CN110067713A - A kind of tandem axial plunger pump - Google Patents
A kind of tandem axial plunger pump Download PDFInfo
- Publication number
- CN110067713A CN110067713A CN201910189021.5A CN201910189021A CN110067713A CN 110067713 A CN110067713 A CN 110067713A CN 201910189021 A CN201910189021 A CN 201910189021A CN 110067713 A CN110067713 A CN 110067713A
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- China
- Prior art keywords
- sliding plate
- plunger
- plate
- oil
- swash plate
- Prior art date
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- 239000004519 grease Substances 0.000 claims abstract description 27
- 239000003921 oil Substances 0.000 claims description 101
- 238000009826 distribution Methods 0.000 claims description 36
- 239000007788 liquid Substances 0.000 claims description 19
- 230000002706 hydrostatic effect Effects 0.000 claims description 18
- 230000000694 effects Effects 0.000 claims description 12
- 230000002093 peripheral effect Effects 0.000 claims description 6
- 239000010720 hydraulic oil Substances 0.000 claims description 5
- 239000012530 fluid Substances 0.000 claims description 4
- 238000004891 communication Methods 0.000 claims description 2
- 208000002925 dental caries Diseases 0.000 claims description 2
- 238000011109 contamination Methods 0.000 abstract 1
- 238000007789 sealing Methods 0.000 description 17
- 230000033001 locomotion Effects 0.000 description 8
- 238000000034 method Methods 0.000 description 8
- 238000006243 chemical reaction Methods 0.000 description 5
- 238000003825 pressing Methods 0.000 description 5
- 230000009471 action Effects 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 238000000605 extraction Methods 0.000 description 3
- 239000011159 matrix material Substances 0.000 description 3
- 230000007246 mechanism Effects 0.000 description 3
- 238000000926 separation method Methods 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 230000006837 decompression Effects 0.000 description 2
- 230000009977 dual effect Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 230000001360 synchronised effect Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 238000005119 centrifugation Methods 0.000 description 1
- 238000005253 cladding Methods 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 230000000452 restraining effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 238000003860 storage Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B1/141—Details or component parts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B1/16—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having two or more sets of cylinders or pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B1/18—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having self-acting distribution members, i.e. actuated by working fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/06—Combinations of two or more pumps the pumps being all of reciprocating positive-displacement type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
Abstract
The invention discloses a kind of tandem axial plunger pumps, including two sliding plate formula axis plunger pumps and the end seat being folded between two sliding plate formula axis plunger pumps, the sliding plate formula axis plunger pump includes flow sliding plate subcomponent, the flow sliding plate subcomponent includes swash plate and the sliding plate being supported on swash plate, the sliding plate is overall structure, the multiple plunger ball-and-sockets being distributed on a side end face are provided on the sliding plate, the large aperture oil-through-hole of the multiple grease chambers and connection the plunger ball-and-socket and grease chamber that are distributed on another side end face, the flow oil groove communicated with oil inlet and outlet is provided on the swash plate, described two swash plates with can the state support that fascinates of opposite main shaft in common end seat.Flow, variable inclination, supporting functions are integrated in sliding plate pair by the present invention, reduce the secondary quantity of friction, reduce cylinder body and topple and the influence of oil contamination, and structure is greatly simplified, improve the functional reliability, operating pressure and working life of axial plunger pump.
Description
Technical field
The invention belongs to hydraulic drive and control technology field, be related to a kind of tandem axial plunger pump, in particular to one
Kind includes the tandem axial plunger pump of flow sliding plate subcomponent.
Background technique
Axial plunger pump is using most wide one of Hydraulic Elements in Modern hydraulic transmission, wherein hingeless formula inclined shaft is pumped and slided
Carrying out cam-type axial piston pump is most widely used at present, is also most important two classes axial plunger pump.With various mainframes
The appearance of tool, to the increasingly demand of high-pressure large-displacement plunger pump, in actual application, to improve discharge capacity, often solely by two
Vertical oblique tray type plunger series connection of pumps, forms double pump structure, and serial dual pump structure includes two sets independent shells, end seat, pump shaft, oblique
The parts such as disk, return plate, plunger, piston shoes, flexural pivot, cylinder body, oil distribution casing, existing double pump structure have the following characteristics that first, structure
Complexity, building block is more, at high cost；Second, this double pump cascaded structure, structure size is big, not compact enough, is often pacified
Fill the limitation in space；Third, it is secondary that this double pump cascaded structure usually contains three pairs of crucial frictions: cylinder body and valve plate, piston shoes with
Swash plate, plunger and cylinder body plunger hole, the secondary reliability that rubs are directly related to entire double pump reliability of structure.For cylinder body with
This is secondary to friction for valve plate, due to being caused cylinder body to tilt by the effect of plunger lateral force, between cylinder body and valve plate often
Wedge gap is formed, which destroys the normal sealing between cylinder body and valve plate, to increase the volume damage of pump
It loses, and the sealing surface between cylinder body and valve plate is made to generate localized contact, cause the scorch between cylinder body and valve plate, i.e.,
Disk phenomenon is burnt, so that pump completely loses function.For piston shoes and swash plate, this is secondary to friction, during high speed exercise due to piston shoes
It is rotated under generated moment of friction comprehensive function by centrifugal moment caused by circumferential movement, reverberation matrix method and with cylinder body, meeting
So that piston shoes is toppled with respect to swash surfaces generation, to form wedge-shaped oil film, and leads to piston shoes eccentric wear, to destroy piston shoes just
Often work.
Summary of the invention
It is an object of the invention to: current serial dual pump structure there are aiming at the problem that, a kind of novel serial axis is provided
To plunger pump, it is intended to meet Modern Large tool to high-power, high reliability, high-pressure high-flow and the small axial columns of structure size
Fill in the demand of pump.
A kind of technical solution implementation of the technology of the present invention: tandem axial plunger pump, it is characterised in that: including two
Sliding plate formula axis plunger pump and the end seat being folded between two sliding plate formula axis plunger pumps, each sliding plate formula axis plunger pump
Comprising flow sliding plate subcomponent, main shaft, the cylinder body for being supported on the main shaft and rotating synchronously with main shaft, the main shaft, which runs through, matches
Fluent disk subcomponent is simultaneously supported in the end seat, and the flow sliding plate subcomponent includes swash plate and the cunning being supported on swash plate
Disk, the sliding plate are overall structure, and the sliding plate end face opposed with swash plate is provided with hydrostatic support face, the sliding plate and cylinder body
Opposed end face is provided with multiple plunger ball-and-sockets, and the logical oil of connection plunger ball-and-socket and hydrostatic support face is provided on the sliding plate
Hole is provided with flow oil groove on the swash plate, and what is be arranged on the flow oil groove and end seat is connected into and out of hydraulic fluid port, and described two
The swash plate of a sliding plate formula axis plunger pump is supported in common end seat.
Tandem axial plunger pump of the present invention is provided with multiple grease chambers on the hydrostatic support face, described
Low pressure oil-distribution port and high pressure oil-distribution port, the high and low pressure oil-distribution port are provided on swash plate on the end face opposed with sliding plate
With grease chamber intermittent communication, the bearing surface opposed with end seat has the cylindrical sliding support face being cylindrically shaped on the swash plate, described
There is the flute profile low pressure port and flute profile high-pressure mouth for being configured as flute profile, the flute profile low pressure port and flute profile on the cylindrical sliding support face of swash plate
High-pressure mouth connection corresponding with low pressure oil-distribution port and high pressure oil-distribution port respectively.
Tandem axial plunger pump of the present invention has connection flute profile low pressure on the cylindrical sliding support face of the swash plate
The connection notch of mouth and the second cavity of sliding plate formula axis plunger pump shell.
Tandem axial plunger pump of the present invention is folded with valve plate, the cunning between the sliding plate and swash plate
Disk is supported on valve plate and is slidably matched with valve plate holding, and high and low pressure is provided on the valve plate with head piece, hydraulic oil
The flow oil groove on swash plate is flowed through under piston reciprocation effect, matches head piece, the grease chamber of sliding plate, oil-through-hole and plunger on valve plate
Centre bore realizes sucking, the discharge of hydraulic oil.
Tandem axial plunger pump of the present invention, one end of the main shaft are supported in first bearing, the other end
End is connected through flow sliding plate subcomponent and by axle sleeve, and in end seat, the first bearing is set as the sleeve supporting
Radial thrust bearing, in rotary work, hydraulic axial power is transferred to shell through first bearing by cylinder body for the main shaft and cylinder body
On body.
Tandem axial plunger pump of the present invention, described cylinder body one end, which is provided with, only allows oil liquid from housing hollow
Into the check valve of plunger hole, the check valve includes the valve body connecting with cylinder body, the spool that valve inner is arranged in, is fixed on
Retaining ring on valve body and the spring being arranged between spool and retaining ring, the check valve only allow low pressure oil liquid from shell
Two cavitys are flowed to the plunger hole direction of cylinder body.
Tandem axial plunger pump of the present invention, the swash plate peripheral part are provided with the bearing stopper of protrusion,
3rd bearing is folded between on the inside of the sliding plate periphery and bearing stopper, the sliding plate is with the bearing of radially constrained state
In 3rd bearing.
Tandem axial plunger pump of the present invention is provided with restraint device in the flow sliding plate pair side, institute
Stating restraint device included in sliding plate has stopper section raised outward close to the side in hydrostatic support face and in the bearing
The clamping close device being arranged in stopper, it is separate that the clamping close device limits sliding plate in a manner of constraining the 3rd bearing and be displaced outwardly
Swash plate end face.
Tandem axial plunger pump of the present invention, any one sliding plate in described two sliding plate formula axis plunger pumps
The spindle nose of formula axis plunger pump is connected with slippage pump or main pump.
Tandem axial plunger pump of the present invention, the plunger include the rod-plunger with pyramidal structure or two
End be provided with bulb rod-plunger or the spherical surface plunger with universal hinge one kind, the plunger at one end can opposing cylinder it is past
The mode slided again is inserted into the plunger hole of cylinder body, and the other end is solid far from state that is limited and can fascinating with opposite sliding plate end face
It is scheduled in the plunger ball-and-socket of sliding plate, the large aperture plunger centre bore of connection plunger ball-and-socket and plunger hole is provided on the plunger.
Based on the above-mentioned technical proposal, the beneficial effects of the present invention are:
1, the present invention by two sliding plate formula axis plunger series connections of pumps together, huge discharge, high pressure, high power requirements can be met.
2, tandem axial piston motor of the invention, opposite disposed swash plate, and swash plate is made to be supported on a common end
On seat, setting is inhaled oil drain passage and is connected to the oil inlet and outlet being arranged in end seat on swash plate, structure can be made to greatly simplify, size
It is smaller, structure is more compact, the weight of pump or motor is smaller, therefore improves its power per unit mass density.
3, flow, variable inclination, hydrostatic support function are integrated in flow sliding plate pair by the present invention, and main friction pairs are to slide
Disk pair and plunger pair, compare existing duplex axial plunger pump: first is that, reduce a Port Plate Pair, therefore reduce the leakage of oil liquid
Damage, improves its efficiency；Second is that the lateral force of plunger substantially reduces, eliminate or reduces cylinder body and topple phenomenon；Third is that by
In cylinder ends without Port Plate Pair, therefore even there is part lateral force to cylinder there is no wearing, leaking in cylinder ends
Body generates overturning effect, and will not generate eccentric wear leads to failure, therefore this structure makes the longer life expectancy of cylinder body, after
Phase maintenance is less, reduces use cost.
4, the present invention in sliding plate structure be overall structure, instead of multiple independent piston shoes in the prior art and with
Using the structure of return plate backhaul, the plunger in the present invention connect relatively reliable with sliding plate, sliding plate and platen, avoids existing skill
Phenomena such as piston shoes neck and shoulder abrasion, failure by shear and return plate boring sites in curing are cracked in art, to improve duplex
The functional reliability of formula plunger pump.Meanwhile the centrifugal force and frictional force of sliding plate each section are cancelled out each other, and are avoided single piston shoes and are existed
The comprehensive work of generated moment of friction is rotated by centrifugal moment caused by circumferential movement and with cylinder body in high speed motions
Toppling under, the abrasion of monoblock type sliding plate structure uniformly, eliminate or reduce original Slipper coupling friction phenomenon.
5, the oil-through-hole in the present invention on sliding plate, plunger centre bore are large aperture, therefore can prevent the blocking of greasy dirt,
The sensibility of greasy dirt is reduced, while large aperture plunger centre bore reduces the quality of plunger, facilitates the centrifugation for reducing plunger
Power effect.
Detailed description of the invention
Fig. 1 is the structural schematic diagram of tandem axial plunger pump in the present invention.
Fig. 2 is the A-A sectional view of tandem axial plunger pump in Fig. 1 in the present invention.
Fig. 3 is the plan view of sliding plate one end in the present invention.
Fig. 4 is sliding plate structure B-B sectional view in Fig. 3 in the present invention.
Fig. 5 is the plan view of the sliding plate other end in the present invention.
Fig. 6 is a kind of plan view of swash plate one end bearing surface opposed with sliding plate in the present invention.
Fig. 7 is the plan view of swash plate opposed with end seat in the present invention.
Fig. 8 is the plan view that swash plate band opposed with end seat in the present invention is connected to notch.
Fig. 9 is the D-D sectional view in the present invention in Fig. 7, Fig. 8.
Figure 10 is another embodiment of tandem axial plunger pump in the present invention.
Figure 11 is the E-E sectional view of tandem axial plunger pump in Figure 10 in the present invention.
Figure 12 is the sliding plate sectional view of Figure 10 in the present invention
Figure 13 is the tandem axial plunger pump that check valve is arranged in the present invention comprising valve plate and cylinder ends.
Figure 14 is the plan view of valve plate in the present invention
Marked in the figure: 10 be main shaft, 10C is spindle axis, 12 attachment devices, and 13 be main axle bumper shoulder, 15 is axle sleeve, 21 is first
Bearing, 23 be 3rd bearing, and 32 be body, and 33 be end seat, and 33a is oil inlet, and 33b is oil outlet, and 33d is runner, and 33e is
Slip circle face, 34 be the first cavity, and 35 be the second cavity, and 38 be swash plate interconnecting piece, and 39 be slippage pump, and 40 be swash plate, and 41 be swash plate
Bearing surface, 41a are bearing stopper, and 42 be flow oil groove, and 43 be low pressure oil-distribution port, and 44 be high pressure oil-distribution port, and 45 be circle
Elastic supports face, 46 be flute profile low pressure port, and 47 be flute profile high-pressure mouth, and 48 be connection notch, and 50 be sliding plate, and 50C is sliding plate axle center, 51
It is boss face for hydrostatic support face, 52,53 be oil-through-hole, and 53a is grease chamber, and 54 be outer seal portion, and 55 be interior sealing, and 56 are
Separation seal portion, 57 be stopper section, and 58 be plunger ball-and-socket, and 59 be sliding plate bearing support, and 60 be pressing plate, and 70 be plunger, and 71 are
Plunger ball, 72 be plunger centre bore, and 73 be taper bar portion, and 74 be plunger portion, and 80 be cylinder body, and 81 be plunger hole, and 82 be main shaft
Pilot hole, 80C are cylinder center axle center, and 90 be valve plate, and 91 flow bearing surfaces, 92 match head piece for low pressure, and 93 be high pressure flow
Mouthful, 100 be center spring, and 101 be flexural pivot, and 102 be backstop, and 110 be check valve, and 111 be valve body, and 112 be spool, and 113 be bullet
Spring, 114 be retaining ring, and 140 be clamping close device, and 141 be cylinder body circlip.
Specific embodiment
With reference to the accompanying drawing, the present invention is described in detail.
Although the present invention admits of various forms of embodiments, the specification and drawings are disclosed only as of the invention
Exemplary some particular forms.However the present invention is not intended to be limited to the embodiment described.The scope of the present invention is in appended power
Benefit provides in requiring.
For the convenience of description, the embodiment of the present invention is shown with being typically oriented, the orientation is so that work as oblique tray type plunger
The central axis horizontal rest of the main shaft of pump is a left side with the shaft coupling end side of main shaft, and end seat is the right side, " is indulged used in description
To ", " transverse direction " "upper", "lower", "front", "rear", "left", "right" "horizontal", "bottom", "inner", the terms such as "outside" be both referred to this
A position and use, be merely for convenience of description of the present invention and simplification of the description, rather than the device of indication or suggestion meaning or
Element must have a particular orientation and specific orientation constructs and operation, it should be understood that the present invention can be different from institute
The orientation for the position stated is manufactured, is stored, is transported, used and is sold.
Embodiment 1:
It as shown in figs 1-9, is the embodiment of tandem axial plunger pump of the invention, it is in the preferred embodiment shown, described
Tandem axial plunger pump includes two sliding plate formula axis plunger pumps and is folded between two sliding plate formula axis plunger pumps
End seat 33, each sliding plate formula axis plunger pump include flow sliding plate subcomponent, main shaft 10, be supported on the main shaft 10 and with master
The cylinder body 80 and plunger 70 that axis 10 rotates synchronously, the main shaft 10 is through flow sliding plate subcomponent and is supported on the end seat 33
On, the flow sliding plate subcomponent includes swash plate 40 and the sliding plate 50 being supported on swash plate 40, and the sliding plate 50 is whole knot
Structure, the sliding plate 50 end face opposed with swash plate 40 are provided with hydrostatic support face 51, are provided on the sliding plate 50 and are distributed in one
Multiple plunger ball-and-sockets 58 on side end face, the multiple grease chamber 53a being distributed on another side end face and the connection plunger ball-and-socket
The large aperture oil-through-hole 53 of 58 and grease chamber 53a, described 70 one end of plunger are placed in plunger ball-and-socket 58, and the other end is inserted into cylinder body 80
Interior, 72 one end of plunger centre bore inside the plunger 70 is connected to oil-through-hole 53, the plunger hole 81 in the other end and cylinder body 80
Connection, is provided with flow oil groove 42 on the swash plate 40, and the swash plate 40 of described two sliding plate formula axis plunger pumps is supported on altogether
In same end seat 33, the oil inlet 33a and oil outlet 33b being arranged on the flow oil groove 42 and end seat 33 are connected to, described two
Swash plate 40 is supported in common end seat 33.
Wherein, it should be noted that the large aperture in the large aperture oil-through-hole 53 and large aperture plunger centre bore 72 is phase
For the size in corresponding position aperture in existing structure, the aperture in existing structure is elongated aperture, the height in plunger hole
Pressure oil liquid only has fraction by this hole, and under the action of elongated aperture, and oil liquid pressure reduces, therefore the hole in existing structure
Diameter mainly plays throttling, depressurization, 72 conduct of large aperture oil-through-hole 53 and large aperture plunger centre bore in the present invention to oil liquid
Main oil-hole structure, the sucking and discharge of hydraulic oil flow through this main oil-hole structure, and oil liquid is by large aperture oil-through-hole 53 and macropore
Diameter plunger centre bore 72 is without obvious pressure drop, therefore its structure has essential distinction.Specifically, in the present embodiment, the logical oil
The aperture in hole 53 compared to corresponding position in existing structure aperture increases to kidney-shaped grease chamber 53a width direction adjoining dimensions or
Unanimously.
As illustrated in fig. 1 and 2, in the tandem axial plunger pump embodiment, end seat 33 is arranged at middle part, and the right and left is each
With a sliding plate formula axis axial plunger pump, distinguishingly, the sliding plate formula axis axial plunger pump of the right and left is symmetrical structure.
The sliding plate formula axis axial plunger pump of the right and left shares an end seat 33, and the end seat 33 is for closing the one of both sides pump case
End opening, sliding plate formula axis axial plunger pump and the end seat 33 of the left and right sides are bolted to connection.Due to 33 two sides of end seat
Sliding plate formula axis axial plunger pump configuration it is similar, be concise explanation, be with the sliding plate formula axis axial plunger pump on wherein one side
Example is illustrated.
Wherein, the end seat 33 is provided with the oil inlet of pump for closing the open at one end of body 32 in the end seat 33
33a and oil outlet 33b, the runner 33d being connected to swash plate flow oil groove 42 and the slip circle face 33e for supporting swash plate；Work as tandem
When axial plunger pump is variable pump, the stroking mechanism (not shown) swung for variable, the variable are connected on body 32
Mechanism is connect with the variable interconnecting piece 38 being arranged on swash plate 40, and under the action of stroking mechanism, the swash plate 40 is together with sliding plate
50 rotate in the second cavity 35.
The tandem axial plunger pump includes two main shafts 10, is folded with first axle between the main shaft 10 and body 32
21 are held, described 10 one end of main shaft is supported on body 32 via first bearing 21, and the other end penetrates through each self-flow-distribution sliding plate pair to end
Seat 33 is simultaneously connected by axle sleeve 15, and the axle sleeve 15 is supported in end seat 33, and main shaft 10 can be relative to body 32 around itself axis
The heart rotates freely, and the key connection structure for connecting cylinder body 80, the main shaft are provided on the circumferential surface at 10 middle part of main shaft
10 drive cylinder body 80 to realize synchronous rotary via key connection structure.
The first bearing 21 include at least one radial thrust bearing, the radial thrust bearing including but not limited to
Heart thrust ball bearing or tapered roller bearing are provided with main shaft shoulder block 13 on the main shaft 10 close to 80 end of cylinder body.When pump work
When making, main shaft 10 drives 80 synchronous rotary of cylinder body, and under axial liquid pressure force, 80 end abutment of cylinder body is in main shaft shoulder block 13
On, and be transferred in first bearing 21 through main shaft shoulder block 13, and then be transferred on body 32.It should be pointed out that cylinder body 80 is logical
Crossing main shaft shoulder block 13 to transmit xial feed not being is the condition for limiting its application, can alternatively, for example, first bearing 21 can be set
It is set to the combination support system that radial ball bearing adds thrust bearing, cylinder body 80 is directly connected on radial thrust bearing and will be axial
Power is transferred on body 32, and radial force is undertaken by the radial ball bearing and axle sleeve 15 for being supported on 10 both ends of main shaft.
The cylinder body 80 is circular column-shaped configuration with radially section, and is contained in the second cavity 35 of body 32
Interior, the cylinder body 80 has with the circumferential equally distributed multiple plunger holes 81 of cylinder center axle center 80C and is used to hold at center
Receive the spindle mounted hole 82 of main shaft, the plunger hole 81 of the cylinder body 80 is structure closed at one end, open at one end.Preferably, institute
It states 81 quantity of plunger hole and is traditionally arranged to be 7 or 9.The main shaft 10 passes through the spindle mounted hole 82 of cylinder body 80 and with its axis body
Outer peripheral surface setting connecting key mode is connect with cylinder body 80, and the cylinder body 80 is supported on master in such a way that it is moved synchronously with main shaft 10
On axis 10.
It should be pointed out that the closed end of cylinder body 80 is not provided with the valve plate abutted with it, therefore reduces one and rub
Pair is wiped, its volumetric efficiency is improved；Due to not abutting valve plate, 80 end of cylinder body does not need Precision Machining, reduce manufacture and
Use cost；Even there is part lateral force without valve plate in 80 end of cylinder body, will not generate eccentric wear causes failure etc. to be asked
Topic.
The plunger 70 includes that one end is supported on the plunger ball-and-socket 58 of sliding plate 50 and is fixed on sliding plate end via pressing plate 60
The plunger ball 71 in face, the plunger centre bore 72 for being connected to plunger hole 81 and plunger ball-and-socket 58, outer peripheral surface are in conical cone
Shape bar portion 73 and with cylinder body plunger hole wall clearance fit and can its move back and forth plunger portion 74.The plunger ball 71
In spherical and can sliding freely be supported on the plunger ball-and-socket 58 of sliding plate 50；The plunger centre bore 72 is large aperture through-hole
Structure, as sucking and discharge oil passage；Plunger portion 74 and 81 clearance fit of cylinder body plunger hole, it is preferable that in plunger portion 74
On at least one sealing ring is often set for sealing liquid, the taper bar portion 73 is substantially from plunger ball end to plunger portion 74
The cone-shaped gradually increased, when plunger 70 moves to a certain position, taper bar portion 74 connects with 81 inner ring of cylinder body plunger hole
Touching, plays intermal force.But it should be recognized that plunger 70 is not limited to cone-shaped plunger type, it can also be ball comprising both ends
Connecting rod-the plunger or spherical surface plunger with universal hinge of head.
The ring of end face of the sliding plate 50 towards cylinder body side is circumferential to be provided with multiple plunger balls with 70 relative position of plunger
Nest 58, the plunger ball-and-socket 58 form opening substantially at hemispherical recess portion in 50 end face of sliding plate, and plunger ball-and-socket 58 is with sliding plate axis
The state of the common even circumferential compartment of terrain distribution of heart 50C supports plunger ball 71, is mounted on plunger in plunger 70
It after ball-and-socket 58, is fixed in by pressing plate 60 on the end face of sliding plate 50, so that plunger 70 is separate with respect to the end face of sliding plate 50
Movement is restricted.Distinguishingly, it is also not necessarily limited to use the side of pressing plate for plunger 70 to be fixed on to the mode of the end face of sliding plate 50
Formula, for example, it is also possible to be provided with the sealed pressing device (not shown) of shape on sliding plate 50, which can be by being greater than
Plunger ball 71 is fixed the cladding of 180 degree.
As shown in Fig. 3,4 and 5, the sliding plate 50 is provided with hydrostatic support face 51, sliding plate axis on the end face opposed with swash plate
Heart 50C and spindle axis 10C at an angle, the hydrostatic support face 51 be supported on swash plate 40 and always with the swash plate 40
Holding is slidably matched.The multiple grease chamber 53a for being configured as kidney-shaped are provided on the hydrostatic support face 51, it is preferable that grease chamber 53a with
It is evenly distributed on hydrostatic support face 51 centered on the 50C of sliding plate axle center, connection plunger ball-and-socket is provided on the sliding plate 50
The large aperture oil-through-hole 53 of 58 and grease chamber 53a.
Further, it is provided on the sliding plate 50 end face opposed with swash plate 40 along sliding plate axle center 50C to swash plate 40 1
The boss face 52 for the protrusion that side extends, which is that the region surrounded by interior diameter R1 and overall diameter R2 is constituted, sliding plate
Boss face 52 is mutually abutted in a manner of it can slide with 40 bearing surface of swash plate.In the boss face 52 with plunger ball-and-socket 58
It sets corresponding position and is provided with multiple grease chamber 53a, it is preferable that grease chamber 53a is that the common circumference centered on the 50C of sliding plate axle center is equal
Even compartment of terrain is distributed in the boss face 52.
Wherein, effective static pressure oil film bearing, the boss face are formed between 40 bearing surface of the boss face 52 and swash plate
The sealing for sealing oil liquid effect is provided on 52, the sealing is arranged with the state for surrounding the grease chamber 53a in oil
The interior periphery of room 53a, the sealing include be distributed in the radially inner and outer interior sealing 55 of grease chamber 53a, outer seal portion 54, and
It is distributed in the separation seal portion 56 between adjacent grease chamber 53a.The interior sealing 55 is by grease chamber 53a inward flange and boss face 52
The region that surrounds interior diameter R1, the outer seal portion 54 is surrounded by grease chamber 53a outer edge and the overall diameter R2 of boss face 52
Region, the separation seal portion 56 is by the spaced-apart bosses face region between adjacent grease chamber 53a.The sealing of the boss face 52
Remain that certain reasonable gap makes oil film leakage in reasonable level between 40 bearing surface of portion and swash plate.
As shown in fig. 6, the swash plate have with the matched swash plate bearing surface 41 in sliding plate hydrostatic support face, in the swash plate branch
Kidney-shaped low pressure oil-distribution port 43 and kidney-shaped high pressure oil-distribution port 44, the low pressure oil-distribution port 43 and high pressure are provided in bearing surface 41
Oil-distribution port 44 is divided into two sides, the low pressure oil-distribution port 43 and high pressure oil-distribution port by the CC plane of swash plate central axis
44 opposite central plane CC can be set to symmetrically or non-symmetrically structure, for example, high pressure oil-distribution port 44 is arranged to multiple tools
There is the window of kidney-shaped.It, can be by 43 He of low pressure oil-distribution port for the purpose for making swash plate that there is certain pre-loading and be depressured in advance
High pressure oil-distribution port or distinguishingly can also be on 43 end of low pressure oil-distribution port along the center axis rotation certain angle of swash plate
Setting from low pressure oil-distribution port 43 be transitioned into 44 direction of high pressure oil-distribution port and on 44 end of high pressure oil-distribution port setting from
High pressure oil-distribution port 44 is transitioned into the throttling channel or hole (not shown) in 43 direction of low pressure oil-distribution port, play from high pressure to low pressure or
Low pressure plays the role of pre- decompression and pre-loading to high pressure.
As Figure 7-9, the swash plate 40 bearing surface opposed with end seat 33 is arranged to the circle being cylindrically shaped
Elastic supports face 45 has slip circle face 33e identical with 45 radius of cylindrical sliding support face of swash plate in the end seat 33, so that swash plate circle
Elastic supports face 45 remains close-fitting state when sliding on the slip circle face of end seat.Have on the cylindrical sliding support face 45 of the swash plate
It is configured as the flute profile low pressure port 46 and flute profile high-pressure mouth 47 of flute profile, flute profile low pressure port 46 and flute profile on the cylindrical sliding support face 45
High-pressure mouth 47 respectively with the low pressure oil-distribution port 43 and high pressure flow on the swash plate bearing surface 41 of swash plate cylindrical surface opposite side
The corresponding connection of window 44.Flute profile low pressure port 46 and flute profile high-pressure mouth 47 on the cylindrical sliding support face 45 are symmetrically or non-symmetrically to tie
Structure, for example, the opening width and/or length of flute profile low pressure port 46 and flute profile high-pressure mouth 47 are equal or unequal configuration.Institute
The periphery for stating the flute profile low pressure port 46 and flute profile high-pressure mouth 47 on cylindrical sliding support face 45 has the band for sealing the notch, makes
It obtains swash plate cylindrical sliding support face 45 and seals oil liquid when sliding on the slip circle face 33e of end seat.Distinguishingly, in the cylinder branch of the swash plate
The connection notch 48 with connection flute profile low pressure port 46 and the second cavity of shell 35 in bearing surface 45, as shown in figure 8, making oil inlet
Mouth is connected to the second cavity of shell 35.
When as pump, oil liquid process is as follows: when oil suction, low pressure oil enters runner 33d from the oil inlet 33a of end seat 33
In, successively pass through flute profile low pressure port 46, low pressure oil-distribution port 43, the grease chamber 53a of sliding plate, the oil-through-hole 53, plunger ball-and-socket of swash plate
58, large aperture plunger centre bore 72 reaches 81 in the plunger hole of cylinder body；When oil extraction, high pressure oil is from the plunger hole 81 of cylinder body, successively
By large aperture plunger centre bore 72, plunger ball-and-socket 58, large aperture oil-through-hole 53, sliding plate grease chamber 53a, high pressure oil-distribution port 44,
Flute profile high-pressure mouth 46 is finally discharged from end seat oil outlet 33b.
When work, action of hydraulic force is further transferred to sliding plate 50 on plunger 70, and generally, plunger 70 acts on
Axial force on sliding plate 50 is greater than swash plate 40 by oil film reaction in the supporting force of sliding plate 50 and the sum of the reverberation matrix method of plunger 70,
Therefore, sliding plate 50 is connected on swash plate 40 by one layer of oil film slides always.But it is on startup in view of plunger pump or motor, sliding
Still need initial sealing between disk 50 and swash plate 40, to establish oil pressure as early as possible, therefore, in order to make sliding plate 50 with swash plate 40 rigid
Pre strained state is kept when start-up operation, and in flow sliding plate pair side, initial sealing device must be set.
The initial sealing device includes central spring 100, flexural pivot 101 and backstop 102, and the central spring 100 is installed
Afterwards, there is certain pretightning force, which acts through flexural pivot 101 and act on platen 60 and be further transferred to sliding plate 50
On, so that sliding plate 50 is connected to always on swash plate 40, keep certain sealability.
Embodiment 2:
As shown in figures 10-13, it is that the peripheral part of sliding plate 50 is supported provided with 3rd bearing 23 with the main distinction of embodiment 1,
40 peripheral part of swash plate setting bearing stopper 41a, on the inside of 50 outside of sliding plate and bearing stopper 41a between be folded with the
Three bearings 23, the sliding plate 50 are supported on 3rd bearing 23 with radially constrained state.The 3rd bearing 23 can be set
It is set to including but not limited to angular contact ball bearing, needle bearing, cylinder roller bearing, tapered roller bearing, radial ball bearing
One kind, in rotary work, the plunger 70 moves reciprocatingly in the plunger cavity of cylinder body 80 for the main shaft 10 and cylinder body 80,
Realize the suction oil work of pump or motor.
In tandem axial plunger pump operational process, higher-pressure region plunger 70 is hydraulic by the high pressure oil of cylinder body plunger hole 81
Power effect applies one close to horizontal action of hydraulic force to sliding plate 50 through plunger ball 71, which pushes sliding plate 50 to
Swash plate 40 is simultaneously in close contact with 40 end face of swash plate.40 end face of swash plate applies a reaction force to sliding plate 50, due to 50 end of sliding plate
Face with 40 end face of swash plate is contacted with bevel-faced form, and the reaction force of swash plate 40 is decomposed into the water along the direction spindle axis 10C
Divide power and the cross component force along the vertical major axle center direction 10C equally, which has the tendency that making sliding plate to lateral movement.
After being folded with 3rd bearing 23 between the swash plate 40 and sliding plate 50, reaction force of the sliding plate by 3rd bearing 23, effect
Reaction force on sliding plate is also decomposed into along the horizontal component in the direction spindle axis 10C and along vertical major axle center 10C
The cross component force in direction.In addition to this, the backhaul restraining force that sliding plate is also subject to acts on, inertia force acts on (cancelling out each other) and rubs
Power effect (not shown) etc. is wiped, above-mentioned several power constitute the balance of the power of sliding plate.It should be noted that each power is along spindle axis side
To horizontal component and plunger 70 act on the fluid pressure balance of sliding plate 50.It acts on sliding plate 50 along vertical major axle center 10C
The cross component force in direction can be offset in sliding plate 50, without being further transferred in cylinder body 80 via plunger 70.
This structure using bearing bearing sliding plate has the following characteristics that 3rd bearing 23 constrains sliding plate 50 radially
Movement or movement tendency, the cross component force of 50 active force of sliding plate is balanced, so that sliding plate 50 acts on cylinder body via plunger 70
Lateral force on 80 is eliminated or is greatly lowered, and improves the functional reliability, operating pressure and working life of plunger pump.
Meanwhile being obviously particularly that the backhaul mode of the axial plunger pump of the sliding plate supporting type obtains larger simplification, it should
Return structures are included in the restraint device of sliding plate pair side setting, and the restraint device limitation sliding plate 50 is remote under reverberation matrix method effect
From 40 end face of swash plate.
Further, as shown in figure 12, the restraint device is included in sliding plate 50 and has close to 51 side of hydrostatic support face
Raised stopper section 57 and the clamping close device 140 being arranged on the bearing stopper 41a outward.The stopper section 57 is used for
The movement of 3rd bearing 23 is limited, the clamping close device is included on the bearing stopper 41a, is arranged at neighbouring 3rd bearing 23
Engaging circumferential groove and on the engaging internal circle groove be arranged circlip (not shown), the circlip is to constrain the 3rd bearing 23
The mode being displaced outwardly limits sliding plate far from 40 end face of swash plate.
Can predictably, it can also be between stopper section 57 and 3rd bearing 23 or between circlip and 3rd bearing 23
It is appropriately arranged with elastomeric pad (not shown), so that restraint assembly other than limitation sliding plate is far from swash plate end face, also has centainly
The Pre strained state of initial pretightening force holding sliding plate and swash plate.
Similarly, the way of restraint of the restraint device 140 can also support stopper 41a's by 3rd bearing 23 and swash plate
Interference fit to realize, on swash plate bearing stopper 41a, at neighbouring 3rd bearing 23 setting engaging circumferential groove and with engage week
The circlip of slot cooperation plays further effect of contraction.
It needs to illustrate, since 80 end of cylinder body is not provided with valve plate, the friction pair of no static pressure oil film bearing is not required to
To reach sealing purpose by applying pretightning force to 80 end of cylinder body, therefore restraint device 140 need to be only set in sliding plate pair,
The backhaul requirements that plunger can be met do not need in addition to add the preloads such as central spring or backhaul component, so that the restraint device
Compared with existing plunger pump, structure is greatly simplified, also avoids phenomena such as central spring is broken because of fatigue damage.
Certainly, axial plunger pump in non-aqueous placing flat (such as storage, transport, be inverted in use process) in order to prevent, cylinder
Body 80 is moved along main shaft 10 to sliding plate direction, to constrain cylinder body 80 on main shaft 10, adjacent to cylinder body end face setting cylinder body circlip 141
Vibration.
Embodiment 3:
As shown in figure 13, the sandwiched between sliding plate 50 and swash plate 40 is in flow sliding plate pair with the main distinction of other embodiments
There is valve plate 90, the hydrostatic support face 51 is supported on valve plate 90 and is slidably matched with the holding of valve plate 90, the flow
Disk is fixed on swash plate by modes such as pins, and high pressure is provided on the valve plate 90 with head piece 93 and low pressure and matches head piece 92,
As shown in figure 14, the high pressure with head piece 93 and low pressure with head piece 92 respectively on swash plate low pressure oil-distribution port 43 and high pressure match
Window 44 is flowed to be connected to.The low pressure can be set to symmetrically or non-symmetrically with head piece 93 with respect to central plane with head piece 92 and high pressure
Structure, for example, high pressure is arranged to multiple window (not shown) with kidney-shaped with head piece 93；It is certain to have valve plate
Pre-loading and the effect that is depressured in advance, can by low pressure with head piece 92 and high pressure with head piece 93 along the center axis rotation one of valve plate
Determine angle；Or distinguishingly, high pressure can also be transitioned into head piece with head piece 92 from low pressure with setting on 92 end of head piece in low pressure
93 directions and the throttling that low pressure matches 92 direction of head piece is transitioned into head piece 93 from high pressure with setting on 93 end of head piece in high pressure
Slot or hole, play the role of from high pressure to low pressure or low pressure to high pressure play it is pre- decompression and pre-loading.
In the present embodiment, valve plate 90 is folded between sliding plate 50 and swash plate 40 to be advantageous in that, later period replacement is matched
Flow table is easier than replacement swash plate and expense more saves.
Embodiment 4:
It is that tandem axial plunger pump is the tandem plunger pump with slippage pump with the main distinction of other embodiments, shown
In embodiment, one slippage pump 39 is connected by attachment device 12 in the end of a wherein main shaft 10, the slippage pump 39 is used
In for hydraulic system fuel feeding or providing hydraulic operation power；The slippage pump is bolted with shell, external slippage pump 39
It can be gear pump or vane pump etc..
Embodiment 5:
As shown in figure 13, it is that 80 one end of cylinder body abutted with the main shaft shaft shoulder 13 is provided with only with the main distinction of other embodiments
Oil liquid is allowed to enter multiple check valves 110 of plunger hole from housing chamber, the check valve 110 is fixedly connected with cylinder body 80, described
Check valve 110 includes the valve body 111 connecting with cylinder body 80, the spool 112 that valve inner is arranged in, is fixed on valve body 111
Retaining ring 114 and the spring 113 being arranged between spool 112 and retaining ring 114,110 permission low pressure oil liquid of the check valve from
Second cavity 35 of shell is flowed to 81 direction of plunger hole of cylinder body, i.e., when cylinder body 80 is in oil suction state, check valve 110
Spool 112 is opened, and low pressure oil liquid enters in plunger hole from the second cavity of shell 35, single when cylinder body 80 is in oil extraction state
It is closed to the spool 112 of valve 110.
When the pump is operated, oil liquid process is as follows: when oil suction, there is two-way oil inlet access, wherein access all the way are as follows: low pressure oil
Enter in runner from the oil inlet 33a of end cap 33, successively passes through flute profile low pressure port 46, the low pressure oil-distribution port 43, sliding plate of swash plate
Grease chamber 53a, large aperture oil-through-hole 53, plunger ball-and-socket 58, large aperture plunger centre bore 72 reach 81 in the plunger hole of cylinder body；It is another
Road access are as follows: by the check valve 110 of the end of cylinder body 80, low pressure oil liquid is directly entered cylinder body plunger from the second cavity of shell 35
In hole 81；When oil extraction, high pressure oil is from the plunger hole 81 of cylinder body, successively by large aperture plunger centre bore 72, plunger ball-and-socket 58, big
Aperture oil-through-hole 53, sliding plate grease chamber 53a, high pressure oil-distribution port 44, flute profile high-pressure mouth 46 are finally discharged from end cap oil outlet 33b.
There is two-way oil inlet access to be advantageous in that when oil suction: first is that, the heat that each component generates can will be pumped in time pass through
Check valve 110 is taken away, and avoids pump inner fluid temperature from increasing, leads to its failure；Second is that suction passage can be increased, pump is improved
Suction capacity；Third is that the oil return line and cooling device of pump can be cancelled, the manufacturing cost and use cost of pump is reduced.
The above content is combine specific optimal technical scheme further detailed description of the invention, and it cannot be said that
Specific implementation of the invention is only limited to and these explanations.For those of ordinary skill in the art to which the present invention belongs, exist
Under the premise of not departing from present inventive concept, a number of simple deductions or replacements can also be made, and all do not depart from essence of the invention
Mind and range technical solution and and its improve, should all cover within the scope of the claims of the present invention.
Claims (10)
1. a kind of tandem axial plunger pump, it is characterised in that: including two sliding plate formula axis plunger pumps and be folded in two
End seat (33) between sliding plate formula axis plunger pump, each sliding plate formula axis plunger pump include flow sliding plate subcomponent, main shaft
(10), the cylinder body (80) for being supported on the main shaft (10) and rotating synchronously with main shaft (10), the main shaft (10) run through flow
Sliding plate subcomponent is simultaneously supported on the end seat (33), and the flow sliding plate subcomponent includes swash plate (40) and is supported on swash plate
(40) sliding plate (50) on, the sliding plate (50) are overall structure, the sliding plate (50) the end face setting opposed with swash plate (40)
Have hydrostatic support face (51), the sliding plate (50) end face opposed with cylinder body (80) is provided with multiple plunger ball-and-sockets (58), in institute
The oil-through-hole (53) that connection plunger ball-and-socket (58) and hydrostatic support face (51) is provided on sliding plate (50) is stated, in the swash plate (40)
On be provided with flow oil groove (42), be arranged on the flow oil groove (42) and end seat (33) into and out of hydraulic fluid port (33a, 33b) even
Logical, the swash plate (40) of described two sliding plate formula axis plunger pumps is supported on common end seat (33).
2. tandem axial plunger pump according to claim 1, it is characterised in that: set on the hydrostatic support face (51)
It is equipped with multiple grease chambers (53a), is provided with low pressure oil-distribution port (43) on the end face opposed with sliding plate (50) on the swash plate (40)
With high pressure oil-distribution port (44), the high and low pressure oil-distribution port (44,43) and grease chamber (53a) intermittent communication, the swash plate (40)
The upper bearing surface opposed with end seat (33) has the cylindrical sliding support face (45) being cylindrically shaped, the cylinder branch of the swash plate (40)
Have in bearing surface (45) and be configured as the flute profile low pressure port (46) and flute profile high-pressure mouth (47) of flute profile, the flute profile low pressure port (46) and
Flute profile high-pressure mouth (47) connection corresponding with low pressure oil-distribution port (43) and high pressure oil-distribution port (44) respectively.
3. tandem axial plunger pump according to claim 2, it is characterised in that: the cylindrical sliding support face of the swash plate (40)
(45) there is the connection notch of the second cavity (35) of connection flute profile low pressure port (46) and sliding plate formula axis plunger pump shell on
(48).
4. tandem axial plunger pump according to claim 1, it is characterised in that: the sliding plate (50) and swash plate (40) it
Between be folded with valve plate (90), the sliding plate (50) be supported on valve plate (90) and with valve plate (90) keep be slidably matched,
High and low pressure is provided on the valve plate (90) with head piece (93,92), hydraulic oil flows through swash plate (40) under piston reciprocation effect
On flow oil groove (42), on valve plate (90) in head piece, the grease chamber (53a) of sliding plate (50), oil-through-hole (53) and plunger
Sucking, the discharge of hydraulic oil are realized in heart hole (72).
5. tandem axial plunger pump according to claim 1, it is characterised in that: one end of the main shaft (10) is supported on
In first bearing (21), other end end is connected through flow sliding plate subcomponent and by axle sleeve (15), axle sleeve (15) branch
It holds on end seat (33), the first bearing (21) is set as radial thrust bearing, and the main shaft (10) and cylinder body (80) are revolving
It changes a job when making, hydraulic axial power is transferred on shell by cylinder body through first bearing (21).
6. tandem axial plunger pump according to claim 1, it is characterised in that: described cylinder body (80) one end is provided with only
Oil liquid is allowed to enter the check valve (110) of plunger hole (81) from housing hollow, the check valve (110) includes to connect with cylinder body (80)
The valve body (111) connect, the spool (112) that valve inner is set, the retaining ring (114) being fixed on valve body (111) and setting
Spring (113) between spool (112) and retaining ring (114), the check valve (110) only allow low pressure oil liquid the from shell
Two cavitys (35) are flowed to plunger hole (81) direction of cylinder body.
7. tandem axial plunger pump according to claim 1, it is characterised in that: swash plate (40) peripheral part is provided with
The bearing stopper (41a) of protrusion is folded with 3rd bearing between the sliding plate (50) periphery and bearing stopper (41a) inside
(23), the sliding plate (50) is supported on 3rd bearing (23) with radially constrained state.
8. tandem axial plunger pump according to claim 7, it is characterised in that: be arranged in the flow sliding plate pair side
There is restraint device, the side that the restraint device is included in sliding plate (50) close hydrostatic support face (51) has raised outward
Stopper section (57) and the clamping close device (140) being arranged on bearing stopper (41a), the clamping close device (140) is with about
The mode that Shu Suoshu 3rd bearing (23) is displaced outwardly limits sliding plate (50) far from swash plate (40) end face.
9. tandem axial plunger pump according to claim 1, it is characterised in that: described two sliding plate formula axis plunger pumps
In main shaft (10) end of any one sliding plate formula axis plunger pump be connected with slippage pump (39) or main pump.
10. tandem axial plunger pump as claimed in any of claims 1 to 10, it is characterised in that: the plunger
(70) rod-plunger of bulb or the spherical surface with universal hinge are provided with comprising the rod-plunger with pyramidal structure or both ends
One kind of plunger, described plunger (70) one end can the mode that reciprocatingly slides of opposing cylinder (80) be inserted into the plunger holes of cylinder body (80)
(81) in, the other end is fixed on the plunger ball of sliding plate (50) with opposite sliding plate (50) end face far from state that is limited and can fascinating
In nest (58), the large aperture plunger centre bore of connection plunger ball-and-socket (58) and plunger hole (81) is provided on the plunger (70).
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910189021.5A CN110067713A (en) | 2019-03-13 | 2019-03-13 | A kind of tandem axial plunger pump |
| PCT/CN2020/079228 WO2020182206A1 (en) | 2019-03-13 | 2020-03-13 | Tandem-type axial plunger pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910189021.5A CN110067713A (en) | 2019-03-13 | 2019-03-13 | A kind of tandem axial plunger pump |
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| Publication Number | Publication Date |
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| CN110067713A true CN110067713A (en) | 2019-07-30 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201910189021.5A Pending CN110067713A (en) | 2019-03-13 | 2019-03-13 | A kind of tandem axial plunger pump |
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| CN (1) | CN110067713A (en) |
| WO (1) | WO2020182206A1 (en) |
Cited By (6)
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| CN110469476A (en) * | 2019-09-04 | 2019-11-19 | 燕山大学 | A kind of axial plunger pump of permanent magnet swash plate and piston shoes |
| CN110513261A (en) * | 2019-09-04 | 2019-11-29 | 燕山大学 | A kind of axial plunger pump of symmetric double valve plate |
| CN111271338A (en) * | 2020-02-22 | 2020-06-12 | 东莞海特帕沃液压科技有限公司 | Filling mechanism of oil cylinder and rear-loading garbage truck |
| WO2020182205A1 (en) * | 2019-03-13 | 2020-09-17 | 青岛科而泰控股有限公司 | Duplex axial plunger motor |
| WO2020182206A1 (en) * | 2019-03-13 | 2020-09-17 | 青岛科而泰控股有限公司 | Tandem-type axial plunger pump |
| CN114412742A (en) * | 2021-10-28 | 2022-04-29 | 中国航发西安动力控制科技有限公司 | Double-output axial plunger pump |
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Effective date of registration: 20240125 Address after: Room J9296, 7th Floor, Building 7, No. 328 Jiajian Road, Jiading District, Shanghai, 2018 Applicant after: Shanghai Qiangtian Drive Technology Co.,Ltd. Guo jiahuodiqu after: Zhong Guo Address before: 610041 No. 6, D District, Tianfu Software Park, 599 Century City South Road, Chengdu High-tech Zone, Sichuan, China. Applicant before: CHENGDU ZHONGWU LIANCHUANG TECHNOLOGY CO.,LTD. Guo jiahuodiqu before: Zhong Guo |