CN101487458A

CN101487458A - Axial variable displacement plunger pump of swash plate

Info

Publication number: CN101487458A
Application number: CNA2009100013829A
Authority: CN
Inventors: 张全根
Original assignee: Individual
Current assignee: Individual
Priority date: 2008-07-14
Filing date: 2009-01-05
Publication date: 2009-07-22
Anticipated expiration: 2029-01-05
Also published as: CN101487458B

Abstract

The invention provides a power element used in a hydraulic transmission system. A swash plate variable axial plunger pump consists of a swash plate, a plunger cylinder body and a port plate. The angle-variable swash plate rotates with a drive rotating shaft which is connected by a hinge, and the swash plate drives the plunger to only have reciprocating motion in a fixed cylinder barrel, thus avoiding the disadvantages of large rotating inertia, large friction surface of port surface and easy leakage of a common swash plate axial plunger pump. The swash plate can be divided into a manual swash plate, a hydraulic-control swash plate and a hydraulic-control and spring combined variable swash plate. The swash plate can be conveniently adjusted by a window above a variable shell. The plunger pump has various uses and advantages of small rotating inertia, little friction surface, and high mechanical efficiency and volumetric efficiency, and being insensitive to pollution, generating little heat, being capable of taking as an economical combination pump with 'low pressure and large flow or high pressure and small flow' and the like. Besides as a common pump, the axial plunger pump can also be used in the superhigh pressure and synchronous cylinder field. The axial plunger pump has the advantages of general working accuracy and low production cost.

Description

Axial variable displacement plunger pump of swash plate

Technical field:

Hydraulic Power Transmission System

Widely used dynamical element in modern Hydraulic Power Transmission System, cam-type axial piston pump is characterized by and drives rotating shaft by the rotary cylinder-block center and drive cylinder body and rotate together, each plunger is only done under the stationary swash plate compressing in cylinder barrel and is done relatively reciprocating motion, and respectively fluid is sucked or extrudes by fixing plane thrust plate.

Background technique:

This plunger pump has following shortcoming:

The shortcoming of this plunger pump is the accuracy of manufacturing height of thrust plate, and rubbing surface is big, and material requirements is special, and the cylinder body rotary inertia is big, and the axial pressure balance has certain degree of difficulty, and responsive to polluting, in case the flow face weares and teares a little, volumetric efficiency will obviously descend.

Summary of the invention:

Axial variable displacement plunger pump of swash plate

Embodiment:

At the shortcoming of above-mentioned sloping tray axial plunger piston pump, this paper has newly designed axial variable displacement plunger pump of swash plate.Fig. 1 is that the design of axial variable displacement plunger pump of swash plate is always schemed.This plunger pump is made up of three parts: 1, fixed thrust plate part: be made up of part 1～7; 2, the plunger cylinder part that maintains static: form by part 8～12; 3, wobbler variable constituent element: form by part 13～22.Wherein part housing 19 is tightened in above-mentioned three parts respectively on same the axis with screw, forms a whole.

What be made up of part 13～22 is rotation variable part.Part 13 is straight pins, part 14 is variable swash plates, and part 15 is copper base alloy ball seats, and part 16 is dribbling screws, part 17 is to drive rotating shaft, part 18 is cover plates of regulating window, and part 19 is variable shell of connection piece 21 and part 7, and part 20 is the clearance seal covers that can radially lead to oil, part 21 is bearing supports of assembling set 17, part 22 is thrust stuffing box bearing lids, and respectively there is a rolling bearing at the two ends of part spare 20, and part 22a is the grooved round nut that the locking bearing is used.

In order to understand the concrete structure and the effect of wobbler variable more, the spy illustrates with Fig. 2:

Fig. 2 is a wobbler variable part, drives rotating shaft 17 and is characterised in that its left end has disk 17b and an a pair of fork 17c concentric with axle.Respectively bore a screw on the diametric(al) of disk, two screw lines of centres intersect vertical with hole 13 center lines on fork 17c top.Wobbler 14 is characterized in that resembling a mountain font of 90 ° of turning left, and its right-hand member is a disk, and left end has an annular groove of placing plane bearing, and central authorities are flat gesture that a top has the projection in hole.There is the slit of a placing piece 8 in flat gesture central authorities, and respectively there is the one and a half months hole both sides of flat gesture.The fork 17c that is characterized as driving rotating shaft 17 tops of wobbler variable passes through the first quarter moon hole of mountain font swash plate 14 with in the hole on the flat gesture of straight pin 13 insertion swash plate projectioies, is coupled to a relatively turnable hinge, and swash plate is rotated with driving rotating shaft.Two screws 16 up and down of disk 17b are tightened respectively, withstood the swash plate plane, use nut check again, make swash plate and driving rotating shaft become a rigid unitary, guarantee its firm safety in rotary course.

Open Fig. 1 cover plate 18,, can regulate the corner size of wobbler easily by this window.When carrying out manual variable, as long as regulate two screws 16 up and down respectively.When corner need increase, the following screw that comes loose earlier, and then tighten a top screw; When corner need diminish, the top screw that comes loose was earlier tightened a following screw then.

Fig. 3 is the hydraulic control variable small oil tank that external control is used, and part 3 is small oil tanks, opens an annular oil groove that is drilled with cross bore on the cylindrical of oil cylinder, drives an oil groove 5 that leads to the bottom from arbitrary cross aperture of annular oil groove at oil cylinder inner wall.Part 4 is plungers, and the dribbling screw 1 that can regulate the flow size is installed in plunger, regulates the back and locks with nut 2.If in Fig. 2,2 dribbling screws 16 are removed, two screws on the disk 17b are processed into two unthreaded holes, 2 hydraulic control variablees of Fig. 3 are regulated cylinder tightly press in the manhole, increase a clearance seal cover 20 that is enclosed within the driving rotating shaft again and just can realize multiple external control variable.Each imaginary line oil circuit along oneself of the pressure oil P1 of external control and P2 leads to the other end d and the e hydraulic fluid port of P1 and P2, and d and e hydraulic fluid port must be aimed at the outer toroid oil groove of Fig. 3 oil cylinder of tightly compressing into.Small oil tank oil return on the P2 oil circuit, the small oil tank on the P1 oil circuit advances pressure oil, and this moment, the swash plate corner increased, and it is big that output flow also becomes; When the small oil tank oil return of P1, P2 advances pressure oil, and this moment, the swash plate corner diminished, and output flow also diminishes.The size that screw 1 in the small plunger can be regulated the swash plate corner arbitrarily.

Fig. 4 is that the variable of laying spring reset in cylinder body 3 is regulated the cylinder part.Part 5 is springs, and part 4 is plungers, and part 1 is the dribbling screw that can regulate swash plate corner size that is screwed in the plunger, part 2 is locking nuts, if the oil cylinder on the P1-d oil circuit (Fig. 3) changes spring reset cylinder (Fig. 4) into, spring 5 has replaced the P1 outside control mouth, i.e. the obstructed pressure oil of P1.When P2 pressure is zero, swash plate will be deflected into the maximum angle that regulates in advance by the thrust of spring 5.The fluid flow of plunger pump output this moment is maximum; When pressure P 2 progressively raises, spring is pressed onto the minimum angles of swash plate, the flow of plunger pump output this moment be a minimum.This regulating and controlling mode is equivalent to the combined pump of " low pressure and mass flow, high-pressure low-flow ", and it is very economical reasonable to move.

In Fig. 1, what be made up of part 8～12 is the plunger cylinder part that maintains static, and part 9 is cylinder bodies, and part 10 is innerspring first order odd number plungers, and part 11 is second level even number plungers, and part 12 is Cuprum alloy ball seats.Part 8 is hinge axis, its right-hand member and pin 13 active bindings, left end and the 5 active bindings of cylindrical oil sucting valve.Cylinder body 9 maintains static, and being distributed on 1/2nd of the identical total number of plunger of diameter on the same circumference of cylinder body must be odd number.Each plunger is only reciprocating under the compressing of wobbler.The secondary mode is adopted in the plunger oil transportation: the helical oil groove of the oil process thrust plate of first order odd number plunger output is pressed into the inlet port of second level even number plunger, through seat valve pressure oil is exported.(first order plunger diameter allows slightly than second level plunger greatly theoretically, but very small).For example, the total number of hypothesis plunger is 14 in Fig. 1, and then 1/2nd of total number is 7,7th, odd number.Their distribution sequence on same circumference are 1#, 2#, 3#, 4#, 5#, 6#, 7#, 8#, 9#, 10#, 11#, 12#, 13#, 14#.

In Fig. 1, what form is the thrust plate part to part by 1～7, after the periphery rectangular coil oil groove of part 6 is processed, is pressed into tightly in part 7 holes, and forms a thrust plate integral body.The right-hand member of hinge axis 8 and pin 13 active bindings, left end and the 5 active bindings of columniform oil sucting valve, the suction inlet of oil sucting valve 5 and the oil suction face of swash plate are under the situation of cophasing rotation synchronously, fluid sucks from the filler opening of fuel inlet fitting 1, through the end face semicircular ring oil groove f of oil sucting valve 5 and the semicircle oil groove g passage of periphery, fluid is the other end hydraulic fluid port even number 8# of same diameter from odd number 1# mouth to the projection plane through the periphery helical oil groove, through seat valve 3,4 and delivery connection 2, pressure oil is exported.The number order of all the other 6 helical oil grooves is: 3# and 10#, and 5# and 12#, 7# and 14#, 9# and 2#, 11# and 4#, 13# and 6# make odd number plunger and even number plunger corresponding one by one with oil-sucking hole on the thrust plate during installation.

Because first order oil suction is to finish by the cylindrical oil sucting valve 5 of rotation, so the oil suction resistance is very little, noiseless, no retardation phenomenon; Because second level oil suction is to supply with by the pressure oil of the first order, so shock mount not in the plunger of the second level, real stem stem plug is equipped with seat valve 3 and 4 and just can realizes not having leakage ultrahigh pressure and export.

In the thrust plate 6 of Fig. 1, it is that the seat valve 3 and 4 of communicating with each other with inclined hole by being distributed on two different circumference is finished that pressure oil is exported outward.The out splice going splice that communicates with seat valve 4 has 2 kinds of forms: the title afflux joint 2 that 1, whole delivery outlets is pooled together output; 2, the title tap that each delivery outlet is exported separately, figure is simple, does not have the figure expression.Back out fuel inlet fitting 1, with regard to interchangeable afflux joint and tap.

The advantage of rotation swash plate Variable plunger pump is a lot:

1, rotary inertia is little, and friction face greatly reduces, except each plunger face and clearance seal cover are the sliding friction, Never again other big sliding friction, oily temperature can further be reduced, and mechanical efficiency also can further improve;

2, because thrust plate is the seat valve structure, good airproof performance can realize not having the output of leakage, and volumetric efficiency is near 100%;

3, insensitive to polluting, component abrasion is few, long working life;

4, the plunger in each cylinder barrel can be distinguished the pressure oil of exporting the ultrahigh pressure low discharge separately;

5, except being used as general plunger pump use, can also be used as synchronous pump uses, in some millwright journey, need balanced when lifting reposefully, when undercarriage rises and falls simultaneously, when large-scale gate starts up and down and the moved cross beam of guillotine shear, bender when working up and down synchronously all available this pump finish, saved complicated servovalve, synchronization hydraulic system and synchronization mechanism;

6, be the highi degree of accuracy except each trunk piston set, remaining parts is general machining accuracy, and low cost of manufacture is easy to the Development and Production by general machining enterprise.

Claims

1, as a kind of dynamical element that is used for Hydraulic Power Transmission System, axial variable displacement plunger pump of swash plate is made up of three parts: wobbler variable part, plunger cylinder part and the thrust plate part of forming with seat valve.

2, according to claims 1 described wobbler variable part, it is characterized by the first quarter moon hole that the fork 17c that drives rotating shaft 17 tops passes through mountain font swash plate 14, insert with oval pin 13 in the hole 13 on the flat gesture of the hole on fork 17c tops and swash plate projection, be coupled to a relatively turnable hinge, swash plate is rotated with live axle.By the control oil channel of two screws 16 up and down on the disk 17b that drives rotating shaft 17 or little control oil cylinder (Fig. 3 or Fig. 4) and process clearance seal cover 20, the swash plate corner is regulated.

3, according to claims 1 described plunger cylinder part, it is characterized by 1/2nd of the total number of plunger that is distributed on the same circumference must be odd number.The secondary mode is adopted in the plunger oil transportation, and the oil of first order odd number plunger output is pressed into the inlet port of second level even number plunger by helical oil groove, through seat valve pressure oil is exported.

4, according to claims 1 described thrust plate part, it is characterized by cylindrical oil sucting valve 5 must with swash plate cophasing, rotation synchronously.