CN102072128A - Eccentric wheel for driving hydraulic piston pump - Google Patents
Eccentric wheel for driving hydraulic piston pump Download PDFInfo
- Publication number
- CN102072128A CN102072128A CN2010105569701A CN201010556970A CN102072128A CN 102072128 A CN102072128 A CN 102072128A CN 2010105569701 A CN2010105569701 A CN 2010105569701A CN 201010556970 A CN201010556970 A CN 201010556970A CN 102072128 A CN102072128 A CN 102072128A
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- Prior art keywords
- eccentric wheel
- piston
- speed
- cylinder body
- described eccentric
- 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.)
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Links
- 239000012530 fluid Substances 0.000 claims abstract description 27
- 239000007788 liquid Substances 0.000 claims description 10
- 230000001050 lubricating effect Effects 0.000 claims description 10
- 230000006835 compression Effects 0.000 abstract 2
- 238000007906 compression Methods 0.000 abstract 2
- 238000007789 sealing Methods 0.000 description 24
- 238000005461 lubrication Methods 0.000 description 15
- 230000002349 favourable effect Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 238000010992 reflux Methods 0.000 description 5
- 230000003902 lesion Effects 0.000 description 4
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical compound OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 description 3
- 238000013461 design Methods 0.000 description 3
- 239000003921 oil Substances 0.000 description 3
- 239000000463 material Substances 0.000 description 2
- 238000013459 approach Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000013508 migration Methods 0.000 description 1
- 230000005012 migration Effects 0.000 description 1
- 239000002480 mineral oil Substances 0.000 description 1
- 235000010446 mineral oil Nutrition 0.000 description 1
- 238000005245 sintering Methods 0.000 description 1
- 238000013519 translation Methods 0.000 description 1
- 230000014616 translation Effects 0.000 description 1
- 230000035899 viability Effects 0.000 description 1
Images
Classifications
-
- 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
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
- F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
- F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics
Abstract
The invention provides an eccentric wheel (10) for driving a hydraulic piston pump; in the piston pump, a piston (11) can move in to and move out of a cylinder (15); the piston restricts a compression chamber (17) filled with a fluid and is driven by an eccentric wheel (10); the ratio of the velocity for the piston (11) to move in to and move out of the cylinder (15) is adjusted by the shape of the eccentric wheel (10) so as to setting the specified leakage amount flowed out from the compression chamber (17).
Description
Technical field
The present invention relates to a kind of eccentric wheel that is used to drive hydraulic piston pump, in described reciprocating pump, piston can move in cylinder body and shift out, and described piston defines the pressing chamber that is filled with fluid and driven by eccentric wheel.In addition, the invention still further relates to described eccentric a kind of application, a kind of oil hydraulic pump and a kind of motor vehicle braking system.
Background technique
Normally eccentric wheel on the live axle drives the oil hydraulic pump of brake regulation system by being installed in by means of motor.According to eccentric throw of eccentric, piston moves into and shifts out with identical speed in cylinder body, and electric motor whenever revolves all hydraulic fluids of delivered constant quantity delivered in pressing chamber that turns around.Here, when piston moved into from the pressing chamber that is filled with hydraulic fluid and shifts out, the hydraulic fluid between piston and cylinder body scraped off by seal arrangement, and had caused the escape of liquid from pressing chamber to the eccentric wheel chamber.
The least possible for the leakage that makes hydraulic fluid, developed various seal ring, these seal rings are arranged between cylinder body and the piston and will be filled with the pressing chamber sealing of hydraulic fluid.
By the sealing guiding device that is used to seal on the known a kind of piston that is located at pump of DE 10 2,006 036 442 A1.Described sealing guiding device comprises guide ring, supporting ring and seal element, and wherein supporting ring is arranged between seal element and the guide ring.Guide ring has at least one towards the surface of contact of supporting ring and is positioned at perpendicular to the zone beyond the plane of piston longitudinal axis, and wherein, described zone is with respect to described plane inclination setting.
This sealing guiding device has at seal arrangement under the situation in long working life provides good sealing, because when pump work, described seal element is pressed against the zone that is not to be arranged in described plane, thereby applies the power of radial inward on supporting ring.Therefore avoided seal element to be pressed into zone between supporting ring and the piston, then may cause the damage of seal element and cause leaking if seal element is pressed into zone between supporting ring and the piston.
Summary of the invention
Task of the present invention is: a kind of hydraulic piston pump is provided, and described hydraulic piston pump can be guaranteed the desired leakage rate of target in other words of the regulation between piston and the cylinder body, perhaps guarantees leak free sealing between piston and the cylinder body.
The present invention proposes a kind of eccentric wheel that is used to drive hydraulic piston pump, in described reciprocating pump, piston can move in cylinder body and shift out, described piston defines one and is filled with the pressing chamber of fluid and is driven by eccentric wheel, and in described reciprocating pump, the immigration of piston in cylinder body and the ratio that shifts out speed be by eccentric shape adjustments, thereby set the escape of liquid amount of the regulation that flows out from pressing chamber.
Described hydraulic piston pump comprises cylinder body with inner chamber of cylinder block and the piston that can move into and shift out in inner chamber of cylinder block.Described piston is driven by the eccentric wheel of rotatable support of the present invention.Described piston will be filled with the pressing chamber sealing of fluid in inner chamber of cylinder block.When piston shifted out from inner chamber of cylinder block, described piston was drawn onto fluid in the pressing chamber, and when moving into, described piston is extruded into the hydraulic system that is used for work done with fluid from pressing chamber.
Here fluid should be interpreted as gas and/or hydraulic fluid, as the hydraulic fluid of mineral oil or ethylene glycol.
Described eccentric wheel of the present invention comprises such shape, and this shape is adjusted to and is used for setting piston and moves into and shift out speed certainty ratio really at cylinder body.That is to say that described piston has different speed when shifting out in the time of can be in moving into cylinder body from cylinder body.According to the present invention, by piston move into speed with shift out speed really certainty ratio set the escape of liquid amount of the regulation that flows out from pressing chamber.
On the one hand, this leakage rate can be set to, and described leakage rate can provide the lubricating film of the regulation between piston and the cylinder body, thereby piston is slipped on cylinder body with less relatively friction, and can not cause significant wearing and tearing.On the other hand, described leakage rate can be set for the very little fluid reflux amount that feeds back in other words in the pressing chamber, thereby the great leakage loss of functional lesion can not occur to cause adjacent component.
In addition, can between piston and cylinder body seal ring be set, described seal ring is used to seal the pressing chamber that is filled with fluid.Described seal ring comprises the sealing lip with definite profile, described sealing lip with otherwise with the inner side surface of cylinder body, or constitute sealing surface with surface that the outer side surface of piston is close to.In this case, owing to the leakage rate of setting in accordance with regulations, sealing surface slips on sealing lip with less relatively friction, and can not cause the noticeable wear of sealing lip.On the other hand, described leakage rate is very little, therefore great leakage loss can not occur.Therefore, here can the immigration speed of piston in cylinder body and the ratio that shifts out speed be set in view of the sealing lip escape of liquid amount of fixed wheel regulation wide and that flow out from pressing chamber really.Particularly advantageous is to use the sealing lip with very long profile in working life.Such sealing lip profile has the low geometrical shape of complexity.These sealing lip low cost of manufactures.
The present invention also comprises a kind of eccentric method that is used to drive hydraulic piston pump of the present invention that is used to make.
According to eccentric first kind of favourable improvement project of the present invention, immigration speed with shift out the ratio of speed greater than 1.
When the leakage rate of wishing fluid is very little when wishing fluid reflux in other words, set immigration speed greater than the ratio that shifts out speed.Such eccentric wheel can be realized the high leak tightness of hydraulic piston pump.
Such eccentric wheel has a kind of shape, and described shape comprises first curved section and second curved section.Described first curved section is to make piston be moved into curved section in the inner chamber of cylinder block when eccentric wheel rotates, and described second curved section is the curved section that when eccentric wheel rotates piston is shifted out from inner chamber of cylinder block.Here, the angle of first curved section leap is less than the angle of second curved section leap.
According to eccentric second kind of favourable improvement project of the present invention, immigration speed is 2 with the ratio that shifts out speed, particularly is 5 to the maximum.
If the immigration speed of piston in cylinder body is higher than the speed of shifting out with the degree that is five times to the maximum, then can provide a kind of sealing extraordinary hydraulic piston pump.If immigration speed is 2 with the ratio that shifts out speed, significantly improving of sealing will appear.
According to eccentric the third favourable improvement project of the present invention, immigration speed with shift out the ratio of speed less than 1.
When hope has higher leakage rate, when for example being used to form lubricating film, then on the contrary, set immigration speed less than the ratio that shifts out speed.
In this case, eccentric shape comprises first curved section and second curved section.Described first curved section makes piston move into when the constant rotation of eccentric wheel, and described second curved section shifts out piston when the constant rotation of eccentric wheel.Here, the angle of first curved section leap is greater than the angle of second curved section leap.
According to eccentric the 4th kind of favourable improvement project of the present invention, eccentric shape adjustments is turned around for making eccentric wheel whenever revolve, piston is covered a stroke in cylinder body.
By such design, hydraulic piston pump and described eccentric wheel can be integrated in the little structure space of size.
According to eccentric the 5th kind of favourable improvement project of the present invention, eccentric shape adjustments is turned around for making eccentric wheel whenever revolve, piston is covered two or three strokes in cylinder body.
Eccentric this improvement project of the present invention, can use provides the motor of less rotating speed to drive eccentric wheel.Described eccentric wheel has enough little size, so that eccentric wheel and hydraulic gear pump are integrated in the little structure space.
In addition, according to the present invention, task of the present invention is solved with the lubricating film that produces regulation by use eccentric wheel of the present invention in hydraulic piston pump.
By in hydraulic piston pump, using eccentric wheel of the present invention, can between piston and cylinder body, provide lubricating film, described lubricating film has been guaranteed the less relatively to-and-fro motion of friction.The escape of liquid amount that flows out from pressing chamber is very little, thereby has avoided the functional lesion to adjacent component.Eccentric wheel of the present invention can be particularly uses in the hydraulic piston pump of viability in other words in the working life that will rectificate.If between cylinder body and piston seal ring is set, then the wearing and tearing meeting of seal ring is especially little.Here guaranteed from the still very little basically escape of liquid amount of pressing chamber outflow.
Eccentric wheel of the present invention can be applied in the hydraulic piston pump of all its Sealing requirement translations.When to requiring in sealing and/or working life when very high, the such eccentric wheel of provable use has superiority especially.
In addition, also provide a kind of eccentric hydraulic piston pump of the present invention that has.
Hydraulic piston pump of the present invention comprises a cylinder body with inner chamber of cylinder block, and piston can be arranged in the described inner chamber of cylinder block with moving into and shift out.Described piston is driven by rotating eccentric wheel, and defines a pressing chamber that is filled with fluid.By the shape of eccentric regulation adjust piston in cylinder body immigration speed with shift out speed certainty ratio really, thereby set the escape of liquid amount of the regulation that flows out from pressing chamber according to feature discussed above.
In addition, also provide a kind of motor vehicle braking system with hydraulic piston pump, described hydraulic piston pump has eccentric wheel of the present invention.
Such motor vehicle braking system can for example be braking system, anti-lock braking system (ABS) or the Electronic Stability Program (ESP) system (ESP) with hydraulic braking regulon.Particularly advantageously for these braking system be when the value that the leakage rate of reciprocating pump has a regulation scribbles the lubricating film of regulation in other words between piston and cylinder body, to be used under long working life, providing optimum braking function.In addition, the leakage rate in the motor vehicle braking system does not allow to have too high value, avoids the functional lesion to adjacent component whereby.
Description of drawings
To be described in detail by the embodiment of appended schematic representation below solution of the present invention.Wherein:
Fig. 1 shows eccentric first kind of embodiment of the present invention with plan view,
Fig. 2 shows eccentric second kind of embodiment of the present invention with plan view,
Fig. 3 shows eccentric the third embodiment of the present invention with plan view,
Fig. 4 shows a plotted curve, this diagram shows under the constant speed that shifts out, lubrication film thickness difference and the variation relation that moves into speed.
Embodiment
Fig. 1 shows eccentric wheel 10 of the present invention.Described eccentric wheel 10 is rotatably supported on the axle, and the piston 11 by constant rotating drive reciprocating piston pump.Described eccentric wheel 10 has size and is the throw of eccentric of 0.1mm to 5mm.
Here, a plurality of eccentric wheels 10 are arranged on the described axle.In addition, each eccentric wheel 10 drives a more than hydraulic piston pump.
Each piston 11 all links by sliding support 13, roller support, tumbler bearing or by direct supporting and eccentric wheel 10.For this reason, described eccentric wheel 10 has groove on working surface, and the sliding element of piston 11 can slide in described groove.By on the working surface of eccentric wheel 10, groove being set, piston 11 can be reduced wear thus with littler defeating on described eccentric wheel.
Described piston 11 can be arranged on with moving into and shift out and define a pressing chamber 17 that is filled with fluid in the cylinder body 15 and in the inside of described cylinder body 15.
In addition, described eccentric wheel 10 has a kind of shape, and this shape is chosen as, and is used for setting piston 11 in the immigration speed of cylinder body 15 with shift out between the speed certainty ratio really.Immigration speed by piston 11 and shift out between the speed escape of liquid amount that certainty ratio really can be set in the regulation that the edge surface between cylinder body 15 and the piston 11 leaks out from pressing chamber 17.
In Fig. 1, the shape of eccentric wheel 10 is adjusted at such working condition, that is, the immigration speed of piston 11 in cylinder body 15 is to shift out the twice of speed.Thus, guaranteed when piston 11 moves in the cylinder body 15, not have the high leak tightness of remarkable escape of liquid.According to shape shown in the eccentric wheel 10, eccentric wheel 10 whenever revolves and turns around, and piston 11 is covered a stroke in cylinder body 15.
Described eccentric wheel 10 comprises a periphery, promptly so-called envelope curver 12, described envelope curver be designed to eccentric and consistently around.
Following relationship is arranged:
v
a/v
b＝x
n*(α+β)＝360°
β/α＝v
a/v
b＝x
h
a＝e/α
h
b=e/ β, wherein
v
aThe immigration speed of=piston 11,
v
bThe speed that shifts out of=piston 11,
X=moves into speed and the ratio that shifts out speed,
N=eccentric wheel 10 whenever revolves the number of stroke that turns around,
The corner that α=make piston 11 moves in the cylinder bodies 15,
The corner of β=piston 11 is shifted out from cylinder body 15,
h
aConstant envelope curver slope when=piston 11 moves into,
h
bConstant envelope curver slope when=piston 11 shifts out,
E=piston maximum stroke
As Fig. 1, the envelope curver 12 of eccentric wheel 10 has first curved section 14 and second curved section 16.Described first curved section 14 is the curved sections that make piston 11 be moved in the cylinder body 15 when eccentric wheel 10 rotations and comprise 120 ° corner α here.Described second curved section 16 is to make piston 11 shift out and comprise the curved section of 240 ° corner β here from cylinder body 15 when eccentric wheel 10 rotations.According to shown in the ratio and the equation beta/alpha=v of corner
a/ v
b=x, drawing immigration speed is 2 with the ratio that shifts out speed.
Fig. 2 shows a kind of eccentric wheel 10, and it is 2 that described eccentric wheel similarly makes the immigration speed of piston 11 in cylinder body 15 and the ratio that shifts out speed by its shape, that is to say that making immigration speed is to shift out the twice of speed.Yet turn around for making described eccentric wheel 10 whenever revolve in this shaped design with eccentric wheel 10, described piston 11 is covered two strokes in cylinder body 15.
The envelope curver 12 of the eccentric wheel 10 among Fig. 2 has four curved sections 14,16,42,44, that is, be to cross over 60 ° corner α successively
1First curved section 14, cross over 120 ° corner β
1Second curved section 16, cross over 60 ° corner α
2The 3rd curved section 42, cross over 120 ° corner β
2The 4th curved section 44.The described first and the 3rd curved section 14,42nd makes piston 11 be moved into curved section in the cylinder body 15 when eccentric wheel 10 rotation.The described second and the 4th curved section 16,44th, the curved section that when eccentric wheel 10 rotations, piston 11 is shifted out from cylinder body 15.According to shown in corner ratio and equality beta
1/ α
1=β
2/ α
2=v
a/ v
b=x, drawing immigration speed is 2 with the ratio that shifts out speed.
Described curved section 14,16,42,44 is respectively limited by the radius 20 of 5mm and the radius 26 of 6mm.Therefore maximum eccentricity in other words piston maximum stroke e be 1mm.
At the threshold switch time of hydraulic reciprocating type reciprocating pump, make the envelope curver slope h of curved section short between two strokes
aAnd h
bApproach 0.That is to say that in the corner of determining, piston 11 does not almost have stroke.
Fig. 3 shows a kind of eccentric wheel 10, and it is 5 that described eccentric wheel makes immigration speed and the ratio that shifts out speed by its shape, that is to say that making immigration speed is to shift out 5 times of speed.Shaped design with eccentric wheel 10 turns around for making described eccentric wheel 10 whenever revolve in addition, and piston 11 is just covered two strokes in cylinder body 15.
The envelope curver 12 of the eccentric wheel 10 among Fig. 3 has four curved sections 14,16,42,44, that is, be to cross over 30 ° corner α successively
1First curved section 14, cross over 150 ° corner β
1Second curved section 16, cross over 30 ° corner α
2The 3rd curved section 42, cross over 150 ° corner β
2The 4th curved section 44.The described first and the 3rd curved section 14,42nd makes piston 11 be moved into curved section in the cylinder body 15 when eccentric wheel 10 rotation.The described second and the 4th curved section 16,44th, the curved section that when eccentric wheel 10 rotations, piston 11 is shifted out from cylinder body 15.According to shown in corner ratio and equality beta
1/ α
1=β
2/ α
2=v
a/ v
b=x, drawing immigration speed is 5 with the ratio that shifts out speed.
Described curved section 14,16,42,44 is respectively limited by the radius 20 of 5mm and the radius 26 of 6mm.Therefore maximum eccentricity or piston maximum stroke e are again 1mm.
Fig. 4 shows the plotted curve with two axis, and wherein, vertical y-axle is represented the lubrication film thickness difference, and unit is nm, and the x-axle of level represents that piston 11 moves into the immigration speed in the cylinder bodies 15, and unit is mm/s.
The lubrication film thickness difference should be interpreted as such lubricating film, this lubricating film is not scraped off in the side away from pressing chamber 17 when piston 11 moves in the cylinder body 15, but is fed back in the pressing chamber 17.Therefore, described lubrication film thickness difference is meant the fluid of output and the difference of leakage, and is to weigh the yardstick that moves into and shift out the fluid reflux amount between the process at piston 11 thus.
Described plotted curve relates to a kind of piston-cylinder-device, in described device, is provided with the seal ring 45 with sealing lip between piston 11 and cylinder body 15.Described piston 11 slips on the sealing lip of seal ring 15 by its outer side surface during moving in cylinder body 15 and shifting out, and forms the lubricating film that is made of the fluid that flows out from pressing chamber 17 between the outer side surface of piston and sealing lip.
Described plotted curve has been described for having four kinds of differently contoured seal rings 45, corresponding lubrication film thickness difference when the immigration velocity variations of piston 11.Here, the speed that shifts out of piston 11 always equals 300mm/s, and to have size at pressing chamber 17 and between away from a side of pressing chamber under room temperature be the pressure difference of 20MPa.
For having such seal ring 45, its profile comprises two supporting legs and has between two supporting legs and long is that the section of 0.1mm, curve 100 show the immigration speed that is moved in the cylinder body 15 at piston 11 and be set to not produced simultaneously lubrication film thickness difference.
For having such seal ring 45, its profile comprises two supporting legs and has between two supporting legs and long is that the section of 0.05mm, curve 102 show the immigration speed that is moved in the cylinder body 15 at piston 11 and be set to not produced simultaneously lubrication film thickness difference.
For having such seal ring 45, its profile comprises two supporting legs and has between two supporting legs and long is that the section of 0.01mm, curve 104 show the immigration speed that is moved in the cylinder body 15 at piston 11 and be set to not produced simultaneously lubrication film thickness difference.
For having such seal ring, its profile comprises two supporting legs and has between two supporting legs and longly is that the section of 0.03mm, curve 106 show the immigration speed that is moved in the cylinder body 15 at piston 11 and be set to not produced simultaneously lubrication film thickness difference.
From curve 100 as can be known, is 1 o'clock in immigration speed with the ratio that shifts out speed, that is to say in immigration speed when shifting out speed and be 300mm/s, and when profile comprises two supporting legs and have the section of the long 0.1mm of being between two supporting legs, described lubrication film thickness difference, promptly the fluid reflux amount is set to about 27nm.
When the immigration speed of piston 11 is elevated to about 650mm/s to about 700mm/s, described lubrication film thickness difference, promptly the fluid reflux amount is about 50nm, and has therefore roughly increased by one times.
For having such seal ring 45, its profile comprises two supporting legs and have the section that is shorter in length than 0.5mm between two supporting leg, lubrication film thickness difference and piston 11 in cylinder body 15 immigration speed and shift out between the ratio between the speed and roughly exist linear relationship (referring to curve 100,102,104,106).
The immigration speed that piston 11 is moved in the cylinder body 15 is high more, and then the lubrication film thickness difference that obtains between the process of the migration process of piston 11 and shifting out is just high more, and leakage loss just more little (referring to curve 100,102,104,106).
By means of the shape of eccentric wheel 10 of the present invention, therefore can provide a kind of hydraulic piston pump, described reciprocating pump has been guaranteed long working time under high leak tightness.Avoided functional lesion to adjacent component.
In Fig. 4, also show the desirable setting (negative oil film thickness difference) that is used for the leakage rate of lubricated purpose.For the leakage rate that obtains stipulating, adjust the shape of described eccentric wheel 10, the immigration speed that makes piston 11 is less than shifting out speed.Comprise two supporting legs and have between two supporting legs under the situation of section that about length is 0.01mm at profile, in immigration speed (100mm/s) when shifting out little three times of speed (300mm/s), the lubrication film thickness difference that just can realize bearing (referring to curve 104, point 108).On the contrary, comprise two supporting legs and have between two supporting legs under the situation of long section for 0.1mm at profile, just reach negative lubrication film thickness difference (referring to curve 100, point 110) when shifting out little six times of speed (300mm/s) in immigration speed (50mm/s).
The example value that provides above depends on various parameters, as the material of surface quality, temperature conditions, type of fluid and the use of the length of stroke of piston 11 in cylinder body 15, piston 11.
Claims (9)
1. eccentric wheel (10) that is used to drive hydraulic piston pump, in described reciprocating pump, piston (11) can move in cylinder body (15) and shift out, and described piston defines one and is filled with the pressing chamber (17) of fluid and is driven by described eccentric wheel (10),
It is characterized in that the immigration of described piston (11) in cylinder body (15) and the ratio that shifts out speed are by the shape adjustments of described eccentric wheel (10), thereby set the escape of liquid amount of the regulation that flows out from pressing chamber (17).
2. according to the described eccentric wheel of claim 1 (10), it is characterized in that, immigration speed with shift out the ratio of speed greater than 1.
3. according to the described eccentric wheel of claim 2 (10), it is characterized in that described ratio is 2, particularly is 5 to the maximum.
4. according to the described eccentric wheel of claim 1 (10), it is characterized in that, immigration speed with shift out the ratio of speed less than 1.
5. according to any described eccentric wheel (10) in the claim 1 to 4, it is characterized in that the shape adjustments of described eccentric wheel (10) is turned around for making described eccentric wheel (10) whenever revolve, and described piston (11) is covered a stroke in cylinder body (15).
6. according to any described eccentric wheel (10) in the claim 1 to 4, it is characterized in that, the shape adjustments of described eccentric wheel (10) is turned around for making described eccentric wheel (10) whenever revolve, and described piston (11) is covered two or three strokes in cylinder body (15).
7. according to the application of any described eccentric wheel (10) in the claim 1 to 6, it is characterized in that described eccentric wheel is used for producing at hydraulic piston pump the lubricating film of regulation.
8. a hydraulic piston pump is characterized in that, described hydraulic piston pump has according to any described eccentric wheel (10) in the claim 1 to 6.
9. a motor vehicle braking system is characterized in that, described motor vehicle braking system has according to the described hydraulic piston pump of claim 8.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE200910046983 DE102009046983A1 (en) | 2009-11-23 | 2009-11-23 | Eccentric for driving hydraulic piston pump in vehicle brake system, drives piston extended in cylinder, where ratio of extension and retraction speed of piston is adapted to shape of eccentric so that leakage of fluid is set from chamber |
| DE102009046983.4 | 2009-11-23 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102072128A true CN102072128A (en) | 2011-05-25 |
| CN102072128B CN102072128B (en) | 2014-10-08 |
Family
ID=43901837
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201010556970.1A Active CN102072128B (en) | 2009-11-23 | 2010-11-19 | Eccentric wheel for driving hydraulic piston pump |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN102072128B (en) |
| DE (1) | DE102009046983A1 (en) |
| FR (1) | FR2952977A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102501879A (en) * | 2011-10-31 | 2012-06-20 | 中国北车集团大连机车车辆有限公司 | Locomotive tread unit brake with constant braking force |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4028018A (en) * | 1974-06-10 | 1977-06-07 | Paterson Candy International Limited | Non-pulsing apparatus |
| JPH09303252A (en) * | 1996-05-13 | 1997-11-25 | Nissan Motor Co Ltd | Hydraulic pump device |
| CN1204384A (en) * | 1995-11-14 | 1999-01-06 | 费卢瓦泵有限公司 | Device with at least two drive cylinders |
| US5960699A (en) * | 1996-09-16 | 1999-10-05 | Robert Bosch Gmbh | Hydraulic pump unit |
| US6237441B1 (en) * | 1998-03-19 | 2001-05-29 | Sumitomo Electric Industries, Ltd. | Combination of shim and cam |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102006036442A1 (en) | 2006-08-04 | 2008-02-07 | Robert Bosch Gmbh | Sealing and guiding device for a piston of a piston pump |
-
2009
- 2009-11-23 DE DE200910046983 patent/DE102009046983A1/en active Pending
-
2010
- 2010-11-19 FR FR1059527A patent/FR2952977A1/en not_active Withdrawn
- 2010-11-19 CN CN201010556970.1A patent/CN102072128B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4028018A (en) * | 1974-06-10 | 1977-06-07 | Paterson Candy International Limited | Non-pulsing apparatus |
| CN1204384A (en) * | 1995-11-14 | 1999-01-06 | 费卢瓦泵有限公司 | Device with at least two drive cylinders |
| JPH09303252A (en) * | 1996-05-13 | 1997-11-25 | Nissan Motor Co Ltd | Hydraulic pump device |
| US5960699A (en) * | 1996-09-16 | 1999-10-05 | Robert Bosch Gmbh | Hydraulic pump unit |
| US6237441B1 (en) * | 1998-03-19 | 2001-05-29 | Sumitomo Electric Industries, Ltd. | Combination of shim and cam |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102501879A (en) * | 2011-10-31 | 2012-06-20 | 中国北车集团大连机车车辆有限公司 | Locomotive tread unit brake with constant braking force |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102009046983A1 (en) | 2011-05-26 |
| FR2952977A1 (en) | 2011-05-27 |
| CN102072128B (en) | 2014-10-08 |
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