CN1087972A - Axial plunger pump and motor - Google Patents
Axial plunger pump and motor Download PDFInfo
- Publication number
- CN1087972A CN1087972A CN 92113526 CN92113526A CN1087972A CN 1087972 A CN1087972 A CN 1087972A CN 92113526 CN92113526 CN 92113526 CN 92113526 A CN92113526 A CN 92113526A CN 1087972 A CN1087972 A CN 1087972A
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- pump
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- plunger
- motor
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Abstract
Axial plunger pump and motor are a kind of fluid energy-mechanical energy conversion elements.The present invention is characterized in: between cylinder body and oil distribution casing, be provided with the spiral groove type hydraulic bearing as aiding support; In the design of backhaul mechanism, adopted the free-standing ball pivot; The surface of contact of backhaul dish and piston shoes is a toroidal surface, and the piston shoes cylinder circumference has buffer ring; Cylinder surface is provided with the thread type dynamic pressure pump that pump housing inner fluid is pumped into inlet port and lubricant housings; Plunger has adopted reinforcement plectane hermetic terminal, and the center is by the no dead volume formula structure of hollow needle tubing Oil Guide.
Description
The present invention is a kind of about axial plunger pump and motor, and particularly a kind of spiral chute hydraulic bearing that adopted between thrust plate and cylinder body is as aiding support, floating type plunger pump of cylinder body and motor.
Axial plunger pump and motor are because advantage such as it is little, in light weight to have a volume, and specific power is big is widely used in each industrial field at present.But, in floating type axial piston pump of existing cylinder body and motor, still exist some problems.Wherein most important also is that one of the most scabrous problem is to keep appropriate gap between cylinder body and the thrust plate and stable fluid lubrication oil film, to improve its efficient and reliability.For addressing this problem, the method that extensively adopts has two kinds at present; A kind of is to adopt so-called horseshoe type or fan-shaped hydraulic bearing aiding support, and a kind of is to adopt the hydrostatic bearing aiding support.Though before a kind of mode solved the problem of wearing and tearing or burning dish to a certain extent, be difficult to the oil film that keeps stable, avoid solid contact and wearing and tearing effectively.A kind of mode in back then needs to sacrifice suitable volumetric efficiency.
In addition, for shaft type axial hydraulic pump and motor,, exist three problems adopting central spring to make in the structure of plunger backhaul by ball pivot and backhaul dish.First problem is owing to usually ball pivot is fixed on the transmission shaft with spline or flat key etc., it to be rotated relative to the axis translation with respect to axle.The weakness that causes thus is: if seek out the design of the bigger diameter of axle, then tend to because of the diminish PV value that makes the sphere friction pair between ball pivot and the backhaul dish of contact pressure angle excessive and even cause serious faults such as adhesive wear.
Second problem be, if processing such as the planeness on the plane that the backhaul dish contacts with piston shoes is bad, when higher rotation speed and oil suction pressure are low, then is difficult to make the piston shoes bottom surface to contact on swash plate abreast all the time.The 3rd problem be, owing to the cylndrical surface cylindrical portion of each piston shoes in turn with the backhaul dish on corresponding through hole contacts side surfaces drive the backhaul dish and rotate, when the quality of processing of above-mentioned through hole is bad, just can causes and impact and noise.
Also have a problem to be owing to be full of fluid all the time in the pump housing, so when pump when working, plunger and piston shoes and backhaul dish etc. will stir in the fluid high speed.Cause at least two problems thus, the one, make a large amount of bubble of generation in the oil, the 2nd, produce suitable loss of machine of torque and heating etc.
Be higher than the 300 ultrahigh pressure plunger pumps that cling to for working pressure, because the existence of the big dead volume between the compressibility of liquid and plunger and the cylinder hole, volumetric efficiency can be subjected to suitable influence.On the other hand, consider the inertial force of plunger when high speed and good backhaul, be difficult to again plunger is processed into solid form to eliminate dead volume.
At this present situation, the object of the present invention is to provide a kind of axial plunger pump and motor that can solve above-mentioned all problems at one stroke.
Invention be intended that such realization; Join the cylindrical position on arbitrary (circle) surface of pasta at cylinder body or thrust plate, offer so-called spiral chute hydraulic bearing (Spiral Groov Bearing is called for short SGB) aiding support zone.The basic characteristics of this spiral grooved bearing are: spiral fluted bar number mostly is several to tens, its degree of depth be several microns to tens of micron, both can be that the source and course type also can be a manifold-type by flowing of should causing of spiral fluted pump efficiency.Generally speaking, spiral chute should be opened on the one side harder in friction pair two surfaces, opens usually on fixing thrust plate, and manifold-type is bigger than the bearing capacity of source and course type.Because this bearing has the very big bearing rigidity of a kind of characteristic very good for hydraulic machinery-exist and the frictional loss hydraulic bearing much smaller than other types in very little interstice coverage, so both can keep stable effectively, very thin fluid lubrication oil film, can obtain very high mechanical efficiency again, volumetric efficiency, fundamentally avoid the solid wearing and tearing, improve the life-span and the reliability of pump greatly.
In addition, in order to solve three problems in the above-mentioned backhaul mechanism, taked following three measures in the present invention:
(1), be Spielpassung between ball pivot and cylinder body overhanging end or the transmission shaft, there be not any relatively rotating and axially movable constraint.Simultaneously, transmit between thimble and the ball pivot bottom plane, settle a ring-like back-up ring that plays the cod effect at retracting spring or spring force.Like this, when pump in when work, the backhaul dish is only done the most limited oscillating motion with respect to ball pivot and is not existed and relatively rotate.Corresponding, ball pivot is made certain back rotation of coming with respect to transmission shaft and ring-like back-up ring, thereby the PV value of the sphere friction pair between ball pivot and the backhaul dish reduced greatly, even design very for a short time get the contact pressure angle between two parts, also any problem can not occur.
(2), the face that the backhaul dish contacts with piston shoes is narrower ring-like of a width, and in other words, the backhaul dish only contacts with (beyond the central distribution circle) excircle part of piston shoes bottom toroidal surface.Thereby both be convenient to the processing of backhaul dish, and can have guaranteed again effectively piston shoes to be pressed on the swash plate.
(3), around the cylndrical surface of each piston shoes, settle rubber cylindraceous or plastics buffer ring, like this, both made the through hole quality of processing on the backhaul dish relatively poor, also can between piston shoes and backhaul dish, not produce hard the impact and noise.
In order to solve the effectively lubricating that movement parts such as plunger are stirred the problem of pump housing inner fluid at a high speed and can be guaranteed bearing and ball pivot face etc. simultaneously again, the method for taking in the present invention is as follows:
Surface at cylinder body, be provided with two sections screw thread slot type dynamic pressure pump districts, cylndrical surface that rotation direction is opposite, be communicated with by a ring shaped slot between two sections thread groove districts, this ring shaped slot communicates with several axial bores of opening at (between the plunger hole) on the cylinder body, and an end of axial bore passes to the fluid storage area in the pump housing.End in two sections thread groove districts has two oil outlets, one-way valve of serial connection on each oil outlet, and the outlet of two one-way valves connects together, and constitutes the conjoint outlet of two thread groove pumps.By the oil that this conjoint outlet flows out, a part is directed parts such as lubricating bearings and ball pivot, and a part is directly to return opening.
At last, in order to eliminate the dead volume between plunger and the cylinder hole, can keep the weight of plunger can not increase again simultaneously, the present invention has taked following method; The disalignment of the garden cylindrical space in the middle part of plunger is to the position, install two blocks of circular seal plates (can certainly be more than one or two), end at plunger, a position suitable at the middle part, there is an aperture at the center of plate, by this aperture, high pressure oil is guided to the bottom of the ball head and the piston shoes of plunger with a hollow needle tubing from the end of plunger.Adopt drive fit between sealing plate and the plunger, hollow needle tubing and sealing plate between the aperture, adopt high performance binder sticking dead, form airtight conditions.Like this, both eliminate dead volume, and can when not increasing plunger weight, improve the flexural strength of plunger again.
Compare with traditional similar pump or motor, the present invention has the efficient height, the reliability height, and running is steady, and noise is low, characteristics such as easy processing.
The embodiment that the present invention is used for axial shaft type quantitative plunger pump is provided by accompanying drawing one-accompanying drawing seven.
Below, one-accompanying drawing seven in conjunction with the accompanying drawings, describe the working principle of the axial shaft type quantitative plunger pump that proposes according to the present invention and characteristics etc. in detail.
Accompanying drawing one is the plan view of pump, figure two be F to view, the relative position relation of expression suction hydraulic fluid port.This pump is by transmission shaft (1), cylinder body (2), plunger (3), the damping ring that nonmetallic material are made (4), piston shoes (5), swash plate (6), ball is (7), backhaul dish (8), ring-like back-up ring (9), attachment screw (10), central backhaul spring (11), power transmission thimble (12), bearing (13) and (14), oil distribution casing (15), the pump housing (16), bonnet (17), locating stud (18), one-way valve (19), oil sealing parts such as (20) constitutes.Transmission shaft (1) is bearing on the pump housing (16) and the bonnet (17) by bearing (13) and (14).Cylinder body (2) links together by spline (S) and axle (1), but can do certain moving to axial.Central backhaul spring (11) is delivered to annular retaining ring (9) with spring force successively by power transmission thimble (12), ball pivot (7), and backhaul dish (8) on the piston shoes (5), can be close on the swash plate (6) piston shoes all the time, keeps the normal suction oil of pump.When transmission shaft drives cylinder body etc. when direction as shown is rotated, low pressure oil is sucked by plunger by (A) hole, discharges through high pressure oil drainage hole (B) then.
Figure three is the A-A sectional view, the position relation of expression spiral chute hydraulic bearing and high low pressure distributing groove.Shown in the figure is the manifold-type structure.Ring-like oil supply (Ca) is communicated with oil-sucking hole (A), and oil is after spiral chute pumps into circular groove (Cb), by the aperture on the thrust plate (C) circular flow resorption oilhole (A) again.The oil that leaks out from oil distribution casing zone of high pressure external sealed face (So) also through this circular groove (Cb) and aperture (C) to return opening.
For the pump or the motor of the two-way rotation of need, should be respectively equipped with on the thrust plate and the different corresponding spiral chute hydraulic bearing zones (El) and (Er) and corresponding oil stream circulation canal of turning to, shown in figure four.
When backhaul dish (8) takes turns by each plunger (3) rotary driving, because of the angular velocity of its axis of rotation relatively and the angular velocity of transmission shaft be a variable clocklike, if have rotational restraint between ball pivot (7) and transmission shaft (1), then this relatively rotates and can only be absorbed by the relatively rotating of sphere friction pair between ball pivot and the backhaul dish owing to what angular velocity difference caused.In the present invention, since ball pivot with spool between without any rotational restraint, so ball pivot must have one to relatively rotate with respect to ring-like back-up ring (9) and transmission shaft (1) surface, eliminated relatively rotating between the sphere friction pair therefrom, reduced the PV value between the sphere friction pair greatly, even under the very little situation in contact pressure angle, can not produce any problem yet.Under the situation of high temperature and high speed, do not produce wearing and tearing for guaranteeing both to have made between ball pivot and cylinder body overhanging end or the transmission shaft yet, offered screw lubrication oil groove (R) at the internal surface of ball pivot.Certainly, this screw lubrication oil groove also can be opened on the surface of the overhanging end of cylinder body and axle.
The buffering apron (4) that is fixed on the piston shoes cylndrical surface can prevent hard impact between piston shoes (5) and the backhaul dish (8) and the noise that causes thus effectively.Its comparatively detailed assembly relation is seen figure five.Certainly, also buffer ring can be placed on the through hole wall on the backhaul dish.
Along with the raising of rotating speed, under action of centrifugal force, piston shoes will outwards be tumbled, and especially in low pressure area, the inner ring of the end of piston shoes circle periphery and swash plate will produce more serious wearing and tearing and increase and leak.Therefore, effectively piston shoes being pressed on the swash plate, also is a problem that can not be ignored.In the present invention, the contact area of backhaul dish and piston shoes bottom toroidal surface is the excircle part of its center distribution circle, that is to say that the side that the backhaul dish contacts with piston shoes is a toroidal surface, and this structure can strengthen the effect that compresses to piston shoes greatly.The structure example of backhaul dish is seen figure six.
On the cylinder of the garden of cylinder body, have the opposite thread groove district (Bl) of two sections rotation directions and (Br), these two sections spiral fluted effects are equivalent to the miniature screw thread dynamic pressure pump that two differences turn to, difference corresponding to cylinder body turns to, and left-handed or right-handed thread pump pumps into the fluid of the oil storage space in the pump housing (Sb) in the place of appointment.Shown in figure one, there is a ring shaped slot (Bs) that is equivalent to public inlet port the centre of two helical pumps, this circular groove communicates with several axial bores (D) of opening at (between the plunger hole) on the cylinder body, and an end of axial bore is communicated to the fluid storage area (Sb) in the pump housing.In spiral fluted end, two ends, have two oil outlets (Cl) and (Cr), each oil outlet links to each other with an one-way valve (19) respectively, and the outlet of two one-way valves connects together, and constitutes the public outlet of two thread groove pumps.Oil from this public outlet is flowed out at first flows into the oil pocket (Ss) that communicates with little bearing (14), because oil pocket (Ss) communicates with inlet port (A) by a fixing throttle orifice (E), so the pressure in this oil pocket is higher than the pressure of inlet port.By opening axial oil through (Z) and the oil through (K radially on transmission shaft (1)
1) and (K
2), oil is guided to the ball pivot friction pair respectively and big bearing (13) is located, to ball pivot (7), backhaul dish (8), the side that the circle portion back side, the end of piston shoes (5) promptly contacts with the backhaul dish, big bearing (13), oil sealing parts such as (20) is lubricated.Do not say and sigh,, can remove one section thread groove district (Bl) or (Br) and two one-way valves (19) etc. for the pump or the motor that only need unidirectional rotation.Adjust the position of axial bore (D), can obtain different fuel head at pump housing shoe cream room.
Figure seven has provided band reinforcement plate and center needle tubing, the detailed structure example of no dead volume formula plunger.By structure among the figure as can be seen, the longitudinal section shape of this plunger approaches the equal strength structure.Add man-hour actual, only, (M2) located required precision little sealing plate (21) and big sealing plate (22) binding site (M1) with the plunger inner cylindrical surface.(A0), (A1) reaching (A2) is the adhesive bond place.This structural type is for high pressure, and at a high speed, big discharge capacity type pump and motor especially have superiority.
Point out that in passing principle that the present invention discusses not only is adapted to above-mentioned metering pump and motor, also be adapted to axial variable plunger pump and motor simultaneously.
Simple declaration about figure number in the accompanying drawing;
(1), transmission shaft; (2), cylinder body; (3), plunger; (4), buffer ring; (5), piston shoes; (6), swash plate; (7), ball pivot; (8), backhaul dish; (9), ring-like back-up ring; (10), attachment screw, (11), central backhaul spring; (12), power transmission thimble; (13), big bearing; (14), little bearing; (15), oil distribution casing; (16), the pump housing; (17), bonnet; (18), locating stud; (19), one-way valve, (20), oil sealing, (21), little sealing plate; (22), big sealing plate;
(A), oil-sucking hole; (B), oil drainage hole; (C), the circulation oilhole on the thrust plate; (D), open axial oil through between the cylinder body plunger hole; (Z), open axial bore at center transmission shaft;
(E), throttling pore; (K1), (K2), the radially oil through on the transmission shaft; (Bs), the public inlet port circular groove of two helical pumps; (Ca), the oil supply of SGB; (Cb), the drain pan of SGB and thrust plate; (Sb), the oil storage space in the pump housing; (Ss), lubricant reservoir;
Claims (3)
1, axial plunger pump and motor, by transmission shaft (1), cylinder body (2), plunger group (3), nonmetal buffer ring (4), piston shoes (5), swash plate (6), ball pivot (7), backhaul dish (8), ring-like back-up ring (9), oil distribution casing parts such as (15) is formed, and it is characterized in that:
Between cylinder body flow face and oil distribution casing, offered the spiral groove type hydraulic bearing as aiding support.This spiral groove type hydraulic bearing can be opened on arbitrary surface in both.
2, according to described pump of claim " 1 " and motor, it is characterized in that;
A, ball pivot can relatively rotate and move axially with respect to transmission shaft.
B, the contact plane of backhaul dish and piston shoes bottom disc is a toroidal surface, promptly the backhaul dish only contacts with the part area of piston shoes bottom toroidal surface.
C around the piston shoes cylndrical surface, has installed the buffer ring of nonmetal system.
3, according to described pump of claim " 1 " and motor, it is characterized in that: be provided with screw thread slot type dynamic pressure pump on the surface of cylinder body, this dynamic pressure pump can be with the pump housing inner fluid suction return opening and the necessary lubricated place of part at any time.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 92113526 CN1087972A (en) | 1992-12-05 | 1992-12-05 | Axial plunger pump and motor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 92113526 CN1087972A (en) | 1992-12-05 | 1992-12-05 | Axial plunger pump and motor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1087972A true CN1087972A (en) | 1994-06-15 |
Family
ID=4946452
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 92113526 Pending CN1087972A (en) | 1992-12-05 | 1992-12-05 | Axial plunger pump and motor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1087972A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102926987A (en) * | 2012-11-28 | 2013-02-13 | 无锡威孚精密机械制造有限责任公司 | Slipper used for plunger type hydraumatic pump |
| CN105423104A (en) * | 2015-12-24 | 2016-03-23 | 衢州学院 | Self-pressurization hydro-hybrid lubricated port plate |
| CN106545462A (en) * | 2015-09-22 | 2017-03-29 | 无锡市德美嘉机械科技有限公司 | A kind of inclined disc type hydraulic plunger motor |
| CN107781157A (en) * | 2017-10-24 | 2018-03-09 | 徐州工业职业技术学院 | A kind of hydraulic pump plunger for reducing flow pulsation |
| CN109162916A (en) * | 2018-10-17 | 2019-01-08 | 江苏汇智高端工程机械创新中心有限公司 | Axial plunger pump/motor |
-
1992
- 1992-12-05 CN CN 92113526 patent/CN1087972A/en active Pending
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102926987A (en) * | 2012-11-28 | 2013-02-13 | 无锡威孚精密机械制造有限责任公司 | Slipper used for plunger type hydraumatic pump |
| CN102926987B (en) * | 2012-11-28 | 2016-05-04 | 无锡威孚精密机械制造有限责任公司 | Pluger type hydraulic pump piston shoes |
| CN106545462A (en) * | 2015-09-22 | 2017-03-29 | 无锡市德美嘉机械科技有限公司 | A kind of inclined disc type hydraulic plunger motor |
| CN105423104A (en) * | 2015-12-24 | 2016-03-23 | 衢州学院 | Self-pressurization hydro-hybrid lubricated port plate |
| CN105423104B (en) * | 2015-12-24 | 2023-06-13 | 衢州学院 | Self-pressurization type dynamic-static pressure lubrication type valve plate |
| CN107781157A (en) * | 2017-10-24 | 2018-03-09 | 徐州工业职业技术学院 | A kind of hydraulic pump plunger for reducing flow pulsation |
| CN107781157B (en) * | 2017-10-24 | 2018-11-16 | 徐州工业职业技术学院 | A kind of hydraulic pump plunger reducing flow pulsation |
| CN109162916A (en) * | 2018-10-17 | 2019-01-08 | 江苏汇智高端工程机械创新中心有限公司 | Axial plunger pump/motor |
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| C01 | Deemed withdrawal of patent application (patent law 1993) | ||
| WD01 | Invention patent application deemed withdrawn after publication |