CN102072128B - Eccentric wheel for driving hydraulic piston pump - Google Patents
Eccentric wheel for driving hydraulic piston pump Download PDFInfo
- Publication number
- CN102072128B CN102072128B CN201010556970.1A CN201010556970A CN102072128B CN 102072128 B CN102072128 B CN 102072128B CN 201010556970 A CN201010556970 A CN 201010556970A CN 102072128 B CN102072128 B CN 102072128B
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- Prior art keywords
- eccentric wheel
- piston
- speed
- cylinder body
- ratio
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- 239000012530 fluid Substances 0.000 claims abstract description 37
- 238000003825 pressing Methods 0.000 claims description 27
- 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 26
- 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
- 239000003921 oil Substances 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000005012 migration Effects 0.000 description 1
- 238000013508 migration Methods 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
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 ofly for driving the eccentric wheel of hydraulic piston pump, in described reciprocating pump, piston can move into and shift out in cylinder body, and described piston defines and is filled with the pressing chamber of 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 by means of motor, by being arranged on, eccentric wheel on live axle drives the oil hydraulic pump of brake regulation system.According to eccentric throw of eccentric, piston moves into and shifts out with identical speed in cylinder body, and electric motor often revolves the hydraulic fluid turning around all to delivered constant quantity delivered in pressing chamber.Here, when moving into from be filled with the pressing chamber of hydraulic fluid at piston and shifting out, the hydraulic fluid between piston and cylinder body scrapes off by seal arrangement, and has caused the fluid leakage from pressing chamber to eccentric wheel chamber.
In order to make the leakage of hydraulic fluid the least possible, developed various seal ring, these seal rings are arranged between cylinder body and piston and will be filled with the pressing chamber sealing of hydraulic fluid.
By the sealing guiding device for sealing 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 guide ring.Guide ring has at least one towards the surface of contact of supporting ring and is positioned at perpendicular to the region beyond the plane of piston longitudinal axis, and wherein, described region is obliquely installed with respect to described plane.
This sealing guiding device provides good sealing long working life in the situation that seal arrangement has, because when pump work, described seal element is pressed against the region that is not to be arranged in described plane, thereby on supporting ring, applies the power of radial inward.Therefore avoided seal element to be pressed into the region between supporting ring and piston, if the region that seal element is pressed between supporting ring and piston may cause the damage of seal element and cause leaking.
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 cylinder body, or guarantees leak free sealing between piston and cylinder body.
The present invention proposes a kind of for driving the eccentric wheel of hydraulic piston pump, in described reciprocating pump, piston can move into and shift out in cylinder body, 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 with the ratio that shifts out speed by eccentric shape adjustments, thereby set the fluid leakage amount of the regulation flowing out from pressing chamber.
Described hydraulic piston pump comprises the piston that has the cylinder body of inner chamber of cylinder block and 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 shifts out from inner chamber of cylinder block, described piston is drawn onto fluid in pressing chamber, and when moving into, described piston is extruded into the hydraulic system for work done by fluid from pressing chamber.
Here fluid should be interpreted as to 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 for setting piston and moves into and shift out speed certainty ratio really at cylinder body.That is to say, described piston has different speed when shifting out from cylinder body in the time of can be in moving into cylinder body.According to the present invention, by piston move into speed with shift out speed really certainty ratio set the fluid leakage amount of the regulation flowing 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 cylinder body, thereby piston is slipped on cylinder body with relatively little friction, and can not cause significant wearing and tearing.On the other hand, described leakage rate can be set for to the very little fluid capacity of reflux feeding back in other words in pressing chamber, thereby there will not be, may cause to adjacent component the great leakage loss of functional lesion.
In addition, can between piston and cylinder body, seal ring be set, described seal ring is for sealing 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 form sealing surface with the surface that the outer side surface of piston is close to.In this case, due to the leakage rate of setting in accordance with regulations, sealing surface slips on sealing lip with relatively little friction, and can not cause the noticeable wear of sealing lip.On the other hand, described leakage rate is very little, therefore there will not be great leakage loss.Therefore, here can be in view of the sealing lip fluid leakage amount of fixed wheel regulation wide and that flow out from pressing chamber really, the immigration speed to piston in cylinder body is set with the ratio that shifts out speed.Particularly advantageously, can apply the sealing lip with very long profile in working life.Such sealing lip profile has the geometrical shape that complexity is low.These sealing lip low cost of manufactures.
The present invention also comprise a kind of for the manufacture of of the present invention for driving the eccentric method of hydraulic piston pump.
According to the favourable improvement project of eccentric the first of the present invention, immigration speed is greater than 1 with the ratio that shifts out speed.
When wishing that the leakage rate of fluid is very little and wish that in other words fluid refluxes, set the ratio that immigration speed is greater than the speed of shifting out.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 the first curved section and the second curved section.Described the first curved section is when eccentric wheel rotates, to make piston be moved into the curved section in inner chamber of cylinder block, and described the 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 that the first curved section is crossed over is less than the angle that the second curved section is crossed over.
According to the favourable improvement project of eccentric the second of the present invention, immigration speed is 2 with the ratio that shifts out speed, is particularly 5 to the maximum.
If the immigration speed of piston in cylinder body, to be the degree of five times to the maximum higher than shifting out speed, can provide a kind of sealing extraordinary hydraulic piston pump.If immigration speed is 2 with the ratio that shifts out speed, just there will be significantly improving of sealing.
According to eccentric the third favourable improvement project of the present invention, immigration speed is less than 1 with the ratio that shifts out speed.
When wishing higher leakage rate, for example, while being used to form lubricating film, on the contrary, set the ratio that immigration speed is less than the speed of shifting out.
In this case, eccentric shape comprises the first curved section and the second curved section.Described the first curved section makes piston move into when the constant rotation of eccentric wheel, and described the second curved section shifts out piston when the constant rotation of eccentric wheel.Here, the angle that the first curved section is crossed over is greater than the angle that the second curved section is crossed over.
According to eccentric the 4th kind of favourable improvement project of the present invention, by eccentric shape adjustments, for making eccentric wheel often revolve and turn around, piston is covered a stroke in cylinder body.
By such design, hydraulic piston pump and described eccentric wheel can be integrated in the structure space that size is little.
According to eccentric the 5th kind of favourable improvement project of the present invention, by eccentric shape adjustments, for making eccentric wheel often revolve and turn around, piston is covered two or three strokes in cylinder body.
Eccentric this improvement project of the present invention, can be with providing the motor of less rotating speed to drive eccentric wheel.Described eccentric wheel has enough little size, to eccentric wheel and hydraulic gear pump are integrated in a little structure space.
In addition,, according to the present invention, task of the present invention by being used eccentric wheel of the present invention to be solved to produce the lubricating film of regulation in hydraulic piston pump.
By use eccentric wheel of the present invention in hydraulic piston pump, can between piston and cylinder body, provide lubricating film, described lubricating film has been guaranteed the relatively little to-and-fro motion of friction.The fluid leakage amount flowing 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 seal ring is set between cylinder body and piston, the wearing and tearing meeting of seal ring is especially little.The still very little fluid leakage amount substantially of here having guaranteed to flow out from pressing chamber.
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 move into and shift out and be arranged in described inner chamber of cylinder block.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 according to feature discussed above, set the fluid leakage amount of the regulation flowing out from pressing chamber.
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 be for example braking system, anti-lock braking system (ABS) or the Electronic Stability Program (ESP) system (ESP) with hydraulic braking regulon.For these braking system particularly advantageously, 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, for providing optimum braking function under the working life long.In addition, the leakage rate in motor vehicle braking system does not allow to have too high value, avoids whereby the functional lesion to adjacent component.
Accompanying drawing explanation
Below the schematic diagram by appended is described in detail the embodiment of solution of the present invention.Wherein:
Fig. 1 shows eccentric the first embodiment of the present invention with plan view,
Fig. 2 shows eccentric the second 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 axle, and by the piston 11 of constant rotating drive reciprocating piston pump.Described eccentric wheel 10 has size for the throw of eccentric of 0.1mm to 5mm.
Here, a plurality of eccentric wheels 10 are arranged on described axle.In addition, each eccentric wheel 10 drives a more than hydraulic piston pump.
Each piston 11 is by sliding support 13, roller support, tumbler bearing or be connected 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 groove being set on the working surface at eccentric wheel 10, piston 11 can, with less defeating on described eccentric wheel, can be reduced wear thus.
Described piston 11 can move into and shift out to be arranged on and in cylinder body 15 and in the inside of described cylinder body 15, define a pressing chamber 17 that is filled with fluid.
In addition, described eccentric wheel 10 has a kind of shape, this shape is chosen as, for setting piston 11 in the immigration speed of cylinder body 15 and shifting out between speed certainty ratio really.Immigration speed by piston 11 and shift out between speed the fluid leakage amount that certainty ratio really can be set in the regulation that the edge surface between cylinder body 15 and piston 11 leaks out from pressing chamber 17.
In Fig. 1, the shape of eccentric wheel 10 is adjusted for such working condition, that is, the immigration speed of piston 11 in cylinder body 15 is to shift out the twice of speed.The high leak tightness that there is no remarkable fluid leakage while thus, having guaranteed in piston 11 moves into cylinder body 15.According to shape shown in eccentric wheel 10, eccentric wheel 10 often revolves and turns around, and piston 11 is covered a stroke in cylinder body 15.
Described eccentric wheel 10 comprises a periphery, i.e. so-called envelope curver 12, described envelope curver be designed to eccentric and consistently around.
There is following relationship:
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 often revolves the number of stroke turning around,
The corner that α=make piston 11 moves in 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 the first curved section 14 and the second curved section 16.Described the first curved section 14 be when eccentric wheel 10 rotation, make piston 11 be moved into cylinder body 15 in and comprise the curved section of the corner α of 120 ° here.Described the second curved section 16 is to make piston 11 from cylinder body 15, shift out and comprise the curved section of the corner β of 240 ° here when eccentric wheel 10 rotation.According to shown in ratio and the equation beta/alpha=v of corner
a/ v
b=x, show that immigration speed and the ratio that shifts out speed are 2.
Envelope curver 12 has the different radiuses 20,22,24,26,28,30,32,34,36,38,40 with respect to center 18.Described the first and second curved sections 14,16 are limited by the radius 20 of 5mm and the radius 26 of 6mm respectively.Therefore maximum eccentricity in other words piston maximum stroke e be 1mm.Described the first curved section 14 has and comprises by radius 20,22, the curve of 24, the 26 radius sequences that form: radius 20 is 5mm, and radius 22 is 5.5mm, and radius 24 is 5.75mm, and radius 26 is 6mm.Described the second curved section 16 has and comprises by radius 26,28,30,32,34,36, the curve of 38,40, the 20 radius sequences that form: radius 26 is 6mm, radius 28 is 5.875mm, and radius 30 is 5.75mm, and radius 32 is 5.625mm, radius 34 is 5.5mm, radius 36 is 5.375mm, and radius 38 is 5.25mm, and radius 40 is that 5.125mm and radius 20 are 5mm.
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 the shape at this by eccentric wheel 10 is designed to make described eccentric wheel 10 often to revolve and turn around, and described piston 11 is covered two strokes in cylinder body 15.
The envelope curver 12 of the eccentric wheel 10 in Fig. 2 has four curved sections 14,16,42,44, that is, be to cross over the corner α of 60 ° successively
1the first curved section 14, cross over the corner β of 120 °
1the second curved section 16, cross over the corner α of 60 °
2the 3rd curved section 42, cross over the corner β of 120 °
2the 4th curved section 44.The described first and the 3rd curved section 14,42nd makes piston 11 be moved into the curved section in 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 rotation, 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, show that immigration speed and the ratio that shifts out speed are 2.
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.
For 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
bclose to 0.That is to say, in definite corner, 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.In addition the shape of eccentric wheel 10 is designed to make described eccentric wheel 10 often to revolve and turn around, piston 11 is just covered two strokes in cylinder body 15.
The envelope curver 12 of the eccentric wheel 10 in Fig. 3 has four curved sections 14,16,42,44, that is, be to cross over the corner α of 30 ° successively
1the first curved section 14, cross over the corner β of 150 °
1the second curved section 16, cross over the corner α of 30 °
2the 3rd curved section 42, cross over the corner β of 150 °
2the 4th curved section 44.The described first and the 3rd curved section 14,42nd makes piston 11 be moved into the curved section in 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 rotation, 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, show that immigration speed and the ratio that shifts out speed are 5.
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.
Eccentric wheel 10 is used to motor vehicle braking system, in the reciprocating pump of ABS or ESP system.Here, described eccentric wheel 10 is made by the cemented carbide of sintering.Such material can be realized high stability, little friction and high hertz stress.
Fig. 4 shows the plotted curve with two axis, and wherein, vertical y-axle represents lubrication film thickness difference, and unit is nm, and the x-axle of level represents that piston 11 moves into the immigration speed in cylinder bodies 15, and unit is mm/s.
Lubrication film thickness difference should be interpreted as to such lubricating film, this lubricating film is not scraped off in the side away from pressing chamber 17 when piston 11 moves in cylinder bodies 15, but is fed back in pressing chamber 17.Therefore, described lubrication film thickness difference refers to the fluid of output and the difference of leakage, and is to weigh the yardstick that moves into and shift out the fluid capacity of reflux between 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 between the outer side surface of piston and sealing lip, forms the lubricating film consisting of the fluid flowing out from pressing chamber 17.
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 under room temperature, to have size at pressing chamber 17 and between away from a side of pressing chamber be the pressure difference of 20MPa.
For thering is such seal ring 45, its profile comprises two supporting legs and between two supporting legs, has length is the section of 0.1mm, and curve 100 shows the immigration speed being moved in cylinder body 15 at piston 11 and is set to not produced simultaneously lubrication film thickness difference.
For thering is such seal ring 45, its profile comprises two supporting legs and between two supporting legs, has length is the section of 0.05mm, and curve 102 shows the immigration speed being moved in cylinder body 15 at piston 11 and is set to not produced simultaneously lubrication film thickness difference.
For thering is such seal ring 45, its profile comprises two supporting legs and between two supporting legs, has length is the section of 0.01mm, and curve 104 shows the immigration speed being moved in cylinder body 15 at piston 11 and is set to not produced simultaneously lubrication film thickness difference.
For having such seal ring, its profile comprises two supporting legs and between two supporting legs, has length is the section of 0.03mm, and curve 106 shows the immigration speed being moved in cylinder body 15 at piston 11 and is set to not produced simultaneously lubrication film thickness difference.
From curve 100, in immigration speed, it is 1 o'clock 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 long section for 0.1mm between two supporting legs, described lubrication film thickness difference, fluid capacity of reflux 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, fluid capacity of reflux is about 50nm, and has therefore roughly increased by one times.
For thering is such seal ring 45, its profile comprises two supporting legs and between two supporting legs, has the section that is shorter in length than 0.5mm, immigration speed in cylinder body 15 of lubrication film thickness difference and piston 11 and shift out between the ratio between speed and roughly exist linear relationship (referring to curve 100,102,104,106).
The immigration speed that piston 11 is moved in cylinder body 15 is higher, and the lubrication film thickness difference that migration process of piston 11 and shifting out obtains between process is just higher, and leakage loss just less (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 the functional lesion to adjacent component.
In Fig. 4, also show the setting (negative oil film thickness difference) of the desirable leakage rate for lubricated object.In order to obtain the leakage rate of regulation, adjust the shape of described eccentric wheel 10, make the immigration speed of piston 11 be less than the speed of shifting out.At profile, comprise two supporting legs and in the situation that there is the section that about length is 0.01mm between two supporting legs, in immigration speed (100mm/s) when shifting out little three times of speed (300mm/s), just can realize negative lubrication film thickness difference (referring to curve 104, point 108).On the contrary, at profile, comprise two supporting legs and in the situation that to have length between two supporting legs be the section of 0.1mm, in immigration speed (50mm/s), just reach negative lubrication film thickness difference (referring to curve 100, point 110) when shifting out little six times of speed (300mm/s).
The example value providing 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 (10)
1. one kind for driving the eccentric wheel (10) of hydraulic piston pump, in described reciprocating pump, piston (11) can move into and shift out in cylinder body (15), and described piston defines one and is filled with the pressing chamber (17) of fluid and 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 fluid leakage amount of the regulation flowing out from pressing chamber (17).
2. according to eccentric wheel claimed in claim 1 (10), it is characterized in that, immigration speed is greater than 1 with the ratio that shifts out speed.
3. according to eccentric wheel claimed in claim 2 (10), it is characterized in that, described ratio is 2.
4. according to eccentric wheel claimed in claim 2 (10), it is characterized in that, described ratio is 5 to the maximum.
5. according to eccentric wheel claimed in claim 1 (10), it is characterized in that, immigration speed is less than 1 with the ratio that shifts out speed.
6. according to the eccentric wheel described in any one in claim 1 to 5 (10), it is characterized in that, by the shape adjustments of described eccentric wheel (10), for making described eccentric wheel (10) often revolve and turn around, described piston (11) is covered a stroke in cylinder body (15).
7. according to the eccentric wheel described in any one in claim 1 to 5 (10), it is characterized in that, by the shape adjustments of described eccentric wheel (10), for making described eccentric wheel (10) often revolve and turn around, described piston (11) is covered two or three strokes in cylinder body (15).
8. according to the application of the eccentric wheel described in any one in claim 1 to 7 (10), it is characterized in that, described eccentric wheel is for producing the lubricating film of regulation at hydraulic piston pump.
9. a hydraulic piston pump, is characterized in that, described hydraulic piston pump has according to the eccentric wheel described in any one in claim 1 to 7 (10).
10. a motor vehicle braking system, is characterized in that, described motor vehicle braking system has according to hydraulic piston pump claimed in claim 9.
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 CN102072128A (en) | 2011-05-25 |
| CN102072128B true 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) |
Families Citing this family (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 (4)
| 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 |
| 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 (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09303252A (en) * | 1996-05-13 | 1997-11-25 | Nissan Motor Co Ltd | Hydraulic pump device |
| 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 CN CN201010556970.1A patent/CN102072128B/en active Active
- 2010-11-19 FR FR1059527A patent/FR2952977A1/en not_active Withdrawn
Patent Citations (4)
| 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 |
| 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 |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102072128A (en) | 2011-05-25 |
| FR2952977A1 (en) | 2011-05-27 |
| DE102009046983A1 (en) | 2011-05-26 |
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