EP0199833B1 - Pompe hydraulique - Google Patents
Pompe hydraulique Download PDFInfo
- Publication number
- EP0199833B1 EP0199833B1 EP19850105181 EP85105181A EP0199833B1 EP 0199833 B1 EP0199833 B1 EP 0199833B1 EP 19850105181 EP19850105181 EP 19850105181 EP 85105181 A EP85105181 A EP 85105181A EP 0199833 B1 EP0199833 B1 EP 0199833B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- flow
- valve
- hydraulic pump
- prolongation
- spool
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
- F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
Definitions
- the invention relates to a hydraulic pump, in particular for steering assistance, with the features of the preamble of claim 1.
- Power steering pumps are usually designed as vane pumps and rigidly connected to the drive motor of the vehicle in which the power steering is used. Accordingly, the pump delivery flow increases with increasing engine speed. However, strong steering assistance is usually not required at higher engine speeds. For this reason, a flow control valve is usually used to regulate part of the pump delivery flow, while the remaining regulated useful flow is fed back to the tank via the steering valve.
- the hydraulic fluid under the so-called dynamic pressure relaxes, which leads to a corresponding loss of performance if the power is not absorbed by the steering.
- Such a high power consumption does not occur practically in the high speed range because you cannot turn in sharply when driving fast. In the high speed range of the pump, a constant readiness to perform is maintained, the level of which is not required and thus leads to an unnecessary loss of performance.
- the invention is based on the object of designing a hydraulic pump of the generic type in such a way that a small range of falling characteristic curve branches of the useful flow pump speed characteristic can be generated by slight changes to the flow control valve. It should therefore be possible to generate a characteristic adapted to the application.
- the annular space formed on the extension of the slide piston has a certain overlap width with respect to the orifice bore and the discharge channels, which are preferably duplicated.
- the annular space is fed by a cavity in the extension of the slide piston.
- the current divides in the annulus in terms of the useful flow and the regulated flow. The latter is quickly discharged into the pump inlet so that there is little flow loss.
- the division of the current in the annular space has the further advantage that the impulse forces exerted are opposite to each other, so that the flow forces on the slide piston are largely compensated for.
- the utility flow bore channel has a second inlet, formed by an annular gap between the extension of the valve slide and the valve bore wall in the range of movement of this extension.
- This inlet cross-section is smaller than the normal opening cross-section between the annulus and the utility flow bore channel.
- the extension of the slide piston can have different geometrical configurations in order to influence the course of the useful current / pump speed characteristic.
- the vane pump has a main housing part 1 and a housing cover 2, which enclose an interior 1 a pressure-tight.
- an interior 1 sit - arranged fixed to the housing - a pressure plate 4 and a cam ring 5, which are secured against rotation by pins 6.
- a rotor 7 is arranged within the cam ring 5 and between the housing cover 2 and the pressure plate 4, which rotor (FIG. 3) has a series of radial guide slots. Wings 8 are radially displaceably mounted within these guide slots.
- the rotor 7 can be driven via a shaft 9 which is mounted in a bearing bore in the housing cover 2.
- the rotor 7 is cylindrical, while the cam ring 5 has an approximately oval inner contour, the small axis of which corresponds approximately to the diameter of the rotor, while the large axis determines the extension length of the vanes 8.
- the cam ring 5 and the rotor 7 there are two crescent-shaped displacement regions 11, 12, which are divided into a number of cell spaces by the vanes 8. The cell spaces increase on the suction side of the system and decrease on the pressure side.
- Hydraulic fluid is supplied from a tank 14 (FIG. 3) and a distribution area 16 via two slightly sloping bores 17 (FIG. 2), knee-shaped feed channel sections 18 and inlet openings 20 into the respective displacement areas of the pump.
- the knee-shaped feed channel sections 18 each have a radial leg which opens into an unloading channel 19 (FIGS. 2 and 4).
- the hydraulic fluid is removed via outlet openings 33 (FIG. 1) through the pressure plate 4 into a pressure chamber 35 on its rear side.
- a flow control valve 40 the pump delivery flow is divided into a regulated useful flow flowing via a bore 38 to an outer pump outlet 37 (FIG. 2) and a regulated delivery flow flowing through the discharge channels 19.
- the bore 38 represents a useful current channel and at the same time part of a measuring orifice 36 through which the useful current flows and whose voltage drop is tapped.
- the useful flow reaches the pump outlet 37 (FIG. 2) via an inclined discharge duct 39 (FIG. 1). From this, a connection leads to a control chamber 47 of the flow control valve 40 via a damping throttle 48.
- the flow control valve 40 has a slide piston 41 guided in a valve bore 55, which is pushed by the force of a spring 42 in the direction of the pressure plate 4 and, if necessary, to abut there brought.
- the slide piston 41 has a first and second piston surface 53, 54 and two piston collars 43, 44, between which an annular groove 45 extends.
- the piston collar 43 is narrower than the discharge channels 19 (FIG. 2) which meet the annular groove 45.
- a partially radially and partially axially extending channel 46 leads from the annular groove 45 through the slide piston 41 into the control chamber 47, and the channel 46 is dominated by a cone valve which responds when a certain permissible pressure in the control chamber 47 is exceeded and discharges this chamber, so that the spool 41 acts as a controlled pressure relief valve, as is known.
- the valve 40 assumes the position shown in FIG. 4.
- the slide piston 41 has an extension 49 in which a cavity 50 is accommodated. This is connected via a series of bores 51 to an annular space 52 of width b.
- the annular space 52 is delimited by the first piston surface 53 and a third piston surface 56, which work in cooperation with the discharge channels 19 and the useful flow bore channel 38 as control edges, so that the valve 40 represents a two-edge controller.
- the radial bore 38 and the radial unloading channel 19 are shown in FIG. 4 in the same axial plane of the valve 40, while in reality they lie in different axial planes which, for example, form an angle of 90 ° to one another. Projected onto the axial sectional plane shown in FIG.
- the pump operates as follows: the rotor 7 is driven by the shaft 9 and the vanes 8 pass through the displacement areas 11 and 12, so that the liquid via the liquid outlet system 33, 35, 50, 38, 39 to the outer pump outlet 37 is fed and liquid is sucked in via the outer pump inlet 16 and the liquid supply system 17, 18, 20. If the liquid flow through the bore 38 exceeds the desired value, the pressure drop across this bore 38 is sufficiently large to overcome the force of the valve spring 42, i.e. the compressive force on the piston surface 53 is greater than the compressive force on the piston surface 54 plus the spring force 42. Now part of the pumped flow is regulated via the discharge channel 19, while the useful flow continues to be withdrawn via the bore 38. Their effective cross-sectional area decreases due to the control edge 56 moving in the closing direction, i.e. the orifice 36 becomes narrower and the pressure drop in the useful flow increases.
- a slide piston 41 is shown, the extension 49 is slightly conical.
- the annular space 52 therefore extends to a certain extent up to the front edge 57 of the slide piston 41. Accordingly, if the slide piston 41 moves against the force of its valve spring 42, the opening width of the annular gap between the extension 49 and the valve bore 55 becomes narrower, the narrowing speed as it approaches the edge 57 to the valve bore 55 increases sharply, so that the proportion of the useful current that flows over the annular gap between the extension 49 and the valve bore 55 decreases sharply.
- a certain proportion of the useful flow remains, as is shown in the assigned characteristic.
- Fig. 7 shows a slide piston 41 with a Extension 49, which is composed of the shapes of the extension according to FIGS. 5 and 6, that is to say has a cylindrical region 58 and a conical region 59.
- a certain proportion of the useful flow can flow through the annular gap between the conical region 59 and the valve bore 55 into the bore 38 until one certain position of the slide piston 41, the cylindrical portion 58 enters the valve bore 55.
- a larger or smaller remaining useful flow is then achieved, as is indicated in the assigned useful flow speed characteristic.
- Fig. 8 shows an embodiment of the slide piston 41 with an extension 49, which has a spherical surface. This shape approximates the design according to FIG. 7, and accordingly a similar useful current-speed characteristic is achieved.
- the gap width, minus d z 0.21 to 0.71 mm, was varied.
- a constant useful current could be achieved regardless of the pump speed n.
- the dimension b was varied between 7.7 and 8.7 mm, whereby higher useful current values were achieved at higher values of b, ie the falling branch of the characteristic dropped less strongly or remained constant.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
- Reciprocating Pumps (AREA)
Claims (8)
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP19850105181 EP0199833B1 (fr) | 1985-04-27 | 1985-04-27 | Pompe hydraulique |
DE8585105181T DE3564603D1 (en) | 1985-04-27 | 1985-04-27 | Hydraulic pump |
CA000506074A CA1253771A (fr) | 1985-04-27 | 1986-04-08 | Pompe hydraulique |
JP61095925A JPH0749797B2 (ja) | 1985-04-27 | 1986-04-26 | 油圧ポンプ |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP19850105181 EP0199833B1 (fr) | 1985-04-27 | 1985-04-27 | Pompe hydraulique |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0199833A1 EP0199833A1 (fr) | 1986-11-05 |
EP0199833B1 true EP0199833B1 (fr) | 1988-08-24 |
Family
ID=8193470
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19850105181 Expired EP0199833B1 (fr) | 1985-04-27 | 1985-04-27 | Pompe hydraulique |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP0199833B1 (fr) |
JP (1) | JPH0749797B2 (fr) |
CA (1) | CA1253771A (fr) |
DE (1) | DE3564603D1 (fr) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3623421A1 (de) * | 1986-07-11 | 1988-01-14 | Vickers Systems Gmbh | Lenkhilfpumpe |
JPH0729267Y2 (ja) * | 1989-06-02 | 1995-07-05 | 株式会社ユニシアジェックス | ベーンポンプ |
US5220939A (en) * | 1991-05-21 | 1993-06-22 | Koyo Seiko Co., Ltd. | Flow control apparatus |
WO1999067534A1 (fr) * | 1998-06-24 | 1999-12-29 | Luk Fahrzeug-Hydraulik Gmbh & Co. Kg | Dispositif de refoulement hydraulique |
AT520109B1 (de) * | 2017-07-11 | 2019-09-15 | Avl List Gmbh | Reversible Pumpe |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE619219C (de) * | 1934-10-14 | 1935-09-27 | Fortuna Werke Spezialmaschinen | Regelbares Drosselventil mit Spueleinrichtung |
US2145533A (en) * | 1936-07-06 | 1939-01-31 | Caterpillar Tractor Co | Fluid transfer mechanism |
DE1108027B (de) * | 1959-08-19 | 1961-05-31 | Bosch Gmbh Robert | Von der Durchflussmenge eines Druckmittels beeinflusstes selbsttaetiges Steuerventil |
US3033221A (en) * | 1960-04-29 | 1962-05-08 | Hough Co Frank | Priority valve |
US3185178A (en) * | 1962-10-15 | 1965-05-25 | Armand A Bonnard | Cylindrical squeeze-type directional valve |
JPS5838536B2 (ja) * | 1975-08-01 | 1983-08-23 | 帝人株式会社 | ゴム補強用ポリエステル系繊維材料の製造法 |
DE3033388A1 (de) * | 1980-09-05 | 1982-04-22 | Robert Bosch Gmbh, 7000 Stuttgart | Mehrstellungs-mehrwegeventil |
DE3211948C2 (de) * | 1982-03-31 | 1984-07-26 | Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen | Regeleinrichtung für eine Verdrängerpumpe, insbesondere Flügelzellenpumpe |
-
1985
- 1985-04-27 EP EP19850105181 patent/EP0199833B1/fr not_active Expired
- 1985-04-27 DE DE8585105181T patent/DE3564603D1/de not_active Expired
-
1986
- 1986-04-08 CA CA000506074A patent/CA1253771A/fr not_active Expired
- 1986-04-26 JP JP61095925A patent/JPH0749797B2/ja not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
JPH0749797B2 (ja) | 1995-05-31 |
JPS61250391A (ja) | 1986-11-07 |
CA1253771A (fr) | 1989-05-09 |
DE3564603D1 (en) | 1988-09-29 |
EP0199833A1 (fr) | 1986-11-05 |
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