CN1297745C - Swing angle type radial plunger variable pump - Google Patents
Swing angle type radial plunger variable pump Download PDFInfo
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- CN1297745C CN1297745C CNB2004100442874A CN200410044287A CN1297745C CN 1297745 C CN1297745 C CN 1297745C CN B2004100442874 A CNB2004100442874 A CN B2004100442874A CN 200410044287 A CN200410044287 A CN 200410044287A CN 1297745 C CN1297745 C CN 1297745C
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- pintle
- plunger
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Abstract
The present invention discloses a swing angle type radial plunger variable pump used for balancing static pressure and dynamic pressure, which solves the problem that shafts twist under the operating condition of transient load. The swing rack of a stator and the rotating shaft of the swing rack are arranged in a pump body, and the roller bearing of the swing rack is positioned on the swing rack of the stator and is matched and connected with one end of the bracket of the stator, and the other end of the bracket of the stator is connected with the stator. The slipper of a plunger connecting rod is provided with a static pressure balance chamber, and both sides of the slipper of the plunger connecting rod are provided with retaining rings; definite matching gaps are formed between the slipper of the plunger connecting rod and the retaining rings. A rotor drives the stator to synchronously rotate via a plunger; both ends of the inner circle of the rotor are provided with needle bearings matched with flow distribution shafts. The rotor and the stator of the present invention basically synchronously rotate, and the slipper of the plunger connecting rod slides on the inner surface of the stator at the line speed of 0 or at low line speed of 0 to 40 r / min; the structural dimension is smaller 1/3 than the radical dimension of a similar parameter radial plunger pump. The present invention changes the eccentricity e between the stator and the rotor by the swing angle of the swing rack of the stator to realize the variable.
Description
Technical field:
The present invention relates to a kind of swing angle type radial piston variable displacement pump, be applicable to the radial piston variable displacement pump of the above discharge capacity of 500mL/r specifically.
Background technique:
The fifties, for the axial and radial piston variable displacement pump more than the 500mL/r, the overwhelming majority was from external import so far, domestic a few family hydraulic parts factory, just researched and developed on probationly for the high-pressure large-displacement oil hydraulic pump, but the performance technologies index is lower, does not satisfy the requirement of industrial production development far away.Tool preliminary inves-tigation China every year will be with the above high-pressure large-displacement oil hydraulic pump of external import 500mL/r more than 1500, particularly metal forming machinery and ship machinery consumption are very big, every 500mL/r high-pressure large-displacement oil hydraulic pump, import price are all (20-40) ten thousand yuan, and the import cycle is long.
The 500mL/r radial piston variable displacement pump is a kind of in the world at present novel radial piston variable displacement pump.In 90 years 0 generations, had only Germany " De Make company " to produce this type high-pressure large-displacement radial plunger pump so far, its structural feature and same parameter axial piston pump ratio, radial dimension is big, and is simple in structure, better than the kinematic pair force-bearing situation of axial piston pump and other types pump.Its main performance index is: rated pressure is 30Mpa, and maximum pressure can reach 40Mpa, noise 86dB, and than same parameter axial pump low (4-5) dB, total efficiency is about 86%, the life-span is more than 6000 hours.So this pump is the reasonable a kind of radial piston variable displacement pump of performance in the world.Yet the problem that this pump mainly exists is: 1, owing to piston shoes tape spool bearing structure, when not only complex structure, and piston shoes contacted with stator, piston shoes did not have reaction thrust, and contact force is too big, and is fragile.2, piston shoes are in stator inner surface low speed sliding process, and piston shoes do not have guiding device, and the piston shoes corner angle contact easily with between the two side cover plate metals in the movement process, cause wearing and tearing of biside plate and piston shoes or damage.3, rotor and plunger radial power, balance of axial force can not effectively be controlled.4, piston shoes adopt ductile cast iron material, and often mill bumps into foam shape particle.
Summary of the invention
The swing angle type radial piston variable displacement pump that the purpose of this invention is to provide a kind of quiet, kinetic pressure balancing is with the problem that solves the piston shoes that existing radial plunger pump exists and biside plate is easy to wear, rotor and plunger radial power, balance of axial force can not effectively be controlled.
Swing angle type radial piston variable displacement pump of the present invention, comprise the pump housing, be placed in the stator in the pump housing, be arranged at rotor eccentric with it in the stator, be positioned at the pintle at rotor axis place, be installed in last locating stud and following locating stud on the pintle, be positioned at the pump cover of the pump housing one end, be installed on the setting sleeve on the pump cover, the axle envelope, shaft seal cover, roller bearing, be placed in the live axle on the roller bearing, be installed on the cross key on the live axle, the joiner that connects with rotor by cross key, pump cover and live axle and pintle coaxial line in above-mentioned parts, axially have high pressure oil drainage hole and low pressure oil-sucking hole along it in the pintle, have radially damping controller of the static balance groove that is interconnected and pintle on the pintle, be provided with the plunger damping controller in plunger base; Axis perpendicular to pintle on rotor is equipped with plunger, is distributed with dispensing window on the pintle; Be mounted with servovalve variable cylinder assembly at the top of the described pump housing; Be mounted with stator rocker and rocker rotating shaft in the pump housing, the rocker roller bearing that is positioned on the stator rocker cooperates connection with an end of stator bracket, and the other end of stator bracket links to each other with stator, and the stator bracket two ends are identical; Plunger is connected with piston shoes by ball pivot becomes the plunger connecting rod piston shoes, and the plunger connecting rod piston shoes are provided with the static balance chamber, and plunger connecting rod piston shoes both sides are provided with retaining ring, plunger connecting rod piston shoes and retaining ring matching gap; Rotor drives stator by plunger and rotates synchronously; The circle two ends are provided with needle bearing in rotor, and needle bearing cooperates with pintle; Axially have axle center control oil channel and the control oil channel that is interconnected along pintle, the termination of axle center control oil channel is mounted with the axial damping controller of pintle, pintle radially damping controller is communicated with the axle center control oil channel, is mounted with the oblique damping controller of pintle on the direction that becomes 30～60 degree angles with control oil channel.
Plunger can connect by straight pin with piston shoes among the present invention.In the middle of rotor inner hole copper sheathing is housed, copper sheathing cooperates with pintle.
Rotor of the present invention and the rotation of stator basic synchronization, the present invention changes stator and rotor eccentricity e by stator rocker pivot angle, promptly realizes variable.The present invention can guarantee that rotor and pintle fastness turn round film lubrication is arranged, and have solved seize problem under the transition load behavior under any operating mode.Stroking mechanism of the present invention adopts the stator pivot angle to change the variable principle of eccentric e, its main performance index is: rated pressure 32Mpa, maximum pressure 45Mpa, noise (83-85) dB, total efficiency is more than 86%, life-span is more than 8000 hours, dynamic response time (50-80) ms, variable format is multiple.Plunger of the present invention adopts the skid shoe type structure, the plunger connecting rod piston shoes are provided with the static balance chamber, by the damping control loop, control plunger connecting rod piston shoes are to stator inner surface contact force size, can guarantee that plunger connecting rod piston shoes and stator do not have relative movement substantially, or relative movement very little (0-40r/min) arranged, can make plunger connecting rod piston shoes and stator inner surface that certain film lubrication is arranged again, big thus amplitude reduces the peripheral velocity of plunger connecting rod piston shoes in the stator inner surface motion, improves the life-span of pump, the noise of reduction pump.Plunger connecting rod piston shoes both sides are provided with retaining ring, plunger connecting rod piston shoes and retaining ring have certain matching gap, and the plunger connecting rod piston shoes can only move in the groove of retaining ring, the plunger connecting rod piston shoes have so just been solved in case when stator inner surface moves, the piston shoes corner angle bump the mill stator bracket, cause both to damage.Because rotor, stator, stator bracket are littler by 1/3 than like product, so physical dimension of the present invention is littler by 1/3 than similar parameter radial plunger pump radial dimension.
Description of drawings
Fig. 1 is a structural representation of the present invention;
Fig. 2 is the enlarged view of plunger connecting rod piston shoes portion among Fig. 1;
Fig. 3 is the structural representation of pintle among the present invention;
Fig. 4 is the right elevation of Fig. 3;
Fig. 5 is that pintle shown in Figure 3 is along A-A line view;
Fig. 6 is that pintle shown in Figure 3 is along B-B line view;
Fig. 7 is the structural representation of plunger among the present invention;
Fig. 8 is the structural representation of retaining ring among the present invention;
Fig. 9 is the schematic representation that rotor of the present invention and stator are subjected to radial load.
Embodiment
The following examples can make those skilled in the art more fully understand the present invention, but do not limit the present invention in any way.
The reference character implication is as follows:
The pump housing 1, cross key 2, live axle 3, roller bearing (4,21), pump cover 5, joiner 6, rocker roller bearing (7,17), stator rocker 8, servovalve variable cylinder assembly 9, stator 10, piston shoes 11, static balance chamber 11-1, plunger 12, rotor 13, needle bearing (14,18), pintle 15, retaining ring 16, copper sheathing 19, stator bracket 20, setting sleeve 22, axle envelope 23, shaft seal cover 24, last locating stud 25, following locating stud 26, rocker rotating shaft 27, straight pin 28, static balance groove 29, high pressure oil drainage hole 30, low pressure oil-sucking hole 31, dispensing window 32, axle center control oil channel 33, control oil channel 34, pintle is damping controller (I radially, II), the axial damping controller III of pintle, the oblique damping controller IV of pintle, plunger damping controller V, stator radial force F, the stressed F of rocker roller bearing
1, F
2, needle bearing is subjected to rotor radial power F
3, F
4, the stressed F of rotor radial
i, rotor and pintle static balance power F
i'
As shown in the figure, swing angle type radial piston variable displacement pump of the present invention, comprise the pump housing 1, be placed in stator 10 in the pump housing 1, be arranged at rotor 13 eccentric with it in the stator 10, be positioned at place, rotor 13 axle center pintle 15, be installed in last locating stud 25 on the pintle 15 and following locating stud 26, upper and lower locating stud the 25, the 26th, make pintle 15 locate and can not rotate.Be positioned at the pump cover 5 of the pump housing 1 one ends, be installed on the setting sleeve 22 on the pump cover 5, axle envelope 23, shaft seal cover 24, roller bearing 4, roller bearing 21, be placed in the live axle 3 on roller bearing 4 and the roller bearing 21, be installed on the cross key 2 on the live axle 3, the joiner 6 that connects with rotor 13 by cross key 2, pump cover 5 and live axle 3 and pintle 15 coaxial lines in above-mentioned parts, axially have high pressure oil drainage hole 30 and low pressure oil-sucking hole 31 along it in the pintle 15, have radially damping controller I of the static balance groove 29 that is interconnected and pintle on the pintle 15, II is provided with plunger damping controller V in plunger 12 bottoms; Axis perpendicular to pintle 15 on rotor 13 is equipped with plunger 12, is distributed with dispensing window 32 on the pintle 15.Be mounted with servovalve variable cylinder assembly 9 at the top of the pump housing 1; Be mounted with stator rocker 8 and rocker rotating shaft 27 in the pump housing 1, the rocker roller bearing 7, the rocker roller bearing 17 that are positioned on the stator rocker 8 cooperate connection to overlap as it with an end of stator bracket 20, the other end of stator bracket 20 links to each other with stator 10, and stator bracket 20 two ends are identical; Plunger 12 adopts the skid shoe type structure, and plunger 12 is connected with piston shoes 11 by ball pivot becomes the plunger connecting rod piston shoes, figure 2 illustrates a kind of Placement, and promptly plunger 12 connects by straight pin 28 with piston shoes 11.The plunger connecting rod piston shoes are provided with static balance chamber 11-1, and plunger connecting rod piston shoes both sides are provided with retaining ring 16, and plunger connecting rod piston shoes and retaining ring 16 have certain matching gap, and rotor 13 drives stator 10 by plunger 12 and rotates synchronously; When 3 rotations of driven by motor transmission shaft, just driven rotor 13 and rotated, because 12 pairs of stator 10 internal surfaces of plunger have certain impacting force, stator also rotates simultaneously.When in a single day the plunger connecting rod piston shoes have relative movement to stator 10, general 0-40r/min, and the plunger connecting rod piston shoes can only move in the groove of retaining ring 16, have so just solved the plunger connecting rod piston shoes in case when stator 10 inner surface movements, the piston shoes corner angle bump mill stator bracket 20, cause both to damage.The circle two ends are provided with needle bearing 14, needle bearing 18 in rotor 13, and needle bearing 14 and needle bearing 18 cooperate with pintle 15.
As shown in Figure 9, stator radial force F is by the stressed F of two ends rocker roller bearing
1, F
2Bear, formed simple beam structure.The stressed F of rotor radial
iMost of static balance power F by rotor and pintle
i' supporting, a part is subjected to rotor radial power F by needle bearing
3, F
4, bear, thereby needle bearing the 14, the 18th, the simple beam structure of bear rotor 13 a part of radial forces, it just begins starting and stops and working during load transient at rotor, and rotor is when proper functioning, by the static balance power F of rotor and pintle
iThe load of ' supporting operating load and variation.Thoroughly solved rotor starting or during stop motion moment the seize problem.
As shown in Figure 6, axially have axle center control oil channel 33 and the control oil channel 34 that is interconnected along pintle 15, the termination of axle center control oil channel 33 is mounted with the axial damping controller III of pintle, pintle radially damping controller I, II is communicated with axle center control oil channel 33, with the direction of 34 one-tenth 30～60 of control oil channel degree angle on be mounted with the oblique damping controller IV of pintle.Pintle radially damping controller I, II in order to control rotor 13 and the balanced radial force of pintle 15 in operation process; Pintle damping controller III, IV are the axial force kinetic pressure balancing of control rotor 13 in operation process.This carries out pressure and oil clearance control to fastness to rotor 13 and pintle 15, guarantees that rotor and pintle fastness turn round under any operating mode film lubrication is arranged, and have solved seize problem under the transition load behavior.The plunger damping controller V of plunger 12 bottoms can control flow and the pressure of plunger connecting rod piston shoes static balance chamber 11-1, and also may command plunger connecting rod piston shoes are to stator 10 internal surface contact force sizes.Because plunger connecting rod piston shoes reaction thrust is controlled, so can accurately determine and pilot plunger 12 and stator 10 impacting force coefficients, can guarantee that plunger connecting rod piston shoes and stator do not have relative movement substantially, or relative movement very little (0-40r/min) arranged, can make plunger connecting rod piston shoes and stator inner surface that certain film lubrication is arranged again, big thus amplitude reduces the peripheral velocity of plunger connecting rod piston shoes in the stator inner surface motion, improves the life-span of pump, the noise of reduction pump.
In the middle of rotor 13 endoporus copper sheathing 19 is housed, copper sheathing 19 cooperates with pintle 15.
Principle of the present invention is formed airtight variable volume by rotor stator, pintle and plunger, hydraulic oil enters dispensing window 32 from pintle 15 ends and enters plunger 12 bottoms again during work, because there is an eccentric e in rotor 13 with stator 10, when motor drives the rotor rotation by live axle 3 and cross key 2, when plunger 12 is protruding, it is oil suction that plunger 12 bottom volumes increase, entad retraction of plunger 12 when rotor 13 turns over 180 °, make plunger 12 bottom volumes be reduced to oil extraction, promptly discharge from pintle 15 ends.
The material of fastness is selected among the present invention: the pintle material is 38CrMoAl, and rotor material is an alloy nodular cast iron, and plunger material is 18Cr2Ni4w, and the piston shoes material is a Cuprum alloy, and stator material is a Bearing Steel.
Variable format: electro-hydraulic servo control, the control of (two-way or unidirectional variable) electric-hydraulic proportion, the control of electric-hydraulic proportion load-sensitive, various ways such as constant voltage control and permanent power control.
The present invention is widely used in metal forming machinery, ship machinery, mechanical equipment of steel rolling, in the machinery such as mining machinery, Petro-Chemical Machinery, war industry, injection moulding and extruded aluminium section, is the hydraulic power supply of above-mentioned each field machinery.
Claims (3)
1, a kind of swing angle type radial piston variable displacement pump, it comprises the pump housing, be placed in the stator in the pump housing, be arranged at rotor eccentric with it in the stator, be positioned at the pintle at rotor axis place, be installed in last locating stud and following locating stud on the pintle, be positioned at the pump cover of the pump housing one end, be installed on the setting sleeve on the pump cover, the axle envelope, shaft seal cover, roller bearing, be placed in the live axle on the roller bearing, be installed on the cross key on the live axle, the joiner that connects with rotor by cross key, pump cover and live axle and pintle coaxial line in above-mentioned parts, axially have high pressure oil drainage hole and low pressure oil-sucking hole along it in the pintle, have radially damping controller of the static balance groove that is interconnected and pintle on the pintle, be provided with the plunger damping controller in plunger base; Axis perpendicular to pintle on rotor is equipped with plunger, is distributed with dispensing window on the pintle; It is characterized in that: be mounted with servovalve variable cylinder assembly (9) at the top of the described pump housing (1), be mounted with stator rocker (8) and rocker rotating shaft (27) in the pump housing (1), the rocker roller bearing (7,17) that is positioned on the stator rocker (8) cooperates connection with an end of stator bracket (20), the other end of stator bracket (20) links to each other with stator (10), and stator bracket (20) two ends are identical; Plunger (12) is connected with piston shoes (11) by ball pivot becomes the plunger connecting rod piston shoes, and the plunger connecting rod piston shoes are provided with static balance chamber (11-1), and plunger connecting rod piston shoes both sides are provided with retaining ring (16), plunger connecting rod piston shoes and retaining ring (16) matching gap; Rotor (13) drives stator (10) rotation synchronously by plunger (12); The circle two ends are provided with needle bearing (14,18) in rotor (13), and needle bearing (14,18) cooperates with pintle (15); Axially have axle center control oil channel (33) and the control oil channel (34) that is interconnected along pintle (15), the termination of axle center control oil channel (33) is mounted with the axial damping controller of pintle (III), pintle radially damping controller (I, II) is communicated with axle center control oil channel (33), is mounted with the oblique damping controller of pintle (IV) on the direction that becomes 30～60 degree angles with control oil channel (34).
2, swing angle type radial piston variable displacement pump according to claim 1 is characterized in that: described plunger (12) connects by straight pin (28) with piston shoes (11).
3, swing angle type radial piston variable displacement pump according to claim 1 and 2 is characterized in that: in the middle of described rotor (13) endoporus copper sheathing (19) is housed, copper sheathing (19) cooperates with pintle (15).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2004100442874A CN1297745C (en) | 2004-05-18 | 2004-05-18 | Swing angle type radial plunger variable pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2004100442874A CN1297745C (en) | 2004-05-18 | 2004-05-18 | Swing angle type radial plunger variable pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1699749A CN1699749A (en) | 2005-11-23 |
| CN1297745C true CN1297745C (en) | 2007-01-31 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004100442874A Expired - Fee Related CN1297745C (en) | 2004-05-18 | 2004-05-18 | Swing angle type radial plunger variable pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1297745C (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103758720B (en) * | 2013-10-18 | 2015-11-25 | 西安交通大学 | The axial-flow type radial plunger hydraulic pump that oil joined by oil-piping layout is joined in a kind of employing |
| CN104153958B (en) * | 2014-07-07 | 2016-06-29 | 西安交通大学 | A kind of radial plunger pump delivery regulates uses AC servo machinery driving device |
| CN108979993A (en) * | 2018-07-04 | 2018-12-11 | 九江中船消防设备有限公司 | A kind of high-pressure bench scale pump group unit shaft flow distribution apparatus |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3508466A (en) * | 1968-06-25 | 1970-04-28 | Oilgear Co | Hydraulic machine |
| US3762276A (en) * | 1971-05-13 | 1973-10-02 | G Gates | Steam engine |
| CN1039286A (en) * | 1988-04-28 | 1990-01-31 | 三电有限公司 | Slant plate type compressor with variable displacement mechanism |
| US6178868B1 (en) * | 1999-05-10 | 2001-01-30 | Denis Comact Chicoutimi, Inc. | External pneumatic cushion system for air cylinder |
| US6467393B2 (en) * | 2000-01-04 | 2002-10-22 | Sauer-Danfoss, Inc. | Zeroing device for a hydrostatic piston/cylinder unit |
| CN2695670Y (en) * | 2004-05-18 | 2005-04-27 | 卢堃 | Swinging angle type radial plunger variable pump |
-
2004
- 2004-05-18 CN CNB2004100442874A patent/CN1297745C/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3508466A (en) * | 1968-06-25 | 1970-04-28 | Oilgear Co | Hydraulic machine |
| US3762276A (en) * | 1971-05-13 | 1973-10-02 | G Gates | Steam engine |
| CN1039286A (en) * | 1988-04-28 | 1990-01-31 | 三电有限公司 | Slant plate type compressor with variable displacement mechanism |
| US6178868B1 (en) * | 1999-05-10 | 2001-01-30 | Denis Comact Chicoutimi, Inc. | External pneumatic cushion system for air cylinder |
| US6467393B2 (en) * | 2000-01-04 | 2002-10-22 | Sauer-Danfoss, Inc. | Zeroing device for a hydrostatic piston/cylinder unit |
| CN2695670Y (en) * | 2004-05-18 | 2005-04-27 | 卢堃 | Swinging angle type radial plunger variable pump |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1699749A (en) | 2005-11-23 |
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