CN1087971A - Axial plunger type variable capacity pump - Google Patents
Axial plunger type variable capacity pump Download PDFInfo
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- CN1087971A CN1087971A CN 92113525 CN92113525A CN1087971A CN 1087971 A CN1087971 A CN 1087971A CN 92113525 CN92113525 CN 92113525 CN 92113525 A CN92113525 A CN 92113525A CN 1087971 A CN1087971 A CN 1087971A
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- plunger
- swash plate
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Abstract
Axial plunger type variable capacity pump is a kind of dynamical element that mechanical energy is changed into the fluid energy.The present invention is characterized in:, adopted the unsteady plunger of " C " shape at the back side of floating thrust plate; Adopted corrugated spring in the backhaul mechanism, free-standing ball pivot, the surface of contact of backhaul dish and piston shoes are a toroidal surface, and the piston shoes cylinder circumference has buffer ring; Cylinder surface is provided with the screw thread slot type dynamic pressure pump that pump housing inner fluid is pumped into return opening; Plunger is no dead volume structure; Adopted the hydrostatic support structure of intermittent type oiling between variable swash plate and the supporting base; Between swash plate supporting base and front pump cover, be provided with a rubber damper.
Description
The present invention is a kind of about axial plunger type variable capacity pump, particularly a kind of floating type Variable plunger pump of thrust plate that has adopted the unsteady plunger of " C " type.
Axial plunger type variable capacity pump, because that it has a volume is little, in light weight, specific power is big, is easy to advantages such as control, is widely used at present in the various hydraulic systems.
In axial plunger type variable capacity pump, be to keep the appropriate gap between cylinder body and the thrust plate, floating type two kinds of the floating type and thrust plate of cylinder body is arranged.The floating type advantage of cylinder body is: structure is comparatively simple, is easier to select to compress ratio, and bearing does not bear thrust load etc.But its shortcoming is that the motional inertia of cylinder body is big, and self-alignment is relatively poor, and the design of inlet port is the design of self-priming rotating speed restriction of being subjected to the required impacting force of cylinder body self balancing etc.Corresponding, the floating type advantage of thrust plate is: little and do not involve parts such as making complicated plunger movable and piston shoes as the thrust plate inertia of float, so its floatability is good, the design of inlet port is comparatively free, can obtain bigger self-priming rotating speed etc.But its shortcoming is if adopt the method for installing several plungers at the thrust plate back side, then must make part number increase and cause some other problem.
In order to lower the noise of pump, the supporting way of variable swash plate is transferred to swinging block formula (Cradle Type) by the more gudgeon formula of former use (Trunnion Type) gradually at present.Between swinging block formula variable swash plate and supporting base, mainly contain three kinds of supporting meanss.The one, non-rounding type rolling bearing supporting, the 2nd, sliding supported condition, the 3rd, hydraulic type supporting.The shortcoming of first kind of supporting means is that price is expensive and mostly be patent right and protect, and the shortcoming of the second way is that frictional force is bigger.The shortcoming of the third mode then is that Oil Guide mechanism sacrifices certain volumetric efficiency than complicated and needs.
Although adopted all measures, compare with vane pump, the noise of plunger pump still seems excessive at present.One of its reason is: because (especially vertically) mechanical vibration of causing of pressure pulsation are by variable swash plate and supporting mass, thrust plate etc. and conduct to two ends housing and connecting base etc. form the air vibration source, produce noise.
In addition,, make in the structure of plunger backhaul, exist several problems adopting central spring for shaft type axial deflection oil hydraulic pump.First problem is owing to usually ball pivot is fixed on the transmission shaft with methods such as spline or flat keys, it to be relatively rotated with respect to the axis translation.The problem that causes thus is: if want to design the diameter of axle bigger, 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 is: if processing such as the planeness on the plane that the backhaul dish contacts with piston shoes is bad, then be difficult to make the piston shoes bottom surface to contact on swash plate abreast in the oil suction district.The 3rd problem is: 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, if be full of fluid in the pump housing all the time, then 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 300 high-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 body, 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.
In view of the foregoing, the object of the present invention is to provide a kind of Variable plunger pump that solves above-mentioned whole issue.
The intention of invention is achieved in that cylinder body and rotatingshaft is adopted drive fit or very little Spielpassung, being cylinder body can not relative movement with respect to rotatingshaft, at the back side of thrust plate, installed the unsteady plunger of " C " type, this plunger causes oil drain out with high pressure oil from thrust plate.Since the thrust plate two sides stressed evenly, so it can be done very thin, make structure very compact and part number is few.
Be noise-decreasing, adopted swinging block formula variable swash plate among the present invention.Between variable swash plate and supporting base, have static pressure oil groove (Ca) and reach (Cb), this two static pressure oil groove lays respectively at the both sides of axle.Oil groove (Ca) communicates with aperture on the swash plate plane by a fixed restriction device, and this aperture is opened on the locus circle that piston shoes slide and is positioned at the high pressure side.Like this, when pump in when work, the high pressure oil of piston shoes bottom will be connected with this aperture successively, enter static pressure oil groove (Ca) between swinging block and the swinging block bearing by this aperture and flow controller, simultaneously, by open with cylindrical hole that the cone bearing periphery cooperates on ring-like oil groove (Cd) high pressure oil is caused the static pressure oil groove (Cb) of the opposite side that is positioned at axle.The oiling mode that this means the static pressure oil groove is the clearance type oiling, and its advantage is simple in structure, and fluid be difficult for to block, and leaks less etc.
In order between variable swash plate supporting base and front case, to lay hardness and the moderate rubber pad of thickness owing to axial mechanical vibration and front case that pressure pulsation causes are kept apart.
In the present invention, adopted following measure to solve three problems in the aforementioned backhaul mechanism:
(1) is Spielpassung between ball pivot and the transmission shaft, do not have any relatively rotating and axially movable constraint.Simultaneously, between corrugated retracting spring and ball pivot bottom, settled a ring-like back-up ring that plays the axial thrust bearing effect.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 is reduced greatly, even design very for a short time, also any problem can not occur to the contact pressure angle of two parts.
(2) face that contacts with piston shoes of backhaul dish is the narrower toroidal surface of a width.In other words, the backhaul dish not with piston shoes bottoms toroidal surface be positioned at the central distribution circle with part contact.This mode both had been convenient to the processing of backhaul dish, can effectively piston shoes be pressed on the swash plate again.
(3) around the cylndrical surface of each piston shoes, settle the picture glue or the plastic ring of a garden tubular.Like this, even the through hole quality of processing on the backhaul dish is relatively poor, can between plunger and backhaul dish, produce yet and 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 simultaneously again, the method for taking in the present invention is as follows: on the surface of cylinder body, be provided with a screw thread slot type dynamic pressure pump.One end of thread groove communicates with the fluid storage area of the pump housing, and the other end then passes to return opening.The oil that leaks out from thrust plate cylindrical portion also directly passes to return opening, but then pass through little bearing from the oil that the thrust plate inner circular part leaks out, the radial hole that axially reaches on the transmission shaft passes to ball pivot surface and big bearing place, and the thread groove pump that is bored in again on the cylinder surface after these two-part are lubricated is evacuated to return opening.
At last,, can guarantee that again the weight of plunger can not increase, and has adopted following method in the present invention simultaneously:, settled a dead volume to eliminate cover at the middle part of hollow plunger in order to eliminate the dead volume between plunger and the cylinder hole.This cover is the monolithic construction of a plate sealing together and an oil guide pipe, and the Oil Guide aperture that is positioned at the cover center causes high pressure oil the bottom of plunger ball portion and piston shoes from the end of plunger.Adopt drive fit (or it is dead to adopt binder to glue) between sealing plate and the plunger, then adopt binder sticking dead between hollow oil guide pipe and the plunger ball portion endoporus, form airtight conditions.Like this, both eliminate dead volume, and can not increase the weight of plunger again.
Compare with existing shaft orientation plunger variable pump, the present invention has the efficient height, the reliability height, and running is steady, and noise is low, advantages such as easy processing.
The embodiment that the present invention is used for axial variable plunger pump is provided by accompanying drawing one-accompanying drawing eight.
Below, one-accompanying drawing eight in conjunction with the accompanying drawings, describe the working principle of the axial deflection shaft type plunger pump that proposes according to the present invention and characteristics etc. in detail.
Accompanying drawing one is the plan view of pump, and figure two is the A-A sectional view, figure three be F to view, the relative position relation of expression suction hydraulic fluid port.
Shown in figure one, this pump is by transmission shaft (1), cylinder body (2), plunger (3), piston shoes (4), the damping ring that nonmetallic material are made (5), ball pivot (6), backhaul dish (7), ring-like back-up ring (8), ripple spring (9), swinging block formula variable swash plate (10), variable swash plate supporting base (11), static pressure flow controller (13), cone bearing (15), little bearing (16), rubber damping pad (17), front pump cover (18), the pump housing (19), thrust plate (20), bonnet (21), " C " type plunger (22) that floats, seal ring (23), retaining spring (24), variable big piston (25), variable small piston (26), spring (27), variable swash plate drive pin (28), drive pin bearing (29), controller parts such as (30) is formed.
When transmission shaft (1) drives cylinder body when direction shown in the figure one rotate, plunger (3) is in the cylinder body rotation, and is reciprocating with respect to cylinder body, by thrust plate (19), oil from inlet port (A) suction, discharged through oil drain out (B) then.
On the pump housing, have axial oil guiding hole (Kl), high pressure oil passes to the bottom of variable piston (26) through this aperture, when big piston (25) end does not have high pressure oil to do the time spent, the hydraulic coupling that produces bottom small piston (26) and the spring force of spring (27) will be by drive pin bearing (29), variable swash plate drive pin (28) is pushed into the maximum inclination angle of setting with variable swash plate (10), makes pump that peak rate of flow output be arranged.After high pressure oil entered big piston (25) acting chamber by controller (30), it oppositely was that the inclination angle will diminish on the contrary that swash plate will be pushed to, and made the flow that pump is only exported to be needed.
Installed the unsteady plunger of " C " type at the unsteady thrust plate back side.Float between plunger and the rear pump cover, adopts plastic seal ring (23) sealing of " C " type, two retaining springs (24) keep the sealing circle to reach that " C " type plunger is relative with the thrust plate back side all the time to be contacted.Certainly, also " C " type plunger and thrust plate can be made of one.The advantage of this scheme is simple in structure, and part number is few.In addition, because the thrust plate two ends is stressed even, there is not problem on deformation, so can do it thinner.Its concrete structure is seen figure six.
In order to make pump have good dynamic characteristic, need to guarantee the stroking mechanism flexible movements, promptly reduce inertia and frictional force as far as possible.In the present invention, adopted the scheme of hydrostatic support swinging block formula variable swash plate (10).Its concrete structure is: on variable swash plate semi-cylindrical, have two static pressure oil grooves (Ca) and reach (Cb).These two oil grooves are positioned at the both sides of transmission shaft (1), by open with the cylindrical hole of cone bearing (15) cylindrical interference fit on circular groove (Cd) and oil guiding hole (Ka), the oil of static pressure oil groove (Ca) is caused the static pressure oil groove (Cb) of opposite side.In swash plate and the contacted surface high pressure of piston shoes (4) district, offer at least one aperture (Kj), between this aperture and static pressure oil groove (Ca), installed a fixing circumferential weld shape flow controller (13).Like this, when pump in when work, each piston shoes is connected with aperture (Kj) in turn, by flow controller (13), off and on high pressure oil is injected static pressure oil groove (Ca) and reach (Cb), guarantee between variable swash plate (10) and swash plate supporting base (11), a minimum oil film is arranged all the time and leak very little.
Lowering vibration and noise, is a vital task in the current axial piston pump development work.For the axial mechanical vibration that decay and cause, between swash plate supporting base (11) and front pump cover (18), thickness and the moderate rubber damping pad (17) of hardness have been installed by pressure pulsation.
When backhaul dish (7) takes turns by each plunger (3) rotary driving, because of the angular velocity of its axis of rotation is a variable clocklike with respect to the angular velocity of rotatingshaft, if have rotational restraint between ball pivot (6) and rotatingshaft (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 exists one to relatively rotate with respect to ring-like back-up ring (8) and transmission shaft (1) surface, thereby eliminated the rotation between the sphere friction pair, reduced greatly between the sphere friction pair＜PV＞value, even under the very little situation in contact pressure angle, can not produce any problem yet.Wearing and tearing can be not produce in order guaranteeing both to have made under the high-speed and high-temperature condition between ball pivot and the axle surface yet, a screw lubrication oil groove can be on the axle surface, to offer.
The buffering apron (5) that is fixed on the piston shoes cylndrical surface can prevent to produce between piston shoes (4) and the backhaul dish (7) impact and noise effectively.
Along with the raising of rotating speed, under action of centrifugal force, piston shoes will outwards be tumbled.Especially in low pressure area, circle outside interior circle with swash plate in the end of piston shoes will produce more serious wearing and tearing and increase and leak.For addressing this problem, the backhaul dish among the present invention is a toroidal surface with the face that the piston shoes bottom contacts.The advantage of this structure is that processing is simple, compresses effective.The structure example of backhaul dish is seen figure seven.
On the periphery of cylinder body, have one section spiral chute (Bl).When pump work, just this spiral chute as same small-sized dynamic pressure type volute pump.Because an end of this thread groove directly passes to space (Sb) in the pump housing, so the oil that is stored in this space can be evacuated to return opening (C).Avoid plunger (3) therefrom, piston shoes (4), backhaul dishes (7) etc. are to the stirring of fluid.
Figure eight has provided the detailed structure example of the no dead volume formula plunger of band integrated type dead volume elimination cover.Can be thought of as drive fit between the sealing plate of end and the plunger, hollow conduit and ball head endoporus then can adopt the high-performance binder sticking dead.(A1) is the binder junction point among the figure.This kind structure is for the major diameter plunger, outstanding tool superiority.
Point out that in passing the mass part of the main points of discussing also can be used for axial metering pump and motor among the present invention.
About the simple declaration of figure number in the accompanying drawing,
(1): transmission shaft, (2): cylinder body, (3): plunger group, (4): piston shoes, (5): damping ring, (6): ball pivot, (7): backhaul dish, (8): ring-like back-up ring, (9): ripple spring, (10): swinging block formula variable swash plate, (11): variable swash plate supporting base, (13): static pressure flow controller, (15): cone bearing, (16): little bearing, (17): rubber damping pad, (18): front pump cover, (19): the pump housing, (20): thrust plate, (21): rear pump cover, (22): " C " type plunger that floats, (23): " C " RunddichtringO, (24): retaining spring, (25): variable big piston, (26): variable small piston, (27): spring, (28): variable swash plate drive pin, (29): drive pin bearing, (30): controller, (31): sealing plate, (32): hollow oil guide pipe
(A): oil-sucking hole, (B): oil drainage hole, (C): spill port, (Ca), and (Cb): the static pressure oil groove, (Cd): ring-like oil guide slot, (Ka), and (Kj): the Oil Guide aperture, (Sb): the oil storage space in the pump housing.
Claims (6)
1, axial plunger type variable capacity pump, by transmission shaft (1), cylinder body (2), plunger group (3), piston shoes (4), the damping ring that nonmetallic material are made (5), ball pivot (6), backhaul dish (7), ring-like back-up ring (8), ripple spring (9), swinging block formula variable swash plate (10), variable swash plate supporting base (11), static pressure flow controller (13), cone bearing (15), little bearing (16), rubber damping pad (17), front pump cover (18), the pump housing (19), thrust plate (20), bonnet (21), " C " type plunger (22) that floats, plastic seal ring (23), retaining spring (24), variable big piston (25), variable small piston (26), spring (27), variable swash plate drive pin (28), drive pin bearing (29), controller parts such as (30) is formed, and it is characterized in that:
At the back side of floating type thrust plate, installed the unsteady plunger of " C " type.By this plunger, high pressure oil is caused oil drain out.
2, according to the described pump of claim " 1 ", it is characterized in that:
A, ball pivot can relatively rotate and move axially with respect to transmission shaft.
B, the surface of contact of backhaul dish and piston shoes bottom toroidal surface is a toroidal surface.
C between piston shoes cylndrical surface and backhaul dish through hole side, has the buffering of nonmetal system to enclose the buffer shock-absorbing effect.
3, according to the described pump of claim " 1 ", it is characterized in that: be provided with spiral chute dynamic pressure pump on the surface of cylinder body, this spiral chute dynamic pressure pump can be evacuated to return opening at any time with the fluid in the pump housing.
4, according to the described pump of claim " 1 ", it is characterized in that:, be provided with an all-in-one-piece dead volume and eliminate cover at the middle part of hollow plunger.This cover is made of plate sealing together and a hollow conduit.By the aperture of sealing plate and catheter center, oil is caused bulb end and piston shoes bottom from the planar ends of plunger.
5, according to the described pump of claim " 1 ", it is characterized in that: on the slip surface that the variable swash plate contacts, have logical oily aperture bottom piston shoes.At this aperture and between the static pressure oil groove on the variable swash plate semicircle column type slip surface, be provided with a fixed restriction device.When pump rotated, high pressure oil was by the piston shoes bottom, and above-mentioned aperture and flow controller inject the static pressure oil groove off and on high pressure oil.
6, according to the described pump of claim " 1 ", it is characterized in that: between variable swash plate supporting base and front pump cover, be provided with a rubber damper.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 92113525 CN1087971A (en) | 1992-12-05 | 1992-12-05 | Axial plunger type variable capacity pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 92113525 CN1087971A (en) | 1992-12-05 | 1992-12-05 | Axial plunger type variable capacity pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1087971A true CN1087971A (en) | 1994-06-15 |
Family
ID=4946451
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 92113525 Pending CN1087971A (en) | 1992-12-05 | 1992-12-05 | Axial plunger type variable capacity pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1087971A (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101876303A (en) * | 2010-07-23 | 2010-11-03 | 浙江苏强格液压有限公司 | Stroking mechanism of plunger pump |
| CN103711689A (en) * | 2014-01-09 | 2014-04-09 | 北京理工大学 | High pressure hydraulic pump plunger of hollow structure |
| CN104989613A (en) * | 2015-08-11 | 2015-10-21 | 贵阳海之力液压有限公司 | Novel minitype swash plate type plunger pump and motor |
| CN105201814A (en) * | 2015-09-09 | 2015-12-30 | 浙江大学 | Device for measuring stirring loss caused by high-speed rotating element of axial plunger pump/motor |
| CN106401892A (en) * | 2016-12-13 | 2017-02-15 | 荆门市召铭液压科技有限公司 | Low-noise swash-plate axial plunger pump |
| CN106762505A (en) * | 2016-11-28 | 2017-05-31 | 太原科技大学 | A kind of hydraulic pump with swing swash plate and rotation valve plate |
| 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 |
| CN115163442A (en) * | 2022-08-24 | 2022-10-11 | 潍柴动力股份有限公司 | Cylinder body, plunger pump and motor |
| CN115507011A (en) * | 2022-09-13 | 2022-12-23 | 厦门大学 | Plunger machine swash plate two-dimensional shimmy suppression device with double springs, mass and liquid resistance |
| CN118148873A (en) * | 2024-05-10 | 2024-06-07 | 沈阳格鲁克自动化设备有限公司 | Plunger pump |
| CN118148873B (en) * | 2024-05-10 | 2024-07-02 | 沈阳格鲁克自动化设备有限公司 | Plunger pump |
-
1992
- 1992-12-05 CN CN 92113525 patent/CN1087971A/en active Pending
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101876303A (en) * | 2010-07-23 | 2010-11-03 | 浙江苏强格液压有限公司 | Stroking mechanism of plunger pump |
| CN101876303B (en) * | 2010-07-23 | 2012-07-18 | 浙江苏强格液压股份有限公司 | Stroking mechanism of plunger pump |
| CN103711689A (en) * | 2014-01-09 | 2014-04-09 | 北京理工大学 | High pressure hydraulic pump plunger of hollow structure |
| CN104989613A (en) * | 2015-08-11 | 2015-10-21 | 贵阳海之力液压有限公司 | Novel minitype swash plate type plunger pump and motor |
| CN105201814A (en) * | 2015-09-09 | 2015-12-30 | 浙江大学 | Device for measuring stirring loss caused by high-speed rotating element of axial plunger pump/motor |
| CN106762505A (en) * | 2016-11-28 | 2017-05-31 | 太原科技大学 | A kind of hydraulic pump with swing swash plate and rotation valve plate |
| CN106401892A (en) * | 2016-12-13 | 2017-02-15 | 荆门市召铭液压科技有限公司 | Low-noise swash-plate axial plunger pump |
| 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 |
| CN115163442A (en) * | 2022-08-24 | 2022-10-11 | 潍柴动力股份有限公司 | Cylinder body, plunger pump and motor |
| CN115507011A (en) * | 2022-09-13 | 2022-12-23 | 厦门大学 | Plunger machine swash plate two-dimensional shimmy suppression device with double springs, mass and liquid resistance |
| CN115507011B (en) * | 2022-09-13 | 2024-04-30 | 厦门大学 | Two-dimensional shimmy suppression device with double springs, mass and liquid resistance for swash plate of plunger machine |
| CN118148873A (en) * | 2024-05-10 | 2024-06-07 | 沈阳格鲁克自动化设备有限公司 | Plunger pump |
| CN118148873B (en) * | 2024-05-10 | 2024-07-02 | 沈阳格鲁克自动化设备有限公司 | Plunger pump |
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