CN106014901B - A kind of pressure-compensated end face oil distributing biserial radial piston variable displacement pump of annular piston - Google Patents
A kind of pressure-compensated end face oil distributing biserial radial piston variable displacement pump of annular piston Download PDFInfo
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- CN106014901B CN106014901B CN201610450228.XA CN201610450228A CN106014901B CN 106014901 B CN106014901 B CN 106014901B CN 201610450228 A CN201610450228 A CN 201610450228A CN 106014901 B CN106014901 B CN 106014901B
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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
-
- 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
A kind of pressure-compensated end face oil distributing biserial radial piston variable displacement pump of annular piston,Including power transmission shaft,Two cylinder bodies are installed side by side on power transmission shaft,One cylinder body is provided with an annular groove and pressure compensation annular piston is housed,The plunger hole of a row radial direction is abreast provided with the periphery of cylinder body respectively,A plunger is fitted with each plunger hole,Retracting spring is housed between plunger hole and plunger base,Piston shoes are installed on plunger,The inner ring for the needle bearing being fixed on stator inner ring is pressed at the top of piston shoes,The both sides up and down of stator are compressed by variable piston,The left and right sides is compressed by brake pad,Brake pad carries out compression positioning by pump end cap,Variable piston is symmetrically in the circular hole of middle casing,Variable end cap is housed accordingly again on boss outside the circular hole of middle casing,Variable spring is compressed with respectively between variable end cap and variable piston,Working stability of the present invention and continuous firing ability is strong,With without axial force,The advantages of automatic hydraulic compensates.
Description
Technical field
The invention belongs to radial plunger pump technical field, and in particular to a kind of pressure-compensated end face oil distributing of annular piston
Biserial radial piston variable displacement pump.
Background technology
Radial plunger pump is widely used among reality.The flow mode of radial plunger pump mainly has two kinds at present, including
Axle flow and unidirectional Flat valve.Pump for axle flow makes axle, it is necessary to process multiple axial holes and radial groove on pintle
Intensity decreases, the increase of processed complex degree, pintle and support shaft be split up into two parts, and its support pattern is complicated, often at present
The pintle seen all is cantilever design, can produce vibration and bending during work, be unfavorable for the long time continuous working of pump, in addition,
It is current existing by way of constant bearing is with oil, such as axle flow, the method not compensated to abrasion, when long-time work
It can aggravate to reveal after wearing.And for unidirectional Flat valve, it is the pressure or vacuum by pump inner chamber body, acts on unidirectional
Valve, valve is set to open or close, fluid will overcome spring to do work in assignment process, can lose the energy of a part, on check valve
Spring element also more difficult design, and fatigue rupture easily occurs.
In view of there is above-mentioned deficiency in the axle flow of radial plunger pump and unidirectional Flat valve two ways, so in Patent No.
Proposed in a kind of CN104358664A patent " end face oil distributing without axial force biserial radial plunger pump " similar to axial columns
The valve plate distribution mode of pump is filled in, but the patent still has some following weak point：It passes through two symmetrical cloth of valve plate
The structure for putting structure elimination axial force is complex；Plunger backhaul jump ring mounting groove difficulty of processing is big；Between stator and piston shoes
Wear larger, be unfavorable for pump long time continuous working.
The content of the invention
The shortcomings that in order to overcome above-mentioned prior art, it is an object of the invention to provide a kind of pressure compensation of annular piston
Formula end face oil distributing biserial radial piston variable displacement pump, compact overall structure are easy for installation；Intensity is high, working stability and continuous firing
Ability is strong；With the advantages of without axial force, automatic hydraulic compensates.
In order to achieve the above object, this invention takes following technical scheme：
A kind of pressure-compensated end face oil distributing biserial radial piston variable displacement pump of annular piston, including power transmission shaft 14, transmission
Middle part on axle 14 is provided with the first cylinder body 24 and the second cylinder body 15 side by side, and the first cylinder body 24 is relative with the second cylinder body 15 one
Side is provided with an annular groove 37, and pressure compensation annular piston 16 is mounted in annular groove 37 and compressed with the second cylinder body 15, the first cylinder
The plunger hole 32 of a row radial direction is abreast provided with the periphery of the cylinder body 15 of body 24 and second respectively, is pacified on each plunger hole 32
Equipped with a plunger 29, retracting spring 31 is housed between the bottom of plunger hole 32 and the bottom of plunger 29, piston shoes are installed on plunger 29
28, connected between plunger 29 and piston shoes 28 by ball pivot, the top of piston shoes 28 is pressed in the first needle bearing 22 and the second needle roller axle
17 inner ring is held, the first needle bearing 22 and the second needle bearing 17 are separately fixed at the inner ring of the first stator 5 and the second stator 9
On, the both sides up and down of the first stator 5 are compressed by two the first variable pistons 3, and the left and right sides is rubbed by the first brake pad 35 and second
Cleaning block 33 compresses；The both sides up and down of second stator 9 are compressed by two the second variable pistons 8, and the left and right sides is again by the first brake pad
35 and second brake pad 33 compress, the first brake pad 35 and the second brake pad 33 are attached separately in the neck of middle casing 7, and are led to
The rectangular boss 45 for crossing the first pump end cap 27 and the second pump end cap 10 carries out compression positioning, two the first variable pistons 3 and two
Second variable piston 8 symmetrically in the circular hole of middle casing 7, is distinguished accordingly again on the boss outside the circular hole of middle casing 7
Equipped with two the first variable end caps 4 and two the second variable end caps 6, two the first variable end caps 4 and two the first variable pistons 3
Between be compressed with two the first variable big springs 21 and two the first variable little springs 20, two Hes of the second variable end cap 6 respectively
Two the second variable big springs 19 and two the second variable little springs 18 are compressed between two the second variable pistons 8 respectively；
The bottom of first cylinder body 24 towards each plunger hole 32 of the side of the first pump end cap 27 is provided with a slotted hole
36, the bottom of the second cylinder body 15 towards each plunger hole 32 of the side of the second pump end cap 10 is also provided with a slotted hole 36,
The bottom of annular groove 37 is corresponded to and a screwed hole 38 is provided with each plunger axially bored line, and check valve 23 is mounted in screwed hole 38, the
One cylinder body 24, the second cylinder body 15 compress with the first valve plate 1, the second valve plate 11 respectively, the 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, and the first pump end cap 27 is identical with the structure of the second pump end cap 10,
The both sides of middle casing 7 are separately mounted to, the first pump end cap 27 and the second pump end cap 10 pass through two pump upper brackets 47 and one respectively
Individual pump lower carriage 46 is supported, and the both ends of power transmission shaft 14 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.
Described the first valve plate 1 and the second valve plate 11 is all provided with mutually isolated oil suction arc groove 39 and force feed arc groove
40, their distribution radius and the distribution radius of the first cylinder body 24 and the slotted hole 36 on the second cylinder body 15 are equal, and with it is corresponding
Slotted hole 36 in orientation connects；Left fuel feed hole 41 and left oil outlet 42 on first pump end cap 27 respectively with the first valve plate 1
Oil suction arc groove 39 connected with force feed arc groove 40, the right fuel feed hole 43 and right oil outlet 44 on the second pump end cap 10 are respectively with second
Oil suction arc groove 39 on valve plate 11 connects with force feed arc groove 40.
The described top of piston shoes 28 is spacing by the first return ring 2 and the second return ring 34 respectively, the first return ring 2 and second
Return ring 34 is respectively and fixedly installed on the inner ring of the first needle bearing 22 and the second needle bearing 17.
The top of described piston shoes 28 is cambered surface, and radius of curvature and the first needle bearing 22 and the second needle bearing 17
Inner radii is identical.
Described middle casing 7 is with the boss of 6 adjacent side of the first variable end cap 4 and the second variable end cap, being equipped with
Two displacement transducers 30, displacement transducer 30 are connected by screw thread with middle casing 7, the stator 5 of displacement transducer 30 and first
Compressed with the second stator 9 to measure the center displacement of the first stator 5 and the second stator 9.
The first described rolling bearing 26 and the second rolling bearing 12 and clutch shaft bearing end cap 25 and second bearing end cap 13
The inner ring of connection, the first rolling bearing 26 and the second rolling bearing 12 is press respectively against corresponding to power transmission shaft 14 on shoulder.
Described clutch shaft bearing end cap 25 and second bearing end cap 13 roll towards the first rolling bearing 26 and second respectively
The side of dynamic bearing 12 is provided with sealing ring.
The first described variable end cap 4 and the second variable end cap 6 and the first variable piston 3 and the second variable piston 8 with
Sealing ring is installed between middle casing 7.
It is provided between the annular groove 37 of the inner ring of described pressure compensation annular piston 16 and outer ring and the first cylinder body 24
Sealing ring.
The present invention has advantages below：
1) compact-sized, intensity is high, and the pump configuration parts are less, and symmetrical, installation dimension is smaller, biserial plunger cloth
Put, space availability ratio is high.
2) stator and needle bearing are engaged, and mechanical wear reduces in work process.
3) automatic hydraulic is compensated, and leakage is reduced, working stability and continuous firing ability is strong.
4) the pump overall structure is symmetrical, and is provided with pressure compensation annular piston, no axial force.
5) stroking mechanism of the pump can use hydraulic variable flow structure, can also use servomotor variant structural.
6) structure type of retracting spring is installed in the backhaul of plunger using plunger base, simple in construction, easy for installation.
Brief description of the drawings
Fig. 1 is the axial sectional view of the present invention.
Fig. 2 is the sectional view of Fig. 1 of the present invention Section A-A.
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 sections of the second pump end cap 10.
Figure 10 is the left view of valve plate.
Embodiment
The present invention is described in detail below in conjunction with the accompanying drawings.
Reference picture 1, Fig. 2, Fig. 3, Fig. 4, Fig. 5, a kind of pressure-compensated end face oil distributing biserial radial plunger of annular piston
Variable pump, including power transmission shaft 14, the middle part on power transmission shaft 14 are provided with the first cylinder body 24 and the second cylinder body 15 side by side, and with transmission
Axle 14 is connected by flat key, and the first cylinder body 24 is provided with an annular groove 37, pressure compensation in the side relative with the second cylinder body 15
Annular piston 16 is mounted in annular groove 37 and compressed with the second cylinder body 15, divides on the periphery of the first cylinder body 24 and the second cylinder body 15
The plunger hole 32 of a row radial direction it is not provided with abreast, the number of plunger hole 32 is uniformly distributed all in two or more, each plunger
A plunger 29 is fitted with hole 32, retracting spring 31 is housed between the bottom of plunger hole 32 and the bottom of plunger 29, on plunger 29
Piston shoes 28 are installed, connected between plunger 29 and piston shoes 28 by ball pivot, can be relatively rotated in certain angle, piston shoes 28
Top be pressed in the inner ring of the first needle bearing 22 and the second needle bearing 17, can mutually slide, the top of piston shoes 28 is arc
Face, and radius of curvature and the first needle bearing 22 are identical with the inner radii of the second needle bearing 17, the top of piston shoes 28 is leaned on respectively
First return ring 2 and the second return ring 34 are spacing, and the first return ring 2 and the second return ring 34 are respectively and fixedly installed to the first needle roller
On the inner ring of the needle bearing 17 of bearing 22 and second, the first needle bearing 22 and the second needle bearing 17 are separately fixed at first and determined
On the inner ring of the stator 9 of son 5 and second, 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 second stator 9 are compressed by two the second variable pistons 8, left
Right both sides are compressed by the first brake pad 35 and the second brake pad 33 again, during the first brake pad 35 and the second brake pad 33 are attached separately to
Between housing 7 neck in, and compression positioning is carried out by the rectangular boss 45 of the first pump end cap 27 and the second pump end cap 10, two
First variable piston 3 and two the second variable pistons 8 are symmetrically mounted 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 are respectively provided with accordingly on boss again, the first variable end cap 4 and the
Be connected by screw between two variable end caps 6 and middle casing 7, two the first variable end caps 4 and two the first variable pistons 3 it
Between be compressed with two the first variable big springs 21 and two the first variable little springs 20, two the second variable end caps 6 and two respectively
Two the second variable big springs 19 and two the second variable little springs 18 are compressed between individual second variable piston 8 respectively；
Middle casing 7 with the boss of 6 adjacent side of the first variable end cap 4 and the second variable end cap, equipped with two positions
Displacement sensor 30, displacement transducer 30 are connected by screw thread with middle casing 7, the stator 5 and second of displacement transducer 30 and first
Stator 9 is compressed to measure the center displacement of the first stator 5 and the second stator 9.
Reference picture 1, Fig. 2, Fig. 3, Fig. 4, the first cylinder body 24 is towards each plunger hole 32 of the side of the first pump end cap 27
Bottom is all provided with a slotted hole 36, and the second cylinder body 15 is towards the bottom of each plunger hole 32 of the side of the second pump end cap 10
A slotted hole 36 is all provided with, the bottom of annular groove 37, which corresponds to, is provided with a screwed hole 38, check valve on each plunger axially bored line
23 are mounted in screwed hole 38, and the first cylinder body 24, the second cylinder body 15 compress with the first valve plate 1, the second valve plate 11 respectively, and first
The valve plate 11 of valve plate 1 and second is separately mounted on the first pump end cap 27 and the second pump end cap 10, is attached by screw,
Carried out by pin circumferentially positioned, the first pump end cap 27 is identical with the structure of the second pump end cap 10, is separately mounted to 7 liang of middle casing
Side, 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, transmission
The both ends of axle 14 are supported on the first pump end cap 27 and the second pump by two the first rolling bearings 26 and two the second rolling bearings 12
On end cap 10, clutch shaft bearing end cap 25 and second bearing end cap 13 are press respectively against two the first rolling bearings 26 and two second rollings
It is right that the inner ring of the outer ring of dynamic bearing 12, two the first rolling bearings 26 and two the second rolling bearings 12 is press respectively against power transmission shaft 14
On the shoulder answered.
Reference picture 1, Fig. 4, Fig. 6, Fig. 7, Fig. 8, Fig. 9, Figure 10, the first valve plate 1 and the second valve plate 11 are all provided with mutually
The oil suction arc groove 39 of isolation and force feed arc groove 40, the slotted hole in their distribution radius and the first cylinder body 24 and the second cylinder body 15
36 distribution radius is equal, and is connected with the slotted hole 36 in corresponding orientation；Left fuel feed hole 41 and a left side on first pump end cap 27
Oil outlet 42 connects with the oil suction arc groove 39 and force feed arc groove 40 of the first valve plate 1 respectively, the right oil-feed on the second pump end cap 10
Hole 43 and right oil outlet 44 connect with the oil suction arc groove 39 on the second valve plate 11 and force feed arc groove 40 respectively.
Described clutch shaft bearing end cap 25 and second bearing end cap 13 roll towards the first rolling bearing 26 and second respectively
The side of dynamic bearing 12 is provided with sealing ring.
The first described variable end cap 4 and the second variable end cap 6 and the first variable piston 3 and the second variable piston 8 with
Sealing ring is installed between middle casing 7.
It is provided between the annular groove 37 of the inner ring of described pressure compensation annular piston 16 and outer ring and the first cylinder body 24
Sealing ring.
The present invention operation principle be：
First cylinder body 24 and the second cylinder body 15 rotate under the drive of power transmission shaft 14, after pump receives brake signal, pass through
The displacement of two the first variable pistons 3 and two the second variable pistons 8 is adjusted, so that the first needle bearing 22 and the second needle roller
There is certain offset, and eccentric direction is opposite between bearing 17 and the axis of power transmission shaft 14.So that plunger 29 is with first
When the cylinder body 15 of cylinder body 24 and second rotates, also radially reciprocated respectively in plunger hole 32 so that when plunger 29 is to outward transport
The volume of plunger hole 32 increase when dynamic, now plunger hole 32 is connected by the slotted hole 36 of its underpart with oil suction arc groove 39, Jin Ertong
Cross left fuel feed hole 41 or right fuel feed hole 43 and suck fluid from outside, when plunger 29 is pressed into plunger hole 32, volume reduces, this
When plunger hole 32 connected by the slotted hole 36 of its underpart with force feed arc groove 40, and then pass through left oil outlet 42 or right oil outlet
44 extrude fluid, and multiple plungers 29 work simultaneously, it is possible to realize continuously from left fuel feed hole 41 or right fuel feed hole
43 suction fluid, fluid is excluded from left oil outlet 42 or right oil outlet 44.
The automatic Compensation Technology of the pump is as follows：Because the annular groove 37 on the first cylinder body 24 passes through the communication channel post of check valve 23
Consent 32 is finally connected with force feed arc groove 40, therefore the hydraulic oil of certain pressure is will be filled with annular groove 37, due to the first cylinder body
24 and second allow between cylinder body 15 and power transmission shaft 14 it is relative slide, therefore the first cylinder body 24 and second in the presence of hydraulic coupling
Cylinder body 15 keeps compressing with the first valve plate 1 and the second valve plate 11 respectively by pressure compensation annular piston 16.Match somebody with somebody when first
For flow table 1 when either the second valve plate 11 wears with the first cylinder body 24 or the second cylinder body 15 respectively, hydraulic coupling can make
One cylinder body 24 or the second cylinder body 15 do corresponding movement to make up wear extent, while suffered by the first cylinder body 24 and the second cylinder body 15
Axial force can offset accordingly, due to having relative movement between the first cylinder body 24 and the second cylinder body 15 and power transmission shaft 14, also protect
Card power transmission shaft 14 is not influenceed by axial force.
Claims (9)
1. a kind of pressure-compensated end face oil distributing biserial radial piston variable displacement pump of annular piston, including power transmission shaft (14), it is special
Sign is：Middle part on power transmission shaft (14) is provided with the first cylinder body (24) and the second cylinder body (15) side by side, and the first cylinder body (24) exists
Relative side is provided with an annular groove (37) with the second cylinder body (15), and pressure compensation annular piston (16) is mounted in annular groove (37)
In and compress with the second cylinder body (15), be abreast provided with a row respectively on the periphery of the first cylinder body (24) and the second cylinder body (15)
The plunger hole (32) of radial direction, a plunger (29), plunger hole (32) bottom and plunger are fitted with each plunger hole (32)
(29) retracting spring (31) is housed between bottom, piston shoes (28) are installed on plunger (29), between plunger (29) and piston shoes (28)
Connected by ball pivot, be pressed in the inner ring of the first needle bearing (22) and the second needle bearing (17) at the top of piston shoes (28), first
Needle bearing (22) and the second needle bearing (17) are separately fixed on the inner ring of the first stator (5) and the second stator (9), and first
The both sides up and down of stator (5) are compressed by two the first variable pistons (3), and the left and right sides is rubbed by the first brake pad (35) and second
Block (33) compresses；The both sides up and down of second stator (9) are compressed by two the second variable pistons (8), and the left and right sides is rubbed by first again
Cleaning block (35) and the second brake pad (33) compress, and the first brake pad (35) and the second brake pad (33) are attached separately to middle casing
(7) in neck, and compression positioning is carried out by the rectangular boss (45) of the first pump end cap (27) and the second pump end cap (10), two
Individual first variable piston (3) and two the second variable pistons (8) are symmetrically mounted in the circular hole of middle casing (7), middle casing (7)
Circular hole outside boss on be respectively provided with two the first variable end caps (4) and two the second variable end caps (6) accordingly again, two
Two the first variable big springs (21) and two are compressed between first variable end cap (4) and two the first variable pistons (3) respectively
Individual first variable little spring (20), two are compressed with respectively between two the second variable end caps (6) and two the second variable pistons (8)
Individual second variable big spring (19) and two the second variable little springs (18)；
The bottom of first cylinder body (24) towards each plunger hole (32) of the side of the first pump end cap (27) be provided with one it is oval
Hole (36), the bottom of the second cylinder body (15) towards each plunger hole (32) of the side of the second pump end cap (10) are also provided with one
Slotted hole (36), annular groove (37) bottom, which corresponds to, is provided with a screwed hole (38), check valve (23) on each plunger axially bored line
In screwed hole (38), the first cylinder body (24), the second cylinder body (15) respectively with the first valve plate (1), the second valve plate (11)
Compressing, the 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),
First pump end cap (27) is identical with second pump end cap (10) structure, is separately mounted to middle casing (7) both sides, the first pump end cap
(27) supported respectively by two pump upper brackets (47) and a pump lower carriage (46) with the second pump end cap (10), power transmission shaft (14)
Both ends are supported on the first pump end cap (27) and second by two the first rolling bearings (26) and two the second rolling bearings (12)
On pump end cap (10).
2. a kind of pressure-compensated end face oil distributing biserial radial piston variable displacement pump of annular piston according to claim 1,
It is characterized in that：Described the first valve plate (1) and the second valve plate (11) be all provided with mutually isolated oil suction arc groove (39) and
Arc groove (40) is pressed oil, the distribution of the slotted hole (36) in their distribution radius and the first cylinder body (24) and the second cylinder body (15) is partly
Footpath is equal, and is connected with the slotted hole (36) in corresponding orientation；Left fuel feed hole (41) and a left side on first pump end cap (27) is fuel-displaced
Hole (42) connects with the oil suction arc groove (39) and force feed arc groove (40) of the first valve plate (1) respectively, on the second pump end cap (10)
Right 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)
Connection.
3. a kind of pressure-compensated end face oil distributing biserial radial piston variable displacement pump of annular piston according to claim 1,
It is characterized in that：It is spacing by the first return ring (2) and the second return ring (34) respectively at the top of described piston shoes (28), the first backhaul
Ring (2) and the second return ring (34) are respectively and fixedly installed to the inner ring of the first needle bearing (22) and the second needle bearing (17)
On.
4. a kind of pressure-compensated end face oil distributing biserial radial piston variable displacement pump of annular piston according to claim 1,
It is characterized in that：The top of described piston shoes (28) is cambered surface, and radius of curvature and the first needle bearing (22) and the second needle roller
The inner radii of bearing (17) is identical.
5. a kind of pressure-compensated end face oil distributing biserial radial piston variable displacement pump of annular piston according to claim 1,
It is characterized in that：Described middle casing (7) is convex with the first variable end cap (4) and the adjacent side of the second variable end cap (6)
On platform, equipped with two displacement transducers (30), displacement transducer (30) is connected by screw thread with middle casing (7), displacement sensing
Device (30) is compressed to measure the center displacement of the first stator (5) and the second stator (9) with the first stator (5) and the second stator (9).
6. a kind of pressure-compensated end face oil distributing biserial radial piston variable displacement pump of annular piston according to claim 1,
It is characterized in that：Described the first rolling bearing (26) and clutch shaft bearing end cap (25) connection, the second described rolling bearing
(12) connected with second bearing end cap (13), the inner ring of the first rolling bearing (26) and the second rolling bearing (12) is press respectively against biography
Corresponding to moving axis (14) on shoulder.
7. a kind of pressure-compensated end face oil distributing biserial radial piston variable displacement pump of annular piston according to claim 6,
It is characterized in that：Described clutch shaft bearing end cap (25) and second bearing end cap (13) are respectively towards the first rolling bearing (26)
Sealing ring is installed with the second rolling bearing (12) side.
8. a kind of pressure-compensated end face oil distributing biserial radial piston variable displacement pump of annular piston according to claim 1,
It is characterized in that：The first described variable end cap (4) and the second variable end cap (6) and the first variable piston (3) and second become
Sealing ring is installed between amount piston (8) and middle casing (7).
9. a kind of pressure-compensated end face oil distributing biserial radial piston variable displacement pump of annular piston according to claim 1,
It is characterized in that：The annular groove (37) of the inner ring of described pressure compensation annular piston (16) and outer ring and the first cylinder body (24) it
Between 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 CN106014901A (en) | 2016-10-12 |
| CN106014901B true CN106014901B (en) | 2018-01-16 |
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| 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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| Publication number | Priority date | Publication date | Assignee | Title |
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| 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 |
| CN112177843B (en) * | 2020-10-09 | 2023-05-16 | 东莞市普林斯机电设备有限公司 | Inner curve radial plunger hydraulic motor |
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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 |
| CN103696921A (en) * | 2013-12-13 | 2014-04-02 | 西安交通大学 | Valve flow distribution radial plunger hydraulic pump adopting hydraulic pressure return stroke |
| 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 |
| 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 |
| 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 |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2014105621A (en) * | 2012-11-27 | 2014-06-09 | Yanmar Co Ltd | Hydraulic device |
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2016
- 2016-06-21 CN CN201610450228.XA patent/CN106014901B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| 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 |
| CN103696921A (en) * | 2013-12-13 | 2014-04-02 | 西安交通大学 | Valve flow distribution radial plunger hydraulic pump adopting hydraulic pressure return stroke |
| 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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| CN106014901A (en) | 2016-10-12 |
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