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WO2015043117A1 - 基于集液器和夹心活塞的液封蓄能器及其液压系统 - Google Patents

基于集液器和夹心活塞的液封蓄能器及其液压系统 Download PDF

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Publication number
WO2015043117A1
WO2015043117A1 PCT/CN2014/000876 CN2014000876W WO2015043117A1 WO 2015043117 A1 WO2015043117 A1 WO 2015043117A1 CN 2014000876 W CN2014000876 W CN 2014000876W WO 2015043117 A1 WO2015043117 A1 WO 2015043117A1
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Prior art keywords
pressure
liquid
piston
gas
chamber
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PCT/CN2014/000876
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English (en)
French (fr)
Inventor
陈启星
罗启宇
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Priority to US15/028,715 priority Critical patent/US10273980B2/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/04—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/04—Accumulators
    • F15B1/08—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor
    • F15B1/24—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor with rigid separating means, e.g. pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/005—Leakage; Spillage; Hose burst
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/30—Accumulator separating means
    • F15B2201/31—Accumulator separating means having rigid separating means, e.g. pistons
    • F15B2201/312—Sealings therefor, e.g. piston rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/40—Constructional details of accumulators not otherwise provided for
    • F15B2201/405—Housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/40—Constructional details of accumulators not otherwise provided for
    • F15B2201/41—Liquid ports
    • F15B2201/411—Liquid ports having valve means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/50—Monitoring, detection and testing means for accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/275—Control of the prime mover, e.g. hydraulic control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members

Definitions

  • the present invention is an accumulator and a hydraulic control system thereof, and belongs to the field of hydraulic transmission systems.
  • the invention is abbreviated as a liquid sealing accumulator.
  • Accumulators include three types of capsule accumulators, piston accumulators and diaphragm accumulators, in which both the capsule accumulator and the diaphragm accumulator have the risk of sudden rupture of the rubber skin. It is not suitable for use in systems with high reliability requirements, such as cars, boats, airplanes, etc.; piston accumulators do not have the risk of sudden rupture of rubber skin, and have high reliability, but the current important problems faced by piston accumulators Yes, it is a contradiction between the performance of the piston to isolate the gas and the liquid, and the friction between the piston and the cylinder.
  • the gas and liquid isolation performance is to be improved, the positive pressure of the piston seal ring relative to the cylinder body needs to be increased, so the frictional force is increased, so that the response is insensitive; in turn, if the response sensitivity is to be increased, it should be reduced.
  • the friction of the piston makes the gas and liquid isolation performance worse, resulting in shortcomings such as leakage of liquid into the air pressure chamber and gas leakage.
  • the piston accumulator is both good for isolating gases and liquids, and the response sensitivity is high, then the piston accumulator can have broader application prospects, such as: in the car, It acts as a booster in equipment such as ships and airplanes.
  • the specific objectives of the accumulator of the invention are: 1 safe and reliable, no sudden damage failure; 2 good gas-liquid isolation; 3 high response sensitivity; 4 durable; 5 high working pressure and quasi-constant pressure; 6 high efficiency; Small size; 8 low production cost; 9 simple structure, easy maintenance; 10 based on this accumulator, can design the corresponding control system, drive brakes, steering gear, throttle, clutch, shifting mechanism, aircraft elevator and other actuators .
  • the pressure liquid chamber YYQ is filled with the pressure liquid YLY, but the pressure liquid YLY is not marked in the figure, only the description is given in the specification; similarly, the high pressure gas GYQT in the air pressure chamber QYQ is also not marked.
  • ⁇ There are three pressure (temperature) set values: nominal value, upper limit value and lower limit value. Quasi-constant pressure (quasi-constant temperature) means that the pressure (temperature) is within a small range centered on the set nominal value. Change, or change between the set upper and lower limits.
  • the sensor always uses a control signal in combination with the comparator. For example, a “refill threshold potential” is set in the position comparator in advance. When the length of the spring reaches a certain length, the position sensor output signal potential exceeds The "rehydration threshold potential”, at this time, the output value of the position comparator is reversed, that is, the "injection signal” is issued to the infusion pump, the infusion pump is started, and the hydraulic cylinder is injected.
  • This process hereinafter referred to as the position sensing/comparator, sends a liquid injection signal; similarly, the pressure sensing/comparator sends a heating signal or a cooling signal, and the full liquid sensing/comparator sends a shutdown signal.
  • the comparator is designed in the control system and is not marked in the figure.
  • the piston has a sealing ring, and it is usually not particularly emphasized.
  • the cylinder in which the piston moves is called a piston cylinder.
  • the highest position of the piston cylinder is called the piston cylinder top.
  • collector drainer The full name of the liquid collector is called “collector drainer”, which combines the functions of liquid collection and drainage.
  • the high pressure gas tank and the high pressure gas chamber are simply referred to as a gas tank QTG and a gas chamber QTQ.
  • the liquid seal accumulator is operated based on high pressure gas, so before describing the working principle of the liquid seal accumulator, the high pressure gas GYQT and the existing piston accumulator are explained.
  • the high pressure gas GYQT includes super fluid (such as carbon dioxide), gas (such as nitrogen, argon, etc.) and saturated gas BHQ (such as refrigerant freon, ammonia, etc.)
  • High pressure gas is also known as a storage pressure gas or a pressure storage agent.
  • a piston HS divides the piston cylinder HSG into two parts: a pneumatic chamber (upper chamber) and a hydraulic chamber (lower chamber).
  • the pressure chamber is filled with high pressure gas, the pressure is P Q , and the bottom of the hydraulic chamber has a discharge port pipe (ZPK).
  • the pressure fluid is injected and discharged, the pressure of the pressure liquid is P Y , the friction force of the piston is F M , and the piston area is S.
  • the main problem currently exists is: in order to prevent the pressure liquid in the hydraulic chamber from leaking to the air pressure, the piston sealing ring is pressed tightly with the inner wall of the piston cylinder, so that the sensitivity of the piston reaction is lowered, and the invention effectively improves the sensitivity of the piston reaction.
  • a liquid seal accumulator based on a liquid trap and a sandwich piston and a hydraulic system thereof
  • the liquid seal accumulator comprises a sealed cylindrical piston cylinder (HSG)
  • a piston (HS) will be a piston cylinder (HSG) is divided into two parts: air pressure chamber (QYQ) and hydraulic chamber (YYQ).
  • QYQ air pressure chamber
  • YYQ hydraulic chamber
  • the air chamber is filled with high pressure gas, and the air pressure is transmitted to the hydraulic chamber through the piston. Therefore, the pressure liquid in the hydraulic chamber has a high pressure, and the bottom of the hydraulic chamber
  • ZPK discharge port pipe
  • a high pressure gas tank (QTG, including QTG 1 and QTG 2 , referred to as a gas chamber for storing high pressure gas (QTQ, including QTQ 1 and QTQ 2 ), a piston-cylinder top to establish a gas-liquid channel (TD, including TD 1 and TD 2 ), a connected air chamber (QYQ) and Gas chamber (QTQ),
  • the gas tank has two functions, one is to act as an extension of the pressure chamber (QYQ), to help the air chamber to store high pressure gas, to increase the total volume of the air chamber, and to reduce the pressure fluctuation of the air chamber;
  • the bottom of the gas tank acts as a liquid collector, since the piston always has The leakage of the pressure will slowly leak from the hydraulic pressure chamber (YYQ) to the air pressure chamber (QYQ).
  • More and more pressure fluid will collect on the top of the piston and need to be cleaned up.
  • the pressure liquid on the top of the piston will flow into the gas chamber (QTQ) through the gas-liquid passage (TD).
  • the pressure liquid on the top of the piston will be cleaned in time, and the pressure liquid collected at the bottom of the gas chamber will be more and more. Raise the pontoon FT (including FT 1 and FT 2 ).
  • a sandwich piston to enhance the sealing performance of the piston, and to reduce the friction loss and improve the sensitivity of the reaction.
  • the piston passes through the spool (HS S ) and the piston under the coupling (HS x ) through the spool.
  • HZ forms a sliding fit with the sliding sleeve (HT), forming a sandwich layer (JXC) filled with sealing liquid (including sealing grease and pressure fluid) with a variable distance between the upper and lower pistons; because the sealing ring and the inner wall of the piston cylinder
  • sealing liquid including sealing grease and pressure fluid
  • the pressure is very small, so the pressure of the hydraulic chamber/air chamber is relatively small, and the pressure of the sandwich layer is at the middle of the hydraulic chamber and the air chamber, and is approximately equal to the two, and the first stage pressure of the hydraulic chamber/pressure chamber is decomposed into a hydraulic chamber.
  • Stabilizing pressure measures Adjust the pressure of the high pressure gas by adjusting the temperature of the high pressure gas to achieve a constant pressure.
  • the liquid discharge port injects the pressure liquid into the working cylinder (GZG) under the control of the electric control valve to drive the corresponding machine, and the high pressure gas transmits the pressure through the piston to press the hydraulic chamber.
  • the pressure fluid causes the pressure fluid to work toward the working cylinder at a pressure equal to the pressure of the high pressure gas.
  • Example 1 Gas tank and piston cylinder integrated liquid seal accumulator. (figure 1).
  • a sealed large-diameter cylindrical high-pressure gas tank (QTG 1 , referred to as a gas tank) forms a high-pressure gas chamber (QTQ 1 , referred to as a gas chamber), and a small-diameter cylindrical piston cylinder (HSG) is disposed inside, a gas tank And the piston cylinder size cylinder is sealed with each other;
  • a piston (HS) divides the piston cylinder into two parts: a pneumatic chamber (QYQ) and a hydraulic chamber (YYQ), and a piston-cylinder top establishes a gas-liquid passage (TD 1 ) to connect the gas chamber (QTQ) 1 ) and the air pressure chamber (QYQ), the high pressure gas is filled through the supplementary port (BCK), and the air pressure is transmitted to the hydraulic chamber through the piston, so the pressure liquid in the hydraulic chamber has a high pressure, and the bottom of the hydraulic chamber has a discharge port pipe (ZPK), whereby the pressure fluid is injected to store the pressure energy, and the pressure fluid is
  • the gas tank has two functions, one is the extension of the gas pressure chamber (QYQ), which acts as a high pressure gas chamber, helps the air chamber to store high pressure gas, increases the total volume of the air chamber, and reduces the pressure fluctuation of the air chamber; the other is acting as a set.
  • QYQ gas pressure chamber
  • Liquidizer because the piston always has a small amount of leakage, the pressure fluid will slowly leak from the hydraulic chamber to the air pressure chamber, and more and more pressure fluid will collect on the top of the piston, which needs to be cleaned up when the piston moves to the top of the piston cylinder.
  • the pontoon (FT) structure is a thin-walled sealing cylinder, and the vent hole (TQK) connects the air inside and outside the pontoon with equal pressure to avoid being crushed.
  • Stabilizing pressure measures Adjust the pressure of the high pressure gas by adjusting the temperature of the high pressure gas to achieve the pressure quasi-constant pressure.
  • a number of controlled heating and cooling devices are wound around the inner wall of the gas tank. For example, a number of coils of liquid pipe with heat exchange sheets are controlled to heat, called a heat exchange tube (RJH), and a gas tank is connected.
  • the pipeline is equipped with a pressure sensor (YLG) or a pressure gauge to monitor the pressure.
  • YLG pressure sensor
  • the pressure of the gas chamber changes, and measures need to be taken to stabilize the pressure.
  • One is to make the high-pressure gas in a saturated steam state, that is, to use a high-pressure gas whose critical temperature is higher than the temperature control.
  • the pressure of the high-pressure gas is also The quasi-constant pressure corresponding to the temperature; the other is to select the high-pressure gas whose critical temperature is lower than the temperature control, the high-pressure gas is in the gas state or the super-fluid state, the pressure change is detected by the pressure sensor, and the temperature of the high-pressure gas is adjusted to adjust the pressure to Reduce the rate of change of pressure fluctuations to form quasi-constant pressure, specifically:
  • the pressure sensor When the pressure is lower than the lower limit, the pressure sensor (YLG) sends a heating signal, and the hot liquid pump (RYB, Fig. 5) pumps the circulating hot liquid to the heat exchange tube (RJH) to heat the high pressure gas, and the high pressure gas rises. After high, the pressure will increase, and the signal threshold of the liquid pump stop can be set at a certain point between the upper and lower pressure limits.
  • the threshold point is set at the nominal value when the pressure is higher than At the nominal value, the pressure sensing/comparator sends a stop plus The heat signal; when the pressure is higher than the upper limit value, the pressure sensor sends a cooling signal, and the circulating liquid coolant is pumped by the cold liquid pump (LYB) to the heat exchange tube to cool the high pressure gas, and the pressure of the high pressure gas is lowered to lower the pressure.
  • the pressure sensing/comparator issues a stop cooling signal.
  • the gas chamber can be heated by a wrap-around controlled electric heating element instead of a heat exchange tube (RJH).
  • RJH heat exchange tube
  • Increasing the total volume of the high pressure gas chamber is also one of the measures to stabilize the pressure.
  • the position of the piston is monitored by a spring (TH) and a position sensor (WZG), that is, the height of the liquid level is monitored.
  • the position sensor is fixed to the top and the spring is connected to the lower side.
  • the drawn spring structure on the upper part of the piston (in the lower part of the piston) is drawn.
  • the structure of the compression spring is also possible, the principle is the same, so it is not shown), when the liquid level is lowered, the piston moves downward, the spring acts on the position sensor, and the output signal of the position sensor is strengthened.
  • the position sensing/comparator sends a “injection signal” to the infusion pump.
  • the infusion pump starts and injects into the hydraulic cylinder until the piston presses the upper gasket. At this time, the sampling signal of the spring length stops changing. According to this, the control system can judge that the hydraulic chamber needs to inject the pressure liquid or stop the injection of the pressure liquid.
  • Example 2 Gas tank and piston cylinder split type liquid seal accumulator. (figure 2).
  • the split structure, the high pressure gas tank (QTG 2 ) and the piston cylinder (HSG) are relatively independent, and the top of the two is connected by the gas-liquid external passage (TD 2 ).
  • the pressure liquid on the top of the piston passes through the passage.
  • the tube (TD 2 ) flows into the gas chamber (QTQ 2 ), and the pressure fluid (collection fluid SJY) collected at the bottom of the gas chamber is increased, causing the float (FT 2 ) to float.
  • Other structures and working principles are the same as those of the one-piece.
  • Example 3 Sandwich Piston (The piston in Figure 3 is an external view and Figure 3.1 is a cross-sectional view of the piston).
  • the requirements for the improvement of the piston are: strengthening the sealing performance, reducing the friction loss, and improving the reaction sensitivity.
  • a sealing seal, a grease sandwich layer seal, a chamfer seal and the like are combined to form a seal.
  • the ring seal is a conventional method in which a groove is formed in the piston and a rubber seal is embedded.
  • One of the important features of the present invention is to propose a grease liquid sandwich piston seal and a chamfer seal;
  • the sandwich piston is a dual piston (including the piston upper (HS S ) and the piston lower (HS x )), the piston lower (HS x ) and the sliding sleeve (HT) are integrated, and the piston is even (HS S ) and The sliding column (HZ) is integrated, and there is a stroke hole (XCK) in the sliding column.
  • the stroke hole communicates with the sandwich layer through the liquid hole (YK), and the stroke pin (XCS) is inserted from the stroke hole and the piston is closed (HS x
  • the bottom of the welding is integrated, and the sealing cover (MFG) covers the stroke hole to form a seal.
  • the space between the upper and lower sides of the piston is a sealed space, called a sandwich layer (JXC), a sandwich layer of a sandwich piston, and a stroke pin.
  • JXC sandwich layer
  • the sliding column and the sliding sleeve are all in the sealing range, the sliding column forms a sliding fit with the sliding sleeve, and the stroke of the stroke bolt head (ST) is limited by the stroke hole (XCK) to the highest point and the lowest point, so the maximum of the sandwich layer
  • the thickness is limited to prevent the spool from disengaging from the sleeve.
  • n-1 sandwich layers can be formed by n-layer dual piston
  • the force acting on the piston is much larger than the friction between the piston and the cylinder, so the pressure of the sandwich layer is approximately equal to the pressure of the air pressure chamber, so that the leakage of the high pressure gas to the sandwich layer is a micro differential pressure leakage; the pressure and hydraulic pressure of the sandwich layer
  • the pressure of the chamber is also approximately equal, so that the leakage of the pressure fluid to the sandwich layer is also a micro differential pressure leak.
  • the sealing layer of the sandwich layer will leak, so it needs to be supplemented.
  • the one-way valve (DXF) is used to supply the liquid layer to the sandwich layer.
  • the check valve is made in the middle of the spool to save space.
  • the sealing grease in the hydraulic chamber The liquid can enter the sandwich layer from the one-way valve, and the grease in the sandwich layer cannot flow back from the check valve to the hydraulic chamber.
  • the grease sandwich seal includes: a grease seal and a liquid seal
  • the grease seal uses the sealing grease as the sandwich layer. If the sealing grease of the sandwich layer leaks, the seal grease stored in the skin capsule (PN) passes through the hose (RG) and the check valve (DXF) under the pressure of the hydraulic chamber. Sandwich layer supplement;
  • the liquid seal uses the pressure fluid as the sandwich layer. If the pressure fluid in the sandwich layer leaks, the pressure fluid in the hydraulic chamber is replenished to the sandwich layer through the check valve. However, according to practical experience, the check valve is not required, and the sandwich layer is filled with pressure. Liquid, so this check valve is optional.
  • the gas will collect in the upper part of the sandwich layer, firstly accumulating in the chamfer (DJ B , the lower end chamfer on the piston) on the sandwich layer, to prevent the pressure liquid from flowing.
  • the pressure chamber penetrates; and the pressure fluid collects in the lower part of the sandwich layer, firstly accumulating in the chamfer below the sandwich layer (DJ c , that is, the upper end chamfer of the piston), which prevents the gas from penetrating into the hydraulic chamber.
  • the gas will first accumulate in the lower end chamfer (DJ D ) of the piston and then be squeezed into the sandwich layer;
  • the pressure chamber is mixed with the pressure fluid, the pressure fluid will first accumulate in the chamber.
  • the upper end chamfer (DJ A ) of the piston is then squeezed into the sandwich layer;
  • the chamfer seal enhances the interception of gas leakage into the hydraulic chamber, and also enhances the interception of the leakage of pressure fluid into the air chamber.
  • Example 4 Electronically controlled thimble valve DKF leaker.
  • the collecting liquid (SJY) at the bottom of the gas chamber will be more and more, so that the float FT floats higher and higher.
  • the float is pressed to the collecting liquid sensor (JYG), the opening ejector valve is leaked.
  • the electronically controlled thimble valve receives the signal of the missing liquid and the valve motor (DK 12 ) rotates forward, and the motor shaft DK 11 drives the nut column (DK 9 ) to rotate because the screw (DK 8 ) and the polyhedral column (DK 7 ) is integrated, and the polyhedral column DK 7 is stuck in the polyhedral hole (DK 6 ) and cannot be rotated. It can only go up with the positive transmission of the nut column DK 9 , and the top needle tip (DK 5 ) is pushed up to open the thimble.
  • the pressure liquid flows back from the leaking tube to the liquid collecting cylinder; when the collecting liquid leaks, the floating tube (FT) is lowered, and when the floating tube is pressed to the bottom sensor (DDG), an electric signal for closing the ejector valve is issued, and the electronically controlled ejector valve is After receiving the closing signal, the motor reverses and the polyhedral column (DK 7 ) goes down with the reverse rotation of the nut column (DK 9 ). The ejector valve closes under pressure and the motor stops.
  • Example 5 Hydraulic system based on a liquid-seal accumulator.
  • the drive shaft (ZZZ) drives the driven shaft (CDZ), and the driven shaft drives the liquid injection pump (YB) to pump the pressure liquid in the liquid cylinder (SYT) into the hydraulic chamber (YYQ); the other is the motor drive.
  • a motor is connected to the liquid injection pump (YB).
  • the sensor/comparator sends a "injection signal" to the liquid injection pump, the motor starts to drive the liquid injection pump to pump the pressure liquid in the liquid cylinder into the hydraulic pressure. Cavity.
  • the pressure liquid pushes the piston upwards, and gradually presses the gas in the air pressure chamber back to the gas tank.
  • the pressure liquid gradually occupies the space of the gas chamber, and the piston stops moving when pressed to the upper seal (SMF) of the hydraulic cylinder.
  • the liquid discharge port injects pressure liquid into the working cylinder under the control of the electric control valve to drive the corresponding machine, and the high pressure gas transmits pressure through the piston to press the pressure liquid in the hydraulic chamber, so that The pressure fluid works at a pressure equal to the pressure of the high pressure gas to the working cylinder.
  • the booster cylinder (ZYG) is optional and requires more pressure than the hydraulic chamber.
  • Figure 1 Gas tank and piston cylinder integrated liquid seal accumulator.
  • YLG-pressure sensor QTG 1 - integrated accumulator gas tank; QTQ 1 - integrated accumulator gas chamber; TD 1 - integrated accumulator gas-liquid passage; MYG-full liquid sensor; SMF-upper gasket ; RJH-heat exchange tube; HSG-piston cylinder; QYQ-pressure chamber; HS-piston; MFQ-seal ring; YYQ-hydraulic chamber; XMF-lower gasket; QYG-liquid deficiency sensor; SJK-heat exchange tube water interface ;GYG-overpressure sensor; PYK-discharge port; ZYK-injection port; ZPK-injection drain port; DDG-bottom sensor; LYG-leakage collection tube; LYGA-leakage return tube; SJY-collection solution ;DKF-electric control valve;TH-spring;WZG-position sensor;FT 1 -
  • TQK-float vent (the vent makes the gas inside and outside the pontoon communicate, the internal and external pressures are equal); NTB-inner wall; WTB-outer wall.
  • Figure 2 Gas tank and piston cylinder split type liquid seal accumulator. Different from the reference numerals of Fig. 1 are: FT 2 - split accumulator buoy; QTG 2 - split accumulator gas tank, QTQ 2 - split accumulator gas chamber, TD 2 - split accumulator gas and liquid External channel; the same are: YLG, MYG, SMF, RJH, HSG, QYQ, HS, YYQ, XMF, QYG, SJK, GYG, PYK, ZYK, ZPK, DDG, LYG, LYGA, SJY, DKF, TH, WZG , TQK, ZJ, WZG, XHX, MFT, BCK; SYT;
  • Figure 2.1 A perspective view of the split accumulator float FT2. TQK-ventilation.
  • Figure 3 Appearance of the sandwich piston.
  • Figure 3.1 Sectional view of the sandwich piston.
  • BCK, SMF, HSG, QYQ, HS S , DJ A , DJ B , HZ, HT, DJ c , DJ D , HS x , JXC, YYQ, RG, XMF, PN, ZZK, PYK , ZYK, ZPK, changed or added symbols are: MFG-sealed cover; ST-plug; XCS-stroke plug; DXF-check valve; XCK-stroke hole; YK-liquid hole;
  • Figure 4 Electronically controlled thimble valve DKF.
  • Figure 4.1 Sectional view of the ejector valve. DK 3 - thimble body; DK 4 - thimble spool; DK 5 - thimble tip.
  • Figure 5 Hydraulic system based on a liquid-seal accumulator.

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Abstract

一种基于集液器和夹心活塞的液封蓄能器及其液压系统，液封蓄能器包括活塞缸（HSG）和高压气体罐（QTG），当活塞（HS）移动到活塞缸顶时，活塞顶上泄漏聚集的压力液通过气液通道（TD）流入气体罐，使得活塞顶上的压力液被及时清理，气体罐底部收集的压力液增加使得浮筒（FT）上升，当浮筒压到收集液传感器（JYG）时，发出信号打开电控阀（DKF），漏出的压力液从漏液管（LYG）流回盛液筒（SYT）。

Description

基于集液器和夹心活塞的液封蓄能器及其液压系统
技术领域：本发明是一种蓄能器及其液压操控系统，属于液压传动系统领域。本发明简称液封蓄能器。
背景技术：蓄能器有囊式蓄能器、活塞式蓄能器和膜片式蓄能器三大类，其中囊式蓄能器和膜片式蓄能器都有橡胶皮突然破裂的危险，不适合应用于可靠性要求高的系统中，比如车、船、飞机等；活塞式蓄能器没有橡胶皮突然破裂的危险，可靠性高，但是，目前活塞式蓄能器面临的重要问题是，既要活塞隔离气体和液体的性能好，又要活塞与缸体的摩擦力小，这是一对矛盾。具体说，如果要提高气体与液体的隔离性能，需要加大活塞密封圈相对于缸体的正压力，所以摩擦力增大，使得响应不灵敏；反过来，如果要增加响应灵敏度，应该减小活塞的摩擦力，又会使得气体与液体的隔离性能变差，产生液体向气压腔渗漏以及气体泄漏等缺点。
发明目的：如果能够克服这些缺点，使得活塞式蓄能器既是隔离气体和液体的性能好，又是响应灵敏度高，那么活塞式蓄能器就能够有更广阔的应用前景，如：在车、船、飞机等设备中充当助力装置。本发明的蓄能器具体目标是：①安全可靠，不会突然损坏失灵；②气液隔离性好；③响应灵敏度高；④经久耐用；⑤工作压力高且准恒压；⑥效率高；⑦体积小；⑧制作成本低廉；⑨结构简单、维护方便；⑩基于这种蓄能器，可以设计相应的控制系统，驱动制动器、转向器、油门、离合器、换挡机构、飞机升降舵等等执行机构。
为了叙述简便，先给出以下约定：
●压力液腔YYQ中充满了压力液YLY，但是压力液YLY并没有在图中标出，仅在说明书中给出描述；同理，气压腔QYQ中的高压气体GYQT也没标出。
●压力(温度)设定值有三个：标称值、上限值和下限值，准恒压(准恒温)是指压力(温度)在以设定的标称值为中心的小范围内变化，或者是在设定的上限值和下限值之间变化。
●传感器总是和比较器结合使用而产生控制信号，比如，预先在位置比较器中设定好一个“补液阈值电位”，当弹簧长度到达某个规定长度时，位置传感器输出信号电位强度就超过了“补液阈值电位”，这时，位置比较器的输出值就翻转，就是向注液泵发出“注液信号”，注液泵起动，向液压缸注液。这个过程，以下简称为位置传感/比较器发出注液信号；类似的，有压力传感/比较器发出加热信号或冷却信号，满液传感/比较器发出停机信号等。比较器设计在控制系统中，没有在图中标出。
●大写字母构成器件标号，数字为下标为器件编号，如ZK1、GZG2、DK1等等。
●活塞上都带有密封圈，通常不再特别强调，活塞在其中运动的缸称为活塞缸，活塞缸的最高位置称为活塞缸顶。
●集液器的全称为“集液排液器”，兼有集液和排液的功能。
●各种传感器的信号线统一由XHX作为示意，不逐个详细标出。
●高压气体罐和高压气体腔简称为气体罐QTG和气体腔QTQ。
液封蓄能器是基于高压气体进行工作的，所以在描述液封蓄能器工作原理之前，先对高压气体GYQT和已有的活塞式蓄能器给出说明，
在常温范围(-20～100℃)内，高压气体GYQT包括超流体(如二氧化碳)、气体(如氮气、氩气等)和液气共存的饱和汽BHQ(如制冷剂氟利昂、氨等)，高压气体又称为储压气体或储压剂。
已有的活塞式蓄能器的基本原理是：
一个活塞HS将活塞缸HSG分割成气压腔(上腔)和液压腔(下腔)两部分，气压腔充注高压气体，压力为PQ，液压腔底部有一个注排口管道(ZPK)，压力液由此注入和排出，压力液压力为PY，活塞的摩擦力为FM；活塞面积为S，当注液泵向液压腔注液时，PQ+FM/S＝PY；当液压腔向外排液作功时，PQ＝PY+FM/S，(符号PQ、PY、FM、S与附图无关，只作理论分析用)，通常PQ和PY远大于FM/S，可以认为PQ≈PY，所以液压腔中的压力液具有很高的压力。
目前存在的主要问题是：为了防止液压腔的压力液漏向气压，活塞密封圈要与活塞缸内壁压得很紧，使得活塞反应灵敏度降低，本发明有效地提高了活塞反应灵敏度。
本发明基本原理：一种基于集液器和夹心活塞的液封蓄能器及其液压系统，液封蓄能器包括一个密封圆筒形活塞缸(HSG)，一个活塞(HS)将活塞缸(HSG)分割成气压腔(QYQ)和液压腔(YYQ)两部分，气压腔充注高压气体，气压通过活塞传递到液压腔，所以液压腔中的压力液具有很高的压力，液压腔底部有一个注排口管道(ZPK)，由此注入压力液以储存压力能，排出压力液以输出压力能，其特征是：还包括一个由高压气体罐(QTG，包括QTG1和QTG2，简称气体罐，用于储存高压气体)形成的气体腔(QTQ，包括QTQ1和QTQ2，)，活塞缸顶建立气液通道(TD，包括TD1和TD2)，连通气压腔(QYQ)和气体腔(QTQ)，气体罐有两个功能，一个是充当气压腔(QYQ)的外延，帮助气压腔存储高压气体，增加了气压腔的总容积，减小气压腔的压力波动；另一个是气体罐底部充当集液器，由于活塞总是有少量的泄漏，压力液会缓慢地从液压腔(YYQ)泄漏到气压腔 (QYQ)，在活塞顶上会聚集越来越多的压力液，需要清理掉，当活塞移动到活塞缸顶时，活塞顶上的压力液会通过气液通道(TD)流入气体腔(QTQ)，活塞顶上的压力液被及时清理，而气体腔底部收集的压力液会越来越多，收集液增加时会使浮筒FT(包括FT1和FT2)上升，当浮筒压到收集液传感器JYG时，发出打开电控阀(DKF)信号，打开电控阀，漏掉收集液，压力液从漏液管(LYG)流回盛液筒(SYT)；收集液漏掉时会使浮筒FT下降，当浮筒压到到底传感器DDG时，发出关闭电控阀的电信号，电控阀关闭，随后电机停止。
其另一个重要特征是：夹心式活塞，用以加强活塞的密封性能，并减小摩擦损耗，提高反应灵敏度，该活塞由活塞上偶(HSS)与活塞下偶(HSx)通过滑柱(HZ)与滑套(HT)形成滑动配合，在活塞上下偶之间形成一个距离可以变化的充满密封液(包括密封油脂和压力液)的夹心层(JXC)；因为密封圈与活塞缸内壁压力很小，所以液压腔/气压腔的压力比较小，夹心层的压力处于液压腔与气压腔的中间值，并与两者近似相等，将液压腔/气压腔的一级压力分解为液压腔/夹心层加夹心层/气压腔两级压力，所以液压腔和气压腔向夹心层的泄漏大大减小，成为微压差渗漏；行程栓(XCS)栓头(ST)的行程，被行程孔(XCK)限制了最高点和最低点，所以夹心层的最大厚度被限制，以免滑柱与滑套相脱离，密封盖(MFG)保证行程孔的密封，行程栓底部焊接在活塞下偶的底部以保证密封，所以夹心式活塞的夹心层、行程栓、滑柱和滑套都处于密封范围内。
稳定压力措施：通过调节高压气体温度来调节高压气体压力，实现压力准恒定。
蓄能阶段。当注液泵通过注液口向液压腔注液时，压力液推动活塞向上运动，储存压力液，逐渐将气压腔中的气体压缩到气体罐，当活塞到达液压缸的上密封垫(SMF，图1)时，控制系统使注液停止，其控制方法有几种，方法1：压到上密封垫(SMF)和满液传感器(MYG)时，满液传感器发出停止注液信号；方法二：在注液管道上安装一个过压传感器(GYG)，压到上密封垫(SMF)时，活塞会停止运动，但是注液泵继续工作，会使液压腔的压力继续升高，当液压腔压力到达预设的过压阈值时，过压传感器(GYG)会测出压力已经到达阈值，发出停机指令，注液泵停机。
作功阶段。当工作油缸(GZG，图5)需要压力液时，排液口在电控阀的控制下向工作油缸(GZG)注入压力液，驱动相应的机械，高压气体通过活塞传递压力，压迫液压腔中的压力液，使压力液以等于高压气体压力值向工作油缸作功。
实施例
实施例1——气体罐与活塞缸一体式液封蓄能器。(图1)。
一密封的大直径圆筒形高压气体罐(QTG1，简称气体罐)形成一个高压气体腔(QTQ1，简称气体腔)，其里面套一个小直径圆筒形活塞缸(HSG)，气体罐和活塞缸大小圆筒相互密封；一个活塞(HS)将活塞缸分割成气压腔(QYQ)和液压腔(YYQ)两部分，活塞缸顶建立气液通道(TD1)，连通气体腔(QTQ1)和气压腔(QYQ)，通过补充口(BCK)充注高压气体，气压通过活塞传递到液压腔，所以液压腔中的压力液具有很高的压力，液压腔底部有一个注排口管道(ZPK)，由此注入压力液以储存压力能，排出压力液以输出压力能。气体罐有两个功能，一个是气压腔(QYQ)的外延，充当高压气体腔，帮助气压腔存储高压气体，增加了气压腔的总容积，减小气压腔的压力波动；另一个是充当集液器，由于活塞总是有少量的泄漏，压力液会缓慢地从液压腔泄漏到气压腔，在活塞顶上会聚集越来越多的压力液，需要清理掉，当活塞移动到活塞缸顶时，活塞顶上的压力液会通过气液通道流入气体腔，活塞顶上的压力液被及时清理，而气体腔底部收集的压力液(收集液SJY)会越来越多，使浮筒(FT1)浮得越来越高，当浮筒压到收集液传感器JYG时，发出打开电控阀信号，打开电控阀(DKF)，漏掉收集液，压力液从漏液管(LYG)流回盛液筒(SYT)；收集液漏掉时会使浮筒FT1下降，当浮筒压到到底传感器DDG时，发出关闭电控阀的电信号，电控阀关闭，随后电机停止。
浮筒(FT)结构为薄壁密封筒，通气孔(TQK)使浮筒内外空气连通而压力相等，以避免被压扁。
稳定压力措施：通过调节高压气体温度来调节高压气体压力，实现压力准恒压。绕着气体罐内壁，缠绕数圈受控加热和降温装置，比如，缠绕数圈带有热交换片的液管受控加热，称为热交换管(RJH)，在气体罐上接出一根管道，安装一个压力传感器(YLG)或者压力表监测压力，当活塞位置变化或者环境温度变化时，气体腔的压力会发生变化，需要采取措施稳定压力。使高压气体形成准恒压有两种办法，一种是令高压气体处于饱和汽状态，即选用临界温度高于温控的高压气体，只要将温度控制为准恒温，高压气体的压力也就处于对应于温度的准恒压；另一种是选用临界温度低于温控的高压气体，高压气体处于气体状态或超流体状态，通过压力传感器检测压力变化，调节高压气体的温度以调节压力，以减小压力波动的变化率，形成准恒压，具体说：
当压力低于下限值时，压力传感器(YLG)发出加热信号，由热液泵(RYB，图5)向热交换管(RJH)泵动循环的热液以加热高压气体，高压气体温度升高后会使得压力升高，可以将液泵停止的信号阈值设置在压力上限与下限之间的某个点，为简单合理起见，本文约定将该阈值点设置在标称值，当压力高于标称值时，压力传感/比较器发出停止加 热信号；当压力高于上限值时，压力传感器发出冷却信号，由冷液泵(LYB)向热交换管泵动循环的冷却液以冷却高压气体，高压气体温度降低后会使得压力降低，当压力低于标称值时，压力传感/比较器发出停止冷却信号。
另一种方法是，用缠绕式受控电热元件取代热交换管(RJH)对气体腔加热。
加大高压气体腔的总容积也是稳定压力的措施之一。
用弹簧(TH)和位置传感器(WZG)监测活塞的位置，也就是监测液位的高度，位置传感器固定于顶部，下接弹簧TH，画出的是在活塞上部的拉簧结构(在活塞下部的压簧结构也是可以的，原理相同，所以没有画出)，当液位降低时活塞下移，弹簧对位置传感器作用力加大，位置传感器输出信号加强，当弹簧作用力到达阈值规定值时，位置传感/比较器就向注液泵发出“注液信号”，注液泵起动，向液压缸注液，一直到活塞压住上密封垫，这时，弹簧长度的采样信号会停止变化，控制系统据此可以判断出液压腔需要注入压力液或停止注入压力液。
实施例2——气体罐与活塞缸分体式液封蓄能器。(图2)。
分体式结构，高压气体罐(QTG2)与活塞缸(HSG)相对独立，两者顶部由气液外部通道(TD2)连通，当活塞运动到顶部时，活塞顶上的压力液会通过通道管(TD2)流入气体腔(QTQ2)，而气体腔底部收集的压力液(收集液SJY)会越来越多，使浮筒(FT2)浮起来。其它结构和工作原理与一体式的相同。
实施例3-夹心式活塞(图3中的活塞是外观图，图3.1是活塞的剖视图)。
对于活塞改进的要求是：加强密封性能、减小摩擦损耗、提高反应灵敏度，为了加强密封性能，采用了密封圈密封、脂液夹心层密封、倒角密封等多种密封相结合的结构，密封圈密封是传统的方法，在活塞上开槽并嵌入橡胶密封圈，本发明的重要特征之一是提出了脂液夹心层式活塞密封和倒角密封；
脂液夹心层式活塞密封
夹心式活塞是一个对偶活塞(包括活塞上偶(HSS)和活塞下偶(HSx))，活塞下偶(HSx)与滑套(HT)为一体，活塞上偶(HSS)与滑柱(HZ)为一体，滑柱中有一个行程孔(XCK)，行程孔通过液孔(YK)与夹心层连通，行程栓(XCS)从行程孔插下，与活塞下偶(HSx)的底部焊接成一体，密封盖(MFG)盖住行程孔形成密封，所以，在活塞上下偶之间的空间为密封空间，称为夹心层(JXC)，夹心式活塞的夹心层、行程栓、滑柱和滑套都处于密封范围内，滑柱与滑套形成滑动配合，行程栓栓头(ST)的行程，被行程孔(XCK)限制了最高点和最低点，所以夹心层的最大厚度被限制，以免滑柱与 滑套相脱离。
在活塞上下偶之间形成一个距离可以变化的充满密封脂液(包括密封油脂或压力液)的夹心层；(原理上可以由n层对偶活塞构成n-1个夹心层)，因为气压和液压作用于活塞上的力远大于活塞与缸体的摩擦力，所以夹心层的压力与气压腔的压力近似相等，使得高压气体向夹心层的泄漏为微压差渗漏；夹心层的压力与液压腔的压力也近似相等，使得压力液向夹心层的泄漏也为微压差渗漏。夹心层的密封脂液是会泄漏的，所以需要有补充，用一个单向阀(DXF)向夹心层提供脂液补充，单向阀做在滑柱中间以节省空间，液压腔中的密封脂液可以从单向阀进入夹心层，夹心层的脂液不能从单向阀往回流至液压腔。
脂液夹心层密封包括：脂密封和液密封，
脂密封是用密封油脂充当夹心层，夹心层的密封油脂如果泄漏，在液压腔压力的作用下，由皮囊(PN)中储存的密封油脂通过软管(RG)和单向阀(DXF)向夹心层补充；
液密封是用压力液充当夹心层，夹心层的压力液如果泄漏，液压腔中压力液通过单向阀向夹心层补充；不过根据实践经验看，不要单向阀，夹心层中也会充满压力液，所以该单向阀是可选项。
倒角密封
假定夹心层混合有气体和压力液，气体会聚集在夹心层的上部，首先会聚集在夹心层上面的倒角(DJB，即活塞上偶的下端面倒角)中，起到阻止压力液向气压腔渗透的作用；而压力液会聚集在夹心层的下部，首先会聚集在夹心层下面的倒角(DJc，即活塞下偶的上端面倒角)中，起到阻止气体向液压腔渗透的作用；
同理，假定液压腔混入了气体，气体首先会聚集在活塞下偶的下端面倒角(DJD)中，再被挤到夹心层中；假定气压腔混入了压力液，压力液首先会聚集在活塞上偶的上端面倒角(DJA)中，再被挤到夹心层中；
所以，倒角密封加强了对气体向液压腔泄漏的拦截，也加强了对压力液向气压腔泄漏的拦截。
实施例4-电控顶针阀DKF漏液器。电控顶针阀关闭时，气体腔底部的收集液(SJY)会越来越多，使浮筒FT浮得越来越高，当浮筒压到收集液传感器(JYG)时，发出打开顶针阀漏掉收集液的电信号，电控顶针阀收到漏掉收集液信号后阀电机(DK12)正转，其电机轴DK11带动螺母柱(DK9)旋转，因为螺杆(DK8)与多面体柱(DK7)一体，而多面体柱DK7被卡在多面体孔(DK6)中不能旋转，只能随着螺母柱DK9的正传而上行，将顶针针尖(DK5)顶上去，打开顶针阀，压力液从漏液管流回盛液筒；收集液漏掉时会 使浮筒(FT)下降，当浮筒压到到底传感器(DDG)时，发出关闭顶针阀的电信号，电控顶针阀收到关闭信号后电机反转，多面体柱(DK7)随着螺母柱(DK9)的反转而下行，顶针阀在压力的作用下关闭，随后电机停止。
漏液器也可以采用已知的其它机械阀和电子阀。
实施例5-基于液封蓄能器的液压系统。
蓄能阶段。当液位降低时，弹簧(TH)的弹力加大，位置传感器(WZG)输出信号加强，当信号大于设定的“补液阈值”时，位置传感/比较器向注液泵发出“注液信号”，注液泵起动，向液压缸注液。注液泵的驱动有两种方式，一种是发动机驱动，当传感/比较器向注液泵发出“注液信号”时，离合控制器(LHK，图5)使电磁离合器(LHQ)啮合，主动轴(ZDZ)带动从动轴(CDZ)，从动轴带动注液泵(YB)，将盛液筒(SYT)中的压力液泵入液压腔(YYQ)；另一种是电动机驱动，将一台电动机与注液泵(YB)连接，当传感/比较器向注液泵发出“注液信号”时，电动机起动，带动注液泵，将盛液筒中的压力液泵入液压腔。注液时，压力液推动活塞向上运动，逐渐将气压腔中的气体挤压回到气体罐，压力液逐步占驻气体腔的空间，活塞压到液压缸的上密封垫(SMF)时停止运动，压力液不再进入液压腔，但是在泵压的作用下液压腔的压力继续升高，到达预设的过压阈值值时，满液传感/比较器(MYG)发出停机指令，注液泵停机。
作功阶段。当工作油缸(GZGk)需要压力液时，排液口在电控阀的控制下向工作油缸注入压力液，驱动相应的机械，高压气体通过活塞传递压力，压迫液压腔中的压力液，使压力液以等于高压气体压力值向工作油缸作功。
增压缸(ZYG)是可选项，需要比液压腔更大的压力时采用。
附图说明
图1——气体罐与活塞缸一体式液封蓄能器。YLG-压力传感器；QTG1-一体式蓄能器气体罐；QTQ1-一体式蓄能器气体腔；TD1-一体式蓄能器气液通道；MYG-满液传感器；SMF-上密封垫；RJH-热交换管；HSG-活塞缸；QYQ-气压腔；HS-活塞；MFQ-密封圈；YYQ-液压腔；XMF-下密封垫；QYG-缺液传感器；SJK-热交换管水接口；GYG-过压传感器；PYK-排液口；ZYK-注液口；ZPK-注液排液口；DDG-到底传感器；LYG-漏液收集管；LYGA-漏液回流管；SJY-收集液；DKF-电控阀；TH-弹簧；WZG-位置传感器；FT1-一体式蓄能器浮筒；TQK-浮筒通气口；ZJ-支架；WZG-位置传感器；XHX-信号线；MFT-密封套；BCK-高压气体补充口；SYT-盛液筒；集液器全称为“集液排液器”，包括(FT-浮筒；LYG-漏液收集管；DKF -电控阀；QTG-气体罐)
图1.1——一体式蓄能器浮筒FT1立体图。TQK-浮筒通气口(通气口使浮筒内外气体连通，内外压力相等)；NTB-内筒壁；WTB-外筒壁。
图2-气体罐与活塞缸分体式液封蓄能器。与图1标号不同的有：FT2-分体式蓄能器浮筒；QTG2-分体式蓄能器气体罐、QTQ2-分体式蓄能器气体腔、TD2-分体式蓄能器气液外部通道；相同的有：YLG、MYG、SMF、RJH、HSG、QYQ、HS、YYQ、XMF、QYG、SJK、GYG、PYK、ZYK、ZPK、DDG、LYG、LYGA、SJY、DKF、TH、WZG、TQK、ZJ、WZG、XHX、MFT、BCK；SYT；
图2.1——分体式蓄能器浮筒FT2立体图。TQK-通气口。
图3-夹心式活塞外观图。与前图相同的有：BCK、SMF、HSG、QYQ、MFQ、MFQ、YYQ、XMF、PYK、ZYK、ZPK；与前图相不同的有：HSS-活塞上偶；DJA-活塞上偶的上倒角；DJB-活塞上偶的下倒角；HZ-滑柱；HT-滑套；DJc-活塞下偶的上倒角；DJD-活塞下偶的下倒角；HSx-活塞下偶；JXC——夹心层；RG-软管；PN-皮囊；ZZK-注脂口。
图3.1-夹心式活塞剖视图。与图3相同的有：BCK、SMF、HSG、QYQ、HSS、DJA、DJB、HZ、HT、DJc、DJD、HSx、JXC、YYQ、RG、XMF、PN、ZZK、PYK、ZYK、ZPK、改变或增加的符号有：MFG-密封盖；ST-栓头；XCS-行程栓；DXF-单向阀；XCK-行程孔；YK-液孔；
图4-电控顶针阀DKF。DK1-接口螺丝；DK2-过滤网；DK3-顶针阀体；DK5-顶针针尖；DK6-多面体孔；DK7-多面体柱；DK8-螺杆(与多面体柱一体)；DK9-螺母柱；DK10-锁定螺丝；DK11-电机轴；DK12-阀电机；DK13-阀外套；DK14-定位螺丝；DK15-漏液出口；。
图4.1-顶针阀剖面图。DK3-顶针阀体；DK4-顶针阀芯；DK5-顶针针尖。
图5-基于液封蓄能器的液压系统。QK-气孔；SYT-盛液筒；YB-注液泵；ZDZ-主动轴；LHQ-电磁式离合器；LHK-离合控制器；CDZ-从动轴；ZHF-止回阀；XNQ-液封蓄能器(虚线框内)；RYY-热液源；RYB-热液泵；LYY-冷液源；LYB-冷液泵；ZYG-增压缸；ZFk-注液阀k(k通配1-n的编号)；ZKk-注液阀控制器k；GZGk-工作缸k；PFk-排液阀k；PKk-排液阀控制器k；HYG-回液管；HYB-回液泵。

Claims (10)

  1. 一种基于集液器和夹心活塞的液封蓄能器及其液压系统，包括一个密封圆筒形活塞缸(HSG)，一个活塞(HS)将活塞缸(HSG)分割成气压腔和液压腔两部分，气压腔充注高压气体，气压通过活塞传递到液压腔，所以液压腔中的压力液具有很高的压力，液压腔底部有一个注排口管道(ZPK)，由此注入压力液以储存压力能，排出压力液以输出压力能，其特征是：
    一密封的大直径圆筒形高压气体罐(QTG，简称气体罐)形成一个高压气体腔(QTQ，简称气体腔)，其里面套一个小直径圆筒形活塞缸(HSG)，气体罐和活塞缸大小圆筒相互密封；一个活塞(HS)将活塞缸分割成气压腔(QYQ)和液压腔(YYQ)两部分，活塞缸顶建立气液通道(TD)，连通气体腔(QTQ)和气压腔(QYQ)，充注高压气体，气压通过活塞传递到液压腔，所以液压腔中的压力液具有很高的压力，液压腔底部有一个注排口管道(ZPK)，由此注入压力液以储存压力能，排出压力液以输出压力能。气体罐有两个功能，一个是气压腔(QYQ)的外延，充当高压气体腔(QTQ)，帮助气压腔存储高压气体，增加了气压腔的总容积，减小气压腔的压力波动；另一个是充当集液器，由于活塞总是有少量的泄漏，压力液会缓慢地从液压腔泄漏到气压腔，在活塞顶上会聚集越来越多的压力液，需要清理掉，当活塞移动到活塞缸顶时，活塞顶上的压力液会通过气液通道流入气体腔，活塞顶上的压力液被及时清理，而气体腔底部收集的压力液(收集液SJY)会越来越多，使浮筒(FT)浮起来，收集液增加时会使浮筒上升，当浮筒压到收集液传感器JYG时，发出打开电控阀信号，打开电控阀，漏掉收集液，压力液从漏液管(LYG)流回盛液筒(SYT)；收集液漏掉时会使浮筒下降，当浮筒压到到底传感器DDG时，发出关闭电控阀的电信号，电控阀关闭，随后电机停止。
  2. 一种基于集液器和夹心活塞的液封蓄能器及其液压系统，其另一个重要特征是：
    脂液夹心层式活塞密封和倒角密封；
    夹心式活塞是一个对偶活塞(包括活塞上偶(HSS)和活塞下偶(HSX))，活塞下偶(HSX)与滑套(HT)为一体，活塞上偶(HSS)与滑柱(HZ)为一体，滑柱中有一个行程孔(XCK)，行程孔通过液孔(YK)与夹心层连通，行程栓(XCS)从行程孔插下，与活塞下偶(HSX)的底部焊接成一体，密封盖(MFG)盖住行程孔形成密封，所以，在活塞上下偶之间的空间为密封空间，称为夹心层(JXC)，夹心式活塞的夹心层、行程栓、滑柱和滑套都处于密封范围内，滑柱与滑套形成滑动配合，行程栓栓头(ST)的行程，被行程孔(XCK)限制了最高点和最低点，所以夹心层的最大厚度被限制，以免滑柱与 滑套相脱离。
    在活塞上下偶之间形成一个距离可以变化的充满密封脂液(包括密封油脂或压力液)的夹心层；(原理上可以由n层对偶活塞构成n-1个夹心层)，因为气压和液压作用于活塞上的力远大于活塞与缸体的摩擦力，所以夹心层的压力与气压腔的压力近似相等，使得高压气体向夹心层的泄漏为微压差渗漏；夹心层的压力与液压腔的压力也近似相等，使得压力液向夹心层的泄漏也为微压差渗漏。夹心层的密封脂液是会泄漏的，所以需要有补充，用一个单向阀(DXF)向夹心层提供脂液补充，单向阀做在滑柱中间以节省空间，液压腔中的密封脂液可以从单向阀进入夹心层，夹心层的脂液不能从单向阀往回流至液压腔。
    脂液夹心层密封包括：脂密封和液密封，
    脂密封是用密封油脂充当夹心层，夹心层的密封油脂如果泄漏，在液压腔压力的作用下，由皮囊PN中储存的密封油脂通过软管(RG)和单向阀(DXF)向夹心层补充；
    液密封是用压力液充当夹心层，夹心层的压力液如果泄漏，液压腔中压力液通过单向阀向夹心层补充；不过根据实践经验看，不要单向阀，夹心层中也会充满压力液，所以该单向阀是可选项。
    倒角密封
    假定夹心层混合有气体和压力液，气体会聚集在夹心层的上部，首先会聚集在夹心层上面的倒角(DJB，即活塞上偶的下端面倒角)中，起到阻止压力液向气压腔渗透的作用；而压力液会聚集在夹心层的下部，首先会聚集在夹心层下面的倒角(DJC，即活塞下偶的上端面倒角)中，起到阻止气体向液压腔渗透的作用；
    同理，假定液压腔混入了气体，气体首先会聚集在活塞下偶的下端面倒角(DJD)中，再被挤到夹心层中；假定气压腔混入了压力液，压力液首先会聚集在活塞上偶的上端面倒角(DJA)中，再被挤到夹心层中；
  3. 根据权利要求1所述的基于集液器和夹心活塞的液封蓄能器及其液压系统，其进一步特征是稳定压力措施：通过调节高压气体温度来调节高压气体压力，实现压力准恒压。绕着气体罐内壁，缠绕数圈受控加热和降温装置，方法1：缠绕数圈带有热交换片的液管受控加热，称为热交换管(RJH)，在气体罐上接出一根管道，安装一个压力传感器(YLG)或者压力表监测压力，当活塞位置变化或者环境温度变化时，气体腔的压力会发生变化，需要采取措施稳定压力。使高压气体形成准恒压有两种办法，一种是令高压气体处于饱和汽状态，即选用临界温度高于温控的高压气体，只要将温度控制为准恒温，高压气体的压 力也就处于对应于温度的准恒压；另一种是选用临界温度低于温控的高压气体，高压气体处于气体状态或超流体状态，通过压力传感器检测压力变化，调节高压气体的温度以调节压力，以减小压力波动的变化率，形成准恒压，具体说：
    当压力低于下限值时，压力传感器(YLG)发出加热信号，由热液泵(RYB)向热交换管(RJH)泵动循环的热液以加热高压气体，高压气体温度升高后会使得压力升高，可以将液泵停止的信号阈值设置在压力上限与下限之间的某个点，为简单合理起见，本文约定将该阈值点设置在标称值，当压力高于标称值时，压力传感/比较器发出停止加热信号。
    当压力高于上限值时，压力传感器发出冷却信号，由冷液泵(LYB)向热交换管泵动循环的冷却液以冷却高压气体，高压气体温度降低后会使得压力降低，当压力低于标称值时，压力传感/比较器发出停止冷却信号。
    方法2，用缠绕式受控电热元件取代热交换管(RJH)对气体腔加热。
    加大高压气体腔的总容积也是稳定压力的措施之一。
  4. 根据权利要求1所述的基于集液器和夹心活塞的液封蓄能器及其液压系统，其进一步特征是：包括一种一体式结构，一密封的大直径圆筒形高压气体罐(QTG1)形成一个高压气体腔(QTQ1)，其里面套一个小直径圆筒形活塞缸(HSG)，气体罐和活塞缸大小圆筒相互密封；一个活塞(HS)将活塞缸分割成气压腔(QYQ)和液压腔(YYQ)两部分，活塞缸顶建立气液通道(TD1)，连通气体腔(QTQ1)和气压腔(QYQ)，充注高压气体，气压通过活塞传递到液压腔，所以液压腔中的压力液具有很高的压力，液压腔底部有一个注排口管道(ZPK)，由此注入压力液以储存压力能，排出压力液以输出压力能。气体罐有两个功能，一个是气压腔(QYQ)的外延，充当高压气体腔，帮助气压腔存储高压气体，增加了气压腔的总容积，减小气压腔的压力波动；另一个是充当集液器，由于活塞总是有少量的泄漏，压力液会缓慢地从液压腔泄漏到气压腔，在活塞顶上会聚集越来越多的压力液，需要清理掉，当活塞移动到活塞缸顶时，活塞顶上的压力液会通过气液通道(TD1)流入气体腔，活塞顶上的压力液被及时清理，而气体腔底部收集的压力液(收集液SJY)会越来越多，使浮筒(FT1)浮得越来越高，当浮筒压到收集液传感器JYG时，发出打开电控阀信号，打开电控阀，漏掉收集液，压力液从漏液管(LYG)流回盛液筒(SYT)；收集液漏掉时会使浮筒FT1，当浮筒压到到底传感器DDG时，发出关闭电控阀的电信号，电控阀关闭，随后电机停止。
  5. 根据权利要求1所述的基于集液器和夹心活塞的液封蓄能器及其液压系统，其进一步特征是：包括一种分体式结构，高压气体罐(QTG2)与活塞缸(HSG)相对独立，两者顶部由气液外部通道(TD2)连通，当活塞运动到顶部时，活塞顶上的压力液会通过通道管(TD2)流入气体腔，而气体腔底部收集的压力液(收集液SJY)会越来越多，使浮筒(FT2)浮起来。其它结构和工作原理与一体式的相同。
  6. 根据权利要求1所述的基于集液器和夹心活塞的液封蓄能器及其液压系统，其进一步特征是：
    用弹簧(TH)和位置传感器(WZG)监测活塞的位置，也就是监测液位的高度，位置传感器固定于顶部，下接弹簧TH，画出的是在活塞上部的拉簧结构(在活塞下部的压簧结构也是可以的，原理相同，所以没有画出)，当液位降低时活塞下移，弹簧对位置传感器作用力加大，位置传感器输出信号加强，当弹簧作用力到达阈值规定值时，位置传感/比较器就向注液泵发出“注液信号”，注液泵起动，向液压缸注液，一直到活塞压住上密封垫，这时，弹簧长度的采样信号会停止变化，控制系统据此可以判断出液压腔需要注入压力液或停止注入压力液。
  7. 根据权利要求2所述的基于集液器和夹心活塞的液封蓄能器及其液压系统，其进一步特征是：倒角密封
    假定夹心层混合有气体和压力液，气体会聚集在夹心层的上部，首先会聚集在夹心层上面的倒角(DJB，即活塞上偶的下端面倒角)中，起到阻止压力液向气压腔渗透的作用；而压力液会聚集在夹心层的下部，首先会聚集在夹心层下面的倒角(DJC，即活塞下偶的上端面倒角)中，起到阻止气体向液压腔渗透的作用；
    同理，假定液压腔混入了气体，气体首先会聚集在活塞下偶的下端面倒角(DJD)中，再被挤到夹心层中；假定气压腔混入了压力液，压力液首先会聚集在活塞上偶的上端面倒角(DJA)中，再被挤到夹心层中；
    所以，倒角密封加强了对气体向液压腔泄漏的拦截，也加强了对压力液向气压腔泄漏的拦截。
  8. 根据权利要求1所述的基于集液器和夹心活塞的液封蓄能器及其液压系统，其进一步特征是：电控顶针阀DKF漏液器。电控顶针阀关闭时，气体腔底部的收集液(SJY) 会越来越多，使浮筒FT浮得越来越高，当浮筒压到收集液传感器JYG时，发出打开顶针阀漏掉收集液电信号，电控顶针阀收到漏掉收集液信号后电机正转，其电机轴DK11带动螺母柱DK9旋转，因为螺杆DK8与多面体柱一体，而多面体柱DK7被卡在多面体孔DK6中不能旋转，只能随着螺母柱DK9的正传而上行，将顶针针尖DK5顶上去，打开顶针阀，压力液从漏液管流回盛液筒；收集液漏掉时会使浮筒FT下降，当浮筒压到到底传感器DDG时，发出关闭顶针阀的电信号，电控顶针阀收到关闭信号后电机反转，多面体柱DK7随着螺母柱DK9的反转而下行，顶针阀在压力的作用下关闭，随后电机停止。
  9. 根据权利要求1所述的基于集液器和夹心活塞的液封蓄能器及其液压系统，其进一步特征是：基于液封蓄能器的液压系统，
    蓄能阶段，当液位降低时，弹簧的弹力加大，位置传感器(WZG)输出信号加强，当信号大于设定的“补液阈值”时，位置传感/比较器向注液泵发出“注液信号”，注液泵起动，向液压缸注液。注液泵的驱动有两种方式，一种是发动机驱动，当传感/比较器向注液泵发出“注液信号”时，离合控制器(LHK)使电磁离合器(LHQ)啮合，主动轴(ZDZ)带动从动轴(CDZ)，从动轴带动注液泵(YB)，将盛液筒(SYT)中的压力液泵入液压腔(YYQ)；另一种是电动机驱动，将一台电动机与注液泵连接，当传感/比较器向注液泵发出“注液信号”时，电动机起动，带动注液泵，将盛液筒中的压力液泵入液压腔。当注液泵通过注排口向液压腔注液时，压力液推动活塞向上运动，逐渐将气压腔中的气体挤压回到气体罐，压力液逐步占驻气体腔的空间，活塞压到液压缸的上密封垫(SMF)时停止运动，压力液不再进入液压腔，但是在泵压的作用下液压腔的压力继续升高，到达预设的过压阈值值时，满液传感/比较器(MYG)发出停机指令，注液泵停机。
    作功阶段，当工作油缸(GZGk)需要压力液时，排液口在电控阀的控制下向工作油缸注入压力液，驱动相应的机械，高压气体通过活塞传递压力，压迫液压腔中的压力液，使压力液以等于高压气体压力值向工作油缸作功。
  10. 根据权利要求1所述的基于集液器和夹心活塞的液封蓄能器及其液压系统，其进一步特征是：漏液器也可以采用已知的其它机械阀和电子阀。
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