WO2013072126A1 - Pump element of a hydraulic unit for a vehicle brake system - Google Patents
Pump element of a hydraulic unit for a vehicle brake system Download PDFInfo
- Publication number
- WO2013072126A1 WO2013072126A1 PCT/EP2012/069474 EP2012069474W WO2013072126A1 WO 2013072126 A1 WO2013072126 A1 WO 2013072126A1 EP 2012069474 W EP2012069474 W EP 2012069474W WO 2013072126 A1 WO2013072126 A1 WO 2013072126A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piston
- cylinder
- brake fluid
- pump element
- active surface
- Prior art date
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
- B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
- B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
- B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
- B60T8/4031—Pump units characterised by their construction or mounting
-
- 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
- F04B3/00—Machines or pumps with pistons coacting within one cylinder, e.g. multi-stage
- F04B3/003—Machines or pumps with pistons coacting within one cylinder, e.g. multi-stage with two or more pistons reciprocating one within another, e.g. one piston forning cylinder of the other
-
- 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
- F04B5/00—Machines or pumps with differential-surface pistons
- F04B5/02—Machines or pumps with differential-surface pistons with double-acting pistons
Definitions
- the invention relates to a pump element of a hydraulic unit of a vehicle brake system for conveying brake fluid with a reciprocally displaceably mounted piston in a cylinder.
- Pump elements of the type relevant here are also referred to as vehicle brake system piston pumps and have a reciprocating piston, which is usually driven by means of an eccentric.
- Such pumping elements as e.g. are used in systems with electronic stability program (ESP), principle, a time per unit time-varying delivery volume of fluid, in particular brake fluid on. This temporally highly non-uniform course of the delivery volume is on the suction side, but in particular on the pressure side of the pump element and leads here optionally to pressure pulsations.
- ESP electronic stability program
- This temporally highly non-uniform course of the delivery volume is on the suction side, but in particular on the pressure side of the pump element and leads here optionally to pressure pulsations.
- These pressure pulsations cause disturbing noises, which are called Noise Vibration Harshness (NVH).
- NVH Noise Vibration Harshness
- the pressure peaks associated with the pressure pulsations
- a pump element of a hydraulic unit of a vehicle brake system for conveying brake fluid with a reciprocally displaceably mounted piston in a cylinder, in which the piston has a first and a second active surface, of which the first active surface when moving the piston brake fluid from the Cylinder encourages and works the second active surface when moving the piston brake fluid from the cylinder promotes out promotes.
- Piston moves into or out of the cylinder.
- the brake fluid flows out of the cylinder, whereby a more uniform volumetric flow of the fluid is created compared to known pump elements.
- stepped piston pumps are used in known hydraulic units, for example in ESP systems.
- additional balance piston are known, which are also driven by the eccentric as a separate component and are typically arranged offset by 180 ° to the direction of movement of the piston pump.
- the use of these additional balancing pistons significantly reduces the hydraulic nonuniformity on the pump pressure side.
- additional space and additional material is consumed.
- the inventive design of the pump element creates in contrast to a more uniform flow largely without additional space and material consumption.
- a pump element is provided in which the first and the second effective area are designed differently sized. In this way, it is advantageous to use a different force for the movement of the first active surface than for the movement of the second effective surface.
- the second active area is preferably smaller than the first active area, so that less force is required for the movement of the second active area than for the movement of the first effective area.
- the first active surface is advantageously coupled non-positively with an eccentric, while the second active surface is non-positively coupled with a return spring of the piston. Coupled in such a way, the first active surface acts on one half revolution of the eccentric, which causes the piston to move, on the one hand compressing to a certain volume of fluid or fluid volume and on the other hand deforming the return spring of the piston.
- A- ⁇ the area of the first effective area
- h- ⁇ the length of the distance that is covered by the first effective area.
- a pump element is provided in which the first active surface acting in a first cylinder chamber and the second active surface are arranged acting in a second cylinder space and a first line is provided, flow through the brake fluid from the first cylinder chamber into the second cylinder chamber when moving the piston can.
- a conveying of the fluid, in particular the brake fluid from the first cylinder chamber into the second cylinder chamber is thus made possible.
- the second cylinder space is advantageously smaller than the first cylinder chamber. Furthermore, the size ratio of the first to the second cylinder space is preferably substantially the same size as the size ratio of the first to the second
- This size ratio is particularly preferably 2: 1.
- the first active surface acts on the movement of the piston as a result of the force of the eccentric compressing a fluid which is located in the first cylinder space.
- the compressed fluid driven by the expansion urge of the fluid itself and by the force of the eccentric, flows through the first conduit into the second cylinder chamber.
- the second cylinder space is smaller, in particular half as large, as the first cylinder space, so that only a portion of the fluid flowing in from the first cylinder space can be accommodated there.
- the remainder of the fluid flowing out of the first cylinder chamber is conveyed out of the pump element. In this way, the conveying of the fluid, in particular of the brake fluid from the first cylinder chamber into the second cylinder chamber with simultaneous pressure build-up of the fluid in the second cylinder chamber is advantageously made possible.
- a first check valve is preferably arranged in the first line, with which a backflow of brake fluid from the second cylinder chamber is prevented in the first cylinder chamber.
- the brake fluid can flow so advantageous only in one direction, so that a pumping or pumping without
- the first line is guided by the piston.
- a pump element is created in a very compact design with short flow paths.
- the short flow paths reduce friction of the fluid on an inner wall of the first conduit, thereby reducing heating of the fluid and adjacent components by friction and the associated loss of kinetic energy.
- Another advantage is that due to the lower material consumption, the pump element according to the invention is very inexpensive to produce, in contrast to a pump element whose first line is guided outside and along the cylinder.
- a pump element is provided in which only one suction line is provided for supplying brake fluid to the piston.
- only one suction line is advantageously a very compact, material and space-saving design of the pump element created.
- the suction line is connected to the first cylinder chamber, so that when moving or when moving out of the piston from the cylinder through the suction line brake fluid flows into the first cylinder chamber until it is filled.
- only one pressure line for discharging brake fluid from the piston is provided, which is connected to the second cylinder chamber.
- the material and space consumption for the pump element is advantageously further reduced and allows an even more compact design.
- an output from the pump element is provided with the pressure line, through which the brake fluid from the second cylinder chamber is forced into a hydraulic system for performing work.
- the process of pushing out of the brake fluid from the second cylinder chamber is carried out according to the invention both in the outward and during the movement of the piston.
- moving that is, when moving out of the piston from the cylinder is sucked on the one hand through the suction brake fluid in the first cylinder chamber, until it is filled.
- the Brake fluid which is located in the second cylinder chamber, pressed by means of the second active surface from the second cylinder chamber in the pressure line.
- the brake fluid in contrast to known pump elements when moving the piston is not only sucked into the cylinder, but is also pushed out of the cylinder.
- the brake fluid is forced through the first line from the first cylinder space into the second cylinder space until it is filled.
- the second cylinder space is smaller than the first cylinder space, so that the excess of fluid volume flows out through the pressure line.
- the second cylinder space is only half as large as the first cylinder space, so that in particular half of the fluid volume flows out through the pressure line.
- a delivery of the brake fluid or volume delivery from the pump element is therefore provided, which extends over both directions of movement of the piston.
- a particularly uniform volume flow of the fluid is achieved by halving the second active surface in comparison to the first active surface since, during the movement and during the movement of the piston, respectively half the volume of fluid and thus a respectively equal volume of fluid are conveyed out of the pump element becomes.
- a suction space is preferably provided in which brake fluid is sucked in as the piston moves.
- a suction line preferably leads into the suction.
- the suction chamber is advantageously smaller than the first cylinder chamber and particularly advantageously half the size of the cylinder designed first cylinder room. In this suction chamber when moving or when driving in the piston through the suction line brake fluid flows into the suction, so that a pre-suction of the brake fluid for the subsequent moving or retracting the piston is created.
- a second line flows through the movement of the piston brake fluid from the suction to the first effective area.
- brake fluid flows from the intake chamber into the first cylinder chamber, which is preferably larger, particularly preferably twice as large as the intake chamber. This means that additional brake fluid is required to fill the first cylinder space and to compensate for the suction created thereby.
- the volume of fluid required for this purpose is promoted by the resulting suction in the first cylinder chamber through the suction line into the suction chamber and from there through the second line into the first cylinder chamber. This happens while moving the piston.
- the second line is guided by the piston, which saves space and material, and in particular a second check valve is arranged in the second line.
- the second check valve advantageously prevents backflow of brake fluid from the first cylinder space into the intake space, in particular during the movement of the piston.
- a suction in the suction which sucks brake fluid through the suction line into the suction again.
- a particularly uniform volume flow of the fluid is achieved, since during the movement and during the movement of the piston in each case half the volume of fluid and thus a respective equal volume of fluid in the pump element is sucked.
- FIG. 1 shows a longitudinal section of a schematically illustrated embodiment of the pump element according to the invention
- FIG. 2 shows a course diagram of a pressure-side volumetric flow of the exemplary embodiment
- FIG 3 shows a course diagram of a pressure-side volumetric flow of a pump element according to the prior art.
- a pump element 10 of a further not shown hydraulic unit of a vehicle brake system for conveying brake fluid is shown.
- the pump element 10 comprises a cylinder 12 having a first cylinder chamber 14, a second cylinder chamber 16 and an intake chamber 18.
- the pump element 10 comprises a piston 20 displaceably mounted in the cylinder 12 for displacement.
- the piston 20 is coupled with an eccentric 22 on one of its front sides and with a return spring 24 on the opposite end side in each case in a compressive manner.
- the piston 20 furthermore has a first active surface 26 in the first cylinder chamber 14 and a second active surface 28 in the second cylinder chamber 16.
- the second cylinder chamber 16 is connected to the first cylinder chamber 14 via a first line 30, which in the present case leads through the piston 20 and has an associated non-return valve 32. Further, a pressure line 34 for discharging brake fluid from the piston 20 is provided from the cylinder 12 to the second cylinder chamber 16. For supplying brake fluid into the cylinder 12, a suction line 36 is provided, which is attached to the suction space 18. At the beginning Suction chamber 18 acts a third active surface 38 of the piston 12. The suction chamber 18 is connected via a second line 40 with the first cylinder chamber 14, which leads in the present case through the piston 20 and has an associated check valve 42.
- the piston 20 is in the present case formed from a piston rod or a piston cylinder 44, which has on one of its end faces a disc 46, which is formed in particular in one piece with the piston cylinder 44.
- the piston cylinder 44 has a smaller diameter than the disk 46.
- the disk 46 in turn has an end face which forms the first active surface 26 of the piston 20 as a circular surface.
- Opposite the first active surface 26 on the piston cylinder 44 is a rear side of the disk 46, which forms an annular surface and represents the third active surface 38 of the piston 20.
- the piston 20 comprises a disk-shaped ring 48 which surrounds the piston cylinder 44 preferably fluid-tightly approximately in the middle of its longitudinal extent and which is particularly preferably formed integrally with the piston cylinder 44.
- This disc-shaped ring 48 has two opposite, flat and equal sized annular surfaces.
- the annular surface of the disc-shaped ring 48, which lies opposite the piston 20 of the first active surface 26, serves as a second active surface 28.
- the active surfaces 26, 28 and 38 have a same diameter and thus also the disc 46 and the disc-shaped ring 48 same diameter, have the
- Active surfaces 26, 28 and 38 are not the same surfaces.
- the first active surface 26 is a circular surface and thus has a larger area than the second active surface 28 or the third active surface 38, which are each designed as an annular surface with the same outer diameter.
- the second active surface 28 and the third active surface 38 are preferably the same size and particularly preferably each half the size of the first active surface 26.
- the cylinder 12 comprises a first cylinder section 50 of a straight circular cylinder with an end face 52 and an opposing annular surface 54 with an inner ring 56. Furthermore, a second cylinder section 58 of a right circular cylinder is provided as a hollow cylinder which is supported by two counter-rotating cylinders. Overlying annular surfaces 60 and 62, each with an inner ring 64 and 66 is limited. The inner rings 56, 64 and 66 have a same diameter. Adjacent to the inner ring 66, at a right angle to the annular surface 62, a third cylinder section 68 is positively coupled at its one end, which is positively coupled at its other end to the inner ring 56 at right angles to the annular surface 54.
- the diameter of the third cylinder section 68 has the same diameter as the inner rings 56 and 66.
- the third cylinder portion 68 connects the first cylinder portion 50 to the second cylinder portion 58.
- the second cylinder portion 58 and the first cylinder portion 50 have a same inner diameter that is substantially equal to the diameter of the disk 46 and the disk-shaped ring 48.
- the inner diameter of the third cylinder portion 68 is smaller and substantially equal to the diameter of the piston cylinder 44. More preferably, the cylinder portions 50, 58 and 68 are designed as one piece.
- the piston 20 is mounted displaceably in a fluid-sealing manner along its longitudinal axis.
- the bearing is made such that the portion of the piston 20 with the disc 46 in the first cylinder section 50 and the portion of the piston 20 with the disk-shaped
- the third cylinder portion 68 is a portion of the piston cylinder 44, which lies between the disc 46 and the disc-shaped ring 48.
- On the disc-shaped ring 48 then is a portion of the piston cylinder 44 which is guided by the inner ring 64 of the annular surface 60 and is coupled non-positively with its end on the eccentric 22.
- this piston 20 In a first movement phase of this piston 20 is moved by a half turn of the eccentric 22 in the cylinder 12 when moving the piston 20. This creates a suction, the brake fluid from a container, not shown, can flow through the suction line 36 into the suction chamber 18 until the suction chamber 18 is filled with brake fluid.
- the check valve 42 in the second line 40 which connects the suction chamber 18 with the first cylinder chamber 14, is closed.
- the restoring spring 24 mounted in the first cylinder space 14 is compressed and tensioned. The resulting
- This retraction or movement of the piston 20 forms a second movement phase in which brake fluid flows from the suction chamber 18 through the second line 40 when the check valve 42 is open into the first cylinder chamber 14.
- the first cylinder chamber 14 in this case has a larger volume than the suction chamber 18, in the present case particularly preferably twice as large a volume as the suction chamber 18.
- a first movement phase again follows the described second movement phase, that is, the piston 20 moves back into the cylinder 12 by a renewed half turn of the eccentric 22.
- the brake fluid is sucked in as described.
- the brake fluid, which is located in the first cylinder chamber 14 is compressed by means of the first active surface 26 and urged via the first line 30 with the check valve 32 open in the second cylinder chamber 16.
- the second cylinder chamber 16 has a smaller volume than the first cylinder chamber 14, particularly preferably half the volume.
- the piston 20 moves out of the cylinder 12 again. During this movement, the brake fluid is sucked in as described.
- the check valve 32 is closed, the second active surface 28 presses the brake fluid present in the second cylinder chamber 16 through the pressure line 34 out of the second cylinder chamber 16 out.
- the volume of brake fluid that is thereby conveyed out is preferably the second half of the volume of brake fluid displaced in the outward movement from the first cylinder chamber 14.
- the pumping out of brake fluid also takes place during both movement phases, that is to say both when the piston 20 is moved back and forth.
- This conveying out during the two directions of movement of the piston 20 advantageously brings about a uniform volume delivery of brake fluid.
- particularly equal volumes of brake fluid are particularly preferably conveyed out in the individual movement phases, thus providing a particularly uniform volume promotion.
- the present particularly uniform volume promotion of the pump element 10 according to the invention is shown in the flow chart of FIG.
- the progression diagram of Fig. 3 shows uneven volume promotion in known pumping elements.
- the volume of brake fluid conveyed out per unit of time, the so-called pressure-side volumetric flow 70 is plotted on the Y-axis.
- the pressure-side volume flow 70 is dependent on a rotation angle 72, which describes the movement of the eccentric 22 and thus the movement of the piston 20. This rotation angle 72 is therefore plotted on the X-axis.
- Q max is the maximum volume flow per unit time 74
- Q min the minimum flow rate per unit time 76
- Qmittei the over time represents the average value of the volume flow.
- the volume profile of the pressure-side volumetric flow 70 shown in FIG. 2 is achieved. Both when moving out and when driving in the piston 20 and the associated respective half eccentric rotation over the rotation angle 72 of 180 ° or ⁇ brake fluid is conveyed out. In the present case, particularly preferred volumes of brake fluid are conveyed out in both movement phases of the piston 20.
- the degree of non-uniformity ⁇ in the present exemplary embodiment is ⁇ / 2 and is halved compared to the known pump element shown in FIG. 3, assuming idealized conditions.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Transportation (AREA)
- Reciprocating Pumps (AREA)
- Details Of Reciprocating Pumps (AREA)
- Regulating Braking Force (AREA)
- Valves And Accessory Devices For Braking Systems (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1020147012879A KR102007686B1 (en) | 2011-11-15 | 2012-10-02 | Pump element of a hydraulic unit for a vehicle brake system |
US14/355,877 US20140298989A1 (en) | 2011-11-15 | 2012-10-02 | Pump Element of a Hydraulic Unit for a Vehicle Brake System |
JP2014537543A JP2015501253A (en) | 2011-11-15 | 2012-10-02 | Pump member for hydraulic assembly of vehicle brake device |
CN201280055778.1A CN103946081B (en) | 2011-11-15 | 2012-10-02 | The pump element of the hydraulic test of motor vehicle braking systems |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102011086347A DE102011086347A1 (en) | 2011-11-15 | 2011-11-15 | Pump element of a hydraulic unit of a vehicle brake system |
DE102011086347.8 | 2011-11-15 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2013072126A1 true WO2013072126A1 (en) | 2013-05-23 |
Family
ID=47010572
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2012/069474 WO2013072126A1 (en) | 2011-11-15 | 2012-10-02 | Pump element of a hydraulic unit for a vehicle brake system |
Country Status (6)
Country | Link |
---|---|
US (1) | US20140298989A1 (en) |
JP (1) | JP2015501253A (en) |
KR (1) | KR102007686B1 (en) |
CN (1) | CN103946081B (en) |
DE (1) | DE102011086347A1 (en) |
WO (1) | WO2013072126A1 (en) |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2038155A (en) * | 1934-09-11 | 1936-04-21 | Union Oil Co | Pump |
FR1075780A (en) * | 1952-04-26 | 1954-10-20 | Improvements to differential pumps | |
WO1998006612A1 (en) * | 1996-08-13 | 1998-02-19 | Kelsey Hayes Company | Dual action ball screw pump |
EP0945614A2 (en) * | 1998-03-26 | 1999-09-29 | Robert Bosch Gmbh | Piston pump for a vehicle brake system |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3472373B2 (en) * | 1995-03-20 | 2003-12-02 | 日信工業株式会社 | Plunger pump |
US5484269A (en) * | 1995-04-24 | 1996-01-16 | Moog Inc. | Fluid intensifier |
JPH10281055A (en) * | 1997-04-03 | 1998-10-20 | Nippon Abs Ltd | Fluid pressure pump of electronic control device for car |
DE102004061813A1 (en) * | 2004-12-22 | 2006-07-06 | Robert Bosch Gmbh | Piston pump with at least one piston element |
JP2007170319A (en) * | 2005-12-26 | 2007-07-05 | Hitachi Ltd | Piston pump |
-
2011
- 2011-11-15 DE DE102011086347A patent/DE102011086347A1/en active Pending
-
2012
- 2012-10-02 CN CN201280055778.1A patent/CN103946081B/en not_active Expired - Fee Related
- 2012-10-02 KR KR1020147012879A patent/KR102007686B1/en active IP Right Grant
- 2012-10-02 US US14/355,877 patent/US20140298989A1/en not_active Abandoned
- 2012-10-02 WO PCT/EP2012/069474 patent/WO2013072126A1/en active Application Filing
- 2012-10-02 JP JP2014537543A patent/JP2015501253A/en active Pending
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2038155A (en) * | 1934-09-11 | 1936-04-21 | Union Oil Co | Pump |
FR1075780A (en) * | 1952-04-26 | 1954-10-20 | Improvements to differential pumps | |
WO1998006612A1 (en) * | 1996-08-13 | 1998-02-19 | Kelsey Hayes Company | Dual action ball screw pump |
EP0945614A2 (en) * | 1998-03-26 | 1999-09-29 | Robert Bosch Gmbh | Piston pump for a vehicle brake system |
Also Published As
Publication number | Publication date |
---|---|
JP2015501253A (en) | 2015-01-15 |
DE102011086347A1 (en) | 2013-05-16 |
KR102007686B1 (en) | 2019-08-07 |
US20140298989A1 (en) | 2014-10-09 |
CN103946081B (en) | 2016-05-18 |
KR20140090628A (en) | 2014-07-17 |
CN103946081A (en) | 2014-07-23 |
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