CN85105369A - Reciprocating hydraulic pump - Google Patents
Reciprocating hydraulic pump Download PDFInfo
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- CN85105369A CN85105369A CN 85105369 CN85105369A CN85105369A CN 85105369 A CN85105369 A CN 85105369A CN 85105369 CN85105369 CN 85105369 CN 85105369 A CN85105369 A CN 85105369A CN 85105369 A CN85105369 A CN 85105369A
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Abstract
Reciprocating hydraulic pump is made up of a plurality of parallel continuous cylinder block plug devices, is driven by a cam mechanism (10) that drives by rotating actuator.Constant in order to guarantee lifting rate, adopted three cylinder block plug devices.Three face cams (14) are contained on the axle (13) alternate successively 120 °, and the lifting curve of each face cam (a1, a2, a3) is designed to that the lift sum corresponding to the unit rotation equals the at the uniform velocity lift of section unit rotation in the lift of accelerating sections unit rotation and braking section.
Description
The present invention relates to a kind of a kind of constant volume, pulsating movement free, reciprocating hydraulic pump that drives the cam mechanism of reciprocatory motion parts and use this cam mechanism.
Reciprocating hydraulic pump is to do the action that suction and drain are finished in reciprocatory motion by the plunger in the pump housing, piston or similar parts (following general designation plunger).Particularly since plunger pump compare with the pump of other kind have the pressure-bearing height, the volumetric efficiency height, so it is applied to every field widely.But the discharge opeing of reciprocating hydraulic pump action is intermittent, and discharge opeing speed changes in a very big scope, has produced so-called pulsation thus.If discharge opeing speed resembles and toply always changes said, will produce many adverse influences.Especially it can not be used for processing factory or other require institute if having time in the invariable equipment of feed flow.
Usually reciprocating hydraulic pump is to be made of pressure chamber, cylinder barrel and a plunger that axially moves in cylinder barrel, one end and the fluid intake of pressure chamber join, make the liquid can only the feed pressure chamber by a liquid sucting valve, and the other end and liquid port join, and make the liquid can only the outflow pressure chamber by liquid discharging valve control.For extremely, spherical valve and poppet valve are used as this liquid sucting valve and liquid discharging valve always up till now, carry out the action of switch valve.The unlatching of valve is the pressure control by liquid, and closing is by action of gravity; In other words, it is a kind of so-called one-way valve, only allows direction of liquid to flow, and alternative valve is arranged, and it is spring to be housed promote valve body in one direction in valve mechanism.In this common valve, valve body must drop on the valve seat under the effect of gravity when valve closing, in the valve body dropping process, when valve body during near the corner angle of valve seat, closes the timing that makes valve inaccurate.If the valve closing time-delay, liquid will flow backwards, and causes the discharge opeing rate variation.Equally, because the pressure surge when valve opening also can cause the delay of valve time opening.Both made under the situation of using spring, and also need harder spring to guarantee the stable of valve closing timing, but because the restriction of structure requires such spring should be contained in the valve mechanism, the rigidity of spring again can not be too high.Even passable, like this high spring force conversely will be as the imbibition drag effect on liquid sucting valve or cause the generation cavitation pitting.For liquid discharging valve, has only pressure when the valve body two ends when the discharge opeing stroke satisfies following relationship, that is:
(fluid pressure of drain side)+(spring pressure)＜(fluid pressure of pressure chambers end) valve is just opened, and the result is the pulsation that spring pressure has slowed down discharge opeing speed.
The material of valve body is answered the corrosion of anti-liquid, as adopting stainless steel, pottery, titanium and acidproof nickel-base alloy.But it all is possible that stainless steel can not be said all corrosion, and pottery, titanium and nickel-base alloy can't guarantee that too gently valve normally closes under the effect of its gravity.Both made is to load onto spring to be difficult to also guarantee that spring can satisfy corrosion-resistant and the constant requirement of spring force.For the viscosity working medium, traditional, rely on gravity or be added with the valve opening of limited elastic spring and closing motion slow sometimes because the effect valve of viscosity even can't move.
And in the valve mechanism that drives with the cam parts, spring is used for making the plunger return.Because the characteristic of spring, promptly spring when compressing when loose elastic force be different, so if satisfy the operating conditions of being given just inevitably will be with a very large pressure, it makes idle work increase the while also to have reduced durability.Also can adopt the slot type cam, but, cause the production of pump and assembling all difficult because constant volume oil hydraulic pump precision prescribed is very high, and the gap between cam path and cam is a difficult problem.
The purpose of this invention is to provide that a kind of discharge opeing speed is pulseless, the reciprocating hydraulic pump of feed flow constant flow.
The present invention provides a kind of cam mechanism for the reciprocating mechanism resemble the reciprocating hydraulic pump.
Another object of the present invention is for reciprocating hydraulic pump provides a kind of drive unit, and it can make valve desired, opens and closes accurately in the precise time corresponding with plunger stroke, and can eliminate the various shortcomings of said prior art in the argumentation in front.
The 3rd purpose of the present invention is for reciprocating hydraulic pump provides simple in structure, can steadily and exactly transmit the plunger returning device of restoring force to plunger under any operating mode.
Cam mechanism among the present invention is by being contained on the axle, and three alternate 120 ° face cams constitute, and each face cam all has a profile line that changes by such rule, promptly in the rising section when corner increases, cam lift increases thereupon; Then when corner continued to increase, cam entered the district that descends, and cam lift reduces thereupon.At least in the rising area or the district that descends, all will include an accelerating region and make cam lift quicken to change, constant speed district makes cam lift be linear change and a deceleration area and cam lift is slowed down change.The lift of per unit corner and the lift sum of unit rotation corresponding in deceleration area should equal the cam lift of per unit corner in the constant speed district in accelerating region.
Adopt the reciprocating hydraulic pump of cam mechanism of the present invention to comprise three plunger pumps, its liquid port is connected on the common liquid-discharging tube, and the cam mechanism between drive unit and plunger pump.
Each plunger pump comprises that liquid sucting port, liquid port, one link to each other as the cylinder barrel of pressure chamber with these two valve ports, and one end that axially rotates in cylinder barrel is into and out of the plunger of pressure chamber and swivel bearing cam follower at the plunger the other end.
Three driven parts of cam are connected with three face cams of cam mechanism respectively.Cam mechanism assembles by aforesaid relation.No matter and be all to include with the corresponding rising area of plunger discharge opeing stroke or the district that descends to make cam lift quicken the accelerating region that changes, lift is the constant speed district of linear change and the deceleration area that lift is slowed down and changed.Cam equals the lift of cam in unit rotation, constant speed district in the lift of accelerating region unit rotation and the lift sum in the deceleration area unit rotation.
In this cam mechanism, if the lifting curve of three face cams is superimposed, so at any corner, just any time, the lift of unit rotation all is a constant, is such with regard to the rising area of lift and the district that descends at least.So in the reciprocating hydraulic pump that uses such cam mechanism, be constant by the output flow after three plungers stacks, time to time change not.
If with cam mechanism of the present invention as be used for the drive system of three reciprocating machines, so at least, be in the working stroke or return-stroke of this reciprocating machine, through the per unit cam angle of stack or the stroke of time per unit, free in institute all is invariable.The total discharge of pump remains unchanged at any time.
The characteristics of the drive unit of reciprocating hydraulic pump are to rely on the active force of spring that liquid sucting valve is closed in the present invention.From the initial process to the end of imbibition stroke, the cam that links to each other with plunger driving device overcomes liquid sucting valve spring counter-force and opens liquid sucting valve at plunger.In the short and small time course of plunger discharge opeing stroke near end of a period, the cam that links to each other with plunger driving device has been eliminated the spring pressure that acts on the liquid discharging valve.
When the imbibition stroke began, the liquid sucting valve driving cam overcame acting force of the spring and opens the imbibition valve, and draining valve is closed under the spring force effect simultaneously.At the end of imbibition stroke, the imbibition valve is closed under the effect of spring force.
At the imbibition end of travel, an initial short and small time course of discharge opeing stroke just, the liquid discharging valve drive unit has been eliminated the spring force that acts on the liquid discharging valve.Like this, the imbibition stroke begins, in case the pressure before and after the liquid discharging valve reaches balance, the liquid in the pressure chamber only need overcome the small resistance that is caused by the weight of liquid discharging valve own just can flow out liquid port.This situation will last till the discharge opeing end of travel always, and promptly the imbibition stroke begins.
According to the present invention, in plunger stroke,, can obtain the time opening of imbibition, draining valve respectively and close according to required time.This is that the reciprocating hydraulic pump of viscous liquid is particularly useful to working medium.
The plunger returning device of reciprocating hydraulic pump of the present invention comprise several be used for collecting by a plurality of plunger pumps supply with, have the liquid liquid collecting room of certain pressure.These liquid collecting room communicate with one another.
In the liquid collecting room of a plurality of plunger pumps, those liquid that are in the collection hydraulic chamber of plunger pump of discharge opeing stroke are forced in the liquid collecting room of those plunger pumps that also are in the imbibition stroke, are then pushed back corresponding plunger again.
When a plunger during in working stroke, liquid is forced out corresponding liquid collecting room and enters and the corresponding liquid collecting room of plunger that is in the reversion journey.And the total amount of liquid in all liquid collecting room and mutual connecting pipeline thereof all is invariable at any time, so that the returning movement of plunger steadily carry out.As for the pressure of fluid, guarantee that the required minimum pressure of plunger return is enough, and, can not produce caused energy loss when resembling the use spring because this pressure is constant in institute if having time.Since act on the surface pressure on the cam follower, constant all the time in the plunger returning movement, so can not cause concentrated wear.Therefore, this mechanism is rational.
Fig. 1 is the cam lifting curve of cam mechanism of the present invention, and y coordinate is represented the lift of cam follower, and abscissa is represented camshaft degree.
Fig. 2 is the flow curve figure of a traditional single-action reciprocating oil hydraulic pump.Y coordinate is represented output flow, and abscissa is a camshaft degree.
Fig. 3 is the flow curve of traditional three plunger single-action reciprocating oil hydraulic pumps similar to Fig. 2.
Fig. 4 is the planimetric map of representative three plunger single-action reciprocating oil hydraulic pumps of the present invention.
Fig. 5 be reciprocating hydraulic pump shown in Figure 4 along a plunger axis to cut-away view.
Fig. 6 is the partial enlarged drawing that comprises the liquid sucting valve door section of reciprocating hydraulic pump shown in Figure 5.
Fig. 7 is the enlarged view of the liquid sucting valve valve seat shown in Fig. 6.
Fig. 8 is the enlarged view of follower lever shown in Figure 6.
Fig. 9 is the partial enlarged drawing that reciprocating hydraulic pump shown in Figure 5 comprises draining valve.
Figure 10 is the enlarged view of liquid discharging valve head shown in Figure 9.
Figure 11 is the enlarged view of follower lever shown in Figure 9.
Figure 12 is the micro-adjusting mechanism shown in Fig. 5 (from the supporting axle head).
Figure 13 is shown in Figure 12, along the cut-away view of A-A line.
Figure 14 is the lifting curve figure of three cams of reciprocating hydraulic pump shown in Figure 5.Abscissa is represented corner, and y coordinate is represented lift.
At first, cam mechanism once is described.
Fig. 1 is cam lifting curve figure.Y coordinate is represented the lift H of cam follower, and abscissa is represented camshaft degree (θ=wt).For better understanding its speed separately, they use solid line respectively, and dot and dash line and double dot dash line are represented.The profile line of face cam guarantees that the lift of cam follower is by this curvilinear motion.
Each bar curve of lifting curve a1, the a2 of face cam and a3 all has a rising area, in this zone along with the increase of corner, lift increases (with regard to the a1 curve, this zone is that θ=0 is ° to 180 °), with the district that descends, in this zone, lift reduces (to same curve, this zone is that θ=180 are ° to 360 °) along with the increase of corner.Comprise an accelerating sections morning in the district, lift is quickened to increase (with regard to lifting curve a1 betwixt, this section is that θ=0 is ° to 60 °), a constant speed section, lift is linear change (for same curve therebetween, this section is that θ=60 are ° to 120 °), with a braking section, lift is slowed down variation (to same curve in this section, this section is that θ=60 are ° to 120 °), with a braking section, lift slow down to change (to same curve, this section is θ=120 °～360 °) in this section.In illustrated curve, the rising area and the district that descends are for axisymmetric.As can be seen from the figure, the shape of lifting curve a1～a3 is identical, and just phase place differs from 120 ° mutually, and crossing form has two kinds, and per 60 ° of conversion once (are shown by I among the figure and II respectively).
Engineering design is exactly lift Δ h1 that makes at the per unit corner Δ θ on the accelerating sections and the lift Δ H that equals per unit corner Δ θ on the constant speed section in the lift Δ h2 sum of per unit corner Δ θ on the braking section, no matter be in other words on the accelerating sections or all be like this on the braking section or on two sections, i.e. relation △ h
1+ Δ h
2=Δ H is correct in any position of area I point.Promptly under this condition, with regard to the rising area, the lift of per unit corner is time-independent constant, considers it also is the same from whole cam mechanism.
In addition, such design can only be used for the rising area of lifting curve figure or the district that descends, and under the situation of illustrated axisymmetric cam, when the cam counterrotating, the performance of cam also is the same.For example this cam mechanism is applied to a reciprocating hydraulic pump, the back will be discussed, with the rising area of curve or the district that descends corresponding to the discharge opeing stroke of pump, and other imbibition stroke corresponding to another pump.Using the design of discussing previously like this is that the discharge opeing stroke corresponding to a pump is distinguished in a rising and decline, just can obtain constant, a pulseless output flow.
Below just specifically discuss reciprocating hydraulic pump according to this principle design.In conventional art, reciprocating hydraulic pump is driven by a crank mechanism, because the angular velocity of output flow and crankshaft is not proportional, so cause pulsation, the situation of single-action reciprocating oil hydraulic pump is shown in Fig. 2, and abscissa is represented the crank angle, and y coordinate is represented output flow.Flow increases in the crank angle range of θ=90 ° gradually in θ=0 °, reaches maximum value at 90 ° of corners, then, reduces gradually.And in θ=180 ° in the plunger reversion journey of θ=360 °, output flow is 0, ° begins discharge opeing again from θ=360.The average output flow of working stroke and return stroke is represented with a dot and dash line.So-called three plunger single-action reciprocating oil hydraulic pumps have three plungers, 120 ° of crank angles, space, and its curve is shown in Fig. 3.
Have three plunger pumps and be shown in Figure 4 and 5 by the reciprocating hydraulic pump that cam mechanism 10 drives.
Each plunger pump comprise 21, one cylinder barrels 22 in a pressure chamber and one in cylinder barrel 22 in axial sliding, the one end can be into and out of the pressure chamber 21 plunger 23.Pressure chamber 21 is formed by the lid 24 that is positioned at cylinder barrel 22 ends, and pressure chamber's one end and liquid sucting port 26 join, and can only flow to pressure chamber 21 by the liquid sucting valve controlling liquid.The other end links to each other with liquid port 28 by liquid discharging valve 27, and liquid discharging valve only allows liquid to flow out pressure chamber 21.Liquid port 28 is connected with a common conduit or liquid-discharging tube (not having picture among the figure).
Returning place force is produced by spring can resembling usually.Further, for the many bodies pump that adopts a plurality of plunger pumps,, also can adopt the method that all empty chambers are interconnected by pipeline to reach same function as example herein.One end of pipeline is connecting top said hydraulic power, the other end sealing.In this case, can be with an oil pump as hydraulic power, and adorn a relief valve at the other end of pipeline.And then, if can guarantee that plunger always equals the displacement of plunger at return stroke in the displacement of working stroke at camshaft degree arbitrarily.The other end of the pipeline that joins with empty chamber just can be closed so, and this also will discuss in the back.
Above-mentioned reciprocating hydraulic pump is work like this.
When 13 rotations of power plant (not having picture among the figure) beginning drive cam shaft, three cam followers are according to the described alternate 120 ° lifting curve motion of Fig. 1.When a certain plunger is in working stroke, discharge opeing stroke just, plunger is as shown in the figure to left movement, and liquid is blocked by one-way valve 25 to the backflow of liquid sucting port.So the liquid in the pressure chamber enters total liquid-discharging tube by one-way valve 27 and liquid port 28.Liquid is pressed into total drain pipe from plunger 23.When plunger is in return stroke, when moving right as shown in the figure, liquid is inhaled into pressure chamber 21 by one-way valve 25.At this moment one-way valve 27 stops liquid to be back in the pressure chamber 21 by liquid port 28.
Be described in detail the relation between the motion of cam mechanism 10 and plunger pump now.Situation shown in Figure 5 is the state of θ=0 ° corresponding to lifting curve figure overhead cam corner among Fig. 1.When camshaft 13 from then on situation begin, rotation in a direction indicated by the arrow, first plunger by lifting curve a1 represents in 60 ° of cam angles of beginning, moves to left shown in Figure 5 with accelerated mode, in 60 ° of corners subsequently, plunger is to same direction, with movement at the uniform velocity, and then, in 60 ° of corners afterwards, plunger reaches the terminal point of this trip with retarded motion on same direction.Second and the 3rd plunger will lag behind successively 120 ° and move in the same way.
In first interval I of 60 °, when first plunger was in the acceleration working stroke, second plunger that Qu Shengcheng line a2 represents was in the constant speed stroke, and the 3rd plunger of being represented by lifting curve a3 is in the deceleration return stroke.On 60 ° of interval II subsequently, first plunger enters the constant speed working stroke, and at this moment second plunger is in the deceleration return stroke, and the 3rd plunger is in the acceleration return stroke.When consideration work (discharge opeing) stroke, what the constant speed stroke of a visible plunger and other two plungers mixed returns the per 60 ° of conversion of a stroke once.
In 60 ° of intervals in II zone shown in Figure 1, have only the plunger corresponding to be in the discharge opeing stroke with lifting curve a1, flowmeter is shown Δ Q: Δ θ.In 60 ° of intervals that another is represented by I, total lifting rate is determined by the lifting rate of other two plungers.Flowmeter is shown (Δ q
1+ Δ q
2): Δ θ.To as described in the cam mechanism, the profile line of each face cam all makes the lift Δ h of on lifting curve figure accelerating sections per unit cam angle as the front
2Lift Δ h with per unit cam angle on the braking section
2Sum equals the lift Δ H at constant speed section per unit cam angle.Thus, relation △ Q=Δ q
1+ Δ q
2Set up, and the flow of reciprocating hydraulic pump is always constant.
The plunger return mechanism of reciprocating hydraulic pump is discussed now.In the reciprocating hydraulic pump represented by Fig. 4 and Fig. 5, if the rising area of the profile line of each face cam 14 and the district that descends are about axisymmetric, the plunger movement amount that is in constant speed section stroke so just equals two amounts of rotation sums that are in the plunger of return stroke in addition, and two plunger movement amounts that are in working stroke just equal the plunger movement amount that another is in the constant speed stroke.Therefore, in this case, because the liquid that plunger is returned just flows between three empty chambers 39 and flows out, amount remains unchanged theoretically, does not promptly increase also and does not reduce, so the other end of pipeline can be closed.Yet, in practice, consider and leak or other suchlike problem, can the afford redress liquid of these leakages of the pump of a minimum capacity.As hydraulic power, except pump, also can adopt the mechanism of topping up again of accumulator or use spring piston formula.Fig. 4 specifically expresses three the empty chambers 39 corresponding with three plungers 23 and is linked together mutually by the pipeline 15 that is connected on the hole 40.One end and the hydraulic power of pipeline 15 join as oil pump or accumulator, and the other end of pipeline 15 connects with relief valve 17, (if hydraulic power is an accumulator, then not needing this valve).So chamber 39 always is full of pressured fluid.These pressured fluids act on the end face 38 of guide piston 33, produce a return force guide piston 33 and plunger 23 are trended towards to the right-hand motion shown in the figure.When the pressure of the area of determining end face 38 and pressure liquid, guarantee to making plunger 23 return required least limit returning place force.
In addition, it is commonly used with spring plunger being returned, but because the characteristic of spring, in spring when elongation,, the pressure during with compression was different, for satisfying the requirement of all conditions, just inevitably will use quite hard spring, thereby cause unnecessary energy consumption, and durability to be considered also.The slide block type cam also can use, but for making pump liquid volume constant, the precision that matching requirements is very high, but the gap between cam path and the driven member becomes a problem, comprising make, the difficulty of assembling.
Adopt liquid double-action form not only can eliminate the shortcoming of old-fashioned structure, also have following advantage:
When some plungers were in working stroke, liquid was forced out corresponding grease chamber and enters two other grease chamber respectively, and corresponding plunger is returned.Therefore three grease chambeies and the total amount of liquid that connects in their pipeline be constant, make the return movement of plunger steady.
With regard to fluid pressure, be enough to the least limit pressure that guarantees that plunger returns, because its constant always, do not exist to resemble the energy loss that produces the spring.Because in plunger return process, the surface pressure that acts on the cam follower is invariable, avoided the concentrated wear of cam.Therefore, this mechanism is rational.
According to various operating conditions (comprise high-speed motion, low-speed motion and be used for high viscosity liquid), by the control relief valve, for reach best effort move desired fluid pressure can be rapidly, obtain easily.
Since with can be controlled by the corresponding fluid pressure of plunger-actuated discharge opeing pressure, thereby can control from the liquid that cylinder barrel leaks.For example, if the pressure of liquid in the pressure chamber is decided to be half of discharge opeing pressure, ullage is let out this liquid to the situation of atmosphere and is reduced half.In this case, if use proper lubrication oil as making the liquid of plunger return lubricate plunger, the durability of quantitative hydraulic pump will obtain very big improvement so.
Certainly, can between plunger and return piston, set up a normal pressure band, the lubricant oil in working liquid body in the pressure chamber and the empty chamber is isolated fully, in case the liquid that stopping leak leaks mixes.
Under the situation of high temperature, by circulating in the effect that the liquid that plays the return effect around the plunger can play the cooling plunger, except cooling off plunger, can prevent heat from plunger and cylinder barrel to other parts transmission, thereby also protected other parts.
Valve actuator is discussed now, and as shown in Figure 6, the liquid sucting valve between liquid sucting port 26 and pressure chamber 21 is made up of the valve rod 41 and the ring-type valve seat 43 of an end band cone type valve head 42.Valve rod 41 passes the circular hole on the valve seat 43, at the other end of bar screw thread 44 is arranged.In screw thread 44 parts a spring seat 45 and a retainer nut 46 are housed.Valve rod 41 is promoted valve head 42 is pressed on the valve seat 43 by a spring 48 that is contained between spring seat 45 and the lock-on connection 47.Lock-on connection 47 usefulness screw threads are tightened on the lid 24, and form a passage 49 between liquid sucting valve 25 and liquid sucting port 26.In addition, as can see from Figure 7, valve seat 43 has a polynary guide way 50 to provide radially-directed for valve head 42.
Rod member 52 1 ends are connected with jam plate 31 by pin 51.The other end is ratchet 54 and the interlock of feed liquor valve driving cam.There is a protruding tooth 55 to contact (see figure 8) at the middle part of bar with retainer nut 46.The axle 56 that cam 53 is housed is supported by pair of brackets 57, and links and run-in synchronism by the camshaft 13 of transmission device (not having expression among the figure) with cam mechanism.Transmission device comprises sprocket wheel and chain, and promptly when cam 13 rotated a circle, axle 56 also rotated a circle.
The profile that liquid sucting valve drives protruding axle is big by a diameter, accounting for nearly half the part 58(of cam circumference, it is corresponding with the imbibition stroke of plunger 23) and a diameter is less, nearly half part 59 formations of circumference that account for that cam is left, this part is corresponding with the discharge opeing stroke of plunger 23.Comprise that than major diameter part 58 an oblique line part 60 makes itself and small diameter portion 59 level and smooth being linked together.Oblique line part 60 correspondences the terminal of imbibition stroke, that is to say corresponding the top of discharge opeing stroke, step 61 of the discontinuous part formation of 58 and 59 two-part.
Liquid discharging valve 27 is between pressing chamber 21 and the liquid port 28, sees Fig. 9.It is to be combined by a circular cone valve head 62 and a ring-type valve seat 63.Can see that by Figure 10 the prolongation 64 of valve head 62 has several guiding ribs 65 that radially extend.Guiding rib 65 is the hole sliding contacts with valve seat 63, thereby provides radially-directed for valve head 62.Valve rod 68 passes lock-on connection 67, and it uses scyewed joint on lid 24, and forms passage at liquid valve 27 and 28 of liquid outlets.Valve rod 68 can endwisely slip, and coaxial with valve head 62.One end of valve rod 68 is equipped with a spring seat 69 with scyewed joint.Be contained in the extension part 31 of fixed plate 31 ' on support plate 70 adjusting screw 71 of screwing on screw thread is arranged, spring 72 is contained between adjusting screw 71 and the spring seat 69 valve rod 68 is pushed to the below shown in the figure.The effect of spring 72 is to promote valve head 62 by valve rod 68 to be pressed on the valve seat 63.
One end of lever 74 by pin 73 be connected in extension part 31 ' on, the other end becomes ratchet shape to contact with liquid discharging valve driving cam 75, the middle part has a projection 77 to contact (seeing Figure 11) with spring seat 69.Cam 75 is housed on the axle 79, and by 78 supportings of a pair of support plate, the camshaft 13 by a drive unit (not shown) driving cam means of being made up of sprocket wheel and chain rotates synchronously, that is to say, when camshaft 13 rotated a circle, axle 79 also rotated a circle.
The profile of liquid discharging valve driving cam 75 comprise account for the bigger section 80(of cam 75 a circumference diameter mostly it be corresponding with the discharge opeing stroke of plunger 23) and account for (corresponding) minor diameter section 81 of cam 75 circumference remainders with the imbibition stroke of plunger 23, enlarged diameter section 80 is than reduced diameter section 81 big θ angles.The size at θ angle is decided by the rotating speed of cam 75 and the discharge opeing pressure of oil hydraulic pump.The initial segment 82 of enlarged diameter section 80 and level and smooth the connecting of reduced diameter section.And with the corresponding section in discharge opeing stroke top, the initial end of imbibition stroke just, 80 and 81 two sections are discontinuous, and a step 83 is arranged.
Figure 12 and Figure 13 represent the micro-adjusting mechanism of each valve opening and timeing closing.Each liquid sucting valve and liquid discharging valve all have such micro-adjusting mechanism, can adjust the opening and closing timing of each valve respectively.Because these mechanisms all are the same, so only narrate a micro-adjusting mechanism of liquid sucting valve 25 here.Figure 12 represents to be equipped with the end of the axle of liquid sucting valve driving cam 53.Be contained in loosely on the axle 56 by chain and the sprocket wheel 85 that the sprocket wheel 84 that is contained on the camshaft 13 of cam mechanism links.Sprocket wheel 85 is one with adjustment disk 86, and adjustment disk 86 is clamped together itself and a disk 87 that is keyed on the axle 56 by bolt.The hole 89 of passing bolt 88 on disk 87 is a slotted hole along circumferencial direction.Have a breach 91 on the adjustment disk 86, have a pin 90 to be contained on the disk 87 in indentation, there, two opposed adjusting screw 92 are contained on the circumferential edges at breach 91 two ends, and pin 90 is in the centre of these two adjusting screw.After bolt 88 is loosened,, change its axial position and just can adjust relative position, angle between adjusting disk 86 and the disk 87 by rotation adjusting screw 92.Like this, just changed the angle of swing of axle 56, changed the opening and closing timing of liquid sucting valve 25 in other words with respect to the stroke of plunger 23 with respect to camshaft 13.That is to say, can adjust the opening and closing timing of three plungers (concerning treble ram pump) simultaneously.Similarly, also can adjust the opening and closing timing of liquid discharging valve 27 with respect to plunger 23 strokes.If open an otch at cylindrical 93 places that regulate disk 86, and engrave graduation line accordingly on the outer rim 94 of disk 86, so, the fine setting actuating is carried out with regard to easier.
Figure 14 has described the movement process of the reciprocating hydraulic pump cam driving gear of arranging by foregoing mode.In addition, the lifting curve a among Figure 14, b, c correspond respectively to plunger actuation cam 14, liquid sucting valve driving cam 53 and liquid discharging valve driving cam 75.
State portion shown in Fig. 5, Fig. 6 and Fig. 9 is corresponding among Figure 14, the working condition when θ=0 °, and promptly the imbibition stroke finishes, and the discharge opeing stroke is about to begin.At this moment, liquid sucting valve 25 has been closed, though and liquid discharging valve 27 has not born the impacting force of spring 72 because in the effect of this valve pressure at two ends difference, liquid discharging valve 27 still is in closed condition.
At first, the discharge opeing stroke lasts till that always camshaft 13 turns over till 180 °.By Fig. 6 and 14 as can be seen, in this process of 180 °, the lift of liquid sucting valve driving cam 53 is 0.In other words, promptly the ratchet 53 of Bars bar 52 always with minor diameter section 59 engagement of cam 53, do not make valve rod 41 produce displacements.So liquid sucting valve 25 is still closed.On the other hand, from Fig. 9 and 14 as can be seen, in this interval of 180 °, liquid discharging valve driving cam 75 is remaining the lift of hc.Be Bars bar 74 ratchet 76 always with enlarged diameter section 80 engagement of cam.So liquid discharging valve 27 does not bear the pressure of spring 72.In addition, at the initial part of this discharge opeing stroke, along with plunger 23 motions, pressure in pressure chamber 21 increases gradually, in case the fluid pressure of its pressure and valve head 62 another sides reaches balance, liquid just will promote valve head 62 and open, and liquid 21 flows to liquid port 28 from the pressure chamber.The resistance of this moment only is the small weight of valve head 62.
When running to discharge opeing stroke top, the step part 83 of liquid discharging valve driving cam 75 makes the ratchet 76 of bar 74 and expanded diameter section 80 break away from engagement, and has fallen on the minor diameter section 81.Thereby bar 74 is descended, and valve rod 68 moves downward under the effect of spring 72, and valve head 62 is pressed on the valve seat 63, as shown in Figure 9.So liquid discharging valve is fully closed immediately.Simultaneously, the ratchet of bar 52 54 breaks away from the minor diameter section 59 of liquid sucting valve driving cam 53, and with oblique line 60 engagements, then the beginning of imbibition stroke of 180 ° of scopes that Here it is.When the imbibition stroke began, liquid sucting valve driving cam 53 made bar 52 overcome the pressure of spring 48, has advanced valve rod 41 gradually, makes valve head 42 lift off a seat 43.Thus, liquid sucting valve 25 is opened, liquid flows to pressure chamber 21 by liquid sucting port 26.As seen from Figure 14, cam 59 is keeping the ratchet 54 of bar 52 to be in lift hb in the feed liquor stroke, and liquid sucting valve is opened always.
When imbibition stroke during near terminal, liquid discharging valve driving cam 75 lifts bar 74 in one of the discharge opeing stroke terminal little section (show be called the θ angle with the corner scale).Because the convex portion 77 of bar 74 contacts with spring seat 69, make upwards (shown in figure) motion of valve rod 68 so overcome the pressure of spring 72, thereby eliminated the pressure of the spring 72 that acts on the valve head 62.At this moment, the downstream of valve head 62, promptly liquid port 28 here, the liquid of being discharged by front discharge opeing stroke is still keeping its original pressure.And in the upstream of valve head 62, promptly in the pressure chamber 21 here, liquid produces negative pressure owing to the imbibition stroke; Therefore, because the pressure difference on valve head 62 both sides, valve head 62 is still contacted with valve seat 63, terminal at the imbibition stroke, the step part 61 of liquid sucting valve driving cam 53 breaks away from the ratchet 54 of bar 52 and expanded diameter section 58, and fall on the minor diameter section 59, thereby make bar 52 get back to state shown in Figure 6.The result is under the pressure effect of spring 48, and liquid sucting valve 25 is closed immediately.
Like this, as shown in figure 14, in the discharge opeing stroke of plunger 23, the lift shown in the lifting curve b of liquid sucting valve driving cam 53 is 0, and the lifting curve C of liquid discharging valve driving cam 75 keeps the lift of hc, when the imbibition stroke begins, the lift of liquid sucting valve driving cam 53 is hb, and liquid discharging valve driving cam 75, lift in the early stage is 0, but a small angle theta place before the imbibition stroke terminal, lift has reached hc again.As previously mentioned, the timing of cam is that the camshaft 13 of the cam mechanism that moved reciprocatingly by drive plunger 23 makes the axle 56 of cam 53 and the axle 78 of cam 75 obtain with its run-in synchronism by sprocket wheel and chain drive.
As previously mentioned, because spring 48 and 72 is the outsides that are placed on valve mechanism, so without limits to the device space of spring.And as spring is placed in the valve mechanism, its device space will be restricted.Like this, the design of spring ratio is easier to, to keep rapid, accurate throttle down.And,, thereby during the dispatch corrosive liquids, concerning valve mechanism, only need consideration valve head and valve seat and corrosion resistance because spring 48 contact with liquid with 72.
If this valve actuator is used for molten surely hydrops press pump to avoid the pulsation of discharge opeing speed, as mentioned above, this device will be by guaranteeing the capacity constant of suction, liquid discharging valve accurate opening and closing improvement oil hydraulic pump.
Specific to this paper is exactly by making valve driving cam and plunger actuation cam control the opening and closing of suction, liquid discharging valve synchronously.Like this, can design a kind of valve driving cam profile too, make the opening degree of each valve, at arbitrary plunger position, all be directly proportional with fluid flow, and then, the opening and closing timing of suction, liquid discharging valve and the interlock of plunger motion, except that above-mentioned specific design, can also make following imagination:
(a) based on the method for guiding valve.
I, according to the distributing valve of planar reciprocating.
II, according to the rotation planar surface distributing valve.
III, based on the distributing valve of cylindrical body surface of revolution.
IV, based on the distributing valve of circular cone surface of revolution
(b) realize the method for electric timing with solenoid valve
(c) by hydraulic pressure or the pneumatic method of timing indirectly of carrying out
(d) pass through mechanical measure or microcomputer method according to oil hydraulic pump rotating speed automatic timing
As example of the present invention, above detailed argumentation the cam mechanism that constitutes by three face cams and use this cam mechanism, and contain the reciprocating hydraulic pump of three cylinder barrel-plunger assemblies.Based on thought of the present invention and scope, can obtain other modification and improvement.
Especially can think that the present invention can be applied to the cam mechanism that comprises three above face cams particularly and form.Equally, reciprocating hydraulic pump can be made of the cylinder barrel-plunger body more than three.
Claims (18)
1, by being contained on the same axis, the cam mechanism that three alternate successively 120 ° face cams are formed, the lifting curve of its each face cam all includes a rising area, and the increase lift along with cam angle in this district also increases; With the district that descends, when the corner of face cam increased, lift reduced in this district, no matter be said rising area, all there is an accelerating sections in the district that still descends, quickens to change in this section lift; A constant speed section is linear change in this section lift; With a braking section, the lift deceleration changes in section.And in this structure, the lift sum of the lift of its accelerating sections unit rotation and braking section unit rotation equals the lift of its constant speed section unit rotation.
2,, be characterised in that its rising area is axisymmetric according to claim 1 described cam mechanism.
3,, be characterised in that its rising area and decline district are asymmetric according to the described cam mechanism of claim 1.
4, reciprocating hydraulic pump is connected on three plunger pumps on the house steward and one by its liquid port and places the cam mechanism between driving mechanism and the plunger pump to form.Each plunger pump comprises a liquid sucting port, a liquid port, cylinder barrel with the pressure chamber that joins with these two mouths, one can be in cylinder barrel in axial sliding, the one end can pass in and out the plunger of pressure chamber, cam follower that can be rotated to support on the plunger the other end and one promote the device that plunger closely contacts cam follower all the time with cam.Above said cam mechanism be contained on the common shaft by three, 120 ° the face cam of joining is successively formed.The lifting curve of each face cam all has a rising area, in this district, cam angle increases, lift increases and the district that descends thereupon, increases lift at this district's cam angle and reduces, in the said rising area and these two districts, district that descend, a district corresponding to plunger discharge opeing stroke comprises the accelerating sections that a lift acceleration changes, and a lift is constant speed section and braking section that lift is slowed down and changed of linear change.The lift of its accelerating sections unit rotation of this cam and the lift sum of braking section unit rotation equal the lift of constant speed section unit rotation.
5,, be characterised in that its device that promotes plunger is the hydraulic chamber that is filled with certain pre-press liquid in each plunger pump according to the reciprocating hydraulic pump of claim 4.All hydraulic chambers all communicate with one another.
6, be characterised in that according to claim 5 described reciprocating hydraulic pumps its said hydraulic chamber all links to each other with the pipeline that one one termination hydraulic power.
7, be characterised in that according to said reciprocating hydraulic pump in the claim 6 its described hydraulic power is an accumulator.And the other end of aforementioned pipeline seals.
8, relief valve is equipped be characterised in that according to said reciprocating hydraulic pump in the claim 6 described hydraulic power is a pump, and the other end of said pipeline.
9, be characterised in that according to claim 4 said reciprocating hydraulic pumps comprising a valve actuator makes the opening and closing of liquid sucting valve and liquid discharging valve regularly synchronous with plunger motion.
10, be characterised in that according to said reciprocating hydraulic pump in the claim 4 its described valve actuator comprises that promotes the spring that liquid sucting valve is closed, a liquid sucting valve driving cam that links with drive unit, initial to the process that stops from plunger imbibition stroke, the pressure that overcomes the said spring in front is opened liquid sucting valve, and comprise a discharge opeing driving cam that links with drive unit, from one of plunger discharge opeing stroke short and small time to the process of discharge opeing stroke end, make liquid discharging valve unload pressure except spring.
11, according to said reciprocating hydraulic pump in the claim 10 be characterised in that the supporting axle of described liquid sucting valve driving cam and liquid discharging valve driving cam all be by sprocket wheel and chain transmission and said drive unit the axle link synchronously.
12, by a liquid sucting port, a liquid port, cylinder barrel with a high pressure chamber that links to each other with top two mouths, one can be slided in cylinder barrel, and make the plunger in one end institute precession hyperbaric chamber, the reciprocating drive unit of drive plunger, one places the liquid sucting valve between liquid sucting port and the pressure chamber, and a reciprocating hydraulic pump that places the liquid discharging valve between pressure chamber and the liquid port to form, it is inhaled, the opening and closing of liquid discharging valve are to reach by the improvement to valve actuator with cooperating of plunger motion regularly.
13, the valve actuator according to the reciprocating hydraulic pump described in the claim 12 comprises that promotes the spring that liquid sucting valve is closed, one links with drive unit, initial during to the process that stops from plunger imbibition stroke, the pressure that overcomes the said spring in front makes the liquid sucting valve driving cam of liquid sucting valve unlatching, and comprise that one and drive unit link, from one of plunger discharge opeing stroke short and small time to the process of discharge opeing stroke end, make the pressure of liquid discharging valve removal spring.
14, it is characterized in that according to the valve actuator of the reciprocating hydraulic pump described in the claim 13 liquid sucting valve drive cam shaft and liquid discharging valve drive cam shaft all are to link up synchronously through a transmission device of being made up of sprocket wheel and chain and the rotating shaft of drive unit.
15, placing between drive unit and the plunger pump by multi plungerpump and one, make in the reciprocating hydraulic pump of the imbibition of pump and the cam mechanism composition that the discharge opeing circulation changes in succession, each plunger pump all comprises a liquid sucting port, a liquid port, tube with the pressure chamber that links to each other with these two mouths, one can be in cylinder barrel axially slide, plunger that the one end can pass in and out the pressure chamber and one promote plunger makes cam follower be pressed in plunger return mechanism on the cam all the time.The improved of plunger return mechanism is characterised in that: this plunger return mechanism a hydraulic chamber that certain pre-press liquid is arranged is abrim all arranged, and all hydraulic chambers interconnects all in each plunger pump.
16, be characterised in that according to the plunger return mechanism of the reciprocating hydraulic pump described in the claim 15 pipeline that the hydraulic chamber of its indication is linked to each other with fluid supply by one one end is linked together.
17, the plunger return mechanism according to the reciprocating hydraulic pump described in the claim 16 is characterised in that the hydraulic power of its indication is an accumulator, and the other end of said pipeline seals.
18, the plunger return mechanism according to the reciprocating hydraulic pump described in the claim 16 is characterised in that its said hydraulic power is an oil hydraulic pump, and the other end of said connecting pipeline is equipped with a relief valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 85105369 CN85105369A (en) | 1985-07-13 | 1985-07-13 | Reciprocating hydraulic pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 85105369 CN85105369A (en) | 1985-07-13 | 1985-07-13 | Reciprocating hydraulic pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN85105369A true CN85105369A (en) | 1987-01-21 |
Family
ID=4794431
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 85105369 Pending CN85105369A (en) | 1985-07-13 | 1985-07-13 | Reciprocating hydraulic pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN85105369A (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102022301A (en) * | 2010-11-26 | 2011-04-20 | 大连依利特分析仪器有限公司 | Three-cam shaft for large-flow high-pressure constant flow pump |
| CN103423120A (en) * | 2013-08-21 | 2013-12-04 | 利穗科技(苏州)有限公司 | Three-plunger high-pressure pump |
| CN103869030A (en) * | 2012-12-18 | 2014-06-18 | 北京普源精电科技有限公司 | Liquid chromatograph having series-connection plunger pump and control method thereof |
| CN104879286A (en) * | 2015-05-19 | 2015-09-02 | 成都皓瀚完井岩电科技有限公司 | Multi-layer radial plunger micro-metering pump |
| CN105422405A (en) * | 2015-12-28 | 2016-03-23 | 中国科学院苏州生物医学工程技术研究所 | Metering pump |
| CN107051832A (en) * | 2015-11-25 | 2017-08-18 | 艾格赛尔工业公司 | The transfer pump of liquid mulch application system |
| CN107429643A (en) * | 2015-04-13 | 2017-12-01 | 三井造船株式会社 | Fuel supply system and fuel feeding method |
| CN107889516A (en) * | 2015-02-23 | 2018-04-06 | 朴俊赫 | A kind of pesticide sprayer bidirectional piston efficient pump |
| CN108350868A (en) * | 2015-08-13 | 2018-07-31 | 温杜姆工程公司 | Improved flexible hose pump and associated method |
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-
1985
- 1985-07-13 CN CN 85105369 patent/CN85105369A/en active Pending
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102022301B (en) * | 2010-11-26 | 2014-05-14 | 大连依利特分析仪器有限公司 | Three-cam shaft for large-flow high-pressure constant flow pump |
| CN102022301A (en) * | 2010-11-26 | 2011-04-20 | 大连依利特分析仪器有限公司 | Three-cam shaft for large-flow high-pressure constant flow pump |
| CN103869030A (en) * | 2012-12-18 | 2014-06-18 | 北京普源精电科技有限公司 | Liquid chromatograph having series-connection plunger pump and control method thereof |
| CN103423120A (en) * | 2013-08-21 | 2013-12-04 | 利穗科技(苏州)有限公司 | Three-plunger high-pressure pump |
| CN107889516A (en) * | 2015-02-23 | 2018-04-06 | 朴俊赫 | A kind of pesticide sprayer bidirectional piston efficient pump |
| CN107429643A (en) * | 2015-04-13 | 2017-12-01 | 三井造船株式会社 | Fuel supply system and fuel feeding method |
| CN107429643B (en) * | 2015-04-13 | 2019-10-15 | 三井易艾斯机械有限公司 | Fuel supply system and fuel feeding method |
| CN104879286A (en) * | 2015-05-19 | 2015-09-02 | 成都皓瀚完井岩电科技有限公司 | Multi-layer radial plunger micro-metering pump |
| CN104879286B (en) * | 2015-05-19 | 2017-02-01 | 成都皓瀚完井岩电科技有限公司 | Multi-layer radial plunger micro-metering pump |
| CN108350868A (en) * | 2015-08-13 | 2018-07-31 | 温杜姆工程公司 | Improved flexible hose pump and associated method |
| CN107051832A (en) * | 2015-11-25 | 2017-08-18 | 艾格赛尔工业公司 | The transfer pump of liquid mulch application system |
| CN107051832B (en) * | 2015-11-25 | 2021-03-12 | 艾格赛尔工业公司 | Supply pump for liquid blanket application system |
| CN105422405A (en) * | 2015-12-28 | 2016-03-23 | 中国科学院苏州生物医学工程技术研究所 | Metering pump |
| CN110423132A (en) * | 2019-08-14 | 2019-11-08 | 许昌市森洋电子材料有限公司 | A kind of semiconductor refrigeration member welder |
| CN110423132B (en) * | 2019-08-14 | 2023-12-22 | 许昌市森洋电子材料有限公司 | Semiconductor refrigeration piece welding set |
| CN110821772A (en) * | 2019-11-15 | 2020-02-21 | 吉林大学 | High-pressure non-pulsation hydraulic pump |
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