WO2021013107A1 - 流体循环系统及其操作方法、计算机可读介质和控制器 - Google Patents

流体循环系统及其操作方法、计算机可读介质和控制器 Download PDF

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Publication number
WO2021013107A1
WO2021013107A1 PCT/CN2020/102854 CN2020102854W WO2021013107A1 WO 2021013107 A1 WO2021013107 A1 WO 2021013107A1 CN 2020102854 W CN2020102854 W CN 2020102854W WO 2021013107 A1 WO2021013107 A1 WO 2021013107A1
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Prior art keywords
fluid
pressure
pipe
circulation system
scroll expander
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PCT/CN2020/102854
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English (en)
French (fr)
Inventor
杨东辉
束宏飞
Original Assignee
艾默生环境优化技术(苏州)有限公司
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Priority to KR1020217043067A priority Critical patent/KR102617229B1/ko
Priority to US17/621,153 priority patent/US11767758B2/en
Priority to EP20844835.7A priority patent/EP4001588A4/en
Publication of WO2021013107A1 publication Critical patent/WO2021013107A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/0207—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F01C1/0215—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/006—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of dissimilar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C13/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/06—Control of, monitoring of, or safety arrangements for, machines or engines specially adapted for stopping, starting, idling or no-load operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/24—Control of, monitoring of, or safety arrangements for, machines or engines characterised by using valves for controlling pressure or flow rate, e.g. discharge valves
    • F01C20/26—Control of, monitoring of, or safety arrangements for, machines or engines characterised by using valves for controlling pressure or flow rate, e.g. discharge valves using bypass channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/04—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C2021/16—Other regulation or control
    • F01C2021/1643—Other regulation or control by using valves regulating pressure and flow rate, e.g. discharge valves
    • F01C2021/165—Other regulation or control by using valves regulating pressure and flow rate, e.g. discharge valves using a by-pass channel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C2021/16—Other regulation or control
    • F01C2021/1693—Stopping or starting, idling or no-load operation
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle
    • 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/026—Compressor control by controlling unloaders
    • F25B2600/0261—Compressor control by controlling unloaders external to the compressor
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass valves
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor

Definitions

  • the present disclosure relates to the field of fluid circulation systems, and more particularly, to a fluid circulation system including a scroll expander and an operation method thereof, as well as a computer readable medium and a controller for executing the operation method.
  • Some fluid circulation systems usually include an expander and an external fluid circulation path.
  • the expander is a device that uses high-pressure fluid to expand into low-pressure fluid to output mechanical or electrical work.
  • a common expander is a scroll expander.
  • the expansion mechanism of the scroll expander includes a movable scroll and a fixed scroll. The movable scroll and the fixed scroll are joined to each other to wind the movable scroll and the fixed scroll.
  • a series of expansion cavities are defined between the scrolls. The series of expansion cavities gradually increase in volume from the center of the expansion mechanism radially outward, thereby making the high-pressure fluid entering the expansion mechanism from the inlet at the center of the expansion mechanism in After passing through the series of expansion chambers, it becomes low-pressure fluid and is discharged from the expansion mechanism through the exhaust port.
  • a driving torque is generated, such as driving a shaft to rotate to output mechanical work or thereby output electrical work.
  • the low-pressure side scroll expander (the expansion mechanism is located in the low-pressure zone with exhaust pressure) as an example.
  • a back pressure chamber is provided on the back side of the end plate of the fixed scroll.
  • the groove on the disk end plate and the floating seal ring are formed.
  • Floating seals need reliable floating to play a sealing role to ensure the normal startup and normal operation of the scroll expander.
  • the suction and exhaust pressure difference is too small, it may cause the floating seal ring to fail to float normally, causing the scroll expander to fail to build properly. Due to the pressure difference, the fluid circulation system cannot operate normally.
  • the purpose of the present disclosure is to improve one or more technical problems mentioned above.
  • the fluid circulation system includes:
  • An external fluid circulation path comprising a high-pressure fluid pipe for supplying fluid to the scroll expander and a low-pressure fluid pipe for conveying fluid from the scroll expander,
  • the operation method includes the following steps:
  • the step of establishing a pressure difference before supplying fluid to the scroll expander, making the fluid pressure in the high-pressure fluid pipe higher than the fluid pressure in the low-pressure fluid pipe by a predetermined pressure difference;
  • the step of starting the scroll expander after the predetermined pressure difference is achieved through the step of establishing the pressure difference, the scroll expander is started and fluid is supplied to the scroll expander.
  • the predetermined pressure difference is such that the fluid pressure in the high-pressure fluid pipe is at least 1.5 times the fluid pressure in the low-pressure fluid pipe.
  • the fluid pressure in the high-pressure fluid pipe and the fluid pressure in the low-pressure fluid pipe are adjusted in advance to achieve the above-mentioned preferred predetermined pressure difference, that is, the fluid pressure in the high-pressure fluid pipe is the same as that in the low-pressure fluid pipe.
  • At least 1.5 times the fluid pressure of the scroll expander which can predictively adjust the possible pressure distribution in the scroll expander housing within an appropriate range to balance the floating seal ring in the scroll
  • the force applied when the cyclone expander is started can avoid the problem of unbalanced force on the floating seal before starting the scroll expander, thereby fundamentally ensuring that the scroll expander in the fluid circulation system and the fluid circulation system are normal Start and work.
  • the fluid circulation system further includes a bypass pipe connected to the high-pressure fluid pipe and the low-pressure fluid pipe to form a bypass circuit
  • the step of establishing a pressure difference includes: Before supplying fluid to the scroll expander, a fluid pressure difference is established between the high-pressure fluid pipe and the low-pressure fluid pipe by throttling the fluid in the bypass pipe.
  • a bypass valve is provided on the bypass pipe, the bypass valve is opened to a predetermined degree of opening during the step of establishing the pressure difference, and the predetermined degree of opening is such that the high pressure
  • the predetermined pressure difference can be reached between the fluid pipe and the low-pressure fluid pipe, and the bypass valve is gradually reduced to be closed when the step of starting the scroll expander is implemented.
  • the fluid circulation system includes a pressurizing part having a heat exchanger so as to be adapted to convert the low-pressure fluid from the low-pressure fluid pipe into a high-pressure fluid and deliver the high-pressure fluid To the high-pressure fluid pipe, and, the operating method further includes a preheating step performed by means of the bypass circuit, the preheating step for preheating the heat exchanger and establishing a pressure difference in the Before implementing the steps.
  • the high-pressure fluid pipe is provided with a high-pressure intake valve for controlling the fluid communication between the high-pressure fluid pipe and the scroll expander, and the high-pressure intake valve is established in the The pressure difference is kept closed during the step and opened when the step of starting the scroll expander is carried out.
  • a computer-readable medium wherein the computer-readable medium stores the steps in the operation method described above when executed.
  • a controller including the computer-readable medium as described above.
  • a fluid circulation system wherein the fluid circulation system includes the controller as described above.
  • the fluid circulation system includes:
  • An external fluid circulation path comprising a high-pressure fluid pipe for supplying fluid to the scroll expander and a low-pressure fluid pipe for conveying fluid from the scroll expander,
  • the fluid circulation system can be controlled by the controller such that: before the fluid is supplied to the scroll expander, the fluid pressure in the high-pressure fluid pipe is higher than the fluid pressure in the low-pressure fluid pipe Reach a predetermined pressure difference.
  • the fluid circulation system includes a bypass pipe connected to the high-pressure fluid pipe and the low-pressure fluid pipe to form a bypass circuit, and the fluid in the bypass pipe is suitable for It is throttled to establish a fluid pressure difference between the high-pressure fluid pipe and the low-pressure fluid pipe.
  • a bypass valve is provided on the bypass pipe, and the bypass valve is adapted to be opened to a predetermined opening degree to achieve the predetermined pressure difference and is also adapted to gradually reduce the opening degree To close.
  • the scroll expander includes a fixed scroll capable of axial floating, and the back side of the fixed scroll end plate of the fixed scroll is provided with a floating seal ring.
  • the back pressure cavity is provided.
  • the high-pressure fluid pipe is provided with a high-pressure intake valve for controlling fluid communication between the high-pressure fluid pipe and the scroll expander.
  • the fluid circulation system and operation method thereof according to the present disclosure bring at least the following beneficial effects:
  • the computer may
  • the reading medium and the controller and the implementation of the fluid circulation system operation method according to the present disclosure can effectively avoid the technical problem that the scroll expander in the fluid circulation system cannot start and work normally, and the fluid circulation system and the computer readable medium according to the present disclosure
  • the operation method of the controller and the fluid circulation system is simple, practical, convenient and easy to implement, has high cost-effectiveness, and can greatly improve work efficiency.
  • Figure 1 shows a schematic diagram of a fluid circulation system
  • Fig. 2 shows a schematic longitudinal cross-sectional view of the scroll expander in the fluid circulation system of Fig. 1;
  • Figure 3 shows a flow chart of a method for operating a fluid circulation system according to the related art.
  • Fig. 4 shows a flowchart of a method for operating a fluid circulation system according to a preferred embodiment of the present disclosure.
  • Fluid circulation system Y scroll expander 1; external fluid circulation path 11
  • Expansion mechanism EM fixed scroll 22; movable scroll 24; fixed scroll end plate 220
  • FIGS. 1-4 The preferred embodiments of the present disclosure will now be described in detail with reference to FIGS. 1-4.
  • the following description is merely exemplary in nature and is not intended to limit the present disclosure and its applications or uses.
  • the corresponding components or parts use the same reference signs.
  • the scroll expander is exemplarily shown as a vertical low-pressure side scroll expander.
  • the scroll expander (hereinafter also referred to as "expander") according to the present disclosure is not limited to this type, but may be any other suitable type of scroll expander such as a horizontal low-pressure side scroll expander.
  • the fluid circulation system Y (for example, the organic Rankine cycle system using the Carnot cycle) includes a scroll expander 1 and an external fluid circulation path 11, and the external fluid circulation path 11 includes: 1
  • the high-pressure fluid pipe 171 for supplying fluid, the high-pressure fluid pipe 171 is provided with a high-pressure inlet valve K1; the low-pressure fluid pipe 181 for conveying fluid from the scroll expander 1; and the high-pressure fluid pipe 171 and the low-pressure fluid pipe 181 is a pressurizing part in fluid communication, and the pressurizing part is used to pressurize the low-pressure fluid from the low-pressure fluid pipe 181 into a high-pressure fluid and enter the high-pressure fluid pipe 171.
  • the pressurizing part is shown as including: a condenser (a heat exchanger suitable for condensing a gaseous low-pressure fluid into a liquid fluid), a working fluid pump (suitable for converting a liquid fluid Pump to evaporator) and evaporator (a heat exchanger suitable for evaporating liquid fluid into high-pressure gaseous fluid) and other devices.
  • a condenser a heat exchanger suitable for condensing a gaseous low-pressure fluid into a liquid fluid
  • a working fluid pump suitable for converting a liquid fluid Pump to evaporator
  • evaporator a heat exchanger suitable for evaporating liquid fluid into high-pressure gaseous fluid
  • the external fluid circulation path 11 further includes a bypass pipe 161 connected to the high-pressure fluid pipe 171 and the low-pressure fluid pipe 181 respectively, and a bypass valve K2 is provided on the bypass pipe 161.
  • a preheating step is required to preheat the external fluid circulation path 11, so that the fluid in the external fluid circulation path 11 reaches a certain pressure.
  • the high-pressure intake valve K1 is usually closed and the bypass valve K2 is opened, so that the high-pressure fluid pipe 171, the bypass pipe 161, and the low-pressure fluid pipe 181 form a fluid circuit.
  • the booster part evaporator, condenser and After the working fluid pump, etc.
  • the fluid circulates along the high-pressure fluid pipe 171, the bypass pipe 161 and the low-pressure fluid pipe 181 and is continuously pressurized.
  • the scroll expander 1 includes a substantially cylindrical casing 10, a top cover 14 provided at one end of the casing 10, and a bottom cover 16 provided at the other end of the casing 10.
  • the casing 10, the top cover 14 and the bottom cover 16 constitute a shell of the scroll expander 1 with a closed space.
  • the scroll expander 1 also includes a partition arranged between the top cover 14 and the housing 10 to separate the inner space of the expander into a high pressure zone A2 (also called a high pressure space) and a low pressure zone A1 (also called a low pressure space).
  • the partition 15 and the top cover 14 form a high pressure area A2, and the partition 15, the housing 10 and the bottom cover 16 form a low pressure area A1.
  • An intake pipe 17 for introducing high-pressure fluid (also called working fluid) is provided in the high-pressure zone, and an exhaust pipe 18 for discharging the expanded low-pressure fluid is provided in the low-pressure zone A1.
  • the high-pressure fluid of the external fluid circulation path 11 is The pipe 171 is connected to the intake pipe 17 to supply high-pressure fluid to the scroll expander 1, and the low-pressure fluid pipe 181 is connected to the exhaust pipe 18 to receive the expanded low-pressure fluid.
  • the scroll expander 1 further includes an expansion mechanism EM composed of a fixed scroll 22 and a movable scroll 24.
  • the movable scroll 24 can rotate in translation relative to the fixed scroll 22 (that is, the center axis of the movable scroll 24 revolves around the center axis of the fixed scroll 22, but the movable scroll 24 itself does not rotate around itself The central axis rotates).
  • the fixed scroll 22 includes a fixed scroll end plate 220, a fixed scroll wrap extending from one side of the fixed scroll end plate 220, and a fixed scroll wrap provided at the center of the fixed scroll end plate 220 for supplying high-pressure fluid.
  • the movable scroll 24 includes a movable scroll end plate and a movable scroll extending from a side surface of the movable scroll end plate.
  • the following are defined in the expansion mechanism EM Cavity: the exhaust chamber fluidly connected to the exhaust port of the expansion mechanism EM, and the intake chamber formed by the joining of the fixed scroll and the movable scroll in fluid communication with the intake port I and the volume of working fluid A series of closed expansion chambers that expand.
  • the radially innermost expansion chamber is adjacent to the intake port I and has substantially the same intake pressure as the introduced high-pressure fluid, so it is called a high-pressure chamber, the radially outermost expansion chamber
  • the cavity has the same exhaust pressure as the low-pressure fluid that will be discharged from the expansion mechanism EM, so it is called the low-pressure cavity.
  • the expansion cavity between the high-pressure cavity and the low-pressure cavity has an intermediate pressure lower than the suction pressure and higher than the exhaust pressure Pressure, therefore called the medium pressure chamber.
  • a back pressure chamber C is provided on the other side of the fixed scroll end plate 220, and the back pressure chamber C is sealed by a floating seal ring S and is in fluid communication with the intermediate pressure chamber.
  • the high-pressure fluid from the high-pressure fluid pipe 171 enters the high-pressure zone A2 in the scroll expander 1 through the intake pipe 17, and then enters the expansion mechanism EM through the intake port I.
  • the high-pressure fluid entering the expansion mechanism EM flows through a series of expansion chambers with gradually increasing volumes to be expanded and become low-pressure fluid.
  • the low-pressure fluid is discharged to the low-pressure zone A1 outside the expansion mechanism EM, and then is discharged to the low-pressure fluid pipe 181 through the exhaust pipe 18 connected to the scroll expander 1.
  • the scroll expander 1 further includes a rotating shaft (may also be referred to as an output shaft) 30.
  • the rotating shaft 30 is rotatably supported by a main bearing provided in the main bearing housing 40.
  • One end of the rotating shaft 30 is coupled to the hub of the movable scroll 24 to be driven to rotate.
  • the scroll expander 1 may further include a generator composed of a stator 52 and a rotor 54.
  • the stator 52 is fixed to the housing 10.
  • the rotor 54 is provided between the stator 52 and the rotating shaft 30.
  • the rotor 54 is fixed to the outer peripheral surface of the rotating shaft 30 to rotate together with the rotating shaft 30 when the scroll expander 1 is operating, thereby enabling the generator to generate electricity.
  • FIG. 3 it can be seen that it includes the following steps: 1) Implement the preheating step as described above (open the bypass valve and open the fluid pump including the working fluid pump in the pressurizing part So that the working fluid (working fluid) starts to circulate, the heat source starts to heat the evaporator and the cold source starts to cool the condenser); and 2) when the fluid in the external fluid circulation path 11 reaches a certain pressure, the scroll expander 1 is started, The high-pressure intake valve K1 is opened to supply fluid to the scroll expander 1, and the bypass valve K2 is gradually closed.
  • the floating seal ring needs to be reliably floated to play a sealing role to ensure the normal startup and normal operation of the scroll expander.
  • the floating seal ring may not float normally, resulting in the normal sealing in the scroll expander.
  • a normal pressure difference cannot be established, and thus cannot start and work normally, which causes the fluid circulation system to fail to operate normally.
  • the steps are generally: the preheating step; the expander operates in the motor mode Step (ie, energize and operate the expander implemented as an induction asynchronous generator motor); gradually close the bypass valve K2 and operate the expander in the generator mode.
  • the preheating step the expander operates in the motor mode Step (ie, energize and operate the expander implemented as an induction asynchronous generator motor); gradually close the bypass valve K2 and operate the expander in the generator mode.
  • the present disclosure improves the related art fluid circulation system operation method.
  • the present disclosure uses the high pressure fluid in the external fluid circulation path during the preheating step before supplying fluid to the scroll expander.
  • a predetermined pressure difference is established between the pipe and the low-pressure fluid pipe to effectively avoid the above-mentioned problems and realize the normal start-up and operation of the scroll expander and the fluid circulation system.
  • the operation method of the fluid circulation system according to the preferred embodiment of the present disclosure will be described in detail below with reference to FIG. 4.
  • Fig. 4 shows a flowchart of a method for operating a fluid circulation system according to a preferred embodiment of the present disclosure.
  • the operating method of the fluid circulation system shown in FIG. 4 includes the following steps: 1) a preheating step, wherein the high-pressure intake valve K1 is closed and the bypass valve K2 is opened, so that the high-pressure fluid pipe 171, the bypass pipe 161 and the low-pressure fluid pipe 181 forms a fluid circuit.
  • the fluid circulates along the high-pressure fluid pipe 171, the bypass pipe 161, and the low-pressure fluid pipe 181 and is continuously pressurized; 2) A step of establishing a pressure difference, wherein the bypass valve K2 is closed to a predetermined opening degree, thereby gradually establishing a pressure difference between the high-pressure fluid pipe 171 and the low-pressure fluid pipe 181 through throttling, and the pressure difference gradually Increase to a desired predetermined pressure difference, wherein the predetermined opening degree can be different according to the magnitude of the predetermined pressure difference expected to be achieved; and 3) the step of starting the scroll expander 1, wherein when the predetermined pressure difference is reached After that, power is supplied to the scroll expander 1 to make it run, open the high-pressure intake valve K1 and gradually close the bypass valve K2 until it is completely closed, so that the scroll expander 1 starts and works normally, and the fluid is in the fluid circulation system Y It flows in a medium circulation, and
  • the predetermined pressure difference between the high-pressure fluid pipe 171 and the low-pressure fluid pipe 181 can be set within an appropriate range to ensure reliable startup of the scroll expander.
  • the predetermined pressure difference The fluid pressure in the high-pressure fluid pipe 171 is made to be at least 1.5 times the fluid pressure in the low-pressure fluid pipe 181.
  • the low-pressure fluid pipe 181 is kept cut off fluid communication with the low-pressure zone A1 of the scroll expander 1 during the preheating step (for example, another valve or the like is used), because the scroll While supplying fluid in the expander 1, the low-pressure fluid pipe 181 needs to be in fluid communication with the low-pressure zone A1 in the scroll expander 1, which will also cause the pressure in the low-pressure zone A1 to quickly coincide with the pressure in the low-pressure fluid pipe 181, thereby It can also ensure the normal starting and working of the scroll expander 1 and the fluid circulation system Y.
  • the present disclosure is not limited thereto, but may be carried out without departing from the spirit and protection scope of the present disclosure Various modifications, replacements and combinations.
  • the method of reducing the opening of the bypass valve is adopted to establish the predetermined pressure difference in the foregoing preferred embodiment, it is understood that the establishment of the predetermined pressure difference can also be achieved by other suitable throttling methods/devices.
  • the fluid circulation system operation method according to the present disclosure may further include a detection step.
  • a computer readable medium a controller of the fluid circulation system, and a fluid circulation system associated with the above-mentioned fluid circulation system operation method are also provided.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Thermal Sciences (AREA)
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Abstract

本公开提供一种流体循环系统及其操作方法、计算机可读介质和控制器。该流体循环系统包括：涡旋膨胀机（1）；以及外部流体循环路径（11），其包括用以向涡旋膨胀机供送流体的高压流体管（171）以及用以输送来自涡旋膨胀机的流体的低压流体管（181）。该操作方法包括如下步骤：建立压差的步骤，在向涡旋膨胀机供送流体之前，使得高压流体管中的流体压力高于低压流体管中的流体压力达预定压差；以及启动涡旋膨胀机的步骤，在通过建立压差的步骤而实现预定压差后，启动涡旋膨胀机并向涡旋膨胀机供送流体。根据本公开的流体循环系统及其操作方法、计算机可读介质和控制器能够避免涡旋膨胀机无法正常启动和工作的技术问题，并且简单实用、便利且易于实施。

Description

流体循环系统及其操作方法、计算机可读介质和控制器
本申请要求以下中国专利申请的优先权：于2019年7月19日提交中国专利局的申请号为201910654955.1、发明创造名称为“流体循环系统及其操作方法、计算机可读介质和控制器”的中国专利申请。该专利申请的全部内容通过引用结合在本申请中。
技术领域
本公开涉及流体循环系统领域，更具体地，涉及一种包括涡旋膨胀机的流体循环系统及其操作方法，以及用于执行所述操作方法的计算机可读介质和控制器。
背景技术
本部分提供了与本公开相关的背景信息，这些信息并不必然构成现有技术。
一些流体循环系统通常包括膨胀机和外部流体循环路径，其中，膨胀机是利用高压流体膨胀成低压流体以向外输出机械功或电功的装置。一种常见的膨胀机为涡旋膨胀机，涡旋膨胀机的膨胀机构包括动涡旋盘和定涡旋盘，动涡旋盘和定涡旋盘彼此接合以在动涡旋涡卷与定涡旋涡卷之间限定一系列膨胀腔，所述一系列膨胀腔从膨胀机构的中心径向向外地体积逐渐增大，由此使得从膨胀机构中心处的进气口进入膨胀机构内的高压流体在经由所述一系列膨胀腔后变为低压流体并通过排气口被排出膨胀机构。在流体膨胀过程中产生驱动力矩，例如带动轴旋转以输出机械功或者进而输出电功。
以低压侧涡旋膨胀机(膨胀机构位于具有排气压力的低压区中)为例，通常在定涡旋盘端板的背侧设置有背压腔，该背压腔由设置在定涡旋盘端板上的凹槽和浮动密封圈构成。浮动密封圈需要可靠的浮动来发挥密封作用，以保证涡旋膨胀机正常启动和正常工作。然而，根据现有技术的流体循环系统的操作方法，在启动涡旋膨胀机之前，如果吸排气压差太小，可能会导致浮动密封圈无法正常浮动，导致涡旋膨胀机内无法建立正常的压力差，从而无法正常启动和工作，这导致流体循环系统无法正常运行。
因此，需要提供一种改进的流体循环系统操作方法，以克服或减轻现有技术中的上述技术问题。
发明内容
在本部分中提供本公开的总体概要，而不是本公开完全范围或本公开所有特征的全面公开。
本公开的目的是在上面提到的一个或多个技术问题方面进行改进。
根据本公开的一个方面，提供了一种流体循环系统的操作方法，
所述流体循环系统包括：
涡旋膨胀机；以及
外部流体循环路径，所述外部流体循环路径包括用以向所述涡旋膨胀机供送流体的高压流体管以及用以输送来自所述涡旋膨胀机的流体的低压流体管，
其中，所述操作方法包括如下步骤：
建立压差的步骤：在向所述涡旋膨胀机供送流体之前，使得所述高压流体管中的流体压力高于所述低压流体管中的流体压力达预定压差；以及
启动所述涡旋膨胀机的步骤：在通过所述建立压差的步骤而实现所述预定压差后，启动所述涡旋膨胀机并向所述涡旋膨胀机供送流体。
根据本公开的一个优选实施方式，所述预定压差使得所述高压流体管中的流体压力为所述低压流体管中的流体压力的至少1.5倍。
通过预先调节所述高压流体管中的流体压力和所述低压流体管中的流体压力以实现上述优选的预定压差，即，使得所述高压流体管中的流体压力为所述低压流体管中的流体压力的至少1.5倍，能够在向涡旋膨胀机供送流体之前预见性地将涡旋膨胀机的壳体内的可能的压力分布调节在一个适当的范围内，以平衡浮动密封圈在涡旋膨胀机启动时的受力，从而能够在启动涡旋膨胀机之前就避免了浮动密封圈受力不平衡的问题，从而从根本上确保流体循环系统中的涡旋膨胀机以及流体循环系统正常启动和工作。
根据本公开的一个优选实施方式，所述流体循环系统还包括连通至所述高压流体管和所述低压流体管以形成旁通回路的旁通管，以及，所述建立压差的步骤包括：在向所述涡旋膨胀机供送流体之前，通过对所述旁通管中的流体进行节流而在所述高压流体管与所述低压流体管之间建立流体压差。
根据本公开的一个优选实施方式，所述旁通管上设置有旁通阀，所述旁通阀在所述建立压差的步骤期间打开至预定打开程度，所述预定打开程度使得所述高压流体管与所述低压流体管之间能够达到所述预定压差，所述旁通阀在实施所述启动所述涡旋膨胀机的步骤时逐渐减小打开程度至关闭。
根据本公开的一个优选实施方式，所述流体循环系统包括增压部，所述增压部具有换热器从而适于将来自所述低压流体管的低压流体转变为高压流体并且将高压流体输送至所述高压流体管，以及，所述操作方法还包括借助于所述旁通回路而进行的预热步骤，所述预热步骤用于预热所述换热器并且在所述建立压差的步骤之前实施。
根据本公开的一个优选实施方式，在所述建立压差的步骤期间，保持所述高压流体管与所述涡旋膨胀机切断流体连通，并且保持所述低压流体管与所述涡旋膨胀机流体连通。
根据本公开的一个优选实施方式，所述高压流体管上设置有用于控制所述高压流体管与所述涡旋膨胀机的流体连通的高压进气阀，所述高压进气阀在所述建立压差的步骤期间保持关闭并且在实施所述启动所述涡旋膨胀机的步骤时打开。
根据本公开的另一个方面，提供了一种计算机可读介质，其中，所述计算机可读介质储存有被执行时实施如上所述的操作方法中的步骤。
根据本公开的另一个方面，提供了一种控制器，所述控制器包括如上所述的计算机可读介质。
根据本公开的另一个方面，提供了一种流体循环系统，其中，所述流体循环系统包括如前所述的控制器。
根据本公开的一个优选实施方式，所述流体循环系统包括：
涡旋膨胀机；以及
外部流体循环路径，所述外部流体循环路径包括用以向所述涡旋膨胀机供送流体的高压流体管以及用以输送来自所述涡旋膨胀机的流体的低压流体管，
其中，所述流体循环系统能够被所述控制器控制成使得：在向所述涡旋膨胀机供送流体之前，所述高压流体管中的流体压力高于所述低压流体管中的流体压力达预定压差。
根据本公开的一个优选实施方式，所述流体循环系统包括连通至所述高压 流体管和所述低压流体管以形成旁通回路的旁通管，以及，所述旁通管中的流体适于被节流而在所述高压流体管与所述低压流体管之间建立流体压差。
根据本公开的一个优选实施方式，所述旁通管上设置有旁通阀，所述旁通阀适于被打开至预定打开程度以达到所述预定压差并且还适于逐渐减小打开程度至关闭。
根据本公开的一个优选实施方式，所述涡旋膨胀机包括能够进行轴向浮动的定涡旋盘，所述定涡旋盘的定涡旋盘端板的背侧设置有由浮动密封圈密封的背压腔。
所述高压流体管上设置有用于控制所述高压流体管与所述涡旋膨胀机的流体连通的高压进气阀。
综上可知，根据本公开的流体循环系统及其操作方法以及用于执行所述操作方法的计算机可读介质和控制器至少带来以下有益效果：通过采用根据本公开的流体循环系统、计算机可读介质和控制器以及实施根据本公开的流体循环系统操作方法能够有效避免流体循环系统中的涡旋膨胀机无法正常启动和工作的技术问题，并且根据本公开的流体循环系统、计算机可读介质和控制器以及流体循环系统操作方法简单实用、便利且易于实施，具有较高的成本效益，能够大大提高工作效率。
附图说明
根据以下参照附图的详细描述，本公开的前述及另外的特征和优点将变得更加清楚，这些附图仅作为示例并且不一定是按比例绘制。在附图中采用相同的参考标记指示相同的部件，在附图中：
图1示出流体循环系统的示意图；
图2示出图1的流体循环系统中的涡旋膨胀机的纵向截面示意图；
图3示出根据相关技术的流体循环系统操作方法的流程图；以及
图4示出根据本公开的一个优选实施方式的流体循环系统操作方法的流程图。
参考标记列表
流体循环系统Y；涡旋膨胀机1；外部流体循环路径11
壳体10；顶盖14；底盖16；隔板15；进气管17
排气管18；主轴承座40；旋转轴30；定子52；转子54
膨胀机构EM；定涡旋盘22；动涡旋盘24；定涡旋盘端板220
高压流体管171；低压流体管181；进气口I
高压进气阀K1；旁通管161；旁通阀K2；背压腔C
浮动密封圈S；低压区A1；高压区A2
具体实施方式
现在将结合附图1-4对本公开的优选实施方式进行详细描述。以下的描述在本质上只是示例性的而非意在限制本公开及其应用或用途。在各视图中，相对应的构件或部分采用相同的参考标记。
在下述示例性实施方式中，所述涡旋膨胀机示例性地示出为立式低压侧涡旋膨胀机。然而根据本公开的涡旋膨胀机(下文又称“膨胀机”)并不限于此类型，而可以是诸如卧式低压侧涡旋膨胀机的任何其他合适类型的涡旋膨胀机。
为了便于对根据本公开的流体循环系统操作方法的理解，下面将参照图1和图2来描述示例性流体循环系统Y的基本构造和原理。
如图1所示，流体循环系统Y(例如利用卡诺循环的有机朗肯循环系统)包括涡旋膨胀机1和外部流体循环路径11，外部流体循环路径11包括：用以向涡旋膨胀机1供送流体的高压流体管171，高压流体管171上设置有高压进气阀K1；用以输送来自涡旋膨胀机1的流体的低压流体管181；以及与高压流体管171和低压流体管181流体连通的增压部，所述增压部用于使来自低压流体管181的低压流体增压成高压流体并进入高压流体管171中。在本公开的示例性流体循环系统Y中，所述增压部示出为包括：冷凝器(适于将气态低压流体冷凝为液态流体的换热器)、工质泵(适于将液态流体泵送至蒸发器)和蒸发器(适于将液态流体蒸发为高压气态流体的换热器)等装置。本领域普通技术人员应当理解的是，本公开的流体循环系统操作方法的应用不限于此。另外，如图1中所示，外部流体循环路径11还包括分别连通至高压流体管171和低压流体管181的旁通管161，旁通管161上设置有旁通阀K2。
通常，在向涡旋膨胀机1供送流体之前需要首先实施预热步骤，以预热外 部流体循环路径11，从而使外部流体循环路径11中的流体达到一定的压力。具体地，通常关闭高压进气阀K1并打开旁通阀K2，使得高压流体管171、旁通管161和低压流体管181形成流体回路，当启动所述增压部(蒸发器、冷凝器和工质泵等)后，流体沿着高压流体管171、旁通管161和低压流体管181循环流通并不断增压。
如图2所示，涡旋膨胀机1包括大致圆筒形的壳体10、设置在壳体10一端的顶盖14以及设置在壳体10另一端的底盖16。壳体10、顶盖14以及底盖16构成涡旋膨胀机1的具有封闭空间的外壳。
涡旋膨胀机1还包括设置在顶盖14和壳体10之间以将膨胀机的内部空间分隔成高压区A2(也称为高压空间)和低压区A1(也称为低压空间)的隔板15。隔板15和顶盖14之间构成高压区A2，而隔板15、壳体10和底盖16之间构成低压区A1。在高压区设置有用于引入高压流体(也称为工作流体)的进气管17，在低压区A1设置有用于排出膨胀后的低压流体的排气管18，其中，外部流体循环路径11的高压流体管171连通至进气管17以向涡旋膨胀机1供送高压流体，低压流体管181连通至排气管18以接收膨胀后的低压流体。
涡旋膨胀机1还包括由定涡旋盘22和动涡旋盘24构成的膨胀机构EM。动涡旋盘24能够相对于定涡旋盘22平动转动(即，动涡旋盘24的中心轴线绕定涡旋盘22的中心轴线公转，但是动涡旋盘24本身不会绕自身的中心轴线自转)。
定涡旋盘22包括定涡旋盘端板220、从定涡旋盘端板220的一侧面延伸的定涡旋涡卷和设置在定涡旋盘端板220的中心处的用于供高压流体进入膨胀机构EM中的进气口I，动涡旋盘24包括动涡旋盘端板以及从动涡旋盘端板的一侧面延伸的动涡旋涡卷，在膨胀机构EM内限定有如下各个腔体：流体连通至膨胀机构EM的排气口的排气腔，以及由定涡旋涡卷和动涡旋涡卷接合形成的与进气口I流体连通的进气腔和用于使工作流体体积膨胀的封闭的一系列膨胀腔。具体地，在所述一系列膨胀腔中，径向最内侧的膨胀腔邻近进气口I并且具有与引入的高压流体基本相同的进气压力，因而称为高压腔，径向最外侧的膨胀腔具有与即将排出膨胀机构EM的低压流体基本相同的排气压力，因而称为低压腔，介于高压腔和低压腔之间的膨胀腔具有低于吸气压力且高于排气压力的中间压力，因而称为中压腔。其中，在定涡旋盘端板220的另一侧面 上设置有背压腔C，背压腔C由浮动密封圈S密封并与所述中压腔流体连通。
来自高压流体管171的高压流体经由进气管17进入涡旋膨胀机1内的高压区A2，然后经由进气口I进入膨胀机构EM中。进入膨胀机构EM的高压流体流经体积逐渐增大的一系列膨胀腔而被膨胀并变为低压流体。低压流体被排出至膨胀机构EM外部的低压区A1中，然后经由连接至涡旋膨胀机1的排气管18而被排出至低压流体管181。
涡旋膨胀机1还包括旋转轴(也可以称为输出轴)30。旋转轴30由设置在主轴承座40中的主轴承以可旋转的方式支撑。旋转轴30的一端联接至动涡旋盘24的毂部从而被驱动旋转。当涡旋膨胀机1运行时，在膨胀机构EM对流体进行膨胀的过程中产生驱动力矩，带动旋转轴30旋转以输出机械功或电功。
涡旋膨胀机1还可以包括由定子52和转子54构成的发电机。定子52固定至壳体10。转子54设置在定子52与旋转轴30之间。转子54固定至旋转轴30的外周面上，以在涡旋膨胀机1运行时随着旋转轴30一起旋转，从而使得发电机能够发电。
根据相关技术的流体循环系统操作方法，参照图3可知包括如下步骤：1)实施如前所述的预热步骤(打开旁通阀并且打开增压部中的包括工质泵在内的流体泵从而使工作流体(工质)开始循环，同时热源开始加热蒸发器而冷源开始冷却冷凝器)；以及2)当外部流体循环路径11中的流体达到一定压力后，启动涡旋膨胀机1，打开高压进气阀K1以向涡旋膨胀机1供送流体，并逐渐关闭旁通阀K2。
浮动密封圈需要需要可靠的浮动来发挥密封作用，以保证涡旋膨胀机正常启动和正常工作。然而，根据现有技术的流体循环系统的操作方法，在启动涡旋膨胀机之前，如果吸排气压差太小，可能会导致浮动密封圈无法正常浮动，导致涡旋膨胀机内无法正常密封从而无法建立正常的压力差，从而无法正常启动和工作，这导致流体循环系统无法正常运行。
另外，在不设置有高压进气阀K1或者在预热步骤即打开高压进气阀K1的根据另一相关技术的操作方法中，其步骤大体为：预热步骤；膨胀机以电动机模式运行的步骤(即，使实施为例如感应异步发电电动机的膨胀机通电运转)；逐渐关闭旁通阀K2并且使膨胀机以发电机模式运行的步骤。然而，在 该根据另一相关技术的操作方法中，会同样存在如上所述的问题(尤其是浮动密封圈S无法发挥密封隔离作用而使得低压区A1与高压区A2直接连通的问题)。
针对上述技术问题，本公开对相关技术的流体循环系统操作方法进行了改进，总体来讲，本公开通过在向涡旋膨胀机供送流体之前的预热步骤期间使外部流体循环路径的高压流体管与低压流体管之间建立预定压差而有效地避免了上述问题，实现了涡旋膨胀机和流体循环系统的正常启动和工作。具体地，下文将参照图4详细描述根据本公开的优选实施方式的流体循环系统操作方法。
图4示出了根据本公开的一个优选实施方式的流体循环系统操作方法的流程图。如图4所示的流体循环系统操作方法包括如下步骤：1)预热步骤，其中，关闭高压进气阀K1并打开旁通阀K2，使得高压流体管171、旁通管161和低压流体管181形成流体回路，当启动所述增压部(蒸发器、冷凝器和工质泵等)后，流体沿着高压流体管171、旁通管161和低压流体管181循环流通并不断增压；2)建立压差的步骤，其中，将旁通阀K2关小至预定打开程度，由此通过节流作用而在高压流体管171与低压流体管181之间逐渐建立压力差，该压力差逐渐增大至期望的预定压差，其中，所述预定打开程度可以根据期望达到的预定压差的大小而不同；以及3)启动涡旋膨胀机1的步骤，其中，当达到所述预定压差后，为涡旋膨胀机1供电而使其运转，打开高压进气阀K1并逐渐关小旁通阀K2至完全关闭，从而使涡旋膨胀机1正常启动和工作，流体在流体循环系统Y中循环流动，进而涡旋膨胀机1转为直接输出机械功或者用作发电机而基于机械功输出电功。
为此，根据本公开的优选实施方式，可以通过将高压流体管171与低压流体管181之间的预定压差设定在恰当范围内来确保可靠地启动涡旋膨胀机优选地，预定压差使得高压流体管171中的流体压力为低压流体管181中的流体压力的至少1.5倍。
显然，通过采用如上所述的根据本公开的流体循环系统操作方法，能够确保浮动密封圈在涡旋膨胀机启动时正常浮动实现密封，保证涡旋膨胀机1和流体循环系统Y的正常启动和工作。
同样，在此需指出的是，即使在预热步骤期间使低压流体管181保持与涡 旋膨胀机1中的低压区A1切断流体连通(比如采用另一个阀等手段)，由于在向涡旋膨胀机1中供送流体的同时需要使低压流体管181与涡旋膨胀机1中的低压区A1流体连通，也会导致低压区A1中的压力快速与低压流体管181中的压力一致，从而也可确保涡旋膨胀机1和流体循环系统Y的正常启动和工作。
尽管在前述实施方式中描述了根据本公开的流体循环系统操作方法的示例性实施方式，但是，本公开并不限于此，而是在不背离本公开的精神及保护范围的情况下，可以进行各种改型、替换和组合。另外，尽管在前述优选实施方式中采用减小旁通阀的开口的方式来建立预定压差，然而可以理解，也可以通过其他合适的节流方式/装置来实现预定压差的建立。另外，尽管上文未具体描述，可以理解的是，可以设置适于检测高压流体管171和低压流体管181中的流体压力的压力检测器或者可以基于相关参数估算出高压流体管171和低压流体管181中的流体压力并且将所获得的流体压力数据传送至控制器以控制涡旋膨胀器的开启正时，由此，根据本公开的流体循环系统操作方法还可以包括检测步骤。
另外，根据本公开，还提供了与上述流体循环系统操作方法相关联的计算机可读介质、流体循环系统的控制器以及流体循环系统。
可以理解的是，通过将不同的实施方式及各个技术特征、步骤以不同的方式进行组合或者对其进行改型，可以进一步设计得出各种不同的实施方式。
上文结合具体实施方式描述了根据本公开的优选实施方式的流体循环系统操作方法。可以理解，以上描述仅为示例性的而非限制性的，在不背离本公开的范围的情况下，本领域技术人员参照上述描述可以想到多种变型和修改。这些变型和修改同样包含在本公开的保护范围内。

Claims (15)

  1. 一种流体循环系统(Y)的操作方法，
    所述流体循环系统包括：
    涡旋膨胀机(1)；以及
    外部流体循环路径(11)，所述外部流体循环路径包括用以向所述涡旋膨胀机供送流体的高压流体管(171)以及用以输送来自所述涡旋膨胀机的流体的低压流体管(181)，
    其中，所述操作方法包括如下步骤：
    建立压差的步骤：在向所述涡旋膨胀机供送流体之前，使得所述高压流体管中的流体压力高于所述低压流体管中的流体压力达预定压差；以及
    启动所述涡旋膨胀机的步骤：在通过所述建立压差的步骤而实现所述预定压差后，启动所述涡旋膨胀机并向所述涡旋膨胀机供送流体。
  2. 根据权利要求1所述的操作方法，其中，所述预定压差使得所述高压流体管中的流体压力为所述低压流体管中的流体压力的至少1.5倍。
  3. 根据权利要求1至2中任一项所述的操作方法，其中，所述流体循环系统还包括连通至所述高压流体管和所述低压流体管以形成旁通回路的旁通管(161)，以及，所述建立压差的步骤包括：在向所述涡旋膨胀机供送流体之前，通过对所述旁通管中的流体进行节流而在所述高压流体管与所述低压流体管之间建立流体压差。
  4. 根据权利要求3所述的操作方法，其中，所述旁通管上设置有旁通阀(K2)，所述旁通阀在所述建立压差的步骤期间打开至预定打开程度，所述预定打开程度使得所述高压流体管与所述低压流体管之间能够达到所述预定压差，所述旁通阀在实施所述启动所述涡旋膨胀机的步骤时逐渐减小打开程度至关闭。
  5. 根据权利要求3所述的操作方法，其中，所述流体循环系统包括增压 部，所述增压部具有换热器从而适于将来自所述低压流体管的低压流体转变为高压流体并且将高压流体输送至所述高压流体管，以及，所述操作方法还包括借助于所述旁通回路而进行的预热步骤，所述预热步骤用于预热所述换热器并且在所述建立压差的步骤之前实施。
  6. 根据权利要求1至2中的任一项所述的操作方法，其中，在所述建立压差的步骤期间，保持所述高压流体管与所述涡旋膨胀机切断流体连通，并且保持所述低压流体管与所述涡旋膨胀机流体连通。
  7. 根据权利要求1至2中的任一项所述的操作方法，其中，所述高压流体管上设置有用于控制所述高压流体管与所述涡旋膨胀机的流体连通的高压进气阀(K1)，所述高压进气阀在所述建立压差的步骤期间保持关闭并且在实施所述启动所述涡旋膨胀机的步骤时打开。
  8. 一种计算机可读介质，其中，所述计算机可读介质储存有被执行时实施如权利要求1至7中任一项所述的操作方法中的步骤的计算机程序。
  9. 一种流体循环系统(Y)的控制器，其中，所述控制器包括如权利要求8所述的计算机可读介质。
  10. 一种流体循环系统(Y)，其中，所述流体循环系统包括如权利要求9所述的控制器。
  11. 根据权利要求10所述的流体循环系统(Y)，其中，所述流体循环系统包括：
    涡旋膨胀机(1)；以及
    外部流体循环路径(11)，所述外部流体循环路径包括用以向所述涡旋膨胀机供送流体的高压流体管(171)以及用以输送来自所述涡旋膨胀机的流体的低压流体管(181)，
    其中，所述流体循环系统能够被所述控制器控制成使得：在向所述涡旋膨 胀机供送流体之前，所述高压流体管中的流体压力高于所述低压流体管中的流体压力达预定压差。
  12. 根据权利要求11所述的流体循环系统(Y)，其中，所述流体循环系统包括连通至所述高压流体管和所述低压流体管以形成旁通回路的旁通管(161)，以及，所述旁通管中的流体适于被节流而在所述高压流体管与所述低压流体管之间建立流体压差。
  13. 根据权利要求12所述的流体循环系统(Y)，其中，所述旁通管上设置有旁通阀(K2)，所述旁通阀适于被打开至预定打开程度以达到所述预定压差并且还适于逐渐减小打开程度至关闭。
  14. 根据权利要求11所述的流体循环系统(Y)，其中，所述涡旋膨胀机(1)包括能够进行轴向浮动的定涡旋盘，所述定涡旋盘的定涡旋盘端板的背侧设置有由浮动密封圈密封的背压腔。
  15. 根据权利要求11至14中任一项所述的流体循环系统(Y)，其中，所述高压流体管上设置有用于控制所述高压流体管与所述涡旋膨胀机的流体连通的高压进气阀(K1)。
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