CN1012273B - Ring valve pump - Google Patents

Abstract

An eccentric ring porting system for hydraulic pumps of the type having a rotating cylinder block. The rotating cylinder block has a flat annular port face with a small cluster of regularly spaced cylinder ports in the face circularly arrayed about the axis of rotation of the cylinder block. A ring valve element has a ring seat surface held flush against the cylinder port face. The axis of the ring seat surface is eccentrically offset from the axis of rotation of the cylinder block, and the cylinder ports are uncovered inside of the inner edge of the ring seat surface for output porting of the pump and outside of the outer edge of the ring seat surface for inlet porting of the pump.

Description

Ring valve pump

The invention belongs to the oil hydraulic pump field, relate in particular to the oil hydraulic pump of rotary cylinder-block, and its import and outlet, be to finish by the fixedly cooperation between the valve port in cylinder mouth in the rotary cylinder-block and the housing, this type oil hydraulic pump is used in particular for fuel injection system.

Hydraulic system of the prior art, most of oil hydraulic pumps are rotating cylinder builds.In this type of pump, device in the pump housing is swash plate for example, the piston engagement that is and rotates with rotary cylinder-block, pass through malleation or compression stroke and negative pressure or intake stroke regularly continuously to promote piston, is to be in malleation or compression stroke moves and make piston in 180 ° of parts of the pump housing, and piston is to be in negative pressure or intake stroke moves in another 180 ° of parts of the pump housing.The rotary cylinder-block pump, estimate at 95% adopt the kidney shape of the mouth as one speaks into and out of valve.

In a kind of kidney shape of the mouth as one speaks valve system, at pump housing internal fixation two big arc kidney mouths are arranged, appear in the end cap of the pump housing.One of them big kidney mouth is distributed in 180 ° of parts and is used to enter, and another is distributed in another 180 ° of parts and is used for discharging.The fixedly kidney mouth that these are big is separated by valve face (land) in their end, so in fact their size is slightly less than 180 °.The little regular alternate cylinder body kidney mouth of annular arrangement is positioned at ring-type cylinder mouth plane, and is communicated with corresponding pumping cylinder separately on rotary cylinder-block.The axis of the axis of rotating cylinder valve port and big fixedly kidney mouth is coaxial, and little cylinder valve mouth is from just being depressed into the unexpected conversion of negative pressure at a valve face, is unexpected conversion from negative pressure to malleation at another valve face.

The kidney shape of the mouth as one speaks valve of the prior art that adopts in the rotary cylinder-block oil hydraulic pump has many serious problems, and it has intrinsic geometric figure, and particularly rotating cylinder valve port and big fixedly kidney mouth is co-axially aligned.One of intrinsic problem is, big fixedly kidney mouth and rotating cylinder valve port, concerning the flow and pumping pressure of regulation, requirement has bigger radial distance from spin axis, this causes the high-speed friction of the right fixedly kidney actinal surface of undesirable rotary cylinder-block valve port face pressing face, and the result is undesirable heavy wear.

Another intrinsic problem of kidney shape of the mouth as one speaks valve is, long fixedly kidney groove is with their steep ends and short middle valve face, the plane overlap joint on the valve port surface that formation is faced, problem in use are to trend towards forming between valve face inexact face-to-face sealing.Bigger valve port radius causes a difficult problem of using the midplane overlap joint.

In the end of long fixedly kidney mouth, rotary cylinder-block valve port and unexpected the intersecting of valve face also produce serious problems.The end arris of the fixedly valve port that the end arris of little rotation valve port is corresponding big is 180 ° of relative geometrical shapies of sudden change, and the result causes the very fast switching function of valve port.180 ° of relative geometric figures of the sudden change of this valve port are mixed problem by valve port from the unwelcome big radial arrangement of spin axis, and the result causes the sizable approaching and escape velocity of valve port.

A kind of like this problem is, 180 ° of intersections of rotary cylinder-block valve port arris and big kidney mouth valve face sudden change have trend to cause paddle-tumble at one or two valve faces, and have pressure fluid to leak out from the valve face intermediate interface subsequently.

The positive and negative pressurization of rotary cylinder-block pump, its piston is subjected to actuating of swash plate, and pressurization is the sine function relation basically, in the valve face pump pressure is zero, at a big fixedly kidney mouth near midpoint malleation pump pressure maximum, and at another big fixedly kidney mouth near midpoint negative pressure or suction pressure maximum.Basically be that full high voltage output and the full negative pressure that the cylinder body valve port sudden change ground of zero-pressure is exposed to pump imported, cause undesirable random pressure or " hydraulic pulsation " inherently in output and input end, and random input, will reflect bigger random output at output terminal.

Because the difficulty on making, and because wearing and tearing such as stroke ditches, cause the deviation of the relative valve face planeness of kidney shape of the mouth as one speaks rotary cylinder-block pump, trend towards causing perpendicular to the leakage way on the axial direction of the general layout of valve face, the bigger periphery of the kidney mouth valve face that requires in accordance with regulations pump duty and pressure simultaneously, all be the factor of accumulation, they trend towards causing along radially or be parallel to the bigger escape of liquid passage of valve face general layout.The serious consequence of these leakage factors is, it makes pump when low speed, and the foundation of delivery pressure is quite slow.Because fuel-injection pump is by engine-driven, this is dangerous shortcoming at the engine start speed stage, and the startup of motor is the rising that relies on pump pressure fully.

In view of these, and other problems in the prior art, general purpose of the present invention provides a kind of novel valve port system that is used for rotating cylinder build oil hydraulic pump, and it has the finer and close sealing of adopting usually than in this pump of kidney shape of the mouth as one speaks valve in long-term working life.

Another object of the present invention provides a kind of valve port system that is used for rotating cylinder build oil hydraulic pump, and it has adopted a kind of novel ring valve seat surface, and the spin axis of the relative rotary cylinder-block of this valve seat surface is located prejudicially.

Another object of the present invention provides a kind of novel SIMULATION OF ECCENTRIC ANNULAR valve arrangement that is used for rotating cylinder build oil hydraulic pump, and it has unbroken symmetric geometry, in use is specially adapted to the plane overlap joint, guarantees the effectively sealing face-to-face of valve port surface.

Another purpose of the present invention provides the ring valve port system that is applicable to rotating cylinder build oil hydraulic pump of above-mentioned characteristic on a kind of tool, the relative novel SIMULATION OF ECCENTRIC ANNULAR valve element of the present invention with the cylinder mouth of its rotating cylinder oral thermometer face has the narrow rotation acute angle that enters and leave, can reduce the wearing and tearing of operation period, the any trend that can avoid stroke ditch again and leak subsequently, and can cause continuous self-cleaning effect and little surface overlap joint in using.

A further object of the invention provides the novel ring valve port system that is used for rotating cylinder build oil hydraulic pump, its curved annular valve seat outlet and inlet arris, and the geometrical shape of rotation circular cluster cylinder mouth, make its ring-type valve seat and cylinder mouth valve surface, compare with the valve surface of the common kidney shape of the mouth as one speaks system with suitable pump duty and pump pressure, its area can be much smaller.This much smaller area has not only reduced leakage owing to its much smaller valve face periphery, and the more accurate cooperation planeness of valve face can be made and keep.

A further object of the invention provides a kind of SIMULATION OF ECCENTRIC ANNULAR valve valve port system that is used for rotating cylinder build oil hydraulic pump, wherein, the validity of valve face and to be used for the area of pressure fluid flow and pressure quite little, pressure fluid leakage in the middle of the valve face that cooperates is reduced greatly, cause when pump speed is very low, the delivery pressure of pump rises very fast, when valve system of the present invention is used in engine-driven fuel-injection pump, and the startup of motor is the rising of pump pressure when fully relying on low engine speed, and this is very crucial advantage.

The present invention also has another purpose to provide a kind of novel SIMULATION OF ECCENTRIC ANNULAR valve port system that is used for the rotary cylinder-block oil hydraulic pump, its rotating cylinder mouth is in the fixing discharge of curved annular valve seat and enter valve port arris place and open and close, be gradually and do not resemble and suddenly change the waist shape shape of the mouth as one speaks valve that usually adopts at similar oil hydraulic pump, what its valve port characteristic was total is to follow pump characteristics, and therefore random delivery pressure or hydraulic pulsation can reduce.

In rotating cylinder build oil hydraulic pump, the rotation of piston and cylinder pressure is by first 180 ° of parts of the pump housing, and its piston moves along compression or delivery stroke, and during second 180 ° of part by the pump housing, its piston is to move along suction or input travel.According to the present invention, cylinder body is provided with the cylinder actinal surface, and normally with respect to the radial direction orientation of the spin axis of cylinder body, cylinder body also has the regular alternate cylinder mouth of rounded arrangement at the cylinder actinal surface, and each cylinder mouth is communicated with a corresponding cylinder pressure.One generally is that the valve element of ring-type has a circular valve base surface, and this surface and cylinder oral thermometer face mesh face-to-face, and the axis of ring valve seating face is offset prejudicially with respect to the spin axis of cylinder body and cylinder mouth.The skew of the off-centre of this ring-type valve seat axis, preferably towards 180 ° of parts of the compression or the discharge of the pump housing, cause compression or discharge cylinder pressure and be exposed within the interior arris of ring valve seat surface, and the malleation exhaust port of the hydraulic fluid that conduct is pumped, cause suction or suction cylinder to be exposed to outside the outer edge of ring valve seat surface simultaneously, and enter the mouth as the suction of the fluid that comes from pressure fluid source.The pressure of discharging fluid acts on the ring valve element, keep the ring-type valve base surface pressing the cylinder actinal surface downwards, therefore more offset the lifting force of pressure fluid, these pressure fluids are in the separating surface that acts between cylinder actinal surface and the valve seat surface, and the bias voltage that starts spring also acts on the ring valve element, so that bias voltage cylinder oral thermometer face simultaneously, finish this function until the hydrodynamic pressure rising of output.

These and other objects of the present invention are by hereinafter in conjunction with the accompanying drawings narration just can be clearer.

Fig. 1 is a stereogram of implementing ring valve pump of the present invention;

Fig. 2 is the side view that ring valve pump of the present invention is looked towards the valve end cap;

Fig. 3 is the axial sectional view along the intercepting of the 3-3 line of Fig. 2, and this section is the spin axis that revolves cylinder body through pump, and skew makes it also to intercept via the axis of ring valve element of the present invention then;

Fig. 4 is that this section both overlapped with the spin axis of rotary cylinder-block along the axial sectional view of the 4-4 line of Fig. 2 intercepting, also with the dead in line of ring valve element of the present invention;

Fig. 5 is the sectional elevation along the 5-5 line intercepting of Fig. 3;

Fig. 6 and Fig. 6 A are the local amplification views along the 6-6 line intercepting of Fig. 4;

Fig. 7 is the local amplification view along the 7-7 line intercepting of Fig. 4.

With reference to accompanying drawing, at first specifically with reference to Fig. 1-4, ring valve pump of the present invention is generally with 10 signs, usually be contained in the cylindrical pump housing 12 that has end 14 and 16, the pump housing 12 comprises circular cylindrical shell 18, is fixed to the valve end cap 20 of shell 18 1 ends, and is fixed to the hubcap 22 of shell 18 the other ends.Valve end cap 20 comprises ring valve element of the present invention, and it matches with the cylinder mouth of the loop configurations of pump prejudicially, has constituted the passage of import of the present invention and outlet.On the other hand, the hubcap 22 coaxial pump shafts that supporting, the drive end of pump shaft is protruding from hubcap.

The valve end cap is fixed to an end of circular cylindrical shell 18 by means of the regular alternate bolt group 24 of annular, and locatees reliably with respect to shell 18 by the regular alternate locating stud 26 of annular.Mating face between Gask-O-Seal 28 seal valve end caps 20 and the circular cylindrical shell 18.

Can see that in Fig. 1, Fig. 2 and Fig. 4 fluid inlet passage 30 passes valve end cap 20, parallel with the central axis 32 of pump 10, but bigger radial deflection is arranged with it, inlet passage is connected and is communicated with fluid provider at the valve end 14 outside openings of the pump housing 12.Outlet passage 34 also part extends through valve end cap 20, at the valve end 14 outside openings of the pump housing 12, with the apparatus of accepting from the pressure fluid of ring valve pump 10, connects and is communicated with as diesel oil or gasoline fuel injector etc.Fig. 2 and Fig. 4 clearly illustrate that the eccentric axis of outlet passage 34 and ring valve element of the present invention in line.This eccentric axis 36 is parallel to the central axis 32 of pump 10, but with offset of central axis 32 radial deflections, in Fig. 2,4 and 6, represent with " e ".So just can realize novel import of the present invention and outlet between static ring valve element and rotary cylinder-block mouth, this will be described in detail hereinafter.

Hubcap 22 has an axial bore 37, and the outer drive end of pump shaft 38 is therefrom stretched out.Hubcap 22 is connected with circular cylindrical shell 18 by means of one group of alternate bolt 40 of rule, locatees reliably with respect to shell 18 by one group of alternate locating stud 42 of rule.Interface between shell 18 and the hubcap 22 seals with sealing gasket 44.

Normally Yuan Xing cylinder body 46 is installed in the inner end of pump shaft 38, and cylinder body 46 has the center hole 48 of the inner end of placed axis 38.Cylinder body 46 is fixing with pump shaft 38 by coaxial screw 50, and screw terminal is recessed within the annular port plane 52 of cylinder body 46.Form fluid-tight between them at 0 shape seal ring 54 between axle 38 the inners and the cylinder body 46.Pump shaft 38 is to make cylinder body 46 drive shaft rotating, therefore, with the elongated key 56 in the alignment slot that is engaged on axle 38 and cylinder body 46 pump shaft 38 and cylinder body is carried out key and is connected.

The cylinder mouth overhang bracket of cylinder body 46 is on needle bearing assembly parts 58, and latter's part is placed in the shell 18, and a part is in the circumference of valve end cap 20.The inner bearing ring 60 of needle bearing assembly parts 58 is fixed on the cylinder body 46.To the swivel bearing of pump shaft 38 and cylinder body 46, be to finish by means of the ball bearing assembly parts 62 that is installed on the hubcap 22.The shaft seal 64 of a pair of lip packing type is installed in the hubcap passage 37, and the space between two Sealings 64 is by passage 65 and the pump housing 12 extraneous ventilations, to prevent producing pressure between two Sealings.

A cylinder sleeve 68 is respectively installed in the one cylinder hole 66 of forming annular array, and their rules are respectively around cylinder body 46.Each cylinder hole 66 is parallel with the central axis of pump 10 with cylinder sleeve 68, and equal spaced radial is arranged with it.In the embodiments of the invention in the accompanying drawings, seven cylinder holes 66 and cover 68 are arranged.The outer dia of cylinder sleeve 68 reduces part 70, outwards stretch to the axle head 16 of the pump housing 12 from cylinder hole 66, these outer dias reduce part 70 and extend through accessory channel on the grip block 72, grip block 72 is fixed on the axial end of cylinder body 46 by means of one group of alternate screw 74 of rule, so that cylinder sleeve 68 is clamped on the cylinder body 46.

The inner of cylinder body or head end 76 form cup-shaped gap by the taper shrinkage pool of shape shown, and cylinder end 76 is by corresponding cylinder head fluid passage 78, are connected with the respective cylinder draught animals 80 on the cylinder mouth plane 52 of cylinder body 46.Cylinder head fluid passage 78, slopes inwardly to cylinder head mouth 80 vertically and radially from cylinder head end 76, so that make the cylinder head mouth 80 and the radial distance of central axis 32 reach very little, this is an importance of the present invention.Yet, but can make cylinder body relatively big, so that, hereinafter will be described in detail for cylinder body, piston and piston actuated mechanism provide needed amount of space by the outside spaced radial of central axis 32.Cylinder head mouth 80 is the circular counter sinks at inclination fluid passage 78 nose ends.

Piston 82 slidably is installed in each cylinder sleeve 68, during cylinder body 46 rotation, when piston when central axis 32 is made circular movement, piston quilt as cam follower back and forth drives.Piston 82 has inner fluid promote-side 83 and outside cam following end 84.External cam follower ends 84 can be illustrated spherical shape usually, also can be improved conical surface shape, and its total cone angle is approximately equal to the tilt angle of cam with respect to pump 10 axis 32.Each piston 82 is acted on by the spiral piston spring 86 that the outer dia that is linked in corresponding cylinder sleeve 68 reduces on the part 70, outwards pushes with respect to its cylinder sleeve 68.The bias voltage of piston spring is to be affacted on the corresponding spring guide 88 by each spring 86, affacts on close its outer end 84 of respective pistons 82 by corresponding guide pin bushing snap ring 90 then.The inner of each piston spring 86 is pressed on the corresponding space washer 92, and the latter is pressed in again on the grip block 72.

The external cam follower ends 84 of piston 82 withstands on the cam swash plate 94, and owing to the rotation of cylinder body 46 is driven, cam swash plate 94 is placed in by means of lobe plate structure 96 on the fixed position in the pump housing 12.Cam swash plate 94 is a kind of form of annular rings, is pressed against on the annular roller bearing assembly parts 98 in mode free to rotate, and the latter is pressed against thrust washer 100 again.Upper bearing (metal) assembly parts 98 and thrust washer 100 all are placed on the lobe plate structure 96.Annulus 102 disposes swash plate coaxially around its rotating shaft.Spin axis is represented with 103 in Fig. 3.The active force of piston spring 86 is with swash plate 94, and Bearing assembly 98 and thrust washer 100 are pressed against on the lobe plate structure 96 together.Lobe plate structure 96 keeps its geometric fixation position in the pump housing 12, this is by rounded ends 104 supportings of lobe plate structure 96 and the outer bearing ring of covering ball bearing assembly parts 62, and is achieved to prevent its rotation by pin 105 pinnings on the hubcap 22.Like this, the axis 103 of cam swash plate 94 has a constant cant angle 106 with respect to the central axis 32 of pump 10 on the plane of Fig. 3 section, and this becomes 90 ° with the plane of Fig. 4 section or with Fig. 2,4 with the direction of the element of ring valve shown in 6 throw of eccentric " e ".The 106 pairs of ring valve pumps 10 of the present invention in the tilt angle of swash plate axis 103 provide second off-centre, and it matches in new ways with valve port throw of eccentric " e ", hereinafter will describe in detail.

Fluid input 101 is located on the wall of shell 18, and the inside of the pump housing 12 can be filled with by the fluid of pump pressure, or it can be found time when needing.Inlet 101 is plugged between ring valve pump 10 on-stream periods.Axle 38 is provided with transmission keyway 108 from hubcap 22 outwardly directed ends.

Ring valve element of the present invention generally represents that with 110 it is installed in the valve end cap 20, so that be connected on face-to-face on the annular port plane 52 of cylinder body 46.The cylindrical body 112 of ring valve element 110 is assemblied in the normally complementary of valve end cap 20 but in longer slightly the cylindrical dimple 114.0 shape seal ring 116 and slip ring 118 are placed in the circular groove of cylindrical body 112, form common fluid-tight between the cylindrical form interior surface of the dimple 114 of the body 112 of valve element 110 and valve end cap 20.

The valve face of ring valve element 110 is smooth annulus seat planes 120 that are pressed against on the cylinder body actinal surface 52, and it is limited between the inside and outside circle cylinder of valve component body 112.The inner edge 122 of ring seat face 120 forms the fixing of valves, promptly non-rotary outlet, it again by valve element 110 in axially the output pipeline 124 of stretching, extension be communicated with cylindrical dimple 114, be communicated with the outlet passage 34 of ring valve pump 10 then.

It is non-rotary import that the excircle 126 of ring seat face 120 forms the fixing of valves.The inner of valve end cap 20 is the dimple of annular, provides around the valve upstream chamber 128 of the internal orifice end of ring valve element 110.From the circumference of ring valve element 110, in upstream chamber 128, stretch out the regular alternate locating stud 132 of annular 130, one groups of ring-types of locating flange dish with locating flange dish 130 pinnings.Also pinning of valve element 110 prevents that it from rotating with respect to valve end cap 20 thereupon.Pin 132 is fixed on the valve end cap 20, but the axial sliding fit of complimentary aperture on it and the valve element locating flange dish 130 makes valve element 110 can be adjusted to an optimal seal position that is pressed on the cylinder body actinal surface 52 vertically.

The helical spring 134 of one group of annular is installed on the valve end cap 20 in the alternate corresponding dimple 136 of rule.Spring 134 presses the flange disk 130 of valve element 110, so that with valve element ring seat surface 120 smooth being pressed against on the cylinder body actinal surface 52.Only before pump is set up very big fluid output pressure, just need produce bias voltage with spring 134, actinal surface 120 and 52 is forced together, after this, itself can provide required biasing force fluid output pressure, hereinafter will describe in detail.

Upstream chamber 128 is isolated with the needle bearing assembly parts 58 of cylinder body by means of the 0 shape seal ring 138 that is installed on the annular retaining device 140, and retainer 140 presses needle bearing circle 60 by wavy spring (marcel spring) 142.

Have among two present the present invention of independent eccentric body, they are worked in coordination, so that eliminate unstability or " pulsation " of the pressure fluid that flows out basically fully from ring valve of the present invention and rotary cylinder-block combination.One of off-centre is the axial angle skew 106 of swash plate axis 103 with respect to pump 10 central axis 32.Another off-centre is ring valve element axis 36 with respect to the throw of eccentric " e " of the center of pump or main axis 32, this center or main axis 32 be pump cylinder 46 and cylinder valve mouth 80 around the axis of rotation.These two eccentric axis are worked in coordination in the present invention, so that eliminate the liquid stream unstability or the hydraulic pulsation in ring valve pump 10 outlet ports basically fully.This typical case for the eductor pump that acts as a fuel of the present invention uses, particularly may very high place at pressure, for example generally be about 2000 to 5000psig(pound/inches at some pressure) the diesel fuel injectors system in, and a kind of very in a short time, its pressure is according to the knowledge of the applicant up to about 15, may be very important in the new diesel fuel injectors system of 000psig.

This off-centre at the tilt angle 106 of the axis 103 of swash plate 94 makes piston 82 along with the rotation of cylinder body 46 and pivoting of cylinder body of ensuing 66 and piston 82, produces pump function.When the offset direction of ring valve element eccentric axis 36 with respect to the throw of eccentric " e " of central axis 32, and cam swash plate axis 103 with respect to the direction at the tilt angle 106 of central axis 32 as shown in the drawing, cylinder body 46 will turn clockwise as shown in Figure 5 and Figure 6 like that, the top cylinder body of from Fig. 3 or Fig. 4, being seen, to leave drawing moves up, and the bottom cylinder body of being seen from Fig. 3 or Fig. 4 will move down and enter drawing.This sense of rotation is represented with imaginary arrow in Fig. 6.

When rotary cylinder-block 46 makes piston 82 when central axis rotates, swash plate 94 and piston spring 86 actings in conjunction in its corresponding cylinder hole 66, are moved piston between full reduced time and the position of stretching out entirely.Can see that in Fig. 3 upper piston 82a is in full reduced return and puts, lower piston 82b is then near its full extended position.When cylinder body 46 turns over first 180 ° from position shown in Figure 3, piston 82a is as cam follower, with respect to swash plate cam 94 operations, in intake stroke, outwards move on to its full extended position from it by fully retracted position shown in Figure 3, promptly roughly corresponding to the position of piston 82b among Fig. 3.On the contrary, from rotated position shown in Figure 3 first 180 ° during, piston 82b will shift to its fully retracted position from its position of roughly stretching out entirely as shown in Figure 3 in compression stroke, promptly roughly corresponding to the position of piston 82a among Fig. 3.Then, when cylinder body 46 rotated another 180 °, piston 82a will retract its fully retracted position as shown in Figure 3 forward in compression stroke, and piston 82b then will retract its full extended position as shown in Figure 3 backward in intake stroke.

As shown in Figure 4, cylinder body 46 rotates leading 90 ° with respect to its position at Fig. 3, and therefore piston 82c and the 82d that sees from Fig. 4 approaches the middle part of its axial stroke, has the highest travelling speed thereby approach it.Upper piston 82c among Fig. 4 approaches the middle part of its intake stroke, and the middle part that the lower piston 82d among Fig. 4 approaches its compression stroke.

Like this, the pump housing 12 of pump 10 may be thought of as has two 180 ° part, and cylinder 66, piston 82 and cylinder mouth 80 pivot by them.180 ° of compression members, it is lower half portion of the pump housing 12 as shown in Figure 3 and as the Lower Half of the observed pump housing 12 of Fig. 4.Also have 180 ° of pumping units, it is the part of the drawing pump housing 12 in addition of Fig. 3, reaches the first half from the viewed pump housing 12 of Fig. 4.

The compression of the axial direction of piston 82 and intake stroke are accompanied by piston sinusoidal curve track around whole cylinder body when axis 32 rotatablely moves, piston motion slows near piston full reduced to advance and be roughly zero during full extended position, has provided sinusoidal summit here.Their the maximum axial motion speed near its midstroke is corresponding to the gradient of the sinusoidal steepest that reflects its motion.Novel SIMULATION OF ECCENTRIC ANNULAR valve port of the present invention, the inlet hole and the exit orifice of the valve port of the sinusoidal motion figure that the variation of cross-sectional dimension is in close proximity to piston 82 are provided, the synchronized movement of they and piston has been eliminated flow instability or hydraulic pulsation basically fully, hereinafter will describe in detail.

The rolling action of swash plate 94 1 Bearing assemblies 98 because piston cam following end 84 has sphere or improved conical surface shape, is rotating freely the friction that produces minimum flow between swash plate 94 and the piston cam following end 84.When piston cam following end 84 headed on swash plate 94 rotations, swash plate face and piston cam following end 84 meshed on the rotation path of action that is called scanning track on the swash plate face.Though piston 82 is free to rotate in its corresponding cylinder hole, they are just some vibration or nutating in the cylinder hole.

The ring seat face 120 of ring valve element 110 and the cooperation valve port between the cylinder actinal surface 52 clearly illustrate out in Fig. 6.Fig. 6 demonstrates, and by the cylinder mouth 80 that corresponding cylinder head fluid passage 78 and corresponding cylinder hole 66 are connected, is how to interconnect with the ring seat face 120 of off-centre, thereby interconnects with the inner outlet circumference 122 and the outer import circumference 126 of ring seat face 120.

Consider that cylinder body 46 is by clockwise direction rotation shown in Figure 6, the cylinder mouth 80a that is connected with cylinder inner carrier 82a by fluid passage 78a, be on its maximum closing position, and become in the radially outer outer rim of the periphery of its ring seat face 120 or import 126 gradually and be uncovered, so that upstream chamber 128 is exposed.At the opposite side of ring seat face 126, the cylinder mouth 80b that is communicated with cylinder inner carrier 82b by passage 78b is at the inner peripheral surface of ring seat face 120 or export 122 inboard and begun to become the part and be uncovered, so that be communicated with pipeline 124.Cylinder mouth 80c is ahead of cylinder mouth 80b, and is communicated with corresponding cylinder by passage 78c, and cylinder mouth 80c almost completely is exposed to its maximum magnitude in the inboard of ring-type exit portion 122.Another is ahead of mouthful 80c but lags behind the cylinder mouth 80e of mouthful 80a, has moved past its maximum open position greatly in the inboard of ring-type outlet 122, existing its closed position of shifting to.

At the opposite side of ring seat face 120, as on the right side of Fig. 6, the outside of the periphery 126 of cylinder mouth 80f present 120 is roughly half-open, and to be communicated with upstream chamber 128, a mouthful 80f is just shifting to its fully open position.Cylinder mouth 80d moves past its maximum open position in periphery 126 outsides of ring seat 120 a little, still near its fully open position, to be communicated with upstream chamber 128.Cylinder mouth 80g has moved past its fully open position greatly, and is just shifting to its closed position in the inboard of the periphery 126 of ring seat 120.

So as can be seen, during the conversion of the cylinder mouth 80 that is caused by the rotation of cylinder body 46, the ring seat face 120 of ring valve element 110 is finished the recognition reaction to cylinder mouth 80.Interior all 122 of ring seat 120 determines that cylinder mouth 80 is communicated with outlet conduit 124 when its corresponding piston is in compressive state, and the cylinder mouth 80 that periphery 126 definite its pistons of ring seat face 120 are in aspiration phases is communicated with upstream chamber.

In Fig. 6, depict inside and outside imaginary circle 144 and 146, with indication cylinder mouth 80 corresponding outer edge around central axis 32.In the moving direction of circle 144 indication inward flanges, and when the opening or closing of its motion output stage and during the major component at output stage, very moment 80 is during near the inward flange of ring seat 120, the inner case of indication outlet 80.Near the bottom in week 122 in the ring seat as shown in Figure 6 the time, the top edge of outlet 80 moves on to its open position, acutangulates with respect to seat inward flange 122.Have only the upper periphery edge part of mouth 80 at first to be opened then with this acute angle.Equally, when the top of the present inner edges 122 of very moment 80 was closed, they were also moving with respect to edge 122 acutangulate situations, and had only mouthfuls 80 very little following outer peripheral edge portion to be closed.On the contrary, most of length in the left side of interior circle 144 and interior seat rim 122 is all parallel to each other with the tangent relation of off-centre usually, so that part of in the outlet of valve port, when large-area cylinder mouth 80 is exposed to the inboard at ring seat edge 122, mouthfuls 80 are exposed to the variation of the opening and closing in the seat rim 122 with regard to slow finishing.By this device, the exposure of mouth 80, from opening near interior seat rim 122 bottoms, major component through outlet, at last closing near the top edge of the outlet edge 122 of seat, very closely following the sinusoidal motion of piston, thereby following the corresponding sine mobile pace of change of cylinder mouth 80 from the liquid stream of its corresponding cylinder acceptance.The correlation of the output liquid stream of the exposure of this outlet and flow direction mouth has been eliminated the unstability or the hydraulic pulsation of output fluid pressure basically fully.

In the same way, the outer rim of cylinder mouth 80 moves with the periphery 126 represented acute angle relations of cylindrical 146 with respect to ring seat 126, no matter be its motion that opens or closes, has only the very little outer part of mouth 80 to be exposed near opening or closing the position.And at the main or core of suction stage, mouthfuls 80 very big outer part is exposed between cylindrical 146 and outer seat rim 126 parts, and they are parallel to each other with tangent relation usually.Therefore, the variation of exposed amount is slow.Like this, in suction stage, the sinusoidal suction movement of respective pistons is more closely being followed in the exposure of 80 pairs of upstream chambers 128 of cylinder mouth, eliminates the fluctuation or the hydraulic pulsation of input fluid basically fully.

Recently see with cooperating mutually of pumping function with the opening function that the present invention is obtained, in traditional waist type valve, opening and covering of cylinder mouth is that wholecircle circular velocity with cylinder body is carried out rapidly, promptly all open and enter into big static waist shape mouth, in the gamut that scans, keep opening entirely, be communicated with big waist shape mouth, then, when arriving big waist shape mouth end, close rapidly.This unexpected opening, and the unexpected high pressure of the thing followed and high delivery volume flow out the variation of volume towards low pressure and low pumping hole, causes huge unstability or hydraulic pulsation in the outlet port.

In illustrated embodiments of the invention, seven cylinder holes 66, cylinder head fluid passage 78, cylinder mouth 80 and piston 82 are arranged, their rules are respectively around cylinder body 46.From Fig. 6 as seen, for seven cylinder pump devices and mouth, two cylinder mouths 80 always large size are exposed to outlet conduit 124 in the outlet periphery 122, the 3rd local exposure of cylinder mouth, and have two cylinder mouth 80 large size to be exposed to upstream chamber 128 simultaneously in import periphery 126 outsides, above local exposure of another one.Empirical discovery, the regular alternate cylinder mouth 80 of seven cylinder holes, piston and ring-types is an enough quantity, is enough to cooperate with ring valve seat surface 120, so that various valve port characteristics to be provided smoothly, describe in detail above, it is usually consistent with pump characteristics, unlikelyly causes any significant hydraulic pulsation.

Ring valve of the present invention has a series of characteristics, and they cooperate jointly with coordinated mode, compares with traditional waist type valve, and finer and close valve port face seal can be provided, no matter they are at the initial stage of the product that produces, still after long-term work.

One of them characteristic is, the cutout hole group 80 of the symmetric geometry of annulus seat surface 120 and ring-type, and the plane overlap joint when being specially adapted to use is to provide best face-to-face sealing.Another characteristics be cylinder actinal surface 52 and cylinder mouth 80 respectively with respect to the geometrical shape of the symmetry of ring seat face 120 and narrow and small near and leave the angle, cause having cleaning action and continuous little surface overlap joint, the latter can keep the accurate planeness of matching surface after wearing and tearing in valve process long-time operation.Because this effect, without any the tendency that produces groove, and the leakproof seal of initial densification can keep for a long time.

In addition providing the extremely important characteristics that match with other characteristics aspect the reliable sealing valve port to be, the geometrical shape of the eccentric ring seat face 120 and the cylinder mouth group 80 of annular, make the area and the thing followed outer periphery of valve face, all much smaller than traditional waist type valve.This littler size makes the planeness of the actinal surface of cooperation make and to keep more accurately.More accurate planeness makes and cooperates valve face in its aspectant direction, and promptly perpendicular to the direction of face more closely together, making vertically is that leak path on the axial direction reduces to minimum at valve.And by the circumference that reduces that littler valve face obtains, make be parallel to the direction on plane, or reduced in total escape of liquid approach in the radial direction of valve.And the radius of rotating cylinder actinal surface 52 parts that engage with ring seat face 120 is littler, causes having reduced friction velocity, and it is proportional to radius, has therefore reduced wearing and tearing.

The part of the cylinder body actinal surface 52 that contacts with 120 in ring seat face, it is very low that the absolute limit of its speed is actually.Like this, be used as in the model machine of fuel-injection pump purpose of the present invention, the external diameter of seal ring seat surface is about 1 inch, and its off-centre is about 3/16 inch.The result, the diameter of the cylinder body actinal surface 52 of inswept ring seat face 120 is about 1/18 inch, this diameter multiply by π (3.14) again, the periphery that draws inswept surface is about 4.32 inches, for a typical rotating speed is 2400 rev/mins of diesel engine, drive ring valve pump 10 with common crank, the outer circular velocity on inswept surface is about 14.4 feet per seconds, and the mean velocity of the actinal surface 52 of this inswept ring seat face 120 is significantly smaller than 14.4 feet per seconds.

Leakage of the present invention is very little, and this epochmaking advantage is obtained by ring-type valve port of the present invention.Ring valve pump 10 of the present invention is to set up full output services pressure under low-down rotating speed.At pump is that this is very important during by engine-driving, preferably adopt pitman shaft speed, but also can adopt camshaft speed, and perhaps can be to adopt belt, any other required speed of gear or shaft drive etc.If to the fuel injector pumping, absolute importantly pump 10 should be able to provide full pressure, this priming speed basically under the priming speed of motor be very low to use ring valve pump 103 with compressed fuel.Should be very fine and close to the sealing of ring-type valve port of the present invention, make that being lower than per minute 70 at the model machine that adopts ring valve pump of the present invention and engine speed can obtain full pressure under changeing.And compare with traditional rotary cylinder-block fuel injector pump (it has waist type valve port), the latter requires to surpass the rotating speed that per minute 300 changes.This is four to one starting (four-to-one start-up) effect that is better than of the present invention, and it shows the order of magnitude that sealing valve port of the present invention reaches.

Ring valve element 110 and the part that is exposed to the cylinder body actinal surface 52 of upstream chamber 128 all are immersed in by in the fluid of pump pressure.In addition, have only the fluid film of several molecule thickness, when cylinder body rotates,, promptly work continuously between the part of ring seat 120 and the cylinder actinal surface 52 aimed at it on two mouthfuls of relative planes.These fluid films between the valve port face play lubricated surface to be prevented to wear and tear.In fact these films are admitted from corresponding cylinder hole due to high-pressure liquids in the cylinder mouth 80 of pressure fluid are pressed in the interface between the valve port by the outlet 122 that is present in ring valve element 110 and those, and these cylinder mouths are the cylinder mouth 80b among Fig. 6,80c, and 80e.These pressure fluids in interface flow out between the actinal surface at work gradually, but speed is very slow, so that do not show the escape of liquid of any amount.These pressure fluids in valve port face interface produce the power of pushing open, and attempt pushes away cylinder actinal surface 52 vertically with ring seat face 120.Push the pressure distribution figure open and in Fig. 6 A, roughly show with imaginary line 148, from radially outwards expansion of ring valve outlet 122, and radially outwards further crooked around pressure cylinder mouth 80.The power of always pushing open on ring valve element 110 is to multiply by pressure in the increment interval by the area increment, and area integral that pressure figure 148 limited determines by pushing open to whole.When pressurized cylinder mouth 80 rotation, pushing pressure figure 148 open can change continuously, and the size of pushing power open can change in pushing the scope of figure open slightly.This pushes power open is greater than the contending with of chucking power under its worst case, and this chucking power is to be acted on the ring valve element 110 by the output fluid pressures in the cylindrical dimple 114 of end cap 120.Chucking power determine by output fluid pressure multiply by valve member cylinder shape body from the internal diameter to the external diameter between cross-section area obtain, wherein this internal diameter is to be limited by 122 of outlets, and external diameter to be periphery by 0 shape seal ring 116 limited.Though the imaginary line 148 general figures of pushing pressure and power open that limit among Fig. 6 A should be appreciated that the pressure of per unit area increment and power radially outwards reduce, up to graph line 148 places therefrom being maximum values near outlet 122 and pressurized cylinder mouth 80 places.Yet, should be appreciated that the interface between the alignment portion of whole ring seat face 120 and cylinder actinal surface 52 is by being lubricated by the fluid film of pump pressure.

Act on the hydrodynamic pressure chucking power on the valve element 110, enough big full annular scope planted agent around ring valve element 110, ring seat face 120 firmly being pressed put on cylinder actinal surface 52, can be eccentric 36 around the ring seat center regardless of the irregular pressure figure 148 of pushing open is arranged.Though this can cause that the power that acts between the valve face is bigger at opposite side at ring seat 120 1 sides ratio, also not finding has bigger wearing and tearing on effect has more energetically a side, this is particularly owing to there is lubricating film between valve face, and the sweep speed between the surface is very low.The pressure of the 118 pairs 0 close rings 116 of shape of slip ring moves axially degrees of freedom fully for ring valve element 110 provides, in order to 120 pairs of cylinder body faces 52 of ring seat face are finely tuned, to guarantee that best sealing is arranged between the two valve port faces.

Though the present invention is described with reference to most preferred embodiment, should be appreciated that the professional and technical personnel can carry out various variations, and does not break away from the scope and spirit of the present invention defined in claims.

Claims (15)

1, valve port system in a kind of oil hydraulic pump, this oil hydraulic pump has one and defines the housing that enters and discharge the fluid passage and have a cylinder body that can rotate within it, cylinder body has the regular alternate cylinder pressure of circular arrangement, a piston is in axial sliding arranged in above-mentioned each cylinder pressure, also has device with above-mentioned piston engagement, be used for moving above-mentioned piston, order is passed through compression stroke and intake stroke regularly in their cylinder pressures separately, and move along compression stroke around the piston that first 180 ° of parts of above-mentioned housing are made circular movement, the piston of making circular movement around second 180 ° of part of above-mentioned housing moves along suction every trade journey simultaneously, and this valve port system comprises:

Cylinder actinal surface on above-mentioned cylinder body, the radial direction orientation of the spin axis of corresponding above-mentioned cylinder body usually;

A plurality of on above-mentioned cylinder actinal surface the alternate cylinder mouth of rule, the number of above-mentioned cylinder mouth is equivalent to the number of above-mentioned cylinder pressure, and around above-mentioned spin axis annular array, each above-mentioned cylinder mouth is communicated with an above-mentioned corresponding cylinder pressure;

Valve member in above-mentioned housing, it has the roughly valve seat surface of ring-type, with above-mentioned cylinder actinal surface complementation and near thereon,

The invention is characterized in:

The corresponding above-mentioned spin axis of the axis of above-mentioned valve seat is offset towards one of them above-mentioned 180 ° of part of above-mentioned housing prejudicially;

Above-mentioned valve base surface has the interior arris of arc and defines an internal orifice, is communicated with one of them above-mentioned shell channel, also has the arc outer edge and defines a collar extension, is communicated with another above-mentioned shell channel;

The above-mentioned cylinder mouth that is communicated with the cylinder pressure of making circular movement around above-mentioned 180 ° of part of housing, expose facing to above-mentioned internal orifice, above-mentioned valve seat axis is towards these 180 ° of branch skews, the above-mentioned cylinder mouth that is communicated with the cylinder pressure of making circular movement around another above-mentioned 180 ° of parts of housing exposes facing to above-mentioned collar extension;

Above-mentioned valve base surface is circular basically, and interior arris of the above-mentioned arc of above-mentioned valve base surface and outer edge are circular basically;

Above-mentioned cylinder actinal surface and above-mentioned valve base surface are flat basically.

2, according to the valve port system of claim 1, it is characterized in that above-mentioned internal orifice is communicated with above-mentioned discharge route, above-mentioned collar extension is communicated with above-mentioned inlet passage, and its above-mentioned valve seat axis is above-mentioned first the 180 ° part skews towards above-mentioned housing, therefore above-mentioned internal orifice is an outlet, it is accepted from the next pressure fluid of above-mentioned compression stroke cylinder pressure, and it is discharged into above-mentioned discharge route, and above-mentioned collar extension is an inlet, it is accepted from the next fluid of above-mentioned inlet passage, and it is issued in the above-mentioned intake stroke cylinder pressure.

3,, it is characterized in that above-mentioned valve element is placed in the end cap of above-mentioned housing according to the valve port system of claim 2.

4, according to the valve port system of claim 2, it is characterized in that above-mentioned valve element comprises a general cylindrical structural spare, usually coaxial with above-mentioned valve seat axis, and above-mentioned housing its columned dimple of one one section is arranged, usually also coaxial with above-mentioned valve seat axis, also be communicated with above-mentioned housing discharge route, said structure spare generally coaxially is installed in the above-mentioned dimple;

Said structure spare has one generally to be axial fluid discharge route, and by wherein, the one end is communicated with above-mentioned exhaust port, and its other end is communicated with above-mentioned dimple, therefore will be communicated with between above-mentioned exhaust port and the above-mentioned housing discharge route.

5,, it is characterized in that above-mentioned valve element is to be installed in the end cap of above-mentioned housing according to the valve port system of claim 4.

6, according to the valve port system of claim 4, it is characterized in that it has comprised a general ring-type inlet chamber, generally radially round above-mentioned collar extension, cause between above-mentioned collar extension and above-mentioned housing inlet passage communication passage is provided.

7,, it is characterized in that it has comprised a retention device that connects between above-mentioned and above-mentioned valve element, be used for preventing above-mentioned valve element rotating relative to above-mentioned housing according to the valve port system of claim 4.

8,, it is characterized in that it has comprised to be used for maintenance biased member in above-mentioned housing above-mentioned valve element is pushed towards above-mentioned cylinder actinal surface, so that keep above-mentioned valve base surface pressing above-mentioned cylinder actinal surface downwards according to the valve port system of claim 4.

9, valve port system according to Claim 8 is characterized in that above-mentioned maintenance biased member, comprises the pressure of drain in above-mentioned dimple, acts on the cross section of said structure spare.

10, according to the valve port system of claim 3, the above-mentioned active force that keeps down that it is characterized in that above-mentioned maintenance biased member, enough more lifting forces of offset pressure fluid, these fluids are the above-mentioned cylinder mouths that are communicated with from above-mentioned internal orifice with above-mentioned internal orifice, work in the boundary of inflow between cylinder actinal surface and valve base surface.

11, according to the valve port system of claim 10, it is characterized in that it is included in the interior startup spring biased member of above-mentioned housing, press against above-mentioned valve element, be used for above-mentioned valve element towards above-mentioned cylinder actinal surface bias voltage, so that in said pump between the starting period, before above-mentioned hydrodynamic pressure maintenance biased member is enough carried out the effect of keeping down, keep above-mentioned valve base surface pressing above-mentioned cylinder actinal surface downwards.

12, valve port system according to claim 1, it is characterized in that above-mentioned piston displacement device, make above-mentioned piston when above-mentioned first of above-mentioned housing made circular movement with second 180 ° of part, along generally being that sinusoidal track moves, and the regional person that the collar extension place in described of each above-mentioned cylinder mouth is not capped, generally change with such piston motion, cause fluid passage by above-mentioned valve port system, with because the flow that piston motion produces is consistent, thereby be reduced by the hydraulic pulsation that above-mentioned valve port system is discharged into the fluid of above-mentioned housing discharge route.

13,, it is characterized in that above-mentioned piston displacement device comprises the swash plate device according to the valve port system of claim 12.

14, valve port system according to claim 2, it is characterized in that above-mentioned piston displacement device, make above-mentioned piston when above-mentioned first of above-mentioned housing made circular movement with second 180 ° of part, make above-mentioned piston by generally being that sinusoidal wave track moves, and each above-mentioned cylinder mouth in above-mentioned the collar extension place not by coverage area, generally change with such piston motion, cause fluid passage by above-mentioned valve port system, with because the flow that piston motion produces is consistent, thereby be reduced by the hydraulic pulsation that above-mentioned valve port system is discharged into the fluid of above-mentioned housing discharge route.

15,, it is characterized in that above-mentioned piston displacement device comprises the swash plate device according to the valve port system of claim 14.

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