横坐标为冷量占比，纵坐标为压比；所述双机头机组效率图谱包括单机头运行时的第一效率等高线和双机头运行时的第二效率等高线；
根据所述冷量占比和所述双机头机组效率图谱中的单、双机头分界线的信息，确定所述双机头机组效率图谱中所述单、双机头分界线与横坐标轴的交点的第一横坐标值，以及最大流量与最高压比点的第二横坐标值；其中，所述单、双机头分界线通过以下方式确定：确定所述双机头机组效率图谱中单机头运行时的最大流量与最高压比点；确定所述双机头机组效率图谱中，相同效率值的第一效率等高线和第二效率等高线在小冷量比例侧的等高线交界点；根据所述最大流量与最高压比点，及所述等高线交界点，确定所述单、双机头分界线；
在所述冷量占比小于或等于所述第一横坐标值的情况下，下一个周期双机头机组开启一个机头；在所述冷量占比大于或等于所述第二横坐标值的情况下，下一个周期双机头机组开启两个机头。
一种示例性的实施例中，所述确定所述双机头机组效率图谱中单机头运行时的最大流量与最高压比点，包括：
确定所述双机头机组效率图谱中单机头运行时的最大冷量占比；
确定所述双机头机组效率图谱中单机头运行时的最高压比；
根据所确定的最大冷量占比与所确定的最高压比确定所述双机头机组效率图谱中单机头运行时的最大流量与最高压比点。本公开实施例还提供了一种双机头机组的控制装置，包括存储器和处理器；所述存储器用于保存用于双机头机组的控制程序，所述处理器用于读取执行所述用于双机头机组的控制程序，执行上述实施例中任一项所述的方法。
本公开实施例还提供了一种计算机可读存储介质，存储有计算机可执行指令，所述计算机可执行指令被处理器执行时进行上述实施例中任一项所述的方法。
在阅读并理解了附图和详细描述后，可以明白其他方面。
附图概述
附图用来提供对本公开实施例技术方案的理解，并且构成说明书的一部分，与本公开实施例的实施例一起用于解释本公开实施例的技术方案，并不构成对本公开实施例技术方案的限制。
图1为本公开实施例的一种双机头机组的控制方法流程图；
图2为本公开实施例的另一种双机头机组的控制方法流程图；
图3为本公开实施例的双机头机组的控制装置示意图；
图4为一些实施例中的离心压缩机效率图谱；
图5是一些示例性实施例中双机头机组效率图谱及切换分界线示意图；
图6是一些示例性实施例中确定双机头机组效率图谱中单机头运行时的最大流量与最高压比点示意图；
图7是一些示例性实施例中双机头机组控制方法示意图；
图8是一些示例性实施例中双机头机组控制方法流程图。
详述
本公开实施例描述了多个实施例，但是该描述是示例性的，而不是限制性的，并且对于本领域的普通技术人员来说显而易见的是，在本公开实施例所描述的实施例包含的范围内可以有更多的实施例和实现方案。尽管在附图中示出了许多可能的特征组合，并在具体实施方式中进行了讨论，但是所公开的特征的许多其它组合方式也是可能的。除非特意加以限制的情况以外，任何实施例的任何特征或元件可以与任何其它实施例中的任何其他特征或元件结合使用，或可以替代任何其它实施例中的任何其他特征或元件。
本公开实施例包括并设想了与本领域普通技术人员已知的特征和元件的组合。本公开实施例已经公开的实施例、特征和元件也可以与任何常规特征或元件组合，以形成由权利要求限定的独特的发明方案。任何实施例的任何特征或元件也可以与来自其它发明方案的特征或元件组合，以形成另一个由权利要求限定的独特的发明方案。因此，应当理解，在本公开实施例中示出和/或讨论的任何特征可以单独地或以任何适当的组合来实现。因此，除了根据所附权利要求及其等同替换所做的限制以外，实施例不受其它限制。此外，可以在所附权利要求的保护范围内进行多种修改和改变。
此外，在描述具有代表性的实施例时，说明书可能已经将方法和/或过程呈现为特定的步骤序列。然而，在该方法或过程不依赖于本文所述步骤的特定顺序的程度上，该方法或过程不应限于所述的特定顺序的步骤。如本领域普通技术人员将理解的，其它的步骤顺序也是可能的。因此，说明书中阐述的步骤的特定顺序不应被解释为对权利要求的限制。此外，针对该方法和/或过程的权利要求不应限于按照所写顺序执行它们的步骤，本领域技术人员可以容易地理解，这些顺序可以变化，并且仍然保持在本公开实施例的精神和范围内。
本公开实施例提供了一种双机头机组的控制方法，如图1所示，该方法包括如下步骤100-130：
步骤100.根据当前周期双机头机组的运行数据及温度值确定需求冷量；
步骤110,根据所确定的需求冷量和名义冷量之比确定冷量占比；
步骤120.获取双机头机组效率图谱，根据所述冷量占比和所述双机头机组效率图谱中的单、双机头分界线的信息确定所述冷量占比对应的分界压比；
步骤130.确定最小压比，并根据所述最小压比和所述分界压比确定下一个周期所述双机头机组运行的机头数。
在本实施例中，温度值包括蒸发器进口水温度值、蒸发器出口水温度值、冷凝进口水温度值、冷凝出口水温度值。
一种示例性的实施例中，在获取双机头机组运行数据、蒸发器进口水温度值EWTe、蒸发器出口水温度值LWTe、冷凝进口水温度值EWTc、冷凝出口水温度值LWTc一系列温度值后，根据下面的4个方程进行联合求解，可以计算出冷却水流量和冷冻水流量：
Qe+P＝Qc；(1)
Qc＝m_flow_cCP(EWTc-LWTc)；(2)
Qe＝m_flow_eCP(EWTe-LWTe)；(3)
P＝CPΔTcm_flow_c-CPΔTem_flow_e+Δ；(4)
上述公式中，Qe表示冷量，P表示压缩机功耗，Qc表示冷凝排热量，CP表示水的比热容，EWTe表示蒸发器进口水温度值，LWTe表示蒸发器出口水温度值，EWTc表示冷凝进口水温度值，LWTc表示冷凝出口水温度值，m_flow_c表示冷却水流量，m_flow_e表示冷冻水流量,Δ表示误差系数，误差系数Δ在理论上是一个接近于0的数，ΔTc＝EWTc-LWTc，ΔTe＝EWTe-LWTe，ΔTc表示冷凝进口水和出口水温度值差；ΔTe表示蒸发器进口水和出口水温度值差。
在本实施例中，根据上述计算出冷却水流量后，根据冷凝进口水温度值、冷凝出口水温度值、冷却水流量和水的比热容，采用公式：
Qc＝m_flow_c CP(EWTc-LWTc)计算出冷凝排热量Qc。
根据上述计算出冷冻水流量后，根据蒸发器进口水温度值，蒸发器出口水温度值、冷冻水流量和水的比热容，采用公式：
Qe＝m_flow_e CP(EWTe-LWTe)计算出冷量Qe。
一种示例性的实施例中，如图4所示的离心压缩机效率图谱，横坐标表示流量因子，纵坐标表示压头因子。横坐标的流量因子是压缩机运行制冷剂流量除以额定制冷剂流量的比值，该流量因子无量纲；纵坐标中的压头因子是压缩机运行压比除以最大压比(最大压比是压缩机设备所能达到的最大值)。压缩机效率图谱是压缩机厂家通过实验测定或其他方法得到的技术数据，表征压缩机运行在不同的制冷剂流量(对应冷量)和不同压比下的效率。在不同的频率和导叶开度下对应的压缩机效率不同，形成等效率线。图4中，IGV＝10°，IGV＝30°，IGV＝50°表示不同的导叶开度；N＝60％，N＝70％，N＝80％，N＝90％，N＝100％表示不同的频率百分比，ηrel＝50％，ηrel＝70％，ηrel＝90％，ηrel＝95％，ηrel＝100％表示不同等效率线。
在压缩机厂家制作压缩机效率图谱时使用了流量(因子)来表征制冷量，由于实际运行时制冷剂流量参数难以实测(系统中一般没有安装流量计)，因此，使用冷量机组制冷量与额定制冷量之比即冷量占比作为横坐标。
根据图4所示的离心压缩机效率图谱可确定，通过冷量占比和压比值可以表征压缩机效率。
基于上述分析，在计算出需求冷量后，可以计算冷量占比和压比；
步骤1、通过用户设定温度、进口水温度和冷冻水流量计算得到需求冷量：
Qe_set＝m_flow_e*CP*(EWTe-LWTe_set)
其中，Qe_set为需求冷量，m_flow_e为冷冻水流量，CP为水的比热容，
4.1868kJ/kg.K，EWTe为蒸发器进口水温度值，LWTe_set为设定的蒸发器出口水温。
步骤2、根据所计算的需求冷量和名义冷量进行相除确定冷量占比：
fQ＝Qe_set/Q_nom；
其中，fQ为冷量占比，Qe_set为需求冷量，Q_nom为名义冷量，该名义冷量是压缩机自带的值，是个已知量。
如图5双机头机组效率图谱及切换分界线所示，双机头机组效率图谱包括单机头运行时的第一效率等高线和双机头运行时的第二效率等高线；图5中的虚线表示双机头运行时的第一效率等高线，实线表示单机头运行时的第二效率等高线，在第一效率等高线和第二效率等高线两者叠合的效率图谱中，确定某个临界点切换至单机头运行以实现节能。比如A点和C点是临界点，线段AC是分界线。
一种示例性的实施例中，双机头机组效率图谱通过以下步骤确定：
步骤1.获取双机头机组在双机头运行模式下的第一效率图谱；
由于双机头机组的两个机头一模一样，且冷量占比是无量钢的参数，因此双机头机组在双机头运行模式下的第一效率图谱与单机头机组的效率图谱是相同的；
步骤2.将所述第一效率图谱中数据的横坐标乘以50％，纵坐标不变，得到双机头机组在单机头运行模式下的第二效率图谱；
本步骤的实现过程是相当于对第一效率图谱进行缩放，横坐标方向缩小为原来的一半，纵坐标方向不变。这样做的原因是：冷量占比等于需求冷量除以名义冷量(固定值)，在绘制双机头机组效率图谱时，无论双机头机组运行于单机头模式还是双机头模式，均是以双机头运行模式下的名义冷量来计算冷量占比，而双机头机组运行于单机头模式时的需求冷量是运行于双机头模式时的50％，因此双机头机组在单机头运行模式下的第二效率图谱可以通过对双机头机组在双机头运行模式下的第一效率图谱进行上述变换得到。
步骤3.将第一效率图谱和第二效率图谱叠加，得到双机头机组在单机头运行和双机头运行时的双机头机组效率图谱。如图5所示，第一效率图谱(双机头机组在双机头运行模式下的第一效率图谱)为虚线，第二效率图谱(双机头机组在单机头运行模式下的第二效率图谱)为实线，将单机头的效率曲线(实线)与双机头的效率曲线(虚线)叠合在同一坐标系下，形成图5所示的双机头机组效率图谱。
一种示例性的实施例中，双机头机组效率图谱中单机头运行时的最大流量与最高压比点(即图5中A点)的确定过程如下：
第一步、确定双机头机组效率图谱中单机头运行时的最大冷量占比；
在本步骤中，该效率图谱上横坐标冷量占比的最大值是冷量的最大值除以额定冷量来确定。该额定冷量是压缩机的产品参数，是已知值。单机头运行时的最大冷量占比是效率图谱上横坐标的一半。
第二步、确定所述双机头机组效率图谱中单机头运行时的最高压比；
在本步骤中，该最高压比可以通过效率图谱上的值来确定。比如图6中，最高压比是5。
第三步、所确定的最大冷量占比线(图6中的线1)与所确定的最高压比线(图6中的线2)的交点作为双机头机组效率图谱中单机头运行时的最大流量与最高压比点(A点)。
一种示例性的实施例中，该单、双机头分界线通过以下方式确定：
第一步、确定双机头机组效率图谱中单机头运行时的最大流量与最高压比点；
第二步、确定双机头机组效率图谱中，相同效率值的第一效率等高线和第二效率等高线在小冷量比例侧的等高线交界点；
第三步、根据所述最大流量与最高压比点，及所述等高线交界点，确定所述单、双机头分界线。在本实施例中，该相同效率值是双机头机组效率图谱上效率最高或次高的效率值。具体的该单、双机头分界线的实现过程如下：如图5所示，该单、双机头分界线通过两个点确定，第一点为单机头运行时最大流量与最高压比点，即A点；第二点为在小冷量比例侧等高线交界点，即B点。在确定了A点和B点两点后，根据两点可以通过直线公式得到单、双机头分界线，具体如下：
已知直线过A(x1,y1)，B(x2,y2)，则直线为y-y1＝(y2-y1)/(x2-x1)*(x-x1)，得到y＝ax+b,a＝(y2-y1)/(x2-x1),b＝y1-x1*(y2-y1)/(x2-x1)。
在确定上述的a、b后，得到冷量占比对应的分界压比分界线：
Pr＝a*fQ+b；
其中，Pr表示分界压比，fQ表示冷量占比，a、b分别为所述单、双机头分界线的斜率和截距。
一种示例性的实施例中，根据最小压比和分界压比确定双机头机组运行的机头数，包括：
在最小压比大于等于分界压比的情况下，双机头机组开启一个机头；
在最小压比小于分界压比的情况下，双机头机组开启两个机头。其中，最小压比的具体计算过程如下：
由于存在热阻，蒸发温度低于冷冻水出水温度，故理论最高蒸发压力可以通过冷冻水出水温度设定值LWTe_set计算得到：
Pe_max＝exp(21.29919+(-2087.7908/LWT_e_set+239.6562))/1000
其中，Pe_max为理论最高蒸发压力，LWTe_set为冷冻水出水温度设定值，单位为℃，Pe_max单位为kPa。同理，由于存在热阻，冷凝压力高于冷却水出水温度对应的制冷剂饱和压力，故理论最低冷凝压力可以通过冷却水出水温度(LWTc)计算得到：
Pc_min＝exp(21.29919+(-2087.7908/LWTc+239.6562))/1000
其中，Pc_min为理论最低冷凝压力，LWTc为冷凝出口水温度值，单位为℃，其可以用冷凝温度替代，或者使用冷凝进口水温加上设计水温差，Pc_min单位为kPa。
最小压比为：
Pr_min＝Pc_min/Pe_max；
上述公式中，Pr_min为最小压比，Pc_min为理论最低冷凝压力，Pe_max为理论最高蒸发压力。
一种示例性的实施例中，根据所述最小压比和分界压比确定双机头机组运行的机头数，方法还包括：在当前运行的是单机头运行模式，而确定下一个周期开启双机头运行模式的情况下，在满足切换的时间间隔时，则切换为双机头运行模式；在当前运行的是双机头运行模式，而确定下一个周期开启单机头运行模式的情况下，在满足切换的时间间隔时，则切换为单机头运行模式。
一种示例性的实施例中，如图7所示，从机组运行数据中获取当前运行状态，双机头效率图谱确定切换分界值；从机组运行数据中输入水流量或计算水流量，进一步计算出需求冷量；根据所确定的切换分界值和需求冷量确定运行的机头数；根据需求冷量、当双机头切换界线值确定出运行的机头数后，根据转速-导叶耦合控制方法进行调整。
一种示例性的实施例中，当双机头切换界线值确定出运行的机头数后，根据转速-导 叶耦合控制方法进行调整。转速-导叶耦合控制核心思想为在加载时尽量先使导叶开度开至最大再调节转速，卸载时则先调节转速(直至喘振转速限制)，再调节导叶开度。例如：当确定下一个周期双机头机组切换的运行模式后，根据转速-导叶耦合控制方法进行调整，具体如下：
第一步、根据当前周期的压比和进口导叶开度分别确定喘振转速和阻塞转速；
第二步、在所述机头加载时，将导叶开度设置为最大开度，调节所述机头的转速至阻塞转速；
第三步、在所述机头卸速时，将所述机头的转速设置为喘振转速，调节导叶开度。其中，喘振转速和阻塞转速可根据当前周期的压比与导叶开度通过如下公式实时计算得到：
阻塞速度Spd_choke＝a+b·Pr+c/Pr2
喘振速度Spd_surge＝a+b/IGV+c·Pr+d/IGV2+e·Pr2+f·Pr/IGV
其中，Pr表示压比，IGV表示进口导叶开度，a～f表示拟合系数，它们为根据压缩机型号确定的系数，预先写入控制程序。
本公开实施例提供了另一种双机头机组的控制方法，如图2所示，该方法包括如下步骤200-230：
步骤200.根据当前周期双机头机组的运行数据及温度值确定需求冷量；
步骤210,根据所确定的需求冷量和名义冷量之比确定冷量占比；
步骤220.获取双机头机组效率图谱，根据所述冷量占比和所述双机头机组效率图谱中的单、双机头分界线的信息，确定所述双机头机组效率图谱中所述单、双机头分界线与横坐标轴的交点的第一横坐标值，以及最大流量与最高压比点的第二横坐标值；
步骤230.在所述冷量占比小于或等于所述第一横坐标值的情况下，在下一个周期所述双机头机组开启一个机头；在所述冷量占比大于或等于所述第二横坐标值的情况下，在下一个周期所述双机头机组开启两个机头。
其中，步骤200和步骤210的方法分别与步骤100和步骤110的方法相同。步骤220中的双机头机组效率图谱与步骤120中的双机头机组效率图谱相同。
在步骤220中，双机头机组效率图谱中单、双机头分界线与横坐标轴的交点的第一横坐标如图5中的C点所示，最大流量与最高压比点的第二横坐标如图5中的A点所示；
在冷量占比大于所述第一横坐标且小于所述第二横坐标的情况下，再根据冷量占比确定相应的分界压比。在冷量占比小于或等于第一横坐标C点的情况下，双机头机组开启一个机头；在冷量占比大于或等于第二横坐标A点的情况下，双机头机组开启两个机头。
本公开实施例提出了一种双机头机组的控制装置，如图3所示，装置包括：存储器310和处理器320；
存储器310用于保存用于双机头机组的控制程序；
处理器320用于读取执行用于双机头机组的控制程序，执行上述任一实施例的双机头机组的控制方法。
本公开实施例提出了一种计算机可读存储介质，存储有计算机可执行指令，计算机可执行指令被处理器执行时进行上述任一实施例的离心冷水机组的控制方法。
本公开实施例提供了又一种双机头机组的控制方法，该控制方法的流程示意图如图8所示，具体实现流程如下：
步骤701.获取双机头机组运行数据及温度值确定冷量占比；
步骤702.根据所确定的冷量占比计算相应的分界压比；
步骤703.确定最小压比，并根据最小压比和分界压比确定双机头机组运行的机头数。
步骤704.根据机头开启数按照转速-导叶耦合PID控制运行参数；
步骤705.将运行参数，发给执行器，通过执行器控制机组运行参数。
本公开实施例所提出的一种双机头机组的控制方法，基于物理特性且结合PID控制，理论解释性强，控制效果稳定，易于实施，无需更改/添加任何硬件；根据最佳运行效率的压缩机转速和进口导叶控制机组，机组控制方法更简单，该控制方法可以实现低负荷工况下的高能效运行。
本领域普通技术人员可以理解，上文中所公开方法中的全部或某些步骤、系统、装置中的功能模块/单元可以被实施为软件、固件、硬件及其适当的组合。在硬件实施方式中，在以上描述中提及的功能模块/单元之间的划分不一定对应于物理组件的划分；例如，一个物理组件可以具有多个功能，或者一个功能或步骤可以由若干物理组件合作执行。某些组件或所有组件可以被实施为由处理器，如数字信号处理器或微处理器执行的软件，或者被实施为硬件，或者被实施为集成电路，如专用集成电路。这样的软件可以分布在计算机可读介质上，计算机可读介质可以包括计算机存储介质(或非暂时性介质)和通信介质(或暂时性介质)。如本领域普通技术人员公知的，术语计算机存储介质包括在用于存储信息(诸如计算机可读指令、数据结构、程序模块或其他数据)的任何方法或技术中实施的易失性和非易失性、可移除和不可移除介质。计算机存储介质包括但不限于RAM、ROM、EEPROM、闪存或其他存储器技术、CD-ROM、数字多功能盘(DVD)或其他光盘存储、磁盒、磁带、磁盘存储或其他磁存储装置、或者可以用于存储期望的信息并且可以被计算机访问的任何其他的介质。此外，本领域普通技术人员公知的是，通信介质通常包含计算 机可读指令、数据结构、程序模块或者诸如载波或其他传输机制之类的调制数据信号中的其他数据，并且可包括任何信息递送介质。

Claims (12)

  1. 一种双机头机组的控制方法，应用于离心式冷水机组，所述方法包括：
    根据当前周期双机头机组的运行数据及温度值确定需求冷量；根据所确定的需求冷量和名义冷量之比确定冷量占比；
    获取双机头机组效率图谱，其中，所述双机头机组效率图谱中横坐标为冷量占比，纵坐标为压比；
    根据所述冷量占比和所述双机头机组效率图谱中的单、双机头分界线的信息，确定所述冷量占比对应的分界压比；
    确定最小压比，并根据所述最小压比和所述分界压比确定下一个周期所述双机头机组运行的机头数；其中，所述最小压比为理论最低冷凝压力和理论最高蒸发压力的比值。
  2. 如权利要求1所述的双机头机组的控制方法，其中，
    所述双机头机组效率图谱包括单机头运行时的第一效率等高线和双机头运行时的第二效率等高线；
    所述单、双机头分界线通过以下方式确定：
    确定所述双机头机组效率图谱中单机头运行时的最大流量与最高压比点；
    确定所述双机头机组效率图谱中，相同效率值的第一效率等高线和第二效率等高线在小冷量比例侧的等高线交界点；
    根据所述最大流量与最高压比点，及所述等高线交界点，确定所述单、双机头分界线。
  3. 如权利要求2所述的双机头机组的控制方法，其中，所述相同效率值是图谱上效率最高或次高的效率值。
  4. 如权利要求1所述的双机头机组的控制方法，其中，
    所述双机头机组效率图谱通过以下步骤确定：
    获取双机头机组在双机头运行模式下的第一效率图谱；
    将所述第一效率图谱中数据的横坐标乘以50％，纵坐标不变，得到双机头机组在单机头运行模式下的第二效率图谱；
    将所述第一效率图谱和第二效率图谱叠加，得到所述双机头机组在单机头运行和双机头运行时的双机头机组效率图谱。
  5. 如权利要求2所述的双机头机组的控制方法，其中，所述确定所述双机头机组效率图谱中单机头运行时的最大流量与最高压比点，包括：
    确定所述双机头机组效率图谱中单机头运行时的最大冷量占比；
    确定所述双机头机组效率图谱中单机头运行时的最高压比；
    根据所确定的最大冷量占比与所确定的最高压比确定所述双机头机组效率图谱中单机头运行时的最大流量与最高压比点。
  6. 如权利要求5所述的双机头机组的控制方法，其中，
    所述确定所述冷量占比对应的分界压比，包括：
    确定所述双机头机组效率图谱中所述单、双机头分界线与横坐标轴的交点的第一横坐标值，以及所述最大流量与最高压比点的第二横坐标值；
    在所述冷量占比大于所述第一横坐标值且小于所述第二横坐标值的情况下，再根据所述冷量占比确定相应的分界压比。
  7. 如权利要求6所述的双机头机组的控制方法，其中，所述根据所述最小压比和分界压比确定下一个周期所述双机头机组运行的机头数，包括：
    在所述最小压比大于或等于分界压比的情况下，下一个周期所述双机头机组开启一个机头，进入单机头运行模式；
    在所述最小压比小于分界压比的情况下，下一个周期所述双机头机组开启两个机头，进入双机头运行模式。
  8. 如权利要求7所述的双机头机组的控制方法，所述方法还包括：
    在当前所述双机头机组运行的是单机头运行模式，确定出下一个周期开启双机头运行模式的情况下，在满足切换的时间间隔时，切换为双机头运行模式；
    在当前运行的是双机头运行模式，确定出下一个周期开启单机头运行模式的情况下，在满足切换的时间间隔时，切换为单机头运行模式。
  9. 一种双机头机组的控制方法，应用于离心式冷水机组，所述方法包括：
    根据双机头机组的运行数据及温度值确定需求冷量；根据所确定的需求冷量和名义冷量之比确定冷量占比；
    获取双机头机组效率图谱，其中，所述双机头机组效率图谱中横坐标为冷量占比，纵坐标为压比；所述双机头机组效率图谱包括单机头运行时的第一效率等高线和双机头运 行时的第二效率等高线；
    根据所述冷量占比和所述双机头机组效率图谱中的单、双机头分界线的信息，确定所述双机头机组效率图谱中所述单、双机头分界线与横坐标轴的交点的第一横坐标值，以及最大流量与最高压比点的第二横坐标值；其中，所述单、双机头分界线通过以下方式确定：确定所述双机头机组效率图谱中单机头运行时的最大流量与最高压比点；确定所述双机头机组效率图谱中，相同效率值的第一效率等高线和第二效率等高线在小冷量比例侧的等高线交界点；根据所述最大流量与最高压比点，及所述等高线交界点，确定所述单、双机头分界线；
    在所述冷量占比小于或等于所述第一横坐标值的情况下，在下一个周期所述双机头机组开启一个机头；在所述冷量占比大于或等于所述第二横坐标值的情况下，在下一个周期所述双机头机组开启两个机头。
  10. 如权利要求9所述的双机头机组的控制方法，其中，所述确定所述双机头机组效率图谱中单机头运行时的最大流量与最高压比点，包括：
    确定所述双机头机组效率图谱中单机头运行时的最大冷量占比；
    确定所述双机头机组效率图谱中单机头运行时的最高压比；
    根据所确定的最大冷量占比与所确定的最高压比确定所述双机头机组效率图谱中单机头运行时的最大流量与最高压比点。
  11. 一种双机头机组的控制装置，包括存储器和处理器；其中，所述存储器用于保存用于双机头机组的控制程序，所述处理器用于读取执行所述用于双机头机组的控制程序，执行如权利要求1-8中任一项所述的控制方法，或如权利要求9-10中任一项所述的控制方法。
  12. 一种计算机可读存储介质，存储有计算机可执行指令，其中，所述计算机可执行指令被处理器执行时进行如权利要求1-8中任一项所述的双机头机组的控制方法，或如权利要求9-10中任一项所述的双机头机组的控制方法。
PCT/CN2024/078404 2023-04-21 2024-02-23 一种双机头机组的控制方法、装置和存储介质 Ceased WO2024217147A1 (zh)

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