WO2012159455A1 - Récipient de stockage de pression de liquide basé sur un liquide de stockage de pression, et système hydraulique relatif à ce récipient - Google Patents

Récipient de stockage de pression de liquide basé sur un liquide de stockage de pression, et système hydraulique relatif à ce récipient Download PDF

Info

Publication number
WO2012159455A1
WO2012159455A1 PCT/CN2012/000701 CN2012000701W WO2012159455A1 WO 2012159455 A1 WO2012159455 A1 WO 2012159455A1 CN 2012000701 W CN2012000701 W CN 2012000701W WO 2012159455 A1 WO2012159455 A1 WO 2012159455A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
liquid
chamber
hydraulic
piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2012/000701
Other languages
English (en)
Chinese (zh)
Inventor
陈启星
罗启宇
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN 201110145401 external-priority patent/CN102840185A/zh
Priority claimed from CN 201110280485 external-priority patent/CN103016724A/zh
Application filed by Individual filed Critical Individual
Publication of WO2012159455A1 publication Critical patent/WO2012159455A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • 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
    • F15B1/10—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor with flexible separating means
    • F15B1/12—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor with flexible separating means attached at their periphery
    • 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
    • F15B2201/20—Accumulator cushioning means
    • F15B2201/205—Accumulator cushioning means using gas
    • 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
    • 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
    • F15B2201/315—Accumulator separating means having flexible separating means
    • F15B2201/3151—Accumulator separating means having flexible separating means the flexible separating means being diaphragms or membranes

Definitions

  • the present invention is a storage hydraulic storage warehouse (hereinafter referred to as a hydraulic pressure storage) and a hydraulic control system thereof, and belongs to the field of hydraulic transmission systems.
  • control devices such as brakes and steering gears are used.
  • vacuum assist the vacuum is vacuum.
  • the assist depends on the state of the engine. Only when the engine is working will the boost be generated. When the engine is turned off, the assist will disappear, the brake will be weak and the steering will be heavy, which may cause a car accident.
  • pneumatic assist The main disadvantage is that there is an air compressor, a gas storage cylinder, a brake valve, etc., so that the structure is complicated, cumbersome, and high in cost, and the working pressure of the pipeline is low, generally 0. 5 - 0. 7MPa, thus the brake gas
  • the diameter of the chamber must be designed to be larger and placed only outside the brakes, and the brake shoes are driven by the rods and cams or wedges, which increases the unsprung mass; the exhaust is very noisy.
  • OBJECT OF THE INVENTION The use of hydraulic assist is a good solution.
  • the advantages of hydraulic boost are: short lag time (0.1 to 0.3 s); high working pressure (up to 10-25 MPa), making the booster structure simple. Low quality; high mechanical efficiency (hydraulic system has self-lubricating effect).
  • the hydraulic power of the eye is facing a fatal problem. Because of the compressibility of the liquid, the hydraulic pressure cannot be stored. When the hydraulic drive is required, the liquid pump needs to be started. The reaction will not be timely and requires a large power. The pump can quickly generate enough hydraulic pressure.
  • the corresponding control system is designed to drive the actuators, brakes, throttles, clutches, shifting mechanisms, aircraft elevators and the like.
  • the separator consists of a piston HS and a diaphragm MP; the piston HS includes various sandwich pistons and conventional pistons.
  • the pressure fluid chamber YYQ is filled with the pressure fluid YLY, but the pressure fluid YLY is not marked in the figure, 'only described in the manual; the same is true for the reservoir chamber CYQ and the reservoir CYJ.
  • Oil storage agent CYJ includes saturated steam BHQ and super fluid CLT with coexisting liquid and gas.
  • Quasi-constant pressure means that the pressure (temperature) changes within a small range centered on the set value.
  • CYQ indicates a reservoir chamber and a is indicated as a.
  • the accumulator chamber is placed in an automatically temperature controlled environment to ensure the desired temperature of the accumulator.
  • the various position switches mentioned also include corresponding sensors.
  • the hydraulic warehouse is based on the oil storage agent, so before describing the working principle of the hydraulic storage, the description of the pressure storage agent CYJ is given.
  • the physical properties of the pressure accumulator are similar to those of the refrigerant. Unlike the refrigerant, the focus is on the pressure-dependent index of the pressure-relief. There are two states of use of the pressure-relieving agent. One is the saturated vapor storage agent, which is called saturated steam.
  • the number BHQ that is, the pressure storage agent is in the coexistence state of liquid and gas, focusing on the critical temperature and critical pressure of the pressure storage agent; one is the super fluid storage agent, referred to as super fluid, the symbol CLT, that is, the pressure storage agent is in the supercritical fluid
  • the state ' focuses on the relationship between the pressure of the pressure accumulator and the temperature and working medium density. If the temperature (pressure) is controlled to a small extent with a change from the set value, this case is referred to as a quasi-constant temperature (quasi-constant pressure). BHQ and CLT are not shown in the figure.
  • the temperature of the car body can easily exceed 50 in summer, if the critical temperature of the pressure storage agent is lower than 60. Will face the danger that the pressure reserve agent will exceed the critical temperature and increase the sudden change of pressure; therefore, the critical temperature of the pressure storage agent is selected to be higher than 60t, and the temperature of the hydraulic pressure tank is selected to be in the range of 60 ⁇ 110 ⁇ .
  • the value of the pressure fluid is between 10 and 25 MPa, so that it can meet the temperature requirements of the pressure storage agent, automobile and tractor, and meet the national standard of pressure value. Unfortunately, through the search, it was found that the pressure storage agent with a critical temperature between 60 and 1101C and a critical pressure between 10 and 25 MPa could not be found.
  • Table 1 Due to the low pressure of the saturated steam storage pressure, a high pressure hydraulic fluid is required, and a booster cylinder or a super fluid storage agent is required.
  • Saturated vapor pressure storage agent that is, a storage agent whose working temperature is lower than the critical temperature of the accumulator and keeps the liquid gas coexisting.
  • the saturated vapor pressure depends only on the saturation temperature.
  • the saturated vapor pressure and saturation temperature are one by one.
  • Corresponding Guan's system is constant pressure at constant temperature. As long as the saturation temperature is constant, the saturated vapor pressure will not change. As long as the saturation temperature rises, the saturated vapor pressure will rise correspondingly, and the density of the accumulator (or gas) Ratio to liquid) does not affect satiety and vapor pressure
  • the composition of the pressure reserve agent in this state, the pressure is saturated vapor pressure, this article is called the saturated vapor pressure storage agent, referred to as "saturated steam" BHQ.
  • the pressure of the accumulating agent chamber CYQ will be in a quasi-constant pressure state, and the pressure of the accumulating agent chamber will change when the size of the accumulating agent chamber changes, so the accumulating agent chamber can be Designed to be relatively small.
  • Super fluid storage agent supercritical fluid storage agent
  • supercritical fluid storage agent referred to as "super fluid” CLT
  • super fluid is the high pressure state of the reservoir CYJ.
  • Tc critical temperature
  • the pressure accumulator is in a saturated vapor storage state, that is, a low pressure state
  • the pressure accumulator is in the state of superfluid storage agent, that is, the high pressure state
  • the pressure of the super fluid depends on two factors: temperature and density, and as the temperature rises or the density increases, the same pressure accumulator is in a superfluid state.
  • the pressure can be much greater than the pressure at which it is in a saturated vapor state.
  • the pressure at C0 2 at the critical temperature ie, the maximum saturated vapor pressure
  • the pressure at the supercritical fluid C0 2 can exceed 7.38 MPa to 40 MPa or higher.
  • the disadvantage is that the fixed temperature does not fix the pressure, and the density changes. It also causes pressure changes.
  • To make the pressure change small it is necessary to make the change rate of the pressure storage agent density small, that is, the pressure change agent chamber needs to be small.
  • the method is to increase the total volume of the pressure storage agent chamber.
  • Working principle of hydraulic warehouse a hydraulic storage tank and hydraulic system based on pressure storage agent.
  • the principle is to use the pressure storage agent with high pressure and compressible characteristics to store hydraulically through the hydraulic chamber;
  • the hydraulic chamber has a tank chamber (or tank) formed by the closure of the tank.
  • the tank chamber is divided into two sub-cavities by a movable separator.
  • One is filled with pressurized liquid and is called a pressure liquid chamber.
  • the pressure chamber has a pressure chamber.
  • the liquid injection port and one liquid discharge port are connected to the outside;
  • the other sub-chamber is filled with a pressure storage agent and is called a pressure storage agent chamber; when the pressure of the pressure storage agent is controlled to a quasi-constant pressure, the pressure storage chamber is a quasi-constant pressure Through the pressure transmission of the separator, the pressure of the pressure liquid chamber is equal to the pressure of the pressure storage chamber;
  • the pressure of the infusion pump is always higher than the pressure of the accumulator.
  • the pressure fluid will push the isolator to compress the reservoir and expand the pressure.
  • the liquid chamber allows more pressure fluid to enter the pressure liquid chamber, because the pressure liquid pressure value in the pressure liquid chamber is equal to the pressure value of the pressure storage agent, so the high pressure value of the chamber is stored in the pressure liquid chamber of the hydraulic pressure chamber.
  • Pressure fluid When the pressure fluid fills the tank cavity, the separator is pressed to the pressure storage chamber position switch WZC, and the liquid pump stops pumping; when the pressure fluid works outward, the pressure of the pressure fluid is equal to the pressure of the pressure storage chamber. This is a high pressure quasi-constant pressure.
  • the liquid discharge port injects pressure fluid into other working cylinders under the control of the electric control valve to drive the corresponding machinery;
  • Embodiment 1 A saturated steam basic piston type hydraulic pressure tank (referred to as a type hydraulic cylinder, Fig. 1).
  • the end cap and the cylinder GT constitute a tank cavity, and the end cap can be manufactured on either side or both sides. Because it is a common structure, the end cap is not drawn in the figure; the piston HS isolates the tank cavity into a pressure fluid
  • the chamber YYQa and the reservoir chamber CYQa are two sub-cavities.
  • the reservoir chamber CYQa stores the saturated vapor BHQ coexisting with liquid and gas, and the end has a supplemental reservoir port BCK to supplement the reservoir; 'pressure chamber YYQa end There is a liquid injection port ZYK and a liquid discharge port PYK, which can inject or discharge H liquid liquid YLY; when the pressure of the liquid replacement liquid pump is greater than the saturated vapor pressure of the pressure storage agent, the pressure liquid YLY is injected into the pressure liquid chamber YYQa and pushes the piston HS direction
  • the pressure accumulating agent chamber moves in the direction of CYQa, compresses the gaseous storage agent CYJ1 into liquid storage agent CYJ2 (not indicated by CYJ1 and CYJ2), and stores pressure;
  • the reservoir chamber position switch WZC is a threshold position switch.
  • WZC When the piston reaches WZC, it means that it is full. WZC sends out the "full warehouse” signal, and the rehydration pump stops pumping. When working externally, the pressure accumulator pushes the piston to squeeze the pressure fluid, and the pressure fluid is equal to the pressure of saturated vapor pressure. The value works outward, the pressure fluid flows out, because WZC has a threshold Value, after the piston is pushed out for a short distance, WZC will send out the "replenishment position" signal, and the rehydration pump will recover the pump liquid; when the piston is in the freely movable position, YYQa and CYQa are in dynamic pressure balance state, and the pressure reserve agent in CYQa is to YYQa.
  • the leakage is zero differential pressure leakage, the leakage is small, negligible; when the fault occurs or does not work for a long time, the pressure fluid may be completely released, the piston top will reach the end of YYQa, then two will start Action, one is issued by WZY "absent pressure fluid" alarm signal, and locks the engine ignition system; one is to suppress a large amount of leakage of the pressure storage agent, because the pressure fluid is completely released, the pressure drops to the lowest point, the piston faces YYQa
  • the side pressure is equal to the atmospheric pressure.
  • the pressure on the CYQa side of the piston is equal to the saturated vapor pressure, which is much greater than the atmospheric pressure.
  • the pressure reserve agent in CYQa forms a large differential pressure leak, and the leakage amount is large.
  • the gasket includes a conical seal and a flat seal, designed as a conical seal (referred to as a cone seal)
  • a conical seal referred to as a cone seal
  • the sealing effect is better than that of the flat gasket.
  • the flat gasket is just a schematic view, all hydraulic chambers can use a cone seal
  • the cone seal includes The outer cone WZT and the inner cone NZT, the outer cone cone WZT is the outer casing conical sealing body WZT, the outer layer is a steel body, the inner layer is a rubber gasket, and the inner cone NZT is a piston end conical sealing body NZT
  • the inner layer is a steel body, and the outer layer is a rubber gasket.
  • Example 2 - Saturated Vapor Basic Film Type Hydraulic Cylinder (referred to as Class B Hydraulic Cylinder. Figure 2).
  • the upper cylinder cover QGs and the lower hemisphere cover QGx form a spherical cylinder shell QGK (QGK is not marked);
  • the edge ring of the diaphragm MP is pressed by the upper hemisphere cover flange and the lower hemisphere cover flange, so that the spherical cylinder shell is formed a spherical tank sealed and divided into two chambers by a diaphragm, one is a pressure liquid chamber YYQb, one is a reservoir chamber CYQb, and the diaphragm MP is a sealing membrane with good resistance to winding and elasticity;
  • the liquid pump YB is working to inject the pressure fluid from the injection port ZYK, the diaphragm will be squeezed toward the reservoir chamber CYQb, compressing the gaseous reservoir of the reservoir
  • Pump YB stops pumping; when external pressure fluid is needed The pressure accumulating agent pushes the diaphragm to squeeze the pressure fluid, and the pressure fluid works outward at a pressure equal to the saturated vapor pressure; because the WZC has a threshold value, the diaphragm is pushed out for a short distance and the W ⁇ C sends a "replenishment position" signal.
  • the rehydration fluid pump recovers the pump fluid and injects the pressure fluid into the hydraulic cylinder.
  • the first is the same as the previous reservoir pressure alarm QC J; the second is the use of multiple membrane hydraulic warehouses. Parallel, one of which breaks the alarm, and the other can maintain safe working conditions to the service station.
  • Examples 3.1 to 3.5 are various sandwich pistons.
  • Example 3.1_Pressure liquid layer sandwich piston (Fig. 3.1).
  • the piston has a sealing ring MFQ, and the piston upper layer HSS and the lower piston HSX form a sliding fit with the sliding sleeve hole HDT through the sliding shaft HDZ, and form a sandwich layer JXC filled with a pressure liquid which can be changed between the upper and lower pistons;
  • the pressure in the sandwich layer is equal to the pressure in the accumulator chamber, so the leakage of the reservoir is zero and the pressure difference is very weak and can be ignored.
  • the dotted line box indicates a single [ ⁇ valve DXF is in the middle of the upper HSS of the piston, when the hydraulic chamber YYQa
  • the one-way valve allows the pressure fluid in the hydraulic chamber to be injected into the sandwich layer.
  • the pressure liquid of the sandwich layer is not allowed to flow back to the hydraulic chamber.
  • the function of the anti-off bolt FTL is to control the layer height of the sandwich layer so as to prevent the sliding shaft from being separated from the sliding sleeve hole, and the sealing cover MFG ensures that the bolt hole and the sandwich layer are relatively opposite. Sealing the pressure storage chamber.
  • Example 3.2 - Rectangular Seal Ring Sandwich Piston (Fig. 3.2).
  • the current piston seal ring wears without self-compensation ability, and the squeeze seal ring piston has some self-compensation ability.
  • the connecting point LJD connects the tensioning spring LTH and the upper and lower pressure caps YG into one body, the spring LTH tensions the upper and lower pressure caps YG to squeeze the sealing ring MFH, and the sealing ring MFH will be extruded radially to become a sealing ring; After the seal ring wears a little, it will be squeezed out to replenish it; since the spring length is approximately constant, the pressing force on the seal ring is approximately constant, within a certain range of wear, The pressing force of the sealing ring on the inner wall of the cylinder is approximately constant, that is, the sealing of the sealing ring is approximately constant.
  • the outer casing WT can be integrated with the inner sleeve NT or can be independent; the through hole TK allows the pressure accumulating agent
  • a pressure cap positioner is used, which is positioned by the positioning nut DWM, the positioning screw DWG, and the positioning ring.
  • the disk DWP positioning plate and the screw pin KX are composed, the positioning nut DWM is fixed on the pressure cover attached thereto, and a counterbore is arranged in the middle of the DWP.
  • the top end of the positioning screw DWG is sleeved into the counterbore and is a dynamic fit.
  • the distance between the positioning nut DWM and the positioning plate DWP will be lengthened, and the pressure cap will be released from the sealing ring; when the piston is placed in the cylinder, the positioning screw will be screwed out to restore the pressure.
  • the sealing of the sealing ring by the cover; the depth of the counterbore of the DWP of the positioning plate is greater than the distance that the pressure cover can move, so that the positioning plate DWP and the positioning screw DWG can be rotated without falling, and then a bayonet KX is used for the card slot. To strengthen the role of making DWP not fall.
  • Example 3.3 V-type seal ring sandwich piston (Fig. 3.3).
  • the connection point UD connects the spring LTH and the upper and lower V-shaped pressure caps VYG into one body.
  • the spring LTH tightens the upper and lower V-shaped pressure caps VYG to press the V-ring seal ring, and the VH, V-ring seal ring VH will be squeezed in the radial direction.
  • V-shaped sealing ring VH can be extruded a distance more than the sealing ring MFH: ⁇ , so the supplementary performance is better;
  • the V-shaped jacket VT is independent of the inner sleeve NT and can be moved to squeeze the V-ring seal ring VH in the middle; the pressure cap positioner is the same as above.
  • Example 3.4 - Serrated inner inner ring sandwich piston (Fig. 3.4 and Fig. 3.5).
  • the connection point LJD connects the spring LTH, the jacket pressure cake WYB and the inner sleeve pressure cake NYB into one body; the spring LTH tensions the upper and lower pressure cakes, presses the zigzag inner sleeve CNT into the zigzag elastic jacket CWT, and the CWT radial direction Extrusion, pressing the inner wall of the cylinder to seal, its compensation performance is very good; this structure is the full length of the piston to seal, equivalent to the entire piston is a sealing ring, so that the sealing effect is better; a few laps in the CWT outer car Very thin annular oil-containing gap HYF for added lubrication; pressure cap positioner is the same as above.
  • Embodiment 4.1 (Fig. 4.1 ) - Pressure-enhanced hydraulic cylinder (referred to as a booster cylinder).
  • the pressure level is 10, 15, 20, 25 ⁇ 3 ⁇ 44, and the pressure of class a and b hydraulic tanks is so high.
  • the hydraulic cylinder and the booster cylinder work together to form a high-pressure hydraulic tank.
  • the hydraulic chamber YYQa (or the hydraulic chamber YYQb in the second embodiment) in the first embodiment is removed from the original liquid inlet and the liquid outlet, and a connecting tube LJG is used instead of the booster cylinder of the embodiment.
  • the low pressure chamber DYQ is connected, and the high pressure chamber GYQ of the booster cylinder is connected to the pipeline as the liquid injection port ZYK and the liquid discharge port PYK.
  • the booster cylinders are prior art and are directly cited in the following examples.
  • the pressure enhancement device can also be implemented using the principle of leverage.
  • the large-area piston rod of the low-pressure hydraulic cylinder pushes the lever, and the lever pushes the small-area piston of the high-pressure hydraulic cylinder, and combines the mast principle with the piston ratio to achieve supercharging.
  • Example 4.2 Saturated steam basic pressure booster cylinder type hydraulic tank (hereinafter referred to as booster cylinder type hydraulic tank, Fig. 4.2).
  • the hydraulic silo is directly formed into a supercharged cylinder structure, which is similar to the basic structure of the booster cylinder of Fig. 4.1, but the working principle is changed.
  • the low pressure cylinder is filled with the pressure accumulating agent to form a saturated vapor pressure, so the low pressure cylinder is renamed as the C type storage pressure.
  • the cylinder CYGc the low pressure chamber is renamed as the C type reservoir chamber CYQc, the connecting tube LJG is changed to the supplementary port BCK (for the supplementary pressure accumulator), the WZC and QCJ are added, and the other is the same as the booster tank of Fig. 4.1, including: HSd, MFQ, MFDx, KQ, MFDy, QK, HSG, HSg, GYQ. GYG, ZYK, PYK;
  • the pressure in the accumulator chamber CYQc is always equal to the saturated vapor pressure
  • the pressure in the high pressure chamber GYQc is equal to the Sd/Sg of the saturation and vapor pressure, and the pressure is increased to the high pressure chamber through the injection port ZYK after the rehydration pump YB is activated.
  • GYQ injects the pressure fluid and pushes the pistons HSg and HSd downward.
  • the piston HSd of the low pressure cylinder compresses the pressure storage chamber OYQc to compress and stores the pressure until the piston reaches the pressure storage chamber position switch WZC, and the WZC sends a stop injection signal.
  • the rehydration liquid pump YB is stopped;
  • the advantage of this hydraulic warehouse is high pressure and simplicity.
  • the shortage is that the pressure storage agent is easy to leak, because one side of HSd is saturated vapor pressure, and the other side is atmospheric pressure. There is a large pressure difference between the two, which makes the pressure storage agent form a large pressure difference. leakage.
  • Example 4.3 Single-charged cylinder hydraulic chamber with pressure balancer (referred to as C- type liquid Jfe warehouse, Figure 4.3)sky
  • the hydraulic warehouse is directly made into a saturated steam booster cylinder structure, and the saturated steam booster cylinder
  • the high pressure cylinder is the pressure liquid cylinder
  • the low pressure cylinder is the pressure storage cylinder CYGc
  • the bottom of the pressure storage cylinder has a supplementary port BCK for injecting saturated steam into the pressure storage chamber CYQc, 'because the pressure in the pressure storage chamber is always equal to the saturated vapor pressure
  • the pressure of the pressure liquid in the high pressure chamber GYQ is equal to the Sd/Sg times of the saturated vapor pressure, and becomes the high pressure pressure liquid.
  • the pressure liquid is injected into the high pressure chamber GYQ through the liquid injection port ZYK.
  • the piston HSd of the low pressure cylinder compresses the saturated steam in the pressure storage chamber CYQc, stores the pressure until the piston reaches the pressure storage chamber position switch WZC, and the WZC sends a stop injection signal to make the rehydration liquid Pump YB is stopped;
  • the high pressure chamber sends the high pressure liquid to the outside through the liquid discharge port PYK;
  • the same parts as the booster cylinder type hydraulic chamber of Embodiment 4.2 are: WZC, QCJ, BCK, CYGc. CYQc, MFQ, MFDx, KQ, MFDy, QK, HSG, HSg, GYQ, GYG, ZYK, PYK; Part of the low-pressure cylinder piston, the low-pressure cylinder piston was changed to a fixed-position sandwich piston HSdj (not shown), the purpose is to reduce the large differential pressure leakage to no differential pressure leakage; HSdj from the upper piston HSS, fixed column GDZ piston The lower layer HSX is fixed into one body, and a sandwich layer is formed between the upper and lower layers, which is filled with sealing grease, and becomes a grease sealing cavity YFQ.
  • the sealing grease is more resistant to leakage than the oil storage agent; similar to the booster cylinder, the high pressure cylinder GYG and CYGc constitute The brother cylinder, the high pressure cylinder piston HSg and the low pressure cylinder fixed distance piston HSdj form a brother piston, the HSdj sandwich layer grease is provided by the seal liquid balancer, and the seal liquid balancer includes the seal liquid balance cylinder and figure of Fig. 4.3.1.
  • a type of sealing liquid balance chamber MPQa and b type seal liquid balance chamber MPQb are collectively referred to as seal liquid balance chamber MPQ
  • the chamber CPQa and b type reservoir balance chamber CPQb are collectively referred to as the reservoir balance chamber CPQ
  • the piston HS and the diaphragm MP are collectively referred to as the separator
  • the pressure equalizer balance tube CPG is connected to the reservoir balance chamber CPQ and the hydraulic tank storage pressure
  • the cavity CYQc so the pressure of CPQ and CYQc is equal
  • the sealed grease balance tube MPG is sealed with the grease balance chamber MPQ and HSdj's sandwich layer oil seal chamber YFQ, so the pressure of MPQ and YFQ is equal
  • MPQ and CPQ pressure are equal, YFQ Equal to the pressure of CYQc, the pressure reducing agent is reduced from large differential pressure leakage to no
  • Embodiment 4.4 A self-compensating sealing liquid saturated steam booster cylinder type hydraulic tank (referred to as a class d hydraulic tank, Figure 4.4).
  • the same parts as the booster cylinder type hydraulic chamber of Embodiment 4.2 are: WZC, QCJ, BCK, MFQ, MFDx, KQ, MFDy, QK, HSG, HSg, GYQ, GYG, ZYK, PYK, CYGd and CYQd correspond to ' Figure 4.2 CYGc and CYQc; the improvement is that the low-pressure cavity piston adopts the self-compensating sealing liquid sandwich layer piston HSbc (not shown), the upper part of the piston HSS and the lower part of the piston HSX cooperate with the sliding sleeve HDK through the sliding column HDZ Therefore, the spacing between HSS and HSX can be changed.
  • the spacing is the thickness of the liquid sealing chamber YFQd.
  • the more leakage of the sealing liquid in the liquid sealing chamber YFQd the smaller the spacing between HSS and HSX, when the spacing is small.
  • the liquid guiding hole D YK and the bolt hole LSK enter into the liquid sealing chamber YFQd, so that the distance between the HSS and the HSX is increased again, and the ejector valve is closed again, so that the thickness of the liquid sealing chamber YFQd is always in the top opening ejector valve and closed.
  • the range of the ejector valve fluctuates, so that the liquid sealing chamber YFQd always has a sealing liquid, and the sealing chamber YFQd and the accumulator chamber CYQd are separated by only one layer of piston, so the pressures of the two chambers are equal, thereby reducing the large pressure difference leakage of the pressure storage agent. In the absence of differential pressure leakage, a large differential pressure leak is formed.
  • the sealing liquid in the sealing chamber YFQd has a leakage speed higher than zero differential pressure leakage, but since the sealing liquid is replenished at any time, even if the leakage is slightly faster, the sealing will not be destroyed; in case the thimble valve has a little leakage, the distance between the HSS and the HSX will be To prevent this from happening, the maximum distance between HSS and HSX is limited by the FTL-proof bolt.
  • the function of the sealing cover MFG is to isolate the bolt hole LSK from the pressure accumulating chamber; for example, the thimble valve leaks into the reservoir.
  • Pressure chamber, liquid leakage alarm LY J alarm, LYJ - is the detection liquid level, the liquid level exceeds the normal value to alarm, one is the pressure liquid sensor, it detects the pressure liquid and alarms.
  • the liquid sealing chamber YFQd and the pressure storage chamber CYQd are separated by only one layer of piston, so the pressure of the two chambers is equal, that is, the pressure of the liquid sealing chamber YFQd is equal to the low pressure (ie, saturated vapor pressure); the liquid sealing chamber YFQd and the high pressure chamber GYQ are replaced by the filling tube BYG Connected, so the pressure of the liquid seal chamber YFQd should be equal to the high pressure (ie saturated steam pressure *Sd/Sg); then the pressure of the liquid seal chamber YFQd is equal to high pressure or low pressure? This is to be analyzed according to the actual situation.
  • Case 1 When the ejector valve is opened, the pressure of the liquid sealing chamber YFQd is close to the high pressure, and the upper and lower layers of the piston are further opened. When the ejector valve is closed, the liquid sealing chamber YFQd and The pressure in the pressure storage chamber CYQd is equal; Case 2: If the thimble valve cannot be closed due to a fault, the high pressure pressure fluid will open the upper and lower layers of the piston to the limit, and the liquid seal chamber YFQd is equal to the pressure of the high pressure chamber;
  • the structure and principle of the thimble is wide (Fig. 4.4.1).
  • the valve sleeve FT is fixed on the upper layer HSS of the piston, the guide column DXZ (with the liquid seam YF on the upper side), the sealing cone MFZ and the thimble DZ as one body. Under the pressure of the compression spring YTH, the sealing cone MFZ presses the cone seal ZFD.
  • the valve is in the closed state; when the sealing liquid continuously leaks so that the upper and lower layers of the piston are getting closer and closer to the thimble DZ, the thimble DZ pushes the sealing cone away from the cone seal ZFD, so that the valve opens, and the sealing liquid flows through the refilling tube BYG, the liquid seam YF
  • the valve port ie, the gap formed by the sealing cone MFZ and the cone seal ZFD
  • YFQd the liquid sealing chamber YFQd.
  • Example 4.5 A low pressure pump with a pressurized cylinder type hydraulic chamber (referred to as a class j hydraulic chamber, Figure 4.5). And Example 4.4' The same parts of the d-type hydraulic chamber are: WZC, QCJ, BCK, MFQ, MFDx, MFDy, HSG, HSg, GYQ, GYG, ZYK.
  • the liquid pump YB injection has two pipes, one is to inject the pressure liquid into the high pressure chamber GYQ through the check valve ZHF and the liquid injection port ZYK; the other is the pressure tube JYG, the liquid pump YB is injected at the same time, the liquid discharge control
  • the PK sends an instruction to close the drain valve PF, and the pressurized liquid pumped by the liquid pump YB is injected into the pressurizing chamber JYQ through the pressurizing tube JYG, and the pressing piston (HSS+HSX) moves toward the bottom of the accumulator chamber CYQj, when the piston is pressed to the reservoir
  • the WZC sends a "stop" signal to the clutch control device NHK.
  • the mesher NHQ Under the control of the NHK, the mesher NHQ is disengaged, the pump YB loses power and stops pumping; the liquid pump stops while draining
  • the controller PK issues a command to open the drain valve PF.
  • Check valve ZHF prevents backflow of pressure in the high pressure chamber.
  • the low-pressure chamber piston is the same as the d-type hydraulic chamber.
  • the sandwich-type piston HSbc (not shown) with self-compensating sealing liquid, the upper HSS of the piston and the lower part of the piston HSX pass through the slide.
  • the moving column HDZ and the sliding sleeve hole HDK In cooperation, the sandwich layer between HSS and HSX is the liquid sealing chamber YFQj, and the upper portion of the piston has a one-way valve DXF.
  • This structure has the advantage that the liquid pump can reduce the pressure requirement; the disadvantage is that the liquid pump must be shut down when the hydraulic chamber is externally infused, which is not suitable for a system that continuously requires a large amount of pressure fluid.
  • Example 5.1 - Superfluid Piston Hydraulic Cylinder (referred to as e-type hydraulic chamber, Figure 5.1).
  • the pressure of the superfluid is an increasing function of both temperature and density. When the temperature is fixed, the smaller the density change of the superfluid is, the smaller the pressure change is.
  • the type A hydraulic silo the reciprocating motion of the piston makes the volume of the accumulator chamber The rate of change is too large, the maximum value of the rate of change - the minimum value / the maximum value, so that the rate of change of the super fluid density is too large, the rate of change of the pressure is too large, and if the pressure of the system is substantially constant, it is necessary to increase the pressure storage chamber.
  • the capacity is to reduce the rate of change of the superfluid density to reduce the rate of change of pressure.
  • the main chamber CYQe volume + auxiliary tank FZQe volume compared with the class a hydraulic chamber, the total volume of the e-type accumulator chamber is greatly increased, so the volume change rate of the accumulator chamber, the change rate of the reservoir density, and the rate of pressure change are all reduced, so that the pressure Close to constant pressure.
  • the piston uses a pressure 'liquid layer sandwich piston to effectively reduce the leakage of the reservoir.
  • Example 5.2 - Super Fluid Film Hydraulic Cylinder (referred to as Class F Hydraulic Cylinder, Figure 5.2).
  • the hydraulic chamber of the f-type hydraulic warehouse, the main pressure chamber and the hydraulic chamber and the pressure storage chamber of the b-type hydraulic chamber are the same.
  • the f-type hydraulic chamber is actually added with a main pressure tank CYGf based on the b-type hydraulic chamber.
  • auxiliary tank FZGf, total pressure storage chamber volume storage chamber CYQf volume + auxiliary tank chamber FZQf volume, the total volume of the pressure storage chamber is greatly increased, so the volumetric change rate of the pressure storage chamber, the change rate of the reservoir density, and the rate of pressure change All are reduced, so that the pressure is close to constant pressure.
  • Example 6 - a capsule hydraulic cylinder (referred to as a capsule pressure tank), the composition of which is shown in Fig. 6.
  • the tank GK of the pressure tank has a built-in pressure storage flexible air bag QN, and the air bag QN is filled with a pressure storage agent CYJ.
  • the liquid replacement liquid pump YB injects the liquid into the capsule pressure tank, the air bag is flattened, and the air bag is removed from the air bag.
  • the pressure is filled outside the pressure; when the pressure fluid is working outward, the pressure of the pressure fluid is provided by the saturated vapor pressure in the bladder, that is, the tank pressure tank stores a tank of pressure fluid at a pressure equal to The saturated vapor pressure of the pressure accumulator; the inner wall of the shell GK has a liquid absorbing layer XYC which is a sponge-like hard layer.
  • the pressure fluid can be guided to pressurize the airbag in all directions;
  • the baffle KDB prevents the air bag from clogging the inlet and outlet.
  • Example 7 Hydraulic tank injection and drainage system, the composition of which is shown in Figure 7.
  • valve in Figure 7 refers to the “electric control valve”, which includes the solenoid valve and the motor-controlled valve.
  • the pair of injection valve ZFy and the discharge valve PFy are reciprocal (y is a wildcard), that is, when the injection valve ZFy is opened, it is equal to saying that the discharge valve PFy is closed, and the discharge valve is not separately said. PFy is closed, and when the discharge valve PFy is opened, it is equal to saying that the injection valve ZFy is closed.
  • the action of the valve has two states: the switch state (completely open, close) and the analog state (gradual open and close).
  • the WZC issues a "replenishment" command to drive the rehydration fluid pump YB.
  • rehydration fluid pump YB There are two types of methods for driving the rehydration fluid pump YB, one is motor drive and the other is engine drive; The control of the motor drive is very simple. It can be controlled by one relay, but it is more favorable to drive with the engine.
  • the principle of the engine drive is: WZC sends the command to drive the liquid replacement pump YB to the mesher control device NHK, in the control of NHK
  • the lower mesher NHQ is engaged, and the power of the engine-powered drive shaft ZDZ is transmitted to the hydraulic cylinder YYC from the 'moving shaft CDZ, CDZ driven rehydration liquid pump YB; when the rehydration is completed (ie, in the YYC)
  • the pressure accumulator chamber position switch WZC sends a "full position" signal to the mesher control device NHK.
  • the mesher NHQ is disengaged, and the liquid pump YB loses power and stops pumping.
  • the check valve ZHF prevents Pressure liquid reflux;
  • a hydraulic cylinder YGk When a hydraulic cylinder YGk needs to remove the pressure fluid, its drain valve control device PKk controls its discharge valve PY k to open, the injection valve control device ZKk controls its injection valve ZFk to close, and the hydraulic cylinder YGk to the liquid cylinder YT Discharge;
  • two methods can be used: 1 install a negative liquid pump FYB on the inlet pipe of the liquid cylinder YT, f pump the pressure liquid to the liquid cylinder YT; 2 at the top of the liquid cylinder YT Install a suction pipe, install a negative air pump FQB pumping on the air suction pipe, so that the liquid cylinder YT maintains a negative pressure, so that the hydraulic cylinder YGk can remove the pressure liquid return liquid cylinder YT, and the negative air pump has a function, which can leak The pressure-relieving agent that comes out and returns to the liquid cartridge is discharged.
  • Figure 1 Figure 2, Figure 4.2, Figure 4.3, Figure 4.4 describe the hydraulic cylinder based on saturated steam, a, b, c, d storage.
  • the pressure chamber is filled with saturated steam, e, f type reservoir chamber Filled with superfluid, the pressure fluid chamber is filled with pressure fluid; bubbles and vapor, superfluid and pressure fluid are not marked in the figure.
  • FIG. 1 A perspective cross-sectional view of a saturated steam basic piston type hydraulic tank (referred to as a type).
  • outer layer is steel body, inner layer is rubber gasket
  • type a pressure liquid chamber YYQa pressure liquid chamber filled with pressure liquid YLY, pressure The liquid is not marked in the figure
  • the piston end tapered seal body NZT (the inner layer is steel body, the outer layer is rubber gasket); the sealing ring MFQ; the piston HS; the cylinder tube G ⁇ ; a type of pressure storage agent Cavity CYQa; reservoir chamber position switch WZC; lack of reservoir regulator sensor QC J; reservoir replenishment port BCK; pressure chamber position switch WZY.
  • Figure 2 Main section view of a saturated vapor-based diaphragm type hydraulic chamber (referred to as category b).
  • Figure 3.1 to Figure 3.5 show various sandwich pistons.
  • Figure 3.1 Sectional view of a sandwich of pressurized liquid layer sandwiches. Cylinder GT; check valve DXF; piston upper layer HSS; sliding shaft HDZ; piston lower layer HSX; sliding sleeve hole HDT; sealing ring MFQ; anti-separation plug FTL; sandwich layer JXC; Bolt hole LSK; sealing cover MFG;
  • FIG 3.2 Schematic diagram of a sandwich seal with a rectangular seal ring.
  • Pressure cap YG connection point UD; tension spring LTH; rectangular seal ring MFH (rectangular to the axial direction); whistle WT; inner ferrule NT; through hole TK; locating nut DWM, positioning screw DWG, DWP positioning plate, bayonet X.
  • FIG. 3.3 Schematic diagram of a V-type seal ring sandwich piston.
  • FIG 3.5 The outer cross-sectional view of the serrated inner jacket ring-type piston, the cylinder GT and the serrated elastic outer ring CWT are cut, and the zigzag inner ferrule is not cut.
  • FIG 4.1 Schematic diagram of the booster cylinder.
  • Connecting pipe LJG (connecting low pressure chamber DYQ with YYQa of Fig. 1 or YYQb of 2); low pressure chamber DYQ (filling low pressure from YYQa or YYQb); DYG ⁇ f cylinder; low pressure chamber piston HSd; sealing ring MFQ MFDx gasket x; cavity KQ; MFDy gasket y; air hole QK; HSG ⁇ piston rod; high pressure chamber piston HSg; high pressure chamber GYQ; high pressure cylinder GYG; liquid injection port ZYK; liquid discharge port PYK.
  • FIG 4.2 Schematic diagram of a pressurized cylinder hydraulic cylinder.
  • the hydraulic cylinder is directly made into a pressurized cylinder structure, which is similar to the basic structure of the pressurized 'cylinder in Figure 4.1, but the working principle is changed.
  • the low pressure cylinder is renamed as the C type storage cylinder CYGc (because the cavity is changed to 'reservoir)
  • the low pressure chamber is renamed as the C type storage agent chamber CYQc; the connecting tube UG is changed to the supplementary port BCK (for the supplemental pressure accumulator); the WZC and QCJ are added; the other is the same as the booster tank of Fig. 4.1, including: HSd, MFQ. - MFDx, KQ, MFDy, QK. HSG, HSg, GYQ, GYG, ZYK, PYK:.
  • FIG 4.3 Schematic of a pressurized cylinder hydraulic cylinder with a pressure balancer. Similar to the basic structure of the booster cylinder hydraulic tank in Figure 4.2, the same parts are: WZC, QCJ, BCK, CYGd (same as CYGc), CYQd (same as CYQc), MFQ, MFDx, KQ, MFDy, QK, HSG , HSg, GYQ, GYG, ZYK.
  • the changed part is the piston, the piston is changed into a sandwich piston, from the upper part of the piston (ie upper layer) HSS, liquid sealing chamber (ie sandwich layer) YFQa, fixed column GDZ, sealed
  • the ring MFQ and the lower part of the piston (ie, the lower layer) are composed of HSX, wherein the sealing liquid of the liquid sealing chamber is provided by the sealing liquid balance chamber MPQa in Fig. 4.3.1 or the sealing liquid balance chamber MPQb in Fig. 4.3.2. - Figure 4.3.1 - Sealing Fluid Balance Cylinder.
  • FIG.3.2 Sealing Fluid Balance Spherical Tank.
  • FIG. 4.4 Schematic diagram of a saturated turbocharged cylinder hydraulic tank with self-compensating sealing fluid.
  • the same parts as the cylinder-type hydraulic chamber of Figure 4.2 are: WZC, QCJ, BCK, CYGd (same as CYGc), CYQd (same as 'CYQc), MFQ, MFDx, KQ, MFDy, QK, HSG (HSGl is HSG In a partial cross-sectional view), HSg (HSgl is a partial cross-sectional view in HSg), GYQ, GYG, ZYK, ⁇ ; the improvement is a sandwich layer piston with self-compensating sealing fluid, the sandwich layer is the liquid sealing chamber YFQd, Filled with pressure-balanced sealant, the sandwich piston includes: check valve DXF (only allows pressure fluid to flow from the high pressure chamber to the liquid seal chamber YFQd), rehydration tube BYG, upper piston part HSS, slide column HDZ,
  • FIG.4.1 Schematic diagram of the structure of the ejector valve.
  • Figure 4.5 Schematic diagram of a low pressure pump with a booster cylinder hydraulic cylinder.
  • the same parts as in Figure 4.4 are: 'WZC, QCJ, BCK, MFQ MFDx, MFDy, HSG, HSg. GYQ, GYG, ZYK, PYK, LYJ, FTL, LSK, MFG.
  • Engager clutch control device ⁇ mesher NHQ, engine drive shaft ZDZ, driven shaft qDZ, rehydration fluid pump YB, check valve ZHF, pressurizing tube JYG, drain controller PK, Drain valve PF, pressurized chamber JYQ, pressure storage chamber CYQj, piston upper part HSS, piston lower part HSX, sliding column HDZ, sliding sleeve hole HDK, liquid sealing chamber YFQj, check valve DXF.
  • the hydraulic silo described in Figure 5.1 and Figure 5.2 is a pressure accumulator based on the working principle of supercritical fluid.
  • FIG. 5.1 Piston hydraulic chamber with supercritical fluid acting as a pressure accumulator.
  • Figure 5.2 – A film-type hydraulic chamber in which supercritical fluid acts as a pressure accumulator.
  • the same reference numerals as in Fig. 2 are: ZYK, PYK, WZY, YYQb, QGs, MP, FLP, LG, QGx, BCK. QCJ, WZC; different from the label of Fig. 2' are: f type main reservoir CYQf; Class F reservoir auxiliary chamber FZQf; Class f main tank CYGf; Class F auxiliary tank FZGf;
  • FIG. 6 Schematic diagram of a capsule hydraulic chamber. Cylinder shell GK; liquid absorbing layer XYC; airbag QN; porous baffle KDB; Fig. 7 - schematic diagram of hydraulic tank system.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)

Abstract

L'invention porte sur un récipient de stockage de pression de liquide basé sur un liquide de stockage de pression, et sur un système hydraulique qui utilise la haute pression et la compressibilité du liquide de stockage de pression pour stocker une pression de liquide au moyen du récipient de pression de liquide. Le récipient de pression de liquide comprend une chambre de réservoir formée par une enceinte de réservoir en forme de coque. La chambre de réservoir est divisée en deux sous-chambres par une séparation mobile (HS). Une sous-chambre est remplie d'un liquide sous pression et est donc appelée la chambre de liquide sous pression (YYQa). La chambre de liquide sous pression est dotée d'une entrée de liquide (ZYK) et d'une sortie de liquide (PYK) reliée à l'extérieur; l'autre sous-chambre est remplie de liquide de stockage de pression et est donc appelée la chambre de liquide de stockage de pression. La pression du liquide de stockage de pression est réglée pour être à une pression standard constante et la chambre de stockage de pression est donc à la pression standard constante. Sous l'effet d'une transmission de pression à travers la séparation (HS), la pression de la chambre de liquide sous pression est égale à la pression de la chambre de stockage de pression. Le récipient de stockage de pression de liquide et le système hydraulique peuvent s'appliquer à un système d'assistance à énergie hydraulique. Etant donné que la pression est stockée dans un liquide, il suffit d'une pompe de faible puissance pour maintenir une pression de liquide suffisante dans le récipient de pression de liquide et l'entraînement par pression de liquide peut réagir en temps voulu.
PCT/CN2012/000701 2011-05-20 2012-05-21 Récipient de stockage de pression de liquide basé sur un liquide de stockage de pression, et système hydraulique relatif à ce récipient Ceased WO2012159455A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CN 201110145401 CN102840185A (zh) 2011-05-20 2011-05-20 一种基于储压剂储存液体压力的液压罐及储压液压系统
CN201110145401.2 2011-05-20
CN 201110280485 CN103016724A (zh) 2011-09-21 2011-09-21 一种基于储压剂的液压存储仓及其液压系统
CN201110280485.0 2011-09-21

Publications (1)

Publication Number Publication Date
WO2012159455A1 true WO2012159455A1 (fr) 2012-11-29

Family

ID=47216603

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2012/000701 Ceased WO2012159455A1 (fr) 2011-05-20 2012-05-21 Récipient de stockage de pression de liquide basé sur un liquide de stockage de pression, et système hydraulique relatif à ce récipient

Country Status (1)

Country Link
WO (1) WO2012159455A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109110723A (zh) * 2018-08-21 2019-01-01 深圳安吉尔饮水产业集团有限公司 真空活塞式储水装置
US10273980B2 (en) 2013-09-27 2019-04-30 Qixing Chen Liquid seal energy-accumulator and hydraulic system thereof based on liquid-collector and sandwich piston

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3856048A (en) * 1970-01-29 1974-12-24 J Gratzmuller Hydropneumatic accumulator
CN1139063A (zh) * 1995-06-21 1997-01-01 大众汽车有限公司 转向助力器及离合器的液压控制装置及其工作方式
CN1529665A (zh) * 2000-11-28 2004-09-15 Л 液压能量存储系统
WO2010087934A1 (fr) * 2009-01-30 2010-08-05 Robert Bosch Gmbh Système de stockage d'énergie hydraulique avec accumulateur et procédé de variation de la charge de celui-ci
CN101868387A (zh) * 2007-11-21 2010-10-20 大陆-特韦斯贸易合伙股份公司及两合公司 用于机动车辆的制动系统

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3856048A (en) * 1970-01-29 1974-12-24 J Gratzmuller Hydropneumatic accumulator
CN1139063A (zh) * 1995-06-21 1997-01-01 大众汽车有限公司 转向助力器及离合器的液压控制装置及其工作方式
CN1529665A (zh) * 2000-11-28 2004-09-15 Л 液压能量存储系统
CN101868387A (zh) * 2007-11-21 2010-10-20 大陆-特韦斯贸易合伙股份公司及两合公司 用于机动车辆的制动系统
WO2010087934A1 (fr) * 2009-01-30 2010-08-05 Robert Bosch Gmbh Système de stockage d'énergie hydraulique avec accumulateur et procédé de variation de la charge de celui-ci

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
LEI, TIANJIAO ET AL., HYDRAULIC ENGINEERING HANDBOOK, April 1990 (1990-04-01), pages 1402 - 1418 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10273980B2 (en) 2013-09-27 2019-04-30 Qixing Chen Liquid seal energy-accumulator and hydraulic system thereof based on liquid-collector and sandwich piston
CN109110723A (zh) * 2018-08-21 2019-01-01 深圳安吉尔饮水产业集团有限公司 真空活塞式储水装置
CN109110723B (zh) * 2018-08-21 2023-11-14 深圳安吉尔饮水产业集团有限公司 真空活塞式储水装置

Similar Documents

Publication Publication Date Title
US10273980B2 (en) Liquid seal energy-accumulator and hydraulic system thereof based on liquid-collector and sandwich piston
CN102182904B (zh) 粘稠油脂二级润滑泵装置
CN201086705Y (zh) 总泵结构
CN102720795A (zh) 一种用于两栖车的油气弹簧及其液压调节装置
CN103016724A (zh) 一种基于储压剂的液压存储仓及其液压系统
US9541099B2 (en) Self replenishing accumulator
WO2021031484A1 (fr) Accumulateur à pression constante du type à vessie de grande capacité et son application
CN204152765U (zh) 微型lng管道增压泵
CN116335913A (zh) 低增压液压活塞式氢气压缩机
WO2012159455A1 (fr) Récipient de stockage de pression de liquide basé sur un liquide de stockage de pression, et système hydraulique relatif à ce récipient
JP2013539525A (ja) 復元圧力装置
CN116335911A (zh) 一种双级高压低温液体柱塞泵
CN105697434B (zh) 一种高效蓄能增压器
CN103233928A (zh) 蓄能增压器
CN207485771U (zh) 液压元件强度测试台
CN205243977U (zh) 弹簧活塞式蓄能器
CN203508981U (zh) 增压型蓄能器
CN115163467B (zh) 一种能够及时补油的往复泵
CN205677891U (zh) 一种高效蓄能增压器
CN215830652U (zh) 单缸无间歇手动泵
CN211009680U (zh) 液压拉力油气弹簧油缸
CN117662535A (zh) 一种复合传感自保压式自增压油箱
CN110878800A (zh) 一种刹车作动筒
CN106762951A (zh) 一种压缩空气回程单作用液压缸
DE102021004010A1 (de) Kolbenpumpe

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12789656

Country of ref document: EP

Kind code of ref document: A1

DPE2 Request for preliminary examination filed before expiration of 19th month from priority date (pct application filed from 20040101)
NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 12789656

Country of ref document: EP

Kind code of ref document: A1