WO2018077048A1 - Procédé de commande d'optimisation d'intervalle de fonctionnement d'éjecteur - Google Patents

Procédé de commande d'optimisation d'intervalle de fonctionnement d'éjecteur Download PDF

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Publication number
WO2018077048A1
WO2018077048A1 PCT/CN2017/106079 CN2017106079W WO2018077048A1 WO 2018077048 A1 WO2018077048 A1 WO 2018077048A1 CN 2017106079 W CN2017106079 W CN 2017106079W WO 2018077048 A1 WO2018077048 A1 WO 2018077048A1
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WIPO (PCT)
Prior art keywords
injector
value
pressure
primary flow
proportional coefficient
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Ceased
Application number
PCT/CN2017/106079
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English (en)
Chinese (zh)
Inventor
王雷
侯文秀
王辰
赵红霞
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Shandong University
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Shandong University
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Publication date
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Publication of WO2018077048A1 publication Critical patent/WO2018077048A1/fr
Anticipated expiration legal-status Critical
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/08—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using ejectors
    • 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

Definitions

  • the invention relates to the technical field of refrigeration, and in particular relates to an optimized control method for an operating range of an injector.
  • the injector replaces the compressor in a conventional refrigeration system and is a key component in a jet refrigeration system.
  • An ejector is a device that mixes two different pressure fluids with each other and exchanges energy to form a mixed fluid at a center pressure. It does not directly consume mechanical work or electrical energy to improve parameters such as fluid pressure and temperature. It has a simple structure, low cost, no moving parts, and is suitable for use in any flow pattern including two-phase flow. Ejectors have long been used in low-grade heat source-driven refrigeration systems and are a good source of energy recovery for waste heat.
  • the injector usually consists of a main nozzle, a receiving chamber, a mixing chamber and a diffusing chamber.
  • the static pressure energy and thermal energy of the gas flow are converted into kinetic energy to form a low pressure at the nozzle outlet to generate a suction effect on the ejector fluid, and due to the turbulent diffusion of the jet boundary layer,
  • the energy is exchanged with the surrounding entrained ejector fluid to form a pressure-centered mixed fluid.
  • the speed equalization of the working fluid and the ejector fluid after entering the mixing chamber is usually accompanied by an increase in pressure. Subsequently, the fluid enters the diffuser chamber, the speed is continuously slowed down, and the kinetic energy is continuously converted into static pressure energy.
  • the injector When the back pressure of the injector is different, the injector is in three different operating modes, namely critical mode, subcritical mode, and reflow mode. As shown in FIG. 2, when the back pressure is small, the injection coefficient of the injector always maintains a constant value as the back pressure increases, and the injection coefficient is the maximum value at this time. When the back pressure increases to the critical point, the back pressure continues to increase, and the injection coefficient decreases rapidly until it decreases to zero. This process is a subcritical mode. The back pressure continues to increase and reflow occurs, at which point the injector operates in reflow mode. Among them, the critical back pressure is the critical value of the transition between the critical mode and the subcritical mode, which is the critical operating point of the injector.
  • the mode of operation of the injector is greatly affected by the primary flow pressure.
  • the object of the present invention is to solve the above problems, and an optimized control method for an operating range of an injector is proposed, which enables the injector to operate in an optimal working range, thereby ensuring stable operation of the system.
  • An optimized control method for an injector operating interval includes the following steps:
  • the relationship between the primary flow pressure of the injector and the critical back pressure is approximately proportional to a linear relationship, wherein the ratio
  • the coefficient is K
  • the unknown constant is B
  • the K value and the B value are determined by least squares method
  • the proportional coefficient K s is a set multiple of the proportional coefficient K*, and the working interval of the injector is divided into three parts according to the proportional coefficient K* and the proportional coefficient K s ;
  • the working state of the injector is determined, and the injector is operated in a stable operating state by adjusting the generated pressure value.
  • step (1) is:
  • the correlation R 2 is used to evaluate the accuracy of the calculated P g value.
  • step 2) is:
  • the calculation method of the correlation R 2 is:
  • the proportional coefficient K* at the critical point of the injector is specifically:
  • P g is the primary flow pressure value when the injector performance is optimal.
  • K* is the proportional coefficient at the critical point of the injector, and ⁇ is a positive number.
  • the method of the invention enables the injector to operate in an optimal working range, which is beneficial to improving the energy efficiency and stability of the system.
  • Figure 1 is a diagram of the composition of the injector and its working pressure diagram
  • Figure 2 is a schematic diagram of three different modes of operation of the injector
  • Figure 3 (b) is a schematic diagram showing the relationship between primary flow pressure and back pressure
  • Figure 3 (c) is a schematic diagram showing the connection of critical back pressure values under different working conditions
  • Figure 4 is a schematic view of the working section of the injector.
  • An optimized control method for an injector operating interval includes the following steps:
  • the relationship between the primary flow pressure of the injector and the critical back pressure is approximately proportional to a linear relationship, wherein the proportional coefficient is K, the unknown constant is B, and the K value and the B value are determined by least squares method;
  • the proportional coefficient K s is a set multiple of the proportional coefficient K*, and the working interval of the injector is divided into three parts according to the proportional coefficient K* and the proportional coefficient K s ;
  • the working state of the injector is determined, and the injector is operated in a stable operating state by adjusting the generated pressure value.
  • Fig. 3(a) The three-dimensional relationship between the available injection coefficient, primary flow pressure and back pressure is shown in Fig. 3(a).
  • Fig. 3(b) can be clearly seen from Fig. 3(b).
  • the primary flow pressure is approximately proportional to the back pressure.
  • Fig. 3(c) the critical back pressure values under different operating conditions are connected.
  • the injector structure is fixed, the increase of the primary flow pressure leads to a decrease in the injection coefficient and an increase in the critical back pressure.
  • y i is the actual value
  • f(x i ) is the function value calculated by x; the closer R 2 is to 1, the higher the correlation, the higher the accuracy.
  • an operating range is defined, in which the injector can operate efficiently and stably, that is, the optimal interval, and the injector operating interval is controlled within this range. Significance.
  • the following provides an optimal operation interval control method for the injector.
  • K* the slope at the critical point of the injector
  • P g the primary flow pressure value when the injector performance is optimal.
  • ⁇ is a positive number, for example 0.1.
  • the injector operating range can be divided into three parts by K*, K s , as shown in Figure 4.
  • the injector is operated in the optimal interval, the shaded part in Fig. 4, in Fig. 4, the primary flow pressure value when P gL is in the critical working state (that is, when K is K*), P gH is the primary flow pressure value when K is K s , and P cL and P cH are determined according to the actual working state.
  • the injector system can operate stably and stably.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Jet Pumps And Other Pumps (AREA)

Abstract

L'invention concerne un procédé de commande d'optimisation d'intervalle de fonctionnement d'un éjecteur qui comprend les étapes suivantes consistant à : approximer la relation entre une pression d'écoulement primaire d'un éjecteur et une contre-pression critique vers une relation linéaire directement proportionnelle, et déterminer un coefficient de proportionnalité K* au niveau d'un point critique de l'éjecteur conformément à une valeur de pression d'écoulement primaire optimale; diviser un intervalle de travail de l'éjecteur en trois parties conformément au coefficient de proportionnalité K* et à un coefficient de proportionnalité Ks; déterminer un état de travail de l'éjecteur conformément à l'intervalle de travail au lequel se trouve le coefficient de proportionnalité K de l'éjecteur pendant un travail pratique, et permettre à l'éjecteur de travailler à un état de fonctionnement stable au moyen d'un réglage d'une valeur d'apparition de pression.
PCT/CN2017/106079 2016-10-27 2017-10-13 Procédé de commande d'optimisation d'intervalle de fonctionnement d'éjecteur Ceased WO2018077048A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201610970116.7 2016-10-27
CN201610970116.7A CN106500383B (zh) 2016-10-27 2016-10-27 一种喷射器运行区间的优化控制方法

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WO2018077048A1 true WO2018077048A1 (fr) 2018-05-03

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CN (1) CN106500383B (fr)
WO (1) WO2018077048A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113553675A (zh) * 2021-07-29 2021-10-26 上海电力大学 一种喷射器优化方法及装置

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106529712B (zh) * 2016-10-27 2019-03-22 山东大学 一种喷射器临界工作点引射比预测优化方法
CN106500383B (zh) * 2016-10-27 2019-07-05 山东大学 一种喷射器运行区间的优化控制方法
CN111857192B (zh) * 2019-04-29 2024-03-05 新奥数能科技有限公司 喷射器的调控方法及装置
CN115569754B (zh) * 2022-09-27 2024-10-25 山东大学 一种可调喷射器变工况运行的控制方法和系统

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1134517A2 (fr) * 2000-03-15 2001-09-19 Denso Corporation Système à cycle d'éjection avec pression critique du fluide frigorigène
CN101532513A (zh) * 2008-03-12 2009-09-16 株式会社电装 喷射器
CN102142048A (zh) * 2011-01-25 2011-08-03 西安交通大学 一种用于引射器的通用优化设计方法
JP4812665B2 (ja) * 2007-03-16 2011-11-09 三菱電機株式会社 エジェクタ及び冷凍サイクル装置
CN103148649A (zh) * 2013-03-27 2013-06-12 上海理工大学 蒸汽压缩制冷循环系统中喷射器设计方法
EP2754978A1 (fr) * 2013-01-15 2014-07-16 Epta S.p.A. Installation frigorifique avec éjecteur
CN104504252A (zh) * 2014-12-10 2015-04-08 广西大学 一种跨临界co2制冷循环中喷射器的扩压室效率的评价方法
CN106500383A (zh) * 2016-10-27 2017-03-15 山东大学 一种喷射器运行区间的优化控制方法

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Publication number Priority date Publication date Assignee Title
CN104406327A (zh) * 2014-12-16 2015-03-11 山东大学 多模废热驱动汽车空调系统

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1134517A2 (fr) * 2000-03-15 2001-09-19 Denso Corporation Système à cycle d'éjection avec pression critique du fluide frigorigène
CN1316636A (zh) * 2000-03-15 2001-10-10 株式会社电装 具有临界致冷剂压力的排出管循环系统
JP4812665B2 (ja) * 2007-03-16 2011-11-09 三菱電機株式会社 エジェクタ及び冷凍サイクル装置
CN101532513A (zh) * 2008-03-12 2009-09-16 株式会社电装 喷射器
CN102142048A (zh) * 2011-01-25 2011-08-03 西安交通大学 一种用于引射器的通用优化设计方法
EP2754978A1 (fr) * 2013-01-15 2014-07-16 Epta S.p.A. Installation frigorifique avec éjecteur
CN103148649A (zh) * 2013-03-27 2013-06-12 上海理工大学 蒸汽压缩制冷循环系统中喷射器设计方法
CN104504252A (zh) * 2014-12-10 2015-04-08 广西大学 一种跨临界co2制冷循环中喷射器的扩压室效率的评价方法
CN106500383A (zh) * 2016-10-27 2017-03-15 山东大学 一种喷射器运行区间的优化控制方法

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113553675A (zh) * 2021-07-29 2021-10-26 上海电力大学 一种喷射器优化方法及装置
CN113553675B (zh) * 2021-07-29 2022-12-13 上海电力大学 一种喷射器优化方法及装置

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CN106500383B (zh) 2019-07-05

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