CN104696214A - Matched sealing design for volumetric vane pumps at inlet and outlet in two sides and pump interior - Google Patents

Matched sealing design for volumetric vane pumps at inlet and outlet in two sides and pump interior Download PDF

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Publication number
CN104696214A
CN104696214A CN201510078085.XA CN201510078085A CN104696214A CN 104696214 A CN104696214 A CN 104696214A CN 201510078085 A CN201510078085 A CN 201510078085A CN 104696214 A CN104696214 A CN 104696214A
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CN
China
Prior art keywords
pump
blade
rotor
intrados
leaf
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CN201510078085.XA
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Chinese (zh)
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不公告发明人
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HE JIAMI
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HE JIAMI
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Priority to CN201510078085.XA priority Critical patent/CN104696214A/en
Publication of CN104696214A publication Critical patent/CN104696214A/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
    • F01C1/344—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F01C1/3446—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/02—Radially-movable sealings for working fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/08—Axially-movable sealings for working fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3446—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/20—Rotors

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

The invention discloses a matched sealing design for volumetric vane pumps at inlet and outlet in two sides and pump interior. Sealed arc sections formed between an inner shell or an inner ring of the pump and two adjacent vanes of the rotor at the smallest or highest volume are communicated with high/low-pressure fluid on two sides in a vane separating pump; the other inner arc sections are connected with the inlet/outlet or a transition arc section; the inlet and outlet are formed in two ends of the arc section on the side with the smallest volume; grooves or windows are formed in two ends of the arc section on the side with the largest volume and are connected with the inlet and outlet in the side with the smallest volume; concave and convex circles on the tops of pump vanes are correspondingly matched with concave and convex circles of rotating bodies at the vane ends, so that the pump vanes and the rotating bodies at the vane ends are stably connected with one another and can realize axial rotation and sealed sliding fit at the largest rotating angle; and the matched sealing piece of the vanes or slide blocks and the rotor is pushed to be in sealed sliding fit with the pump interior end surface through small proper force by virtue of springs for the vanes and the rotor. According to the pump in the invention, the efficiency can be improved by utilizing dynamic energy and fluid force, the sealing property between the pump interior arc surface and the end surface is high, the needed sealing pressure is small, and the wear and energy loss can be reduced.

Description

Fitted seal design in the volume leaf pump that a kind of both sides are imported and exported and pump
Technical field
The present invention relates to volume leaf pump or motor, mainly the slipper seal design of the import and export of convection cell and blade, rotor operation.
Background technique
At present, volume leaf pump or motor have single shaft running, fluctuate little and stable feature, be used widely, but utilizing of existing leaf pump or motor convection current muscle power is unreasonable, flow is less, blade and rotor bad relative to the sealability of the pump housing, general adopt larger power to strengthen axially and radial sealing, loss in efficiency and blade wear can be made to accelerate and be subject to certain restrictions.
Summary of the invention
The structure that the present invention wants the object of technical solution problem to be to provide a kind of fluid to be passed in and out by leaf pump intrados both sides, improves hydrokinetic utilization, and blade, rotor and the pump housing just can be made to form good sealing effect with less power.
The structure that the present invention wants technical solution problem to be to provide a kind of fluid to be passed in and out by leaf pump intrados both sides, need the pump housing to add when leaf pump or motor are liquid fluid variable displacement pumps and fill liquid drainage device, add end of blade in the longitudinal end of blade to turn to be formed with pump intrados and coordinate slipper seal, add spring with the end cap fit inside slipper seal of less axial force and axial restraint at blade, rotor.
Usefulness of the present invention is that the power of energy Appropriate application pump or motor is raised the efficiency, and increases it in the application compared with low pressure and mass flow, can reach good sealing effect in pump with less radial and axial power.
Accompanying drawing explanation
Fig. 1 is that enforcement illustration is imported and exported in the pump intrados both sides of single-acting four leaf pump or motor.
Fig. 2 is the single-acting four leaf pump of pump intrados both sides import and export or the end cap of motor and adds pressure relief device enforcement illustration.
Fig. 3 is double-acting pump or the motor cross sectional view of 9,10 leaf pump intrados both sides import and export.
Fig. 4 is that the blade of pump or motor coordinates slipper seal to implement illustration.
Fig. 5 is that the rotor end-face of pump or motor coordinates slipper seal to implement illustration.
Specific embodiment
Embodiment 1: as in Fig. 1,2, R 1it is inner ring (1) arc length of stator or inner ring peak rate of flow side, metering pump in this way, during the maximum volume that the position of interior arc length is just being formed itself and rotor two blade, the angle of arc length equals or forms slightly larger than two blades at this moment and arc the angle that two seal contacting point; Variable displacement pump in this way, the angle of arc length equal or is formed slightly larger than arc itself and rotor two blade when being adjusted to pump peak rate of flow maximum volume time two blades and arc form the angle that two seal contacting point, when the position of interior arc length is also the maximum volume just formed own and rotor two blade.R 2the interior arc length of stator or inner ring (2) minimum discharge side, metering pump in this way, during the minimum volume that the position of interior arc length is just being formed itself and rotor two blade, the angle of arc length equals or forms slightly larger than two blades at this moment and arc the angle that two seal contacting point; Variable displacement pump in this way, the angle of arc length equals or forms slightly larger than two blades when being adjusted to minimum volume that pump minimum discharge (being namely the adjustable minimum range at rotor axis and shell or inner ring center) arc itself and rotor two blade formed and arc the angle that two seal contacting point, when the position of interior arc length is also the minimum volume just formed own and rotor two blade; Metering pump in this way, because when volume leaf pump rotates, the volume of every two leaves and inner casing or interior interannular is all ceaselessly change, R 1, R 2arc length can not be greater than or less than and seal the too much of contacting point with corresponding two leaves, avoid the volume between two leaves and inner casing or inner ring arc larger positive/negative-pressure occurs or does not have sealing intensity, when rotor rotates, two leaves are at R 1, R 2arc internal conversion time be the separation of fluid high low pressure, ensure there is the R being equivalent to a blade and pump intrados at any time 1, R 2sealing intensity; Variable displacement pump in this way, when volume leaf pump rotates, R 1, R 2arc length angle major part time be greater than two corresponding leaf angles, larger positive/negative-pressure occurs the volume between two leaves and inner casing or inner ring arc changes, and at R 2the volume-variation ratio that end is formed compares R 3the volume-variation ratio that end is formed is more greatly, and the positive/negative-pressure change according to fluid determines whether out relief hole to the impact of pump or motor, is at R 1, R 2that one end open relief hole, time as larger in impact, relief hole (3) can be opened, connect accumulator or pressure relief device.
As pump or motor be single direction rotation time, pressure relief device is by (3), (03) as in Fig. 2-2, and the import and export on the left side are high voltage terminal, do not need through (01), as pump leaf and R 2when formation high pressure is greater than the inlet and outlet pressure on the left side, fluid is flowed directly to (03) by relief hole, then the one-way valve pushing (03) open flows to left side high pressure import and export; As pump leaf and R 2when formation low pressure is less than the inlet and outlet pressure on the right, fluid is imported and exported by low pressure and is flowed directly to (03), then the one-way valve pushing (03) open flows to relief hole.As pump or motor be bidirectional rotation time, pressure relief device is made up of (01), (03), (02), (3), if the import and export on the right are high voltage terminal, through commutator (01), as pump leaf and R 2when formation high pressure is greater than the inlet and outlet pressure on the left side, (03) runner breakdown (02) runner is closed in the pressure effect that commutator (01) imports and exports fluid by the right, fluid is flow to (01) by relief hole simultaneously, then the one-way valve pushing (02) open flows to the right high pressure import and export; As pump leaf and R 2when formation low pressure is less than the inlet and outlet pressure on the left side, fluid is imported and exported by low pressure and is flowed directly to (02), then the one-way valve pushing (02) open flows to commutator and relief hole (3); R 1the pressure release connecting means of end and R 2the same, but R 1the volume variable displacement ratio of end is little more, can determine whether to connect pressure relief device according to use.
R 3be the stator of small flow compressed side or the angle of inner ring import and export and inner arc, when ensureing the intensity of shell or inner ring, preferably get and being less than 90 .angle, is conducive to fluid flowing; R 6the angle of inner ring or inner casing cross central line and import and export, value 0 < R 6namely < 90 degree is that import and export is at R 2two ends, import and export the R of center at pump inner arc center near inner casing or inner ring place 2side, be conducive to fluid to pass in and out from the pump housing, as the flow arrow in Fig. 1-1, fluid enters from right side, flow out from left side, when being as the pump used time, two, right side cavity volume is while volume increases absorption fluids, upper, right, under blade also stir fluid, fluid is flowed from bottom to top more to the left with power; At this moment two cavity volumes in left side reduce while displacement fluids at volume, upper, left, under blade also stir fluid, make fluid with power by upper output flow to left down; When being as the motor used time, two, right side cavity volume is while volume increases absorption fluids, fluid also jet promote right, on blade, the power making rotor obtain upper and lower blade difference adds right and winding-up Driving force that is upper blade, and fluid is along rotor sense of rotation when entrance, pump housing output flow, makes efficiency be increased.
(8) of Fig. 1, (9) be interior runner or the window (number is not limit) with carrying out fluid communication of pump, as pump or motor flow hour, can as Fig. 1-2, runner is formed at the intrados fluting of shell or inner ring, flow as pump or motor is larger, can directly at shell or inner ring windowing, fluid in pump in each blade in each side is exchanged by window with turnover mouth region (4), the cross section of fluid channel that groove or window are formed amasss compared with the fluid line sectional area with pump casing or set casing, fluid is preferably made to be less than pump casing or the ducted speed of set casing at groove or window to the flowing velocity of volume between any blade, reduce cavitation or reduce at pump intrados, blade generation cavitation, (8), (9) centre, both sides are inner ring or housing, because blade does not seal needs through here time, for reducing uneven or unnecessary wearing and tearing, can reduce (8), (9) at the opening of axis, increase blade area of contact here, also can be split into oblique, make even wearing, R in Figure 2-1 7it is the arc length of transition cambered surface in inner ring or shell, it is the mode that the sliding distance and reducing of a kind of rotor adoptable increase blade and intrados when using blade more weares and teares, namely be, as in Fig. 3-1, (8), (9) are being divided into two-section, arc length should not be greater than two blade movements symmetrical time two blades between seal arc length, fluid is preferably from R 1the import and export at two ends flow to R 2the import and export at two ends become total import and export.
(10,11) in Fig. 1 are the set casing of variable displacement pump and the interface of the interior movable pump housing, (10) be the telescopic interface of pipeline, (11) be the interface of sliding contact, be the interface making the set casing of variable displacement pump and the interior movable pump housing carry out fluid communication, also can connect by such as other modes such as flexible pipe.
(5), (1), (2) in Fig. 1,2, (07), (08), (09) are the import and export of the interior movable pump housing, pump casing or inner ring, can be one or Split assembled.
(04) be end face regulator hole, (05) be pressure regulation groove bottom rotor blade, (06) be end cap or end face supercharging sheet, because blade rotation does not have sealing-fluid pressure when (8,9), only has the pressure of rotor convection cell power, the radial motion of blade is easier to, and if blade does radial motion with fluid in the mode of bottom compression, (04) connects high-pressure liquid opening at symmetrical R 1, R 2position, make blade movement to R 1, R 2in time, is subject to promoting sealing from (04) high-pressure liquid, rotates and only slides by centrifugal force low pressure when (8,9); If pump blade does radial motion with spring or centrifugal force in the mode of bottom compression, (04) is connected with the position of negative pressure fluid opening in symmetrical (8), (9), makes blade movement to R 1, R 2time be subject to spring or centrifugal force pulls sealing, rotate and slide by low pressure in (8,9) time, do not have the motor of negative pressure then not act on; No matter take which kind of mode to make it do radial motion at blade bottom, the hydrodynamic pressure flowing into (04) makes blade movement to R 1, R 2time be subject to necessary promotion slipper seal, rotate blade and pump intrados when (8,9) only not bounce back again by low pressure sliding force, also sulculus (010) can be opened in the interior side in (04) hole, avoid blade radial to suddenly change to impact, (04,05,06) can determine whether assembling according to different pumps or motor, be generally use when large discharge, make (8,9) in axis or turn to comparatively big uncork, reduce pump external and internal pressure difference and do not make again blade impaired.
Fig. 3 is double-acting pump or motor, R 4r 2the import and export at two ends inner ring or the housing angle near intrados best>=0 degree be namely make the opening of this part toward the direction outside pump to R 2centerline dip, R 1, R 2, R 3, R 7the same with above-mentioned single-acting pump, R 1, R 2shell or the inner ring arc length of large and small flow end, R 3that its angle of wedge angle of small flow extreme direction shell or inner ring is preferably less than 90 degree and forms wedge angles, R 7be blade more time adoptable transition arc length, (001), (002) are blade more employing R 7distance R during transition arcs 2the opening that two ends are far away, each is imported and exported and makes segmentation subtend with the cross centre line in such as Fig. 3-2 and concentrate, and if the upper right in figure and lower-left are with concentrating in together, importing and exporting in inner ring or the housing angle near intrados is also to R 2centerline dip, upper left and bottom right are with concentrating in together, and the runner that can be formed from inner ring or inner casing and shell as figure left side (001) leads to R 2the import and export at two ends, also can as right side (002), R 7opening above and the opening of lower-left are at pump Ligation in vitro.
Embodiment 2: in the diagram, (413,414,415,416,417,422) are that end of blade is turned, itself and pump blade are rotatably assorted apart from rotor axis far-end for making circle, just sealing purpose is reached with less outward radial force when blade radial is moved, end of blade is turned and to be coordinated with pump intrados approaching face, strengthen wear resistance, sealing, R 5it is the arc angle of the indent circle that blade or end of blade are turned, when its angle is greater than 180 degree of certain angles, blade and end of blade just can be made to turn can only mutually axial rotation and movement, is namely to turn and can not radial direction throw off mutually (for preventing from certain reason end of blade from turning coming off making interior pump invalid and damage) without straight pin (402) blade and end of blade, as R 5≤ 180 degree, that turns for preventing blade and end of blade comes off, can add (402), in the axial of blade as two hinge mated condition, (419) segmentation processing at corresponding (403) place and (420) corresponding (405) place is on end of blade, in axially as corresponding in (413) (405) place that end of blade is turned and (416) corresponding (403) place segmentation processing, namely be blade recessed (420), convex (419) circle and end of blade turn convex (as 413), recessed (as 416) circle correspondence together with round pin (402) pass be connected, segmentation position and quantity are not limit, B is the maximum rotation angle that end of blade is turned, and turning for avoiding blade and end of blade interferes with each other in corner B scope, can as being processed at the bottom of the left side dome of (421) blade, re-entrant angle strengthens cylindrical angle, right side end of blade round end radius is greater than the thick or R of leaf 5reduce angle in part or match as the both sides re-entrant angle etc. of (413), requirement end of blade is turned can rotate in angle B and have to make again blade and end of blade turn with the sealing of blade nose circle to stablize to be connected, (413), (416) being is that the end of blade of full fitting surface is turned with pump intrados, more adapting to cross section in pump is circular camber line, (422), (417) be that load type can be turned by both sides (407) rotating end of blade, in rotor eccentricity difference or pump, the larger ellipse of cross-sectional curve semidiameter also can ensure that end of blade is turned and to coordinate with the slipper seal of pump inner arc, end of blade (407) of turning on two ends are the rotors sealed that is slidably matched with pump intrados, rotor (407) and the fitting surface of pump intrados can be overall cambered surfaces suitable with pump intrados fitting surface radius (417 is left), also can be that middle concave two ends cambered surface (407) coordinate with the slipper seal of pump inner arc, the Placement that the connection that itself and end of blade turn two ends can be turned as blade and end of blade, can axial rotation or swing sealing and be stabilized in the two ends that end of blade turns, adapt to the change in radius of pump inner arc, (414) ellipse that, in (415) adaptation pump, cross-sectional curve semidiameter is less and circle, the end of blade outer arc two ends of turning can slightly seal impact because the change in radius of pump inner arc first has certain skewed wear (more galling tilt angle is wider for the semidiameter of the longer and pump inner arc of the fitting surface arc of rotor), (407,414) split can coordinate heat treatment with applicable processing or wear-out part, (401) be pump intrados, the matching part that itself and end of blade are turned is for the most frayed, and material and processing process make it have well relative lubricity and wear resistance.
As end of blade is turned larger than the thickness of pump leaf in the part near pump intrados, blade can not entirety be reduced in rotor, when being gas as pump fluid, because the compressibility of gas is large, pressurized gas can be made from the compression end R reducing volume 2take back fluid input, thus reduce delivery pressure and loss efficiency.The concavity of turning close to end of blade can be processed in leaf groove exterior angle as the edge face sealing member of (507) rotor of Fig. 5 or rotor, blade integral or major part can be reduced in rotor leaf groove, overcome fluid backflow.Its shortcoming is the stressed distance owing to needing the stressed distance adding blade root and rotor when trochiterian radius just can make blade radial stretch out to equal the rotor of undressed re-entrant angle, the pump of certain flow and pressure, and rotor radius and whole pump are than greatly original.
Embodiment 3: in volume leaf pump, the rotation of rotor and blade is not substantially subject to axial force and moves axially, the pump interior edge face coordinated with blade is again the plane balanced mutually, each corner of rotor and blade end is right angle and both ends of the surface are mutual correcting plane, only need add less power in the axis of blade and rotor just can have good and pump body end surface sealing can reduce again loss and the wearing and tearing of energy.(426) in the middle of (421) and (418) in Fig. 4 are the vane end faces pressure unit of figure (421 vane end faces supercharging view), comprise (410), or (411 (409), 412), can find out that half vane (408) is by slide block (409) and spring (410) power left from figure (421 vane end faces supercharging view), make the left side pressing slipper seal of this half vane (408) and pump, the pressure surface holding spring block groove contrast wheel (412) on the right side of it has certain vacant amount to do blade wear compensation, the blade being applicable to not moving radially between two halves leaf is (as 419, 420), the blade of downside is that (409) left side is free surplus, right side is by spring (410), slide block (411), wheel (412) power to the right, make the right side pressing slipper seal of this half vane and pump, be applicable to two half vanes in (as 418) to have and mutually radially sliding, slide block coordinates the friction that can reduce radial motion with wheel, as fluid lubrication well also can be taken turns and with skid, the groove that blade (418) holds (426) is namely that radial direction is free surplus up and down, and two half vanes can radially slided mutually.
(419) in Fig. 4, (420) (426) in the middle of are the vane end faces pressure unit of figure (419 vane end faces supercharging view), comprise (423) or (425) and spring, can find out that slide block (423) promotes to rub with the end face of pump fitted seal by the spring in blade groove from figure (419 vane end faces supercharging view), can be blade two ends also can directly to rub fitted seal with the bidirectional propulsion that blade and the end face of pump pass through spring by one end (423) the other end with (423) sealing, because (423) thinner with the cooperation place of blade, the gap of blade (419 or 420) axis and pump end face should be reduced, its axially stretch out blade pitch from less by steering force and hydrodynamic pressure less, can add pivot pin or (423) and cooperation blade groove makes (423) move axially only and can not move radially in blade bottom shortening etc., namely the bottom being (423) can be flat or shorten a bit of with blade bottom, its top is to the end face of blade.At one section of blade that (424) of figure (419 vane end faces supercharging view) are blade (420 or 419) end face seals, as being (424) at the intermediate section of (420), (425) make (420) by acting force of the spring, (424) with the slipper seal of pump both ends of the surface pressure, when axially having distance due to the apposition position of wearing and tearing (420) and (424) as schemed two sections of leaves in (419 vane end faces supercharging view), (420) radial bottom to (424 and 425) bottom extend a segment length (426) slipper seal this apart from possible leakage, but radial length (424) shortens, make sealing effect slightly poor, if figure is in the coordinating of (424) and (419), (424) have the thickness radial direction of half to be lengthened to top at blade tip, and bottom is identical with (420), (425) there is interfoliaceous clearance seal, can with arbitrary leaf or two leaves slide axially and two leaf power turn to synchronous function, (425) when such as (420) top is recessed round section, its radial tip length is to recessed disc, (425) when such as (419) top is dome section, its radial tip length is to dome face, (425) the leaf groove that (424) are inserted in axial one end is interior until bottom land or (425, 424) combine, the other end inserts (420 or 419) segment distance and accepts spring force, namely be that (425) are across (419 or 420, 424) apposition position, be that the sealing that can move axially is slided with thickness both sides blade.
Above blade, (424), (423) etc. are just made compensate for wear by the axial force of spring and are not had dynamic moving axially, but coordinate slipper seal to have certain friction with the end face of end cap, the face of slipper seal and the end face of end cap is coordinated to balance with the end face of end cap and dual-side is right angle, substantially fluid can be eliminated from the opposite force of end face to spring, when ensureing sealing, make spring force value less, more reduce damage by friction and energy loss, material and processing process also will make it have well relative lubricity and wear resistance.
Embodiment 4: rotor is also the same with blade with the end face fitted seal of end cap, and only need add less power in the axis of rotor just can have good sealing can reduce again loss and the wearing and tearing of energy.(501, 506, 510) be the edge face sealing member of rotor, face outside the face and rotor in axle center seals and axial sliding fit, its axial length preferably to make the two ends of rotor respectively install the edge face sealing member of a rotor, available (508) or (502) mounting spring make that (501 or 506 or 510) are stressed is pressed onto end face slipper seal, (504) be (501 or 506 or 510) axial length at rotor leaf groove side cylindrical, on leaf groove (505) side plane, because be apart from rotor axis farthest, substantially be the maximum position that rotor is subject to BLADE FORCE, length can be reduced, intermediate section be workpiece strengthen being fixed on outside rotor or rotor evagination to (501, 506 or 510) (509) of periphery, bear and mainly revolve steering pressure from blade, rotate to thickness stressed and determine according to institute, (504) also can be longer, but need to strengthen the edge face sealing member of rotor and the intensity of axial traveller (503) and join strength, as the radial thickness of (510) and traveller all strengthen, prevent it be subject to the pressure of blade and radial force and damage or be out of shape.Axial traveller (503) is used to be fixedly connected with (501 or 506 or 510) makes (501 or 506 or 510) be attached on the fit on face of rotor, prevent the edge face sealing member of rotor by the fit on face of the power disengaging rotor of blade, and can only move vertically, as larger by the power of blade in (501 or 506 or 510), then at least need two (503) axial travellers to add intensity near leaf groove place with the edge face sealing member both sides of rotor and be connected, the edge face sealing member connection request of the shape of traveller and itself and rotor is the edge face sealing member (501 that can make rotor, 506, 510) fit with suitable intensity and rotor fit on face and pressing pump interior edge face can only be moved axially, the edge face sealing member of rotor and pump end face coordinate sliding sealing surface and pump interior edge face to balance and also the lateral arcs limit in face be right angle (with above-mentioned leaf end face seal in like manner).

Claims (7)

1. fitted seal design in the volume leaf pump imported and exported of both sides and pump, it is characterized in that, variable displacement pump or motor are that pump is adjusted to adjustable minimum discharge, when the shortest pump intrados of any adjacent two pump blade symmetry distance rotor axis forms minimum volume between two blades, two blades and pump intrados are formed and contact pump intrados section (2) arc length sealed is R 2, R 2two ends be import and export; Pump or motor are adjusted to peak rate of flow, and when the maximum pump intrados of any adjacent two pump blade symmetry distance rotor axis forms maximum volume between two blades, contact canned pump intrados section (1) arc length that two blades and pump intrados are formed is R 1, R 1both ends open or pump intrados fluting be switched to R 2the import and export at two ends, can at R when the number of blade of pump is greater than 8 leaf 1, R 2medium design add transition cambered surface section R 7; Import and export when regulating as variable with rotor shaft and be outwards fixedly connected with, when regulating as variable with the movable pump housing, with flexible interface (10), end face slip interface (11) or flexible pipe by R 2the import and export at two ends are connected with the fixing pump housing pipeline of outside.
2. fitted seal design in the volume leaf pump that a kind of both sides required according to right 1 are imported and exported and pump, is characterized in that, when produce in pump or motor running pump positive and negative be pressed with affect time, can at R 1with or R 2open relief hole (3), the relief hole (3) of one-way pump connects pressure releasing device (03), its height pressure side respectively with the height press bond imported and exported; The relief hole (3) of two-way pump is connected commutator (01) and is connected to the contrary pressure releasing device in direction (02), (03), commutator (01) two ends connect both sides according to (02,03) correspondence and import and export, pressure releasing device height pressure side is also corresponding with the height pressure side imported and exported respectively to be connected, and makes R 1or R 2fluid pressure flows to high voltage terminal higher than during the high pressure imported and exported, and hydrodynamic pressure is flowed in pump by low voltage terminal lower than during the low pressure imported and exported.
3. .fitted seal design in the volume leaf pump that a kind of both sides are imported and exported and pump, it is characterized in that, metering pump or motor are any adjacent two pump blade symmetry distance rotor axis the shortest pump intrados when forming minimum volume between two blades, and contact canned pump intrados section (2) arc length that two blades and pump intrados are formed is R 2, R 2two ends be import and export, when the maximum pump intrados of any adjacent two pump blade symmetry distance rotor axis forms maximum volume between two blades, contact canned pump intrados section (1) arc length that two blades and pump intrados are formed is R 1, R 1both ends open or pump intrados fluting be switched to R 2the import and export at two ends are that the double-acting pump of cross section ellipse or motor are with two sections of R in pump 1center line and two sections of R 2center line become cross to be boundary, the pump housing or inner ring are divided into four angular segments, importing and exporting in each angular segments is connected becomes two total import and export with importing and exporting in the angular segments at diagonal angle to be connected again, can at R when the number of blade of pump is greater than 8 leaf 1, R 2centre can design and add transition cambered surface section R 7.
4. fitted seal design in the volume leaf pump imported and exported of both sides and pump, it is characterized in that, pump leaf is recessed near the end of pump intrados, it is recessed that convex circle and end of blade are turned, convex circle correspondence combines, end of blade is turned can in maximum rotation angle B axial rotation, what blade and end of blade were turned match mutually seal axial rotation and radial direction and stablizes and be connected between circle, it is cambered surface (413 of entirely fitting that end of blade is turned with the fitting surface of pump intrados, 416) or the end of blade two ends of turning coordinate slipper seal with pump intrados, end of blade two ends coordinated with pump intrados of turning can be turn with end of blade to be fixedly connected with (414, 415), split connect (415) or can axial rotation connect (422, 417), what end of blade turned two ends can the rotor that connects of axial rotation be whole (417 is left) or two ends (407) and pump intrados slidable sealing, rotor and end of blade are turned the recessed of two ends, it is can axial rotation that convex circle correspondence combines, seal be connected stable with radial direction.
5. fitted seal design in the volume leaf pump imported and exported of both sides and pump, it is characterized in that, the thick direction of leaf of same rotor vane groove forms a pump blade by half leaf of two pieces of face indents that match, there are spring, slide block or are added with runner in the middle of the indent of two and half leaves, two and half leaves are respectively by an end face slipper seal in each pressing pump of axial opposed active force of spring, two and half leaves are when radial direction has relative movement, and the indent of blade and the spring of the inside and slide block must have enough removable spaces in radial direction.
6. fitted seal design in the volume leaf pump imported and exported of both sides and pump, it is characterized in that, when the thick direction of leaf of same rotor vane groove is a pump blade, at the axial one or both ends thickness intermediate radial fluting of blade, spring and slide block is equipped with in groove, slide block can slide axially in the both sides of thickness direction and blade groove both sides sealing, when being axially a blade, can be one end slide block by spring to a side end face slipper seal of blade opposite force pressing pump, the other end is the other end slipper seal of vane end faces and pump, may also be blade two ends and all add slide block and the slipper seal of pump both ends of the surface, when being axially two sections of blades, slide block to insert in the groove of two blades or wherein one section of blade has evagination to form slide block to insert in another section of blade groove respectively at two sections of blade apposition positions, spring adverse effect is had on slide block and blade in the groove of blade, make two sections of sharfs to two ends slipper seal in reverse pressing pump, wherein one section of blade has one section of axis to extend to another section of blade bottom near the bottom of rotor axis, wide in the thick direction of leaf, after guaranteeing two sections of blade wears, fluid does not flow to opposite side from the hole between two leaves and slide block from bottom.
7. fitted seal design in the volume leaf pump imported and exported of both sides and pump, it is characterized in that, rotor seal part (501 or 506 or 510) is added with at the outer surface of rotor-end, the internal surface of rotor seal part and the fit on face of rotor are cambered surface or plane and the close fit that can slide axially, at least respectively there is one section of side (504) rotor seal part both sides on rotor leaf groove (505) side plane in rotor-end, (504) when length is shorter, groove side intermediate section is that the outer convex surface (509) of rotor bears the main lateral force of blade, round shape hole or interior sipes is had at rotor axial, inside there is the traveller (503) being fixed on rotor seal part (501 or 506 or 510) internal surface, (503) the fit on face making the internal surface higher-strength of rotor seal part seal to be combined in rotor can only be in axial sliding, at rotor seal part and the end-acted backward end of pump or there is spring (508 or 502) in the inner of (503), spring thrust acting in opposition is on rotor and rotor seal part, making the rotor seal part of two ends of rotor or one end be the rotor seal part the other end is that rotor end-face coordinates slipper seal with the both ends of the surface in pump.
CN201510078085.XA 2015-02-14 2015-02-14 Matched sealing design for volumetric vane pumps at inlet and outlet in two sides and pump interior Pending CN104696214A (en)

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105386970A (en) * 2015-10-21 2016-03-09 何家密 Seal for fit of inlet and outlet in two sides of displacement blade pump, blades and pump interior
CN111601949A (en) * 2018-01-11 2020-08-28 托瑟克工业公司 Rotary sliding vane machine with sliding and pivoting bearings for vanes
CN113847239A (en) * 2020-06-25 2021-12-28 爱塞威汽车有限责任公司 Pump comprising an attached sealing gasket
CN116119776A (en) * 2023-03-28 2023-05-16 广东海洋大学 Butterfly type fluid pressure energy recovery device and sea water desalination system

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105386970A (en) * 2015-10-21 2016-03-09 何家密 Seal for fit of inlet and outlet in two sides of displacement blade pump, blades and pump interior
CN111601949A (en) * 2018-01-11 2020-08-28 托瑟克工业公司 Rotary sliding vane machine with sliding and pivoting bearings for vanes
CN111601949B (en) * 2018-01-11 2022-05-17 托瑟克工业公司 Rotary sliding vane machine
CN113847239A (en) * 2020-06-25 2021-12-28 爱塞威汽车有限责任公司 Pump comprising an attached sealing gasket
CN113847239B (en) * 2020-06-25 2023-08-04 爱塞威汽车有限责任公司 Pump comprising an attachment seal
CN116119776A (en) * 2023-03-28 2023-05-16 广东海洋大学 Butterfly type fluid pressure energy recovery device and sea water desalination system
CN116119776B (en) * 2023-03-28 2023-08-22 广东海洋大学 Butterfly fluid pressure energy recovery device

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