CN1598288A - Dual-active blade type secondry component - Google Patents
Dual-active blade type secondry component Download PDFInfo
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- CN1598288A CN1598288A CNA2004100357655A CN200410035765A CN1598288A CN 1598288 A CN1598288 A CN 1598288A CN A2004100357655 A CNA2004100357655 A CN A2004100357655A CN 200410035765 A CN200410035765 A CN 200410035765A CN 1598288 A CN1598288 A CN 1598288A
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- variable
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- secondary component
- oil
- shell
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
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Abstract
A double-effect vane secondary element, which is made up of a rotator, a stator, a vane, variable cylinder, a shell and a distributing plate. The variable cylinder is made up of a variable pole, variable piston, and variable shell. The variable shell is fixed on the shell through bolt, the sphere head of the variable pole is connected to the concave groove of the variable piston, another end of the variable pole is fixed on the external surface of the stator long radius arc center. The merits of the invention are: through the control to the stator position, the 'hydraulic motor' condition of the secondary element and the 'hydraulic pump' condition can convert each other, it realizes the reclaim and the reuse of energy.
Description
Affiliated technical field
The present invention relates to a kind of Double-action Vane Secondary Component, belong to mechanical field.
Background technique
Secondary component is meant can realize hydraulic pressure energy and the mechanical energy element of conversion mutually, also claim variable hydraulic motor/pump, it both can be operated in " oil hydraulic motor " operating mode, can be operated in " oil hydraulic pump " operating mode again, when secondary component when " dragging load " carries out the transition to the operating mode of " load drags ", it just carries out the transition to " oil hydraulic pump " operating mode by " oil hydraulic motor " operating mode, promptly changes the recovered energy operating mode into by the consumed energy operating mode, thereby provides possibility for the recovery and reuse of energy.
Existing secondary component mostly is to improve design on the basis of oblique tray type plunger variable displacement motor, structure mainly is a plunger type, its working pressure height, more than 20Mpa, range of flow is big, generally be used for high pressure, high-volume hydraulic system, in, use in the low-pressure hydraulic system, efficient is very low, and plunger type secondary component complex structure, machining accuracy height, to the oil pollution sensitivity, oil strain required precision height, price is expensive, therefore makes the application area of secondary component be subjected to very big restriction.
Summary of the invention
The purpose of this invention is to provide a kind of compact structure, flow is even, noise is little, running accuracy is high and steady, can be applicable to the Double-action Vane Secondary Component of mesohigh, middle pressure, low-pressure hydraulic system, to enrich the kind of secondary component, enlarge the application area of secondary component.
The present invention solves the technological scheme that its technical problem is taked: the present invention changes position relation between thrust plate and the stator by the stator of variable oil cylinder rotation secondary component, thereby change is advanced, the size and the position of oil extraction window, realize the change of flow size and oily flow path direction, make secondary component carry out the transition to " oil hydraulic pump " operating mode by " oil hydraulic motor " operating mode, or carry out the transition to " oil hydraulic motor " operating mode, thereby realize the recovery and reuse of energy by " oil hydraulic pump " operating mode.The variable oil cylinder can be controlled the size and Orientation of stator angle of rotation, and stator is rotated in-45 ° of-45 ° of scopes.
The invention has the beneficial effects as follows by control, " oil hydraulic motor " operating mode of secondary component and " oil hydraulic pump " operating mode are changed mutually, realize the recovery and reuse of energy the stator angle of swing; The present invention can be applicable in mesohigh, middle pressure, the mesolow hydraulic system, promptly more than the 7Mpa, in the hydraulic system below the 20Mpa, has enlarged the application area of secondary component, has enriched the kind of secondary component.
Description of drawings
The present invention is further described below in conjunction with drawings and Examples.
Fig. 1 is the structure diagram of Double-action Vane Secondary Component
Fig. 2 is the A-A view of Double-action Vane Secondary Component
Fig. 3 is the stator initial position figure of Double-action Vane Secondary Component
Fig. 4 is the schematic diagram of Double-action Vane Secondary Component
1. housing 2. stators 3. blades 4. rotors 5. transmission shafts 6. variable bars 7. end caps 8. variable pistons 9. variable cylinder bodies 10. variable oil cylinders 11,12. thrust plates
Embodiment
A kind of Double-action Vane Secondary Component mainly is made up of rotor 4, stator 2, blade 3, variable oil cylinder 10, housing 1 and thrust plate 11,12 etc.Variable oil cylinder 10 is made of variable bar 6, variable piston 8, variable cylinder body 9 etc.Variable cylinder body 9 is by being bolted on the housing 1, the spherical head end of variable bar 6 is connected with the groove of variable piston 8, the other end of variable bar 6 is fixed on the semi major axis center of arc line place or the short radius center of arc line place of stator 2, in the embodiments of the invention shown in Figure 2, the other end of variable bar 6 is fixed on the outer surface at stator 2 semi major axis center of arc line places.
Secondary component identical into and out of the hydraulic fluid port size, blade 3 is radially settled (being that laying angle is zero) along rotor 4, and the center of rotor 4 and stator 2 is fixed, and stator 2 can rotate around the center under the drive of variable piston 8.
When secondary component was not worked, in Fig. 3, stator 2 semi major axis center of arc lines overlapped with assembly oil window center line, and at this moment, the corner of stator 2 is a zero degree, is the initial rotational position (zero point) of stator 2.Stator 2 is when initial position, and the discharge capacity of secondary component is zero.Suppose the direction facing to secondary component transmission shaft 5, stator clockwise direction angle of rotation is for just, and counterclockwise angle of rotation is for bearing.When stator 2 clockwise or when being rotated counterclockwise, along with stator 2 corner forwards or negative sense increase, the discharge capacity of secondary component is forward or negative sense increase also, when corner reached 45 °, the discharge capacity forward maximum of secondary component was when corner is-45 °, the discharge capacity negative sense maximum of secondary component, therefore, stator can rotate in-45 ° of-45 ° of angle ranges, and the discharge capacity of secondary component is constantly changed.
During work, under the effect of variable oil cylinder 10, the direction facing to secondary component transmission shaft 5 makes stator 2 clockwise rotate a positive-angle around the center by variable bar 6.Hydraulic fluid port oil-feed on secondary component, during following hydraulic fluid port oil return, in Fig. 4 (a), left and right two the dispensing window places that are communicated with hydraulic fluid port on the secondary component, in two symmetrical closed areas forming by rotor, stator, two adjacent blades and both sides thrust plate, because the compression area of blade h, n is greater than the compression area of blade m, f, under action of pressure, rotor and transmission shaft be (facing to the direction of secondary component transmission shaft 5) rotation in a clockwise direction, secondary component is with the work of " oil hydraulic motor " operating mode, consume the energy of hydraulic system, drive loaded work piece.
If stop to the secondary component fuel feeding, under the effect of load inertia kinetic energy, rotor and transmission shaft will continue in a clockwise direction (facing to the direction of secondary component transmission shaft 5) rotation, at this moment, by the effect of variable oil cylinder, make stator counterclockwise rotate a negative angle (Zero Crossing Point).In Fig. 4 (b), upper and lower two the dispensing window places that are communicated with hydraulic fluid port under the secondary component, two symmetrical closed area volumes being made up of rotor, stator, two adjacent blades and both sides thrust plate constantly increase, and produce vacuum, suck fluid, following hydraulic fluid port just becomes inlet port; Two symmetrical closed area volumes that last oil port is made up of rotor, stator, two adjacent blades and both sides thrust plate constantly reduce, fluid is forced out through last hydraulic fluid port and enters in the hydraulic system, with the work of " oil hydraulic pump " operating mode,, and play braking action to the hydraulic system feedback energy.
If stator continues to be in the negative angle position, to the logical pressure oil of hydraulic fluid port on the secondary component, during following hydraulic fluid port oil return, in Fig. 4 (c), a left side that is communicated with hydraulic fluid port on the secondary component, right two dispensing window places, by rotor, stator, in two symmetrical closed areas that two adjacent blades and both sides thrust plate are formed, because blade u, the compression area of r is greater than blade s, the compression area of v, under action of pressure, rotor and transmission shaft be (facing to the direction of secondary component transmission shaft 5) rotation with counterclockwise, secondary component consumes the energy of hydraulic system again with the work of " oil hydraulic motor " operating mode, drives loaded work piece.
Effect by the variable oil cylinder, the rotatable stator Zero Crossing Point is in a positive-angle, and stop to the secondary component fuel feeding, if still (facing to the direction of the secondary component transmission shaft 5) rotation of rotor and transmission shaft with counterclockwise, at this moment, in Fig. 4 (d), upper and lower two the dispensing window places that are communicated with hydraulic fluid port under the secondary component, two symmetrical closed area volumes being made up of rotor, stator, two adjacent blades and both sides thrust plate constantly increase, and produce vacuum, suck fluid, following hydraulic fluid port just becomes inlet port; Two symmetrical closed area volumes that last oil port is made up of rotor, stator, two adjacent blades and both sides thrust plate constantly reduce, fluid is forced out through last hydraulic fluid port and enters in the hydraulic system, with the work of " oil hydraulic pump " operating mode,, and play braking action to the hydraulic system feedback energy.
The size and Orientation of stator angle of swing is by the displacement decision of variable piston, and the displacement of variable piston can be by electro-hydraulic servo (ratio) valve and position transducer control.In the work, the corner by position transducer detection variable bar feeds back to controller, sends instruction by controller and gives electro-hydraulic servo (ratio) valve, the displacement of Moderator Variable piston (size and Orientation).
Claims (2)
1, a kind of Double-action Vane Secondary Component, form by rotor (4), stator (2), blade (3), transmission shaft (5), variable oil cylinder (10), housing (1) and thrust plate (11,12) etc., it is characterized in that variable oil cylinder (10) is by variable bar (6), variable piston (8), variable cylinder body formations such as (9), variable cylinder body (9) is by being bolted on the housing (1), the spherical head end of variable bar (6) is connected with the groove of variable piston (8), and the other end of variable bar (6) is fixed on the outer surface at stator (2) semi major axis center of arc line place.
2, secondary component as claimed in claim 1, the position of the initial rotational position that it is characterized in that stator (2) when to be stator (2) semi major axis center of arc line with assembly oil window center line overlap, at initial rotational position place, the angle of rotation of stator (2) is a zero degree, the discharge capacity of secondary component is zero, the position of stator (2) can be on the left side or the right side of initial rotational position, and position range is-45 °-45 °.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2004100357655A CN100513775C (en) | 2004-09-22 | 2004-09-22 | Dual-active blade type secondry component |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2004100357655A CN100513775C (en) | 2004-09-22 | 2004-09-22 | Dual-active blade type secondry component |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1598288A true CN1598288A (en) | 2005-03-23 |
| CN100513775C CN100513775C (en) | 2009-07-15 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004100357655A Expired - Fee Related CN100513775C (en) | 2004-09-22 | 2004-09-22 | Dual-active blade type secondry component |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN100513775C (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101418773B (en) * | 2008-12-11 | 2010-12-08 | 宁波华液机器制造有限公司 | High performance spherical hydraulic motor |
| CN101566177B (en) * | 2009-05-26 | 2010-12-29 | 山东交通学院 | Double-acting vane type hydraulic transformer |
| CN101566178B (en) * | 2009-05-26 | 2012-05-09 | 山东交通学院 | Double-acting vane type hydraulic transformer controlled by hydraulic cylinder |
| CN105257210A (en) * | 2015-11-18 | 2016-01-20 | 西南石油大学 | Novel turbodrill capable of achieving accurate positioning of stator and rotor |
| CN107131123A (en) * | 2017-07-21 | 2017-09-05 | 世特科汽车工程产品（常州）有限公司 | A kind of Double-discharge vane pump |
| CN108757809A (en) * | 2018-06-08 | 2018-11-06 | 淮阴工学院 | Vehicular vibration energy recovery type damper |
-
2004
- 2004-09-22 CN CNB2004100357655A patent/CN100513775C/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101418773B (en) * | 2008-12-11 | 2010-12-08 | 宁波华液机器制造有限公司 | High performance spherical hydraulic motor |
| CN101566177B (en) * | 2009-05-26 | 2010-12-29 | 山东交通学院 | Double-acting vane type hydraulic transformer |
| CN101566178B (en) * | 2009-05-26 | 2012-05-09 | 山东交通学院 | Double-acting vane type hydraulic transformer controlled by hydraulic cylinder |
| CN105257210A (en) * | 2015-11-18 | 2016-01-20 | 西南石油大学 | Novel turbodrill capable of achieving accurate positioning of stator and rotor |
| CN107131123A (en) * | 2017-07-21 | 2017-09-05 | 世特科汽车工程产品（常州）有限公司 | A kind of Double-discharge vane pump |
| CN108757809A (en) * | 2018-06-08 | 2018-11-06 | 淮阴工学院 | Vehicular vibration energy recovery type damper |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100513775C (en) | 2009-07-15 |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20090715 Termination date: 20100922 |