CN106014901A - Pressure compensation type end face oil distribution double-row radial plunger variable pump with annular piston - Google Patents
Pressure compensation type end face oil distribution double-row radial plunger variable pump with annular piston Download PDFInfo
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- CN106014901A CN106014901A CN201610450228.XA CN201610450228A CN106014901A CN 106014901 A CN106014901 A CN 106014901A CN 201610450228 A CN201610450228 A CN 201610450228A CN 106014901 A CN106014901 A CN 106014901A
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- variable
- plunger
- pump
- end cap
- cylinder body
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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
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
- F04B1/113—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the inner ends of the cylinders
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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
- 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
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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
- 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
- F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
- F04B53/162—Adaptations of cylinders
Abstract
The invention discloses a pressure compensation type end face oil distribution double-row radial plunger variable pump with an annular piston. The plunger variable pump comprises a transmission shaft. The transmission shaft is provided with two cylinder bodies in parallel. One cylinder body is provided with an annular groove and the pressure compensation annular piston. A row of radial plunger holes are formed in the outer circular surface of each cylinder body in parallel. Each plunger hole is provided with a plunger. A return spring is installed between the bottom of each plunger hole and the bottom of the corresponding plunger. Each plunger is provided with a piston shoe. The tops of the piston shoes are pressed on the inner circles of needle bearings fixed to the inner circles of stators. The upper side and lower side of one stator are compressed by variable pistons, and the left side and right side of the stator are compressed by friction blocks. The friction blocks are compressed and positioned through pump end covers. The variable pistons are symmetrically installed in a circular hole of a middle shell. Variable end covers are correspondingly installed on a boss located outside the circular hole of the middle shell. Variable springs are compressed between the variable end covers and the variable pistons. The pressure compensation type end face oil distribution double-row radial plunger variable pump with the annular piston has the advantages of being stable to work, high in continuous operational capability, free of axial force and capable of achieving automatic hydraulic compensation.
Description
Technical field
The invention belongs to radial plunger pump technical field, be specifically related to the pressure-compensated of a kind of annular piston
End face oil distributing biserial radial piston variable displacement pump.
Background technology
Radial plunger pump is widely used in the middle of reality.The flow mode of radial plunger pump mainly has two at present
Kind, including axle flow and check valve flow.For the pump of axle flow, needs are processed multiple on pintle
Axial hole and radial groove, make the intensity of axle reduce, and processed complex degree increases, and pintle and support shaft are divided
Opening is two parts, and its support pattern is complicated, and the most common pintle is all cantilever design, during work
Vibration and bending can be produced, be unfavorable for the long time continuous working of pump, it addition, the most existing by solid
The mode of oil is joined in orientation, and such as axle flow, the method not compensated abrasion, when working long hours
Can aggravate after abrasion to reveal.And for check valve flow, be the pressure by pump inner chamber body or vacuum,
Acting on check valve, make valve open or close, in assignment process, the acting of fluid spring to be overcome, can damage
Losing the energy of a part, the spring element on check valve also compares difficult design, and is susceptible to fatigue rupture.
In view of axle flow and the check valve flow two ways of radial plunger pump exist above-mentioned deficiency, so
Patent " the radial plunger of biserial without axial force of a kind of end face oil distributing of Patent No. CN104358664A
Pump " in propose the valve plate distribution mode being similar to axial plunger pump, but this patent yet suffers from following
Some weak point: its structure being arranged symmetrically with structure elimination axial force by two valve plates is complex；
Plunger backhaul jump ring mounting groove difficulty of processing is big；Abrasion between stator and piston shoes is relatively big, is unfavorable for that pump is long
Time Continuous works.
Summary of the invention
In order to overcome the shortcoming of above-mentioned prior art, it is an object of the invention to provide a kind of annular piston
Pressure-compensated end face oil distributing biserial radial piston variable displacement pump, compact overall structure, easy for installation；Intensity
Height, working stability and continuous firing ability are strong；Have without axial force, the advantage that automatic hydraulic compensates.
In order to achieve the above object, this invention takes following technical scheme:
The pressure-compensated end face oil distributing biserial radial piston variable displacement pump of a kind of annular piston, including power transmission shaft
14, the middle part on power transmission shaft 14 is provided with the first cylinder body 24 and the second cylinder body 15, the first cylinder body side by side
24 have a cannelure 37, pressure compensation annular piston 16 in the side relative with the second cylinder body 15
It is contained in cannelure 37 and compresses with the second cylinder body 15, the first cylinder body 24 and cylindrical of the second cylinder body 15
Have string plunger hole 32 radially on face the most abreast, each plunger hole 32 is fitted with one
Plunger 29, bottom plunger hole 32 and bottom plunger 29 between equipped with retracting spring 31, plunger 29 is pacified
Equipped with piston shoes 28, being connected by ball pivot between plunger 29 and piston shoes 28, the top of piston shoes 28 is pressed in
One needle bearing 22 and the inner ring of the second needle bearing 17, the first needle bearing 22 and the second needle roller axle
Hold on 17 inner rings being separately fixed at the first stator 5 and the second stator 9, up and down the two of the first stator 5
Side is compressed by two the first variable pistons 3, and the left and right sides is by the first brake pad 35 and the second brake pad 33
Compress；The both sides up and down of the second stator 9 are compressed by two the second variable pistons 8, and the left and right sides is again by
One brake pad 35 and the second brake pad 33 compress, and the first brake pad 35 and the second brake pad 33 fill respectively
In the draw-in groove of middle casing 7, and by the first pump end cap 27 and rectangular boss of the second pump end cap 10
45 carry out compressing location, during two the first variable pistons 3 and two the second variable piston 8 symmetries are contained in
Between housing 7 circular hole in, the boss outside the circular hole of middle casing 7 is respectively provided with two the most accordingly
One variable end cap 4 and two the second variable end caps 6, two the first variable end caps 4 and two the first variablees
Two the first variable big springs 21 and two the first variable little springs 20 it are compressed with respectively between piston 3,
Two the second variablees it are compressed with respectively big between two the second variable end caps 6 and two the second variable pistons 8
Spring 19 and two the second variable little springs 18；
First cylinder body 24 has towards the bottom of each plunger hole 32 of the side of the first pump end cap 27
One slotted hole 36, the second cylinder body 15 is towards each plunger hole 32 of the side of the second pump end cap 10
Bottom the most all has a slotted hole 36, has bottom cannelure 37 on corresponding each plunger hole axis
One screwed hole 38, check valve 23 is contained in screwed hole 38, first cylinder body the 24, second cylinder body 15
Compress with first valve plate the 1, second valve plate 11 respectively, the first valve plate 1 and the second valve plate 11
It is separately mounted on the first pump end cap 27 and the second pump end cap 10, the first pump end cap 27 and the second pump end
Cover 10 structures identical, be separately mounted to middle casing 7 both sides, the first pump end cap 27 and the second pump end cap
10 are supported by two pump upper brackets 47 and a pump lower carriage 46 respectively, and power transmission shaft 14 two ends are passed through
Two the first rolling bearings 26 and two the second rolling bearings 12 are supported on the first pump end cap 27 and second
On pump end cap 10.
The first described valve plate 1 and the second valve plate 11 all have mutually isolated oil suction arc groove 39 He
Slotted hole 36 on force feed arc groove 40, their distribution radius and the first cylinder body 24 and the second cylinder body 15
Distribution radius equal, and connect with the slotted hole 36 in corresponding orientation；A left side on first pump end cap 27
Fuel feed hole 41 and left oil outlet 42 respectively with oil suction arc groove 39 and the force feed arc groove 40 of the first valve plate 1
Connection, right fuel feed hole 43 on the second pump end cap 10 and right oil outlet 44 respectively with the second valve plate 11
On oil suction arc groove 39 connect with force feed arc groove 40.
Described piston shoes 28 top is spacing by the first return ring 2 and the second return ring 34 respectively, first time
Cheng Huan 2 and the second return ring 34 are respectively and fixedly installed to the first needle bearing 22 and the second needle bearing
On the inner ring of 17.
The top of described piston shoes 28 is cambered surface, and radius of curvature and the first needle bearing 22 and second roll
The inner radii of needle bearing 17 is identical.
Convex with the first variable end cap 4 and the second adjacent side of variable end cap 6 of described middle casing 7
On platform, equipped with two displacement transducers 30, displacement transducer 30 is connected with middle casing 7 by screw thread,
It is fixed that displacement transducer 30 and the first stator 5 and the second stator 9 compress to measure the first stator 5 and second
The center displacement of son 9.
The first described rolling bearing 26 and the second rolling bearing 12 and clutch shaft bearing end cap 25 and second
Bearing (ball) cover 13 connects, and the inner ring of the first rolling bearing 26 and the second rolling bearing 12 is press respectively against biography
On the shoulder of moving axis 14 correspondence.
Described clutch shaft bearing end cap 25 and the second bearing (ball) cover 13 are respectively towards the first rolling bearing
26 and second rolling bearing 12 side sealing ring is installed.
The first described variable end cap 4 and the second variable end cap 6 and the first variable piston 3 and second become
Between amount piston 8 and middle casing 7, sealing ring is installed.
The cannelure 37 of the inner ring of described pressure compensation annular piston 16 and outer ring and the first cylinder body 24
Between sealing ring is installed.
The invention have the advantages that
1) compact conformation, intensity is high, and these pump configuration parts are less, symmetrical, and installation dimension is relatively
Little, biserial plunger is arranged, space availability ratio is high.
2) stator and needle bearing match, and in work process, mechanical wear reduces.
3) automatic hydraulic compensates, and reveals and reduces, and working stability and continuous firing ability are strong.
4) this pump overall structure is symmetrical, and is provided with pressure compensation annular piston, without axial force.
5) stroking mechanism of this pump can use hydraulic variable flow structure, it would however also be possible to employ servomotor variable
Structure.
6) backhaul of plunger uses plunger base to install the version of retracting spring, simple in construction, peace
Dress is convenient.
Accompanying drawing explanation
Fig. 1 is the axial sectional view of the present invention.
Fig. 2 is the sectional view of the Section A-A of Fig. 1 of the present invention.
Fig. 3 is the left view of the first cylinder body 24.
Fig. 4 is the right view of the first cylinder body 24.
Fig. 5 is the left view of the first pump end cap 27.
Fig. 6 is the right view of the first pump end cap 27.
Fig. 7 is the sectional view of the section B-B of the first pump end cap 27.
Fig. 8 is the left view of the second pump end cap 10.
Fig. 9 is the sectional view in the C-C cross section of the second pump end cap 10.
Figure 10 is the left view of valve plate.
Detailed description of the invention
Below in conjunction with the accompanying drawings the present invention is described in detail.
With reference to Fig. 1, Fig. 2, Fig. 3, Fig. 4, Fig. 5, the pressure-compensated end face of a kind of annular piston is joined
Oil biserial radial piston variable displacement pump, including power transmission shaft 14, the middle part on power transmission shaft 14 is provided with the side by side
One cylinder body 24 and the second cylinder body 15, and being connected by flat key with power transmission shaft 14, the first cylinder body 24 with
The side that second cylinder body 15 is relative has a cannelure 37, and pressure compensation annular piston 16 is contained in ring
Compress in shape groove 37 and with the second cylinder body 15, the periphery of the first cylinder body 24 and the second cylinder body 15 divides
Having string plunger hole 32 radially the most abreast, the number of plunger hole 32 is all in two or more, and all
Even distribution, each plunger hole 32 is fitted with a plunger 29, with plunger 29 bottom plunger hole 32
Equipped with retracting spring 31 between Di Bu, plunger 29 is provided with piston shoes 28, plunger 29 and piston shoes 28
Between connected by ball pivot, can relatively rotate in certain angle, the top of piston shoes 28 is pressed in
One needle bearing 22 and the inner ring of the second needle bearing 17, can mutually slide, the top of piston shoes 28
For cambered surface, and radius of curvature is identical with the inner radii of the second needle bearing 17 with the first needle bearing 22,
Piston shoes 28 top is spacing by the first return ring 2 and the second return ring 34 respectively, the first return ring 2 and the
Two return ring 34 is respectively and fixedly installed on the inner ring of the first needle bearing 22 and the second needle bearing 17,
First needle bearing 22 and the second needle bearing 17 are separately fixed at the first stator 5 and the second stator 9
Inner ring on, the both sides up and down of the first stator 5 are compressed by two the first variable pistons 3, left and right sides quilt
First brake pad 35 and the second brake pad 33 compress；The both sides up and down of the second stator 9 are by two second changes
Amount piston 8 compresses, and the left and right sides is compressed by the first brake pad 35 and the second brake pad 33 again, and first rubs
Cleaning block 35 and the second brake pad 33 are attached separately in the draw-in groove of middle casing 7, and by the first pump end cap
27 and second the rectangular boss 45 of pump end cap 10 carry out compressing location, two the first variable piston 3 Hes
Two the second variable piston 8 symmetries are contained in the circular hole of middle casing 7, outside the circular hole of middle casing 7
Two the first variable end caps 4 and two the second variable end caps 6 it are respectively provided with the most accordingly on boss, first
It is connected by screw between variable end cap 4 and the second variable end cap 6 and middle casing 7, two first changes
Two the first variable big spring 21 Hes it are compressed with respectively between amount end cap 4 and two the first variable pistons 3
Two the first variable little springs 20, between two the second variable end caps 6 and two the second variable pistons 8
It is compressed with two the second variable big springs 19 and two the second variable little springs 18 respectively；
Middle casing 7 with on the boss of the first variable end cap 4 and the second adjacent side of variable end cap 6,
Equipped with two displacement transducers 30, displacement transducer 30 is connected with middle casing 7 by screw thread, displacement
Sensor 30 and the first stator 5 and the second stator 9 compress to measure the first stator 5 and the second stator 9
Center displacement.
With reference to Fig. 1, Fig. 2, Fig. 3, Fig. 4, the first cylinder body 24 towards the side of the first pump end cap 27
The bottom of each plunger hole 32 has a slotted hole 36, and the second cylinder body 15 is towards the second pump end cap
The bottom of each plunger hole 32 of the side of 10 also has a slotted hole 36, bottom cannelure 37
Having a screwed hole 38 on corresponding each plunger hole axis, check valve 23 is contained in screwed hole 38,
First cylinder body the 24, second cylinder body 15 compresses with first valve plate the 1, second valve plate 11 respectively, and first
Valve plate 1 and the second valve plate 11 are separately mounted on the first pump end cap 27 and the second pump end cap 10,
It is attached by screw, carries out circumferentially positioned by pin, the first pump end cap 27 and the second pump end cap
10 structures are identical, are separately mounted to middle casing 7 both sides, the first pump end cap 27 and the second pump end cap 10
Being supported by two pump upper brackets 47 and a pump lower carriage 46 respectively, power transmission shaft 14 two ends pass through two
Individual first rolling bearing 26 and two the second rolling bearings 12 are supported on the first pump end cap 27 and the second pump
On end cap 10, clutch shaft bearing end cap 25 and the second bearing (ball) cover 13 are press respectively against two first axis of rolling
Hold 26 and the outer ring of two the second rolling bearings 12, two the first rolling bearings 26 and two second rollings
The inner ring of dynamic bearing 12 is press respectively against on the shoulder of power transmission shaft 14 correspondence.
With reference to Fig. 1, Fig. 4, Fig. 6, Fig. 7, Fig. 8, Fig. 9, Figure 10, the first valve plate 1 and second
Valve plate 11 all has mutually isolated oil suction arc groove 39 and force feed arc groove 40, their distribution radius
Equal with the distribution radius of the slotted hole 36 on the first cylinder body 24 and the second cylinder body 15, and and respective party
Slotted hole 36 on position connects；Left fuel feed hole 41 on first pump end cap 27 and left oil outlet 42 difference
Connect with oil suction arc groove 39 and the force feed arc groove 40 of the first valve plate 1, the right side on the second pump end cap 10
Fuel feed hole 43 and right oil outlet 44 respectively with the oil suction arc groove 39 on the second valve plate 11 and force feed arc groove
40 connections.
Described clutch shaft bearing end cap 25 and the second bearing (ball) cover 13 are respectively towards the first rolling bearing
26 and second rolling bearing 12 side sealing ring is installed.
The first described variable end cap 4 and the second variable end cap 6 and the first variable piston 3 and second become
Between amount piston 8 and middle casing 7, sealing ring is installed.
The cannelure 37 of the inner ring of described pressure compensation annular piston 16 and outer ring and the first cylinder body 24
Between sealing ring is installed.
The operation principle of the present invention is:
First cylinder body 24 and the second cylinder body 15 rotate, when pump receives braking under the drive of power transmission shaft 14
After signal, by two the first variable pistons 3 of regulation and the displacement of two the second variable pistons 8, thus
Make to have between the first needle bearing 22 and the second needle bearing 17 and power transmission shaft 14 axis certain inclined
Heart amount, and eccentric direction is contrary.Make plunger 29 with the first cylinder body 24 and the second cylinder body 15 turns
Time dynamic, radially reciprocate in plunger hole 32 the most respectively so that the post when plunger 29 moves out
Consent 32 volume increases, and now plunger hole 32 passes through slotted hole 36 and the oil suction arc groove 39 of its underpart
Connection, and then suck fluid from outside, when plunger 29 by left fuel feed hole 41 or right fuel feed hole 43
When being pressed into plunger hole 32, volume reduces, now plunger hole 32 by the slotted hole 36 of its underpart with
Force feed arc groove 40 connects, and then is extruded by fluid by left oil outlet 42 or right oil outlet 44, many
Individual plunger 29 works simultaneously, it is possible to realize continuously from left fuel feed hole 41 or right fuel feed hole
43 suck fluid, get rid of fluid from left oil outlet 42 or right oil outlet 44.
The automatic Compensation Technology of this pump is as follows: owing to the cannelure 37 on the first cylinder body 24 passes through check valve
23 communication channel plunger holes 32 finally connect with force feed arc groove 40, therefore will be filled with certain in cannelure 37
The hydraulic oil of pressure is relative owing to allowing between the first cylinder body 24 and the second cylinder body 15 and power transmission shaft 14
Sliding, therefore under the effect of hydraulic coupling, the first cylinder body 24 and the second cylinder body 15 are annular by pressure compensation
Piston 16 keeps compressing with the first valve plate 1 and the second valve plate 11 respectively.When the first valve plate 1 or
When there is abrasion with the first cylinder body 24 or the second cylinder body 15 respectively in person's the second valve plate 11, hydraulic coupling
The first cylinder body 24 or the second cylinder body 15 can be made to do and corresponding mobile to make up wear extent, simultaneously first
Axial force suffered by cylinder body 24 and the second cylinder body 15 can be offset accordingly, due to the first cylinder body 24 and
There is relative movement between two cylinder bodies 15 and power transmission shaft 14, also ensure that power transmission shaft 14 is not affected by axial force.
Claims (9)
1. a pressure-compensated end face oil distributing biserial radial piston variable displacement pump for annular piston, including passing
Moving axis (14), it is characterised in that: the middle part on power transmission shaft (14) is provided with the first cylinder body (24) side by side
With the second cylinder body (15), the first cylinder body (24) has one in the side relative with the second cylinder body (15)
Individual cannelure (37), pressure compensation annular piston (16) be contained in cannelure (37) and with the second cylinder
Body (15) compresses, and the periphery of the first cylinder body (24) and the second cylinder body (15) is opened the most abreast
There is string plunger hole (32) radially, each plunger hole (32) be fitted with a plunger (29),
Equipped with retracting spring (31), plunger (29) between plunger hole (32) bottom and plunger (29) bottom
On piston shoes (28) are installed, connected by ball pivot between plunger (29) and piston shoes (28), piston shoes (28)
Top be pressed in the first needle bearing (22) and the inner ring of the second needle bearing (17), the first needle roller axle
Hold (22) and the second needle bearing (17) is separately fixed at the first stator (5) and the second stator (9)
Inner ring on, the both sides up and down of the first stator (5) by two first variable pistons (3) compress, left and right
Both sides are compressed by the first brake pad (35) and the second brake pad (33)；Second stator (9) upper and lower
Both sides are compressed by two the second variable pistons (8), and the left and right sides is again by the first brake pad (35) and the
Two brake pads (33) compress, and the first brake pad (35) and the second brake pad (33) are attached separately to centre
In the draw-in groove of housing (7), and by the first pump end cap (27) and the rectangle of the second pump end cap (10)
Boss (45) carries out compressing location, two the first variable pistons (3) and two the second variable pistons (8)
Symmetry is contained in the circular hole of middle casing (7), the most corresponding on the boss outside the circular hole of middle casing (7)
Be respectively provided with two the first variable end caps (4) and two the second variable end caps (6), two first changes
Two the first variable big springs it are compressed with respectively between amount end cap (4) and two the first variable pistons (3)
(21) and two the first variable little springs (20), two the second variable end caps (6) and two second changes
It is compressed with two the second variable big springs (19) respectively between amount piston (8) and two the second variablees are little
Spring (18)；
First cylinder body (24) is towards under each plunger hole (32) of the side of the first pump end cap (27)
Portion all has a slotted hole (36), and the second cylinder body (15) is towards the side of the second pump end cap (10)
The bottom of each plunger hole (32) also have a slotted hole (36), cannelure (37) bottom
Having a screwed hole (38) on corresponding each plunger hole axis, check valve (23) is contained in screwed hole
(38) in, the first cylinder body (24), the second cylinder body (15) respectively with the first valve plate (1), second
Valve plate (11) compresses, and the first valve plate (1) and the second valve plate (11) are separately mounted to first
On pump end cap (27) and the second pump end cap (10), the first pump end cap (27) and the second pump end cap (10)
Structure is identical, is separately mounted to middle casing (7) both sides, the first pump end cap (27) and the second pump end
Lid (10) is supported by two pump upper brackets (47) and a pump lower carriage (46) respectively, power transmission shaft
(14) two ends are supported on by two the first rolling bearings (26) and two the second rolling bearings (12)
On first pump end cap (27) and the second pump end cap (10).
The pressure-compensated end face oil distributing biserial footpath of a kind of annular piston the most according to claim 1
To plunger variable pump, it is characterised in that: described the first valve plate (1) and the second valve plate (11)
All have mutually isolated oil suction arc groove (39) and force feed arc groove (40), their distribution radius and
The distribution radius of the slotted hole (36) on one cylinder body (24) and the second cylinder body (15) is equal, and with phase
The slotted hole (36) in orientation is answered to connect；Left fuel feed hole (41) on first pump end cap (27) and a left side
Oil outlet (42) respectively with oil suction arc groove (39) and force feed arc groove (40) of the first valve plate (1)
Connection, right fuel feed hole (43) on the second pump end cap (10) and right oil outlet (44) are respectively with second
Oil suction arc groove (39) on valve plate (11) connects with force feed arc groove (40).
The pressure-compensated end face oil distributing biserial footpath of a kind of annular piston the most according to claim 1
To plunger variable pump, it is characterised in that: described piston shoes (28) top is respectively by the first return ring (2)
Spacing with the second return ring (34), the first return ring (2) and the second return ring (34) are fixed respectively
It is arranged on the inner ring of the first needle bearing (22) and the second needle bearing (17).
The pressure-compensated end face oil distributing biserial footpath of a kind of annular piston the most according to claim 1
To plunger variable pump, it is characterised in that: the top of described piston shoes (28) is cambered surface, and radius of curvature
Identical with the inner radii of the second needle bearing (17) with the first needle bearing (22).
The pressure-compensated end face oil distributing biserial footpath of a kind of annular piston the most according to claim 1
To plunger variable pump, it is characterised in that: described middle casing (7) with the first variable end cap (4)
With on the boss of the second variable end cap (6) adjacent side, equipped with two displacement transducers (30), displacement
Sensor (30) is connected with middle casing (7) by screw thread, and displacement transducer (30) is fixed with first
Son (5) and the second stator (9) compress to measure the first stator (5) and the bias of the second stator (9)
Displacement.
The pressure-compensated end face oil distributing biserial footpath of a kind of annular piston the most according to claim 1
To plunger variable pump, it is characterised in that: described the first rolling bearing (26) and the second rolling bearing (12)
Connect with clutch shaft bearing end cap (25) and the second bearing (ball) cover (13), the first rolling bearing (26) and
The inner ring of the second rolling bearing (12) is press respectively against on the shoulder that power transmission shaft (14) is corresponding.
The pressure-compensated end face oil distributing biserial footpath of a kind of annular piston the most according to claim 1
To plunger variable pump, it is characterised in that: described clutch shaft bearing end cap (25) and the second bearing (ball) cover (13)
Towards the first rolling bearing (26) and the second rolling bearing (12) side, sealing ring is being installed respectively.
The pressure-compensated end face oil distributing biserial footpath of a kind of annular piston the most according to claim 1
To plunger variable pump, it is characterised in that: the first described variable end cap (4) and the second variable end cap (6)
And first be provided with between variable piston (3) and the second variable piston (8) and middle casing (7)
Sealing ring.
The pressure-compensated end face oil distributing biserial footpath of a kind of annular piston the most according to claim 1
To plunger variable pump, it is characterised in that: the inner ring of described pressure compensation annular piston (16) and outer ring
And between the cannelure (37) of the first cylinder body (24), sealing ring is installed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610450228.XA CN106014901B (en) | 2016-06-21 | 2016-06-21 | A kind of pressure-compensated end face oil distributing biserial radial piston variable displacement pump of annular piston |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610450228.XA CN106014901B (en) | 2016-06-21 | 2016-06-21 | A kind of pressure-compensated end face oil distributing biserial radial piston variable displacement pump of annular piston |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106014901A true CN106014901A (en) | 2016-10-12 |
| CN106014901B CN106014901B (en) | 2018-01-16 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610450228.XA Active CN106014901B (en) | 2016-06-21 | 2016-06-21 | A kind of pressure-compensated end face oil distributing biserial radial piston variable displacement pump of annular piston |
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| CN (1) | CN106014901B (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108266372A (en) * | 2018-03-04 | 2018-07-10 | 太原理工大学 | A kind of valve type flow radial plunger emulsion pump |
| CN108953138A (en) * | 2018-09-18 | 2018-12-07 | 杭州力龙液压有限公司 | Hydraulic planger pump and hydraulic device |
| CN112177843A (en) * | 2020-10-09 | 2021-01-05 | 东莞海特帕沃液压科技有限公司 | Inner curve radial plunger hydraulic motor |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN101368552A (en) * | 2008-09-23 | 2009-02-18 | 北京理工大学 | Heeling moment full-balancing shaft distribution mechanism and bidirectional variable radial ball piston pump |
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| JP2014105621A (en) * | 2012-11-27 | 2014-06-09 | Yanmar Co Ltd | Hydraulic device |
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| CN101368552A (en) * | 2008-09-23 | 2009-02-18 | 北京理工大学 | Heeling moment full-balancing shaft distribution mechanism and bidirectional variable radial ball piston pump |
| DE102012218078A1 (en) * | 2012-10-04 | 2014-04-10 | Robert Bosch Gmbh | High-pressure fuel pump for internal combustion engine used in vehicle, has pump piston that is connected with cam of cam shaft which is provided to drive oil pump or vacuum pump located adjacent to high pressure pump main portion |
| JP2014105621A (en) * | 2012-11-27 | 2014-06-09 | Yanmar Co Ltd | Hydraulic device |
| CN103758721A (en) * | 2013-10-18 | 2014-04-30 | 西安交通大学 | Axial-flow type hydraulic pump with double rows of radial plungers |
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| CN104358664A (en) * | 2014-09-17 | 2015-02-18 | 西安交通大学 | Non-axial force biserial radial piston pump distributing oil on end surface |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN108266372A (en) * | 2018-03-04 | 2018-07-10 | 太原理工大学 | A kind of valve type flow radial plunger emulsion pump |
| CN108266372B (en) * | 2018-03-04 | 2024-02-20 | 太原理工大学 | Valve type flow distribution radial plunger emulsion pump |
| CN108953138A (en) * | 2018-09-18 | 2018-12-07 | 杭州力龙液压有限公司 | Hydraulic planger pump and hydraulic device |
| CN112177843A (en) * | 2020-10-09 | 2021-01-05 | 东莞海特帕沃液压科技有限公司 | Inner curve radial plunger hydraulic motor |
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| Publication number | Publication date |
|---|---|
| CN106014901B (en) | 2018-01-16 |
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