CN101761463A - Drive unit - Google Patents
Drive unit Download PDFInfo
- Publication number
- CN101761463A CN101761463A CN200910261507A CN200910261507A CN101761463A CN 101761463 A CN101761463 A CN 101761463A CN 200910261507 A CN200910261507 A CN 200910261507A CN 200910261507 A CN200910261507 A CN 200910261507A CN 101761463 A CN101761463 A CN 101761463A
- Authority
- CN
- China
- Prior art keywords
- driver element
- motor reel
- support
- eccentric
- mechanical transmission
- 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.)
- Granted
Links
- 230000009347 mechanical transmission Effects 0.000 claims abstract description 10
- 238000005096 rolling process Methods 0.000 claims description 34
- 230000007246 mechanism Effects 0.000 claims description 10
- 230000009467 reduction Effects 0.000 claims description 4
- 238000009434 installation Methods 0.000 claims description 3
- 230000005540 biological transmission Effects 0.000 abstract description 3
- 230000033001 locomotion Effects 0.000 description 9
- 230000002349 favourable effect Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 239000000470 constituent Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 239000013589 supplement Substances 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Hydraulic Motors (AREA)
- Valves And Accessory Devices For Braking Systems (AREA)
- Regulating Braking Force (AREA)
- Retarders (AREA)
- Friction Gearing (AREA)
- Braking Arrangements (AREA)
Abstract
The invention relates to a drive unit, in particular to the operation of radial piston pumps of a hydraulic apparatus of a motor vehicle with an electronic slip-proof brake system. According to the invention, it is proposed that the eccentric devices (14, 16, 18) of the drive unit (10) includes mechanical transmission devices (16, 20, 22, 24) for the support body (18) which embraces eccentric devices (14, 16, 18). The mechanical transmission device (16, 20, 22, 24) allows the difference in rotation speed between the electric motor shaft (12) and the support body (18). More specially, the transmission device (16, 20, 22, 24) in reduced speed allows the use of drive motor in high rotation speed having relatively little drive torque and compact structure.
Description
Technical field
The present invention relates to a kind of driver element, it has the radial plunger pump of hydraulic pressure installation of the brake device for car of electronic anti-breaking control function especially for manipulation, this driver element comprises that the drive motor that has motor reel and at least one are arranged on the eccentric on the described motor reel, wherein, described eccentric is surrounded by the support that is bearing on a plurality of roller supports at periphery.
Background technique
This class driver element is well known in the prior art.They comprise drive motor that has the motor reel that stretches out and the eccentric that is arranged on this motor reel.This eccentric usually by rolling bearing and the eccentric wheel that is arranged on prejudicially on the motor reel constitute, this rolling bearing is pressed on the eccentric wheel.The outer collar bearing of this rolling bearing is configured for the support of the plunger of radial plunger pump to be driven.
The rotational motion of motor reel is transformed into the linear reciprocating motion of plunger from eccentric.The rolling bearing that has been provided with prevents to cause noise to wear and tear in other words at plunger near sliding friction occurring on the end face of eccentric when this movement conversion.
In known driver element, eccentric wheel can be to be pressed on the axle with relatively rotating, and perhaps scheme as an alternative can be integrally formed with motor reel.Therefore, in these two kinds of variants, the rotating speed of drive motor and eccentric is consistent forcibly.This is to use through the special drive motor of adjusting to prerequisite, is predetermined and relevant with rotating speed because have the transmission power (quantity delivered and pressure maximum) of the brake device for car of anti-skidding control function.
The drive motor that can be used in the brake device for car with anti-skidding control function needs higher driving torque.What use up to now is the drive motor with corresponding relatively slow speed than the macrostructure volume.These drive motors are for the brake device for car that is applied to have anti-skidding control function and custom-designed and be difficult to be applied to the other technologies field.This makes this drive motor cost an arm and a leg.
Summary of the invention
In order to overcome above-mentioned shortcoming, the present invention proposes a kind of driver element that starts described type, and wherein, described eccentric has the mechanical transmission that is used for described support
Compared with prior art, driver element of the present invention has following advantage, that is, eccentric externally also comprises the mechanical actuation device that is used for support under the constant situation of size and stroke bore ratio.This drive unit is integrated in the eccentric and allows drive motor with the rotational speed higher than support.Therefore, the present invention makes the drive motor of the high speed rotating with less driving torque also can be applied to have in the hydraulic pressure installation of brake device for car of anti-skidding control function.At various commercial Application purposes, the drive motor of high speed rotating can obtain on market inexpensively.Another outstanding feature of the drive motor of high speed rotating is to have compact and lightweight structural type.In addition, simple relatively thereby with low cost based on structure of driving unit of the present invention.
In a kind of favourable mode of execution of the present invention, described mechanical transmission has the driving mechanism that forms between described motor reel and described support.Preferably, described driving mechanism is a gear drive, this gear drive comprises the outer gearing portion that is positioned on the described live axle, be positioned on the described support engaging piece and with the intermediate gear of described engaging piece and the engagement of described outer gearing portion.Described intermediate gear preferably is arranged on the axle identical with one of them described rolling element.In addition, described gear drive preferably is designed to reduction gearing mechanism.
In the favourable mode of execution of another kind of the present invention, described mechanical transmission comprises the rolling element with the external diameter that differs in size from one another, and these rolling elements are bearing in described support on the described motor reel.Preferably, described rolling element is a needle roller.
Other advantages of the present invention and favourable improvement project can be by obtaining in the following description.
Description of drawings
Accompanying drawing shows embodiments of the invention, in the following description it is elaborated.Accompanying drawing comprises three figure altogether, and wherein, Fig. 1 and Fig. 2 show the opposite sectional elevation of both direction of driver element of the present invention respectively, and Fig. 3 shows the longitudinal section of driver element.
Embodiment
Fig. 1 and Fig. 2 show the driver element 10 that is made of motor reel 12, the retainer 14 that has rolling element 16 and support 18 respectively.Motor reel 12 is constituent elements of unshowned drive motor, and motor reel 12 imposed on rotational motion by this drive motor under "on" position.Motor reel 12 visible part in Fig. 1 is designed to cylindrical.The outer circumferential face of motor reel constitutes the raceway of rolling element 16.
As example, be provided with six rolling elements 16, they are designed to needle roller in the present embodiment.According to the present invention, rolling element 16 has the external diameter that varies in size., select rolling element 16 here along the circumferential layout of motor reel 16, make their external diameters separately from rolling element 16 beginnings with minimum outer diameter up to rolling element 16 with maximum outside diameter, increase continuously and reduce continuously again then.
All rolling elements 16 movably are maintained in the same retainer 14.Retainer 14 for example is made of the strip material elastic ring, processes the pocket hole that is used to keep rolling element 16 in this ring.Distance between the size in the diameter of this ring, pocket hole and the pocket hole is coordinated mutually with the external diameter of the external diameter of motor reel 12 and rolling element 16, makes all rolling elements 16 contact with motor reel 12 at periphery.Therefore, rolling element 16 is positioned on the same imaginary envelope circle center M of this envelope circle inevitably away from the peripheral part of motor reel
HCenter M with respect to motor reel 12
WBiasing.Two center M
HAnd M
WBetween distance determined the throw of eccentric E of driver element 10.
The support 18 of the sleeve shape that internal diameter is suitable with the envelope circular diameter surrounds rolling element 16.The outer circumferential face of this support is designed to support the plunger of radial plunger pump, and these plungers are driven by driver element 10 and do linear reciprocating motion.18 transmission of torque can realize by the connection of the friction motor reel 12, rolling element 16 and the support 18 or by the mechanical transmission mechanism between motor reel 12 and the support 18 from motor reel 12 to support.Fig. 2 shows a kind of structure of mechanical transmission mechanism.
According to Fig. 2, the part of motor reel 12 is along circumferentially having outer gearing portion 20.Be similarly the intermediate gear 20 and these outer gearing portion 20 engagements of outer gearing.Intermediate gear 22 is positioned on the axle identical with one of them rolling element 16.This rolling element 16 prolongs and integrally formed bearing journal 26 (Fig. 3), to form the supporting point of intermediate gear 22.Preferably, the rolling element 16 that has a bearing journal 26 is rolling elements 16 of external diameter maximum.Interior engaging piece 24 engagements that intermediate gear 22 and support 18 in sleeve shape form.
The outer gearing portion 20 of motor reel 12, intermediate gear 22 and the engaging piece 24 that is positioned on the support 18 constitute gear drive together, design the engagement data of this gear drive, make the diameter of rolling element 16 be equivalent to the pitch diameter of intermediate gear 22.Similarly, this pitch diameter of the external diameter of the internal diameter of support 18 and engine shaft 12 and intermediate gear 22 adapts.Therefore, avoided in the rotational motion process of driver element 10, taking place between the rolling element 16 unnecessary slip.
For the sake of completeness, Fig. 3 shows the longitudinal section of driver element 10 again, wherein, describes Fig. 1 and the used reference character of Fig. 2 and also continues on for Fig. 3.
As a supplement, from this view as seen, the outer gearing portion 20 of motor reel 12 is designed on end of motor reel.For this reason, motor reel 12 has an extension part 30, and outer gearing portion 20 is arranged on this extension part integratedly or is designed to be fixed on gear on this extension part 30 with relatively rotating.Intermediate gear 22 is rotatably supported on the bearing journal 26 of a rolling element 16.Support 18 driver element 10 axially on rolling element 16 overlap joints and directly be supported on the motor reel 12 whereby.
If this moment, motor reel was carried out the rotational motion of being forced by drive motor, this rotational motion is delivered to intermediate gear 22 from the outer gearing portion 20 of motor reel 12 so.So driven like this intermediate gear 22 drives support 18, therefore this support rotates relatively with the motor reel 12 that rotates.Because the gear drive that is provided with is designed to reduction gearing mechanism, motor reel 12 is with the rotational speed higher than support 18.Therefore, two parts are reciprocally carried out relative movement.
As described in the beginning, be integrated in eccentric 14,16, the reduction gearing mechanism in 18 also can be applicable in the brake device for car with anti-skidding control function the drive motor of the high speed rotating with less driving torque and corresponding small construction volume.
Certainly, under the condition that does not deviate from basic design of the present invention, can change or favourable improvement the present invention.
Claims (7)
1. driver element,
The radial plunger pump of hydraulic pressure installation that has the brake device for car of electronic anti-breaking control function especially for manipulation,
This driver element comprises: has the drive motor of motor reel (12) and at least one and is arranged on eccentric (14,16,18) on the described motor reel (12),
Wherein, described eccentric (14,16,18) is surrounded by the support (18) that is bearing on a plurality of roller supports (16) at periphery,
It is characterized in that described eccentric (14,16,18) has the mechanical transmission (16 that is used for described support (18); 20,22,24).
2. driver element as claimed in claim 1 is characterized in that, described mechanical transmission (20,22,24) has the driving mechanism that forms between described motor reel (12) and described support (18).
3. driver element as claimed in claim 2, it is characterized in that, described driving mechanism is a gear drive, and this gear drive comprises the outer gearing portion (20) that is positioned on the described live axle (12), the intermediate gear (22) that is positioned at the engaging piece (24) on the described support (18) and meshes with described engaging piece (24) and described outer gearing portion (20).
4. driver element as claimed in claim 3 is characterized in that, described intermediate gear (20) is arranged on the axle identical with one of them described rolling element (16).
5. as the driver element of claim 3 or 4, it is characterized in that described gear drive is designed to reduction gearing mechanism.
6. driver element as claimed in claim 1 is characterized in that, described mechanical transmission (16; 20,22,24) comprise the rolling element (16) with the external diameter that differs in size from one another, these rolling elements are bearing in described support (18) on the described motor reel (12).
7. as the driver element of claim 1 or 6, it is characterized in that described rolling element (16) is a needle roller.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102008055070.1 | 2008-12-22 | ||
| DE200810055070 DE102008055070A1 (en) | 2008-12-22 | 2008-12-22 | Drive unit for operation of radial piston pumps of hydraulic unit of electronically slip-adjustable brake system of motor vehicle, has drive motor with motor shaft and eccentric devices mounted on motor shaft |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101761463A true CN101761463A (en) | 2010-06-30 |
| CN101761463B CN101761463B (en) | 2015-07-08 |
Family
ID=42220600
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200910261507.1A Expired - Fee Related CN101761463B (en) | 2008-12-22 | 2009-12-18 | Drive unit |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP5641732B2 (en) |
| CN (1) | CN101761463B (en) |
| DE (1) | DE102008055070A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102010028584A1 (en) * | 2010-05-05 | 2011-11-10 | Robert Bosch Gmbh | eccentric |
| DE102010040889A1 (en) * | 2010-09-16 | 2012-03-22 | Robert Bosch Gmbh | pump unit |
| DE102014221515B4 (en) * | 2014-10-23 | 2021-12-09 | Robert Bosch Gmbh | ABS / ESP hydraulic unit and ABS / ESP system |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2999401A (en) * | 1958-11-28 | 1961-09-12 | Wheland Company | Drive for reciprocating power pumps and the like |
| DE2628840A1 (en) * | 1976-06-26 | 1978-01-05 | Dieter Brox | Reciprocating pump with no crank - has hollow piston element driven by eccentric disc rotated by internal planetary gearing |
| JPH0712049A (en) * | 1993-06-24 | 1995-01-17 | Maruyama Mfg Co Ltd | Driving transmitting device for reciprocating pump |
| CN1145657A (en) * | 1995-02-03 | 1997-03-19 | 罗伯特·博施有限公司 | Reciprocating pump |
| DE102006035055A1 (en) * | 2006-07-28 | 2008-01-31 | Robert Bosch Gmbh | Sealing and guiding unit for piston, has guide bush for guiding piston, and pretensioning unit arranged outside internal sealing region of sealing unit and bearing radially directed force on internal sealing region |
-
2008
- 2008-12-22 DE DE200810055070 patent/DE102008055070A1/en active Pending
-
2009
- 2009-12-18 CN CN200910261507.1A patent/CN101761463B/en not_active Expired - Fee Related
- 2009-12-22 JP JP2009290136A patent/JP5641732B2/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2999401A (en) * | 1958-11-28 | 1961-09-12 | Wheland Company | Drive for reciprocating power pumps and the like |
| DE2628840A1 (en) * | 1976-06-26 | 1978-01-05 | Dieter Brox | Reciprocating pump with no crank - has hollow piston element driven by eccentric disc rotated by internal planetary gearing |
| JPH0712049A (en) * | 1993-06-24 | 1995-01-17 | Maruyama Mfg Co Ltd | Driving transmitting device for reciprocating pump |
| CN1145657A (en) * | 1995-02-03 | 1997-03-19 | 罗伯特·博施有限公司 | Reciprocating pump |
| DE102006035055A1 (en) * | 2006-07-28 | 2008-01-31 | Robert Bosch Gmbh | Sealing and guiding unit for piston, has guide bush for guiding piston, and pretensioning unit arranged outside internal sealing region of sealing unit and bearing radially directed force on internal sealing region |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102008055070A1 (en) | 2010-07-01 |
| CN101761463B (en) | 2015-07-08 |
| JP2010143576A (en) | 2010-07-01 |
| JP5641732B2 (en) | 2014-12-17 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20150708 |
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| CF01 | Termination of patent right due to non-payment of annual fee |