CN100462552C - Mono-active blade type secondary component - Google Patents
Mono-active blade type secondary component Download PDFInfo
- Publication number
- CN100462552C CN100462552C CNB2004100357640A CN200410035764A CN100462552C CN 100462552 C CN100462552 C CN 100462552C CN B2004100357640 A CNB2004100357640 A CN B2004100357640A CN 200410035764 A CN200410035764 A CN 200410035764A CN 100462552 C CN100462552 C CN 100462552C
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- China
- Prior art keywords
- secondary component
- stator
- rotor
- oil
- cylinder
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- Expired - Fee Related
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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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- Hydraulic Motors (AREA)
Abstract
A single effect vane secondary element, which is made up of a rotator, stator, and vane, adjusting pole, variable cylinder and shell, the variable cylinder is made up of an end cap, piston, and cylinder, the end cap is fixed on the cylinder through bolt, one end of the variable cylinder piston is connected to the upper end of the adjusting pole, the subjacent end of the adjusting pole is connected to the upper part of the stator, the lower part of the stator is connected to the pendulum shaft, one end of the pendulum is fixed on the shell, another end is fixed on the rear end cap of the secondary element. It can control the stator position effectively, the 'hydraulic motor' condition of the secondary element and 'hydraulic pump' condition can convert each other, it can realize the reclaim and reuse of energy.
Description
Affiliated technical field
The present invention relates to a kind of single-acting blade-type 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 that a kind of compact structure, noise are little, the steady precision height of running, in can be applicable to, the single-acting blade-type secondary component of low-pressure hydraulic system,, enlarged the application area of secondary component to enrich the kind of secondary component.
The present invention solves the technological scheme that its technical problem is taked: the present invention is controlled the position of stator by the variable oil cylinder, promptly the size and Orientation of rotor and stator throw of eccentric is controlled, 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 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 position of stator; The present invention can be applicable to enlarge the application area of secondary component, enrich the kind of secondary component in the following low-pressure hydraulic system of 7Mpa.
Description of drawings
The present invention is further described below in conjunction with drawings and Examples.
Fig. 1 is the structure diagram of single-acting blade-type secondary component
Fig. 2 is the A-A view of single-acting blade-type secondary component
Fig. 3 is the fundamental diagram of single-acting blade-type secondary component
1. housing 2. stators 3. blades 4. rotors 5. transmission shafts 6. adjustable levers 7. end caps 8. pistons 9. cylinder bodies 10. variable oil cylinders 11. swing axiss
Embodiment
A kind of single-acting blade-type secondary component mainly is made up of rotor 4, stator 2, blade 3, adjustable lever 6, variable oil cylinder 10 and housing 1 etc.Variable oil cylinder 10 is made of end cap 7, piston 8, cylinder body 9 etc.End cap 7 is by being bolted on the cylinder body 9, one end of variable oil cylinder 10 piston rods and adjustable lever 6 upper ends link together, adjustable lever 6 lower ends are connected with stator 2 tops, the bottom of stator 2 is connected with swing axis 11, one end of swing axis 11 is fixed on the housing 1, and the other end is fixed on the secondary component rear end cover.The oil inlet and outlet size of secondary component is identical, and blade 3 is radially settled (being that laying angle is zero) along rotor 4, and the center of rotor 4 is fixed, and stator 2 can be around swing axis 11 swings under the effect of variable oil cylinder 10 piston rods.When the center of stator 2 overlapped with the center of rotor 4, throw of eccentric was zero, and the discharge capacity of secondary component is zero, and this position is the zero point of secondary component.
During work, under the effect of variable oil cylinder 10, the direction facing to secondary component transmission shaft 5 makes stator 2 swing an angle to the right around swing axis 11 by adjustable lever 6, stator 2 centers are on the right side at rotor 4 centers, and the center of the center of stator 2 and rotor 4 has just produced a throw of eccentric.Hydraulic fluid port oil-feed on secondary component, during following hydraulic fluid port oil return, hydraulic fluid port oil inlet end on the secondary component shown in Fig. 3 (a), in the closed area of forming by rotor, stator, two adjacent blades and both sides thrust plate, because the compression area of right side blade is greater than the compression area of left side blade, 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 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 center be in the left side (Zero Crossing Point) of rotor center.In Fig. 3 (b), the closed area volume that oil port is made up of rotor, stator, two adjacent blades and both sides thrust plate under the secondary component constantly increases, and produces vacuum, sucks fluid, and following hydraulic fluid port just becomes inlet port; The closed area volume that last oil port is made up of rotor, stator, two adjacent blades and both sides thrust plate constantly reduces, and fluid is forced out through last hydraulic fluid port and enters in the hydraulic system, with the work of " oil hydraulic pump " operating mode, to the hydraulic system feedback energy, and plays braking action.
If stator center is in the left side of rotor center, to the logical pressure oil of hydraulic fluid port on the secondary component, during following hydraulic fluid port oil return, hydraulic fluid port oil inlet end on the secondary component shown in Fig. 3 (c), by rotor, stator, in the closed area that two adjacent blades and both sides thrust plate are formed, because the compression area of left side blade is greater than the compression area of right side blade, under action of pressure, rotor and transmission shaft be (facing to the direction of secondary component transmission shaft 5) rotation with counterclockwise, secondary component is again with the work of " oil hydraulic motor " operating mode, consume the energy of hydraulic system, drive loaded work piece.
Effect by the variable oil cylinder, the secondary component stator center is transferred to the right side (Zero Crossing Point) of rotor center, 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. 3 (d), the closed area volume that oil port is made up of rotor, stator, two adjacent blades and both sides thrust plate under the secondary component constantly increases, produce vacuum, suck fluid, following hydraulic fluid port just becomes inlet port; The closed area volume that last oil port is made up of rotor, stator, two adjacent blades and both sides thrust plate constantly reduces, and fluid is forced out through last hydraulic fluid port and enters in the hydraulic system, with the work of " oil hydraulic pump " operating mode, to the hydraulic system feedback energy, and plays braking action.
The size and Orientation of throw of eccentric is by the displacement decision of variable oil cylinder piston bar, and the displacement of variable oil cylinder piston bar can be by electro-hydraulic servo (ratio) valve and position transducer control.In the work, the corner by position transducer detection adjustable lever feeds back to controller, sends instruction by controller and gives electro-hydraulic servo (ratio) valve, the displacement (size and Orientation) of Moderator Variable oil cylinder piston bar.
Claims (2)
1. single-acting blade-type secondary component, by rotor (4), stator (2), blade (3), adjustable lever (6), variable oil cylinder (10) and housing (1) are formed, it is characterized in that variable oil cylinder (10) is by end cap (7), piston (8), cylinder body (9) constitutes, end cap (7) is by being bolted on the cylinder body (9), one end of variable oil cylinder (10) piston rod and adjustable lever (6) upper end link together, adjustable lever (6) lower end is connected with stator (2) top, the bottom of stator (2) is connected with swing axis (11), one end of swing axis (11) is fixed on the housing (1), and the other end is fixed on the secondary component rear end cover.
2. single-acting blade-type secondary component as claimed in claim 1 is characterized in that stator (2) center can be in the left side or the right side at rotor (4) center.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2004100357640A CN100462552C (en) | 2004-09-22 | 2004-09-22 | Mono-active blade type secondary component |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2004100357640A CN100462552C (en) | 2004-09-22 | 2004-09-22 | Mono-active blade type secondary component |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1598287A CN1598287A (en) | 2005-03-23 |
| CN100462552C true CN100462552C (en) | 2009-02-18 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004100357640A Expired - Fee Related CN100462552C (en) | 2004-09-22 | 2004-09-22 | Mono-active blade type secondary component |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN100462552C (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN118356283B (en) * | 2024-06-20 | 2024-08-23 | 兰州理工大学 | Energy regeneration type magnetorheological fluid damping active lower artificial limb knee joint and control method |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3918855A (en) * | 1973-11-16 | 1975-11-11 | Rexroth Gmbh G L | Adjustable vane pump |
| GB2151705A (en) * | 1983-12-24 | 1985-07-24 | Teves Gmbh Alfred | Variable-delivery sliding-vane rotary pump |
| GB2198482A (en) * | 1986-12-13 | 1988-06-15 | Ruling Chen | Piston drive transmission structure in a rotary compressor |
| US5100308A (en) * | 1989-03-25 | 1992-03-31 | Gebr. Becker Gmbh & Co. | Vane pump with adjustable housing and method of assembly |
| CN1312436A (en) * | 2001-04-06 | 2001-09-12 | 燕山大学 | Double-function variable vane pump |
| CN1346019A (en) * | 2000-09-25 | 2002-04-24 | 付云树 | Flexible swing rotary compressor |
| CN2752472Y (en) * | 2004-09-22 | 2006-01-18 | 山东交通学院 | Single-acting blade type secondary element |
-
2004
- 2004-09-22 CN CNB2004100357640A patent/CN100462552C/en not_active Expired - Fee Related
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3918855A (en) * | 1973-11-16 | 1975-11-11 | Rexroth Gmbh G L | Adjustable vane pump |
| GB2151705A (en) * | 1983-12-24 | 1985-07-24 | Teves Gmbh Alfred | Variable-delivery sliding-vane rotary pump |
| GB2198482A (en) * | 1986-12-13 | 1988-06-15 | Ruling Chen | Piston drive transmission structure in a rotary compressor |
| US5100308A (en) * | 1989-03-25 | 1992-03-31 | Gebr. Becker Gmbh & Co. | Vane pump with adjustable housing and method of assembly |
| CN1346019A (en) * | 2000-09-25 | 2002-04-24 | 付云树 | Flexible swing rotary compressor |
| CN1312436A (en) * | 2001-04-06 | 2001-09-12 | 燕山大学 | Double-function variable vane pump |
| CN2752472Y (en) * | 2004-09-22 | 2006-01-18 | 山东交通学院 | Single-acting blade type secondary element |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1598287A (en) | 2005-03-23 |
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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: 20090218 Termination date: 20100922 |