CN109682137B - Control method and system of water chilling unit - Google Patents

Control method and system of water chilling unit Download PDF

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Publication number
CN109682137B
CN109682137B CN201811547523.2A CN201811547523A CN109682137B CN 109682137 B CN109682137 B CN 109682137B CN 201811547523 A CN201811547523 A CN 201811547523A CN 109682137 B CN109682137 B CN 109682137B
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pressure
intermediate pressure
water chilling
chilling unit
target value
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CN109682137A (en
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周登青
王永
李镇杉
张运乾
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Midea Group Co Ltd
Chongqing Midea General Refrigeration Equipment Co Ltd
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Midea Group Co Ltd
Chongqing Midea General Refrigeration Equipment Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/004—Gas cycle refrigeration machines using a compressor of the rotary type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/077—Compressor control units, e.g. terminal boxes, mounted on the compressor casing wall containing for example starter, protection switches or connector contacts

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

The application provides a control method and a control system of a water chilling unit. The control method of the water chilling unit comprises the following steps: detecting the evaporator pressure and the condenser pressure of the water chilling unit; obtaining a target value of an intermediate pressure according to the pressure of the evaporator and the pressure of the condenser, wherein the intermediate pressure refers to the pressure between a first-stage throttling and a second-stage throttling in the water chilling unit; and adjusting the secondary throttle opening according to the target value of the intermediate pressure. The control method of the water chilling unit can effectively improve the operable frequency range of the water chilling unit and improve the operation energy efficiency of the water chilling unit under partial operation load.

Description

Control method and system of water chilling unit
Technical Field
The application relates to the technical field of refrigeration equipment, in particular to a control method and a control system for a water chilling unit.
Background
In the related art, a two-stage centrifugal compressor is widely used in a centrifugal chiller, in the centrifugal chiller, an economizer (or a power saver) is usually arranged behind a first-stage throttling device, refrigerant liquid is throttled and flashed (i.e., rapidly evaporated) through the first-stage throttling device, a gas-liquid two-phase refrigerant enters an economizer shell through an input pipe, part of the refrigerant liquid is continuously flashed in the economizer shell, and flashed gas enters a compressor air supplement port through an air supplement pipe, so that the temperature of gas at a second-stage inlet of the compressor is reduced, the mass flow is increased, and the efficiency of the compressor is improved. The unevaporated refrigerant liquid flows out of the liquid outlet pipe, enters the evaporator for evaporation and refrigeration after secondary throttling, so that the refrigerating capacity of the unit is increased, the power consumption is reduced, and the purpose of energy conservation is achieved.
For a two-stage centrifugal water chiller, because the energy efficiency of the chiller is more sensitive to the first-stage throttling, in order to improve the whole-time operation energy efficiency of the chiller, an electronic expansion valve or an analog quantity electric butterfly valve is usually adopted for carrying out first-stage auxiliary adjustment on the centrifuge with smaller energy, so that the flow of a refrigerant is adjusted, and further load adjustment is realized; a fixed orifice is typically used for the second stage restriction, primarily to reduce control difficulties, and also because the second stage restriction is less sensitive to load changes than the first stage restriction. In the actual operation of the unit, especially under the working conditions of high pressure ratio and low load, the second-stage orifice plate is larger at the moment, so that the pressure of the economizer, namely the air supply pressure is reduced, the pressure ratio of the first stage of the centrifugal machine is also reduced, and the pressure ratio of the second stage of the centrifugal machine is increased; typically, for centrifugal compressors, the second stage is poorly organized due to aerodynamic design characteristics and the second stage airflow inlet, resulting in an airflow that is more prone to backflow at the second stage, i.e., compressor surge, limiting the operating range of the compressor. Therefore, in the case of a large pressure ratio and a small load, the fixed orifice plate is adopted, and the operation range of the compressor is limited.
However, most centrifugal chiller units employ a primary adjustable flow restriction and a secondary fixed orifice. The unit with adjustable second-stage throttling mostly adopts the suction superheat degree as a target parameter, which is improved for the capacity of fully utilizing a container, but in consideration of certain application conditions, when a user needs the unit to work under the conditions of large compression ratio and small load, the unit can not be unloaded at the moment, or the operation range of the unit is expanded by introducing hot gas bypass, and the hot gas bypass can sharply reduce the operation energy efficiency of the unit. Considering that in practical application, the second-stage pneumatic structure (the second-stage impeller + the diffuser + the volute) is relatively easy to generate surging phenomenon (airflow counterflow) for the two-stage compressor, and the first-stage pneumatic structure (the first-stage impeller + the diffuser + the return device and the like) is relatively good in airflow organization, if the control of the electronic expansion valve with a single target of liquid level or suction superheat degree is adopted, the actual operation pressure ratio of the first-stage compressor can have a larger margin from the surging pressure ratio when the second-stage pneumatic structure surges, so that the operation frequency range of the compressor is limited, and the energy consumption is higher when the partial load is small.
Disclosure of Invention
The present application is directed to solving at least one of the above problems.
To this end, an object of the present application is to provide a control method for a water chiller. The method can effectively improve the operable frequency range of the water chilling unit and improve the operation energy efficiency of the water chilling unit under partial operation load.
A second objective of the present application is to provide a control system for a chiller.
A third object of the present application is to propose a non-transitory computer-readable storage medium.
A fourth object of the present application is to provide an hvac apparatus.
In order to achieve the above object, a first aspect of the present application discloses a control method for a water chiller, including: detecting the evaporator pressure and the condenser pressure of the water chilling unit; obtaining a target value of an intermediate pressure according to the pressure of the evaporator and the pressure of the condenser, wherein the intermediate pressure refers to the pressure between a first-stage throttling and a second-stage throttling in the water chilling unit; and adjusting the secondary throttle opening according to the target value of the intermediate pressure.
The control method of the water chilling unit can effectively improve the operable frequency range of the water chilling unit and improve the operation energy efficiency of the water chilling unit under partial operation load.
In some examples, the adjusting the secondary throttle opening based on the target value of the intermediate pressure includes: obtaining a difference between the target value of the intermediate pressure and the actual value of the intermediate pressure; and adjusting the secondary throttle opening according to the difference.
In some examples, the adjusting the secondary throttle opening based on the target value of the intermediate pressure includes: acquiring a saturation temperature corresponding to the target value of the intermediate pressure; and adjusting the secondary throttling opening according to the saturation temperature corresponding to the target value of the intermediate pressure and the saturation temperature corresponding to the actual value of the intermediate pressure.
In some examples, wherein the target value of the intermediate pressure is:
Figure BDA0001909757010000031
wherein Pm is the target value of the intermediate pressure, PcFor the evaporator pressure, the PeThe ξ is the coefficient for the condenser pressure.
In some examples, the ξ is between [1, 1.2 ].
A second aspect of the present application discloses a control system of a water chilling unit, including: the detection module is used for detecting the evaporator pressure and the condenser pressure of the water chilling unit; the pressure acquisition module is used for obtaining a target value of intermediate pressure according to the pressure of the evaporator and the pressure of the condenser, wherein the intermediate pressure refers to the pressure between the first-stage throttling and the second-stage throttling in the water chilling unit; and the control module is used for adjusting the secondary throttle opening according to the target value of the intermediate pressure.
The control system of the water chilling unit can effectively improve the operable frequency range of the water chilling unit and improve the operation energy efficiency of the water chilling unit under partial operation load.
In some examples, the control module is to: obtaining a difference between the target value of the intermediate pressure and the actual value of the intermediate pressure; and adjusting the secondary throttle opening according to the difference.
In some examples, the control module is to: acquiring a saturation temperature corresponding to the target value of the intermediate pressure; and adjusting the secondary throttling opening according to the saturation temperature corresponding to the target value of the intermediate pressure and the saturation temperature corresponding to the actual value of the intermediate pressure.
In some examples, wherein the target value of the intermediate pressure is:
Figure BDA0001909757010000041
wherein Pm is the target value of the intermediate pressure, PcFor the evaporator pressure, the PeThe ξ is the coefficient for the condenser pressure.
In some examples, the ξ is between [1, 1.2 ].
A third aspect of the present application discloses a non-transitory computer-readable storage medium on which a control program of a water chiller is stored, the control program of the water chiller, when executed by a processor, implementing the control method of the water chiller according to the embodiment of the first aspect.
An embodiment of a fourth aspect of the present application discloses a heating and ventilation device, which includes a memory, a processor, and a control program of a water chilling unit stored on the memory and capable of running on the processor, wherein the processor implements the control method of the water chilling unit described in the embodiment of the first aspect when executing the control program of the water chilling unit. The heating and ventilation equipment has the advantage of wide operating frequency range, and can effectively improve the operating energy efficiency under partial operating load.
Additional aspects and advantages of the present application will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the present application.
Drawings
The foregoing and/or additional aspects and advantages of the present application will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:
FIG. 1 is a flow chart of a method of controlling a chiller according to one embodiment of the present application;
FIG. 2A is a schematic illustration of the intermediate pressure prior to it being raised;
FIG. 2B is a schematic diagram of a control method of a chiller according to one embodiment of the present application after an intermediate pressure has been raised;
FIG. 3 is a schematic diagram of the achievable compressor operating frequencies of a method of controlling a chiller according to one embodiment of the present application;
fig. 4 is a block diagram of a control system of a chiller according to an embodiment of the present application.
Description of reference numerals:
the control system 400, the detection module 410, the pressure acquisition module 420 and the control module 430 of the water chilling unit.
Detailed Description
Reference will now be made in detail to embodiments of the present application, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are exemplary only for the purpose of explaining the present application and are not to be construed as limiting the present application.
In the description of the present application, it is to be understood that the terms "center," "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like are used in the orientation or positional relationship indicated in the drawings for convenience in describing the present application and for simplicity in description, and are not intended to indicate or imply that the referenced devices or elements must have a particular orientation, be constructed in a particular orientation, and be operated in a particular manner, and are not to be considered limiting of the present application. Furthermore, the terms "first" and "second" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
The following describes a control method and a control system of a water chilling unit according to an embodiment of the present application with reference to the accompanying drawings.
The chiller, among other things, includes a compressor, which in the following description is a two-stage centrifugal compressor, for example.
Fig. 1 is a flowchart of a control method of a water chiller according to an embodiment of the present application. As shown in fig. 1, a method for controlling a water chilling unit according to an embodiment of the present application includes the following steps:
s101: and detecting the pressure of an evaporator and the pressure of a condenser of the water chilling unit.
In a particular example, the chiller's evaporator pressure and condenser pressure may be detected by pressure sensors.
S102: and obtaining a target value of intermediate pressure according to the pressure of the evaporator and the pressure of the condenser, wherein the intermediate pressure refers to the pressure between the first-stage throttling and the second-stage throttling in the water chilling unit.
In a specific example, the target value of the intermediate pressure is, for example:
Figure BDA0001909757010000061
wherein Pm is the target value of the intermediate pressure, PcFor the evaporator pressure, the PeThe ξ is the coefficient for the condenser pressure.
It should be noted that ξ may be calibrated beforehand, either experimentally or empirically, and is generally located between [1, 1.2 ].
S103: and adjusting the secondary throttle opening according to the target value of the intermediate pressure.
For example: and acquiring a difference value between the target value of the intermediate pressure and the actual value of the intermediate pressure, and adjusting the secondary throttle opening according to the difference value.
Specifically, under most working conditions of the water chilling unit, the effect of the second-stage throttling (namely, the second-stage throttling) on the energy efficiency of the water chilling unit is not obvious, so that the second-stage throttling can be optionally not adjusted, but under the working conditions of large compression ratio and small operation load of the compressor, the PID adjustment can be carried out on the second-stage adjustable throttle valve according to the intermediate pressure, namely: and adjusting the opening degree of the secondary throttle.
As shown in fig. 2A and 2B, fig. 2A is a schematic diagram before the intermediate pressure Pm is raised, and fig. 2B is a schematic diagram after the intermediate pressure Pm is raised.
For example: according to the difference between the target value of the intermediate pressure and the actual value of the intermediate pressure, performing PID closed-loop adjustment on the opening of the second-stage adjustable throttle valve, wherein the second-stage adjustable throttle valve is adjusted to a small opening under the working conditions of large compression ratio and small running load of the compressor, namely: the intermediate pressure is increased, and further, the operation compression ratio of the second-stage pneumatic structure is reduced, so that surge can be eliminated; in addition, because the first-stage pneumatic efficiency is higher, after the intermediate pressure is increased, more work is given to the first-stage pneumatic structure with higher working efficiency, so that the operation energy efficiency of the water chilling unit under a small-load working condition is improved, and meanwhile, the loss of energy efficiency and efficiency caused by the introduction of hot gas bypass can be avoided.
As shown in fig. 3, the region indicated by the arrow is the frequency range of operation that can be achieved by the chiller after the intermediate pressure is raised.
According to the control system of the water chilling unit, the operable frequency range of the water chilling unit can be effectively enlarged, and the operation energy efficiency of the water chilling unit under partial operation load is improved.
In addition, since the temperature of the make-up air is the saturation temperature corresponding to the intermediate pressure, in the embodiment of the present invention, adjusting the opening of the secondary throttle according to the target value of the intermediate pressure may further include: acquiring a saturation temperature corresponding to the target value of the intermediate pressure; and adjusting the secondary throttling opening according to the saturation temperature corresponding to the target value of the intermediate pressure and the saturation temperature corresponding to the actual value of the intermediate pressure. Therefore, the intermediate pressure can be increased, and the operation compression ratio of the second-stage pneumatic structure is reduced, so that the surge can be eliminated; in addition, because the first-stage pneumatic efficiency is higher, after the intermediate pressure is increased, more work is given to the first-stage pneumatic structure with higher working efficiency, so that the operation energy efficiency of the water chilling unit under a small-load working condition is improved, and meanwhile, the loss of energy efficiency and efficiency caused by the introduction of hot gas bypass can be avoided.
Further, the embodiment of the application discloses a control system of a water chilling unit. As shown in fig. 4, a control system 400 of a water chiller according to an embodiment of the present application includes: a detection module 410, a pressure acquisition module 420, and a control module 430.
The detection module 410 is configured to detect an evaporator pressure and a condenser pressure of the chiller. The pressure obtaining module 420 is configured to obtain a target value of an intermediate pressure according to the evaporator pressure and the condenser pressure, where the intermediate pressure is a pressure between a first-stage throttling and a second-stage throttling in the chiller. The control module 430 is configured to adjust the secondary throttle opening based on the target value of the intermediate pressure.
In an embodiment of the present invention, the control module 430 is configured to: obtaining a difference between the target value of the intermediate pressure and the actual value of the intermediate pressure; and adjusting the secondary throttle opening according to the difference.
In an embodiment of the present invention, the control module 430 is configured to: acquiring a saturation temperature corresponding to the target value of the intermediate pressure; and adjusting the secondary throttling opening according to the saturation temperature corresponding to the target value of the intermediate pressure and the saturation temperature corresponding to the actual value of the intermediate pressure.
In one embodiment of the present invention, wherein the target value of the intermediate pressure is:
Figure BDA0001909757010000081
wherein Pm is the target value of the intermediate pressure, PcFor the evaporator pressure, the PeThe ξ is the coefficient for the condenser pressure.
In one embodiment of the invention, ξ is between [1, 1.2 ].
According to the control system of the water chilling unit, the operable frequency range of the water chilling unit can be effectively enlarged, and the operation energy efficiency of the water chilling unit under partial operation load is improved.
It should be noted that a specific implementation manner of the control system of the water chilling unit in the embodiment of the present application is similar to a specific implementation manner of the control method of the water chilling unit in the embodiment of the present application, and please refer to the description of the method part specifically, and details are not described here in order to reduce redundancy.
Further, an embodiment of the present application discloses a non-transitory computer-readable storage medium, on which a computer program is stored, on which a control program of a chiller is stored, which when executed by a processor implements the control method of the chiller described above.
Further, the embodiment of the application discloses heating and ventilation equipment, which comprises a memory, a processor and a control program of a water chilling unit, wherein the control program of the water chilling unit is stored in the memory and can be run on the processor, and the control method of the water chilling unit is realized when the processor executes the control program of the water chilling unit. The heating and ventilation equipment has the advantage of wide operating frequency range, and can effectively improve the operating energy efficiency under partial operating load.
In addition, other configurations and functions of the heating and ventilation device according to the embodiment of the present application are known to those skilled in the art, and are not described herein in detail to reduce redundancy.
The non-transitory computer readable storage medium described above may take any combination of one or more computer readable media. The computer readable medium may be a computer readable signal medium or a computer readable storage medium. A computer readable storage medium may be, for example, but not limited to, an electronic, magnetic, optical, electromagnetic, infrared, or semiconductor system, apparatus, or device, or any combination of the foregoing. More specific examples (a non-exhaustive list) of the computer readable storage medium would include the following: an electrical connection having 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), a 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. In the context of this document, a computer readable storage medium may be any tangible medium that can contain, or store a program for use by or in connection with an instruction execution system, apparatus, or device.
A computer readable signal medium may include a propagated data signal with computer readable program code embodied therein, for example, in baseband or as part of a carrier wave. Such a propagated data signal may take any of a variety of forms, including, but not limited to, electro-magnetic, optical, or any suitable combination thereof. A computer readable signal medium may also be any computer readable medium that is not a computer readable storage medium and that can communicate, propagate, or transport a program for use by or in connection with an instruction execution system, apparatus, or device.
Program code embodied on a computer readable medium may be transmitted using any appropriate medium, including but not limited to wireless, wireline, optical fiber cable, RF, etc., or any suitable combination of the foregoing.
Computer program code for carrying out operations for aspects of the present application may be written in any combination of one or more programming languages, including an object oriented programming language such as Java, Smalltalk, C + +, and conventional procedural programming languages, such as the "C" programming language or similar programming languages. The program code may execute entirely on the user's computer, partly on the user's computer, as a stand-alone software package, partly on the user's computer and partly on a remote computer or entirely on the remote computer or server. In the case of a remote computer, the remote computer may be connected to the user's computer through any type of Network, including a Local Area Network (LAN) or a Wide Area Network (WAN), or the connection may be made to an external computer (for example, through the Internet using an Internet service provider).
While embodiments of the present application have been shown and described, it will be understood by those of ordinary skill in the art that: various changes, modifications, substitutions and alterations can be made to the embodiments without departing from the principles and spirit of the application, the scope of which is defined by the claims and their equivalents.

Claims (12)

1. A control method of a water chilling unit is characterized by comprising the following steps:
detecting the evaporator pressure and the condenser pressure of the water chilling unit;
obtaining a target value of an intermediate pressure according to the pressure of the evaporator and the pressure of the condenser, wherein the intermediate pressure refers to the pressure between a first-stage throttling and a second-stage throttling in the water chilling unit;
adjusting the secondary throttling opening according to the target value of the intermediate pressure so as to improve the intermediate pressure and reduce the operation compression ratio of a second-stage pneumatic structure; and controlling the work done by the first-stage pneumatic structure to be larger than the work done by the second-stage pneumatic structure.
2. The control method of the water chilling unit according to claim 1, wherein the adjusting of the secondary throttle opening according to the target value of the intermediate pressure includes:
obtaining a difference between the target value of the intermediate pressure and the actual value of the intermediate pressure;
and adjusting the secondary throttle opening according to the difference.
3. The control method of the water chilling unit according to claim 1, wherein the adjusting of the secondary throttle opening according to the target value of the intermediate pressure includes:
acquiring a saturation temperature corresponding to the target value of the intermediate pressure;
and adjusting the secondary throttling opening according to the saturation temperature corresponding to the target value of the intermediate pressure and the saturation temperature corresponding to the actual value of the intermediate pressure.
4. A control method of a water chilling unit according to any one of claims 1-3, wherein the target value of the intermediate pressure is:
Figure FDA0003044484460000011
wherein Pm is the target value of the intermediate pressure, PcFor the evaporator pressure, the PeThe ξ is the coefficient for the condenser pressure.
5. The control method of the water chilling unit according to claim 4, wherein ξ is located between [1, 1.2 ].
6. A control system for a chiller, comprising:
the detection module is used for detecting the evaporator pressure and the condenser pressure of the water chilling unit;
the pressure acquisition module is used for obtaining a target value of intermediate pressure according to the pressure of the evaporator and the pressure of the condenser, wherein the intermediate pressure refers to the pressure between the first-stage throttling and the second-stage throttling in the water chilling unit;
and the control module is used for adjusting the secondary throttling opening according to the target value of the intermediate pressure so as to improve the intermediate pressure and reduce the operation compression ratio of the second-stage pneumatic structure, and is also used for controlling the work done by the first-stage pneumatic structure to be greater than the work done by the second-stage pneumatic structure.
7. The chiller control system of claim 6, wherein the control module is configured to:
obtaining a difference between the target value of the intermediate pressure and the actual value of the intermediate pressure;
and adjusting the secondary throttle opening according to the difference.
8. The chiller control system of claim 6, wherein the control module is configured to:
acquiring a saturation temperature corresponding to the target value of the intermediate pressure;
and adjusting the secondary throttling opening according to the saturation temperature corresponding to the target value of the intermediate pressure and the saturation temperature corresponding to the actual value of the intermediate pressure.
9. The control system of a water chilling unit according to any one of claims 6-8, wherein the target value of the intermediate pressure is:
Figure FDA0003044484460000021
wherein Pm is the target value of the intermediate pressure, PcFor the evaporator pressure, the PeThe ξ is the coefficient for the condenser pressure.
10. The chiller control system of claim 9, wherein ξ is between [1, 1.2 ].
11. A non-transitory computer-readable storage medium having stored thereon a computer program, characterized in that a control program of a water chiller, which when executed by a processor, implements the control method of the water chiller according to any one of claims 1 to 5.
12. An heating and ventilation device, comprising a memory, a processor and a control program of a water chilling unit stored on the memory and capable of running on the processor, wherein the processor implements the control method of the water chilling unit according to any one of claims 1 to 5 when executing the control program of the water chilling unit.
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