GB2486532A - Drive unit of pump with integrated seal - Google Patents
Drive unit of pump with integrated seal Download PDFInfo
- Publication number
- GB2486532A GB2486532A GB1120607.5A GB201120607A GB2486532A GB 2486532 A GB2486532 A GB 2486532A GB 201120607 A GB201120607 A GB 201120607A GB 2486532 A GB2486532 A GB 2486532A
- Authority
- GB
- United Kingdom
- Prior art keywords
- roller
- drive unit
- saddle
- pressure pump
- pressure
- 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.)
- Withdrawn
Links
- 238000007789 sealing Methods 0.000 claims abstract description 63
- 230000005540 biological transmission Effects 0.000 claims abstract description 24
- 239000000463 material Substances 0.000 claims abstract description 5
- 229920003023 plastic Polymers 0.000 claims abstract description 5
- 239000004033 plastic Substances 0.000 claims abstract description 5
- 238000001746 injection moulding Methods 0.000 abstract description 4
- 238000004519 manufacturing process Methods 0.000 description 11
- 238000010276 construction Methods 0.000 description 4
- 239000012530 fluid Substances 0.000 description 3
- 230000033001 locomotion Effects 0.000 description 3
- 238000005096 rolling process Methods 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000002950 deficient Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
- 238000009827 uniform distribution Methods 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
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0448—Sealing means, e.g. for shafts or housings
-
- 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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details Of Reciprocating Pumps (AREA)
- Valves And Accessory Devices For Braking Systems (AREA)
- Regulating Braking Force (AREA)
Abstract
A drive unit 10 for a high-pressure pump comprising a cylindrical roller saddle 12 made of plastics material and a roller 16, which is accommodated in a recess 14 of the roller saddle and interacts with a transmission element 18, where the roller saddle has an integrated high-pressure sealing ring 20. Preferably the sealing ring is a circumferential sealing lip and disposed on an opposite end face of the roller saddle to the recess, where the sealing lip may be flush with the end face of the saddle or projecting. The roller may be clipped or inserted into the recess, the saddle may be formed by injection moulding and the transmission element may be a cam or eccentric. A high pressure pump that can be used in ESP or ABS of a vehicle is also claimed.
Description
Drive unit for a highpressure pump and hiQh-pressure pump
Background art
The invention proceeds from a drive unit for a high-pressure pump according to the preamble of the independent claim 1 and from a high-pressure pump having such a drive unit according to the preamble of the independent claim 9.
High-pressure pumps of various designs are known from the background art. In vehicles high-pressure pumps are frequently used to feed fluids within hydraulic systems. Typically such high-pressure pumps comprise a piston bore formed in a piston housing, a piston element that interacts via a drive unit with a transmission means, and at least one sealing element disposed between the piston element and the transmission means. In this case, the fitted sealing element prevents fluid from flowing from a discharge end back into an interior of the high-pressure pump. The piston housing generally takes the form of a cylinder.
From DE-OS 10 2005 025 869 Al for example such a drive unit for a high-pressure pump is known. The drive unit comprises a guide element, which is configured as a roller saddle and guided in a piston bore, and a rolling body, which is configured as a roller and supported in the guide element. The rolling body is situated in direct contact with the transmission means and the piston element. Provided in the drive unit, between the guide element and an inner wall of the piston bore, is a radially disposed sealing ring that functions as a seal between the piston element and the transmission means.
DE-OS 102 42 116 B3 describes a further drive unit for a high-pressure pump. This drive unit for a high-pressure pump comprises a shaft, which is connected to a transmission means, and a roller, which is disposed between the transmission means and a piston element and held by means of a retaining sleeve in a recess of the piston element. As a result of this arrangement the roller is situated in direct contact with the\ transmission means and the piston element.
Disclosure of the invention
In contrast, the drive unit according to the invention for a high-pressure pump having the features of the independent claim 1 has the advantage that the roller saddle has an integrated high-pressure sealing ring. The high-pressure sealing ring is advantageously an integral component of the roller saddle and hence is formed integrally with the roller saddle. The high-pressure sealing ring according to the invention is situated always in the correct position and owing to its broad base connection has a particularly high load capability. As the high-pressure sealing ring is capable of elastic deformation and ideally may be applied both radially and axially against adjacent components, reliable operation is permanently guaranteed even in the overpressure range of the high-pressure pump. The high-pressure sealing ring lies for example against the inner wall of the piston bore and is pressed under the action of pressure against the inner wall and hence fulfils the desired sealing function. For this reason, in the high-pressure pump the region of the piston element and the region of the transmission means are advantageously effectively separable from one another even in the event of very high pressures, thereby resulting in high endurance and/or a long useful life for the high-pressure pump. Because according to the invention the high-pressure sealing ring is formed integrally with the roller saddle, there is no longer any need to manufacture a separate sealing ring and then press it into the roller saddle.
The structure and manufacture of the roller saddle are accordingly simplified because the manufacture of a sealing ring and the introduction thereof into the roller saddle no longer apply. This advantageously enables an economical manufacture of the roller saddle according to the invention, wherein in particular the assembly of the components of a high-pressure pump may be realized more easily.
By virtue of the measures and developments outlined in the dependent claims, advantageous improvements of the drive unit indicated in the independent claim I for a high-pressure pump and of the high-pressure pump indicated in the independent claim 9 are possible.
In an advantageous form of the invention the high-pressure sealing ring is provided on an opposite end face of the roller saddle to the recess. In an advantageous manner the simple form of an integral high-pressure sealing ring enables effective sealing in a radial and/or axial direction against adjacent components. This advantageously S prolongs the useful life of the high-pressure sealing ring according to the invention, with the result that the maintenance intervals of the high-pressure pump are also lengthened and/or the down times of the high-pressure pump as a result of defective sealing rings are entirely eliminated. A further result is easy and economical manufacture of the roller saddle according to the invention. In an advantageous manner a symmetrical structure of the roller saddle leads to a uniform take-up and transfer of the effective forces. There is moreover no longer any need for laborious checking of the correct positioning of the sealing ring in the high-pressure pump and incorrect assembly is reliably avoided. Thus, in an advantageous manner the manufacture and assembly of the high-pressure sealing ring may be carried out in a particularly economical manner.
In a further advantageous form of the invention the high-pressure sealing ring is configured as a circumferential sealing lip. Such a sealing lip has the advantage of being very flexible in its tapering edge region and hence of being already expandable at low pressure. In this case, the diameter of the sealing lip increases under pressure loading and the sealing lip is pressed against the inner wall of the piston bore, with the result that the desired sealing function is fulfilled. In the present embodiment the sealing lip of the roller saddle in a marginal zone of the end face of the roller saddle is preferably configured as a thin deformable ring, wherein however other shapes and regions on the roller saddle that are deemed meaningful by a person skilled in the art are conceivable for the integration and/or moulding-on of the high-pressure sealing ring.
In a preferred manner the circumferential sealing lip terminates flush with the end face of the roller saddle. In alternative embodiments, however, the sealing lip may be configured so as to project and/or be recessed in relation to the end face. The sealing lip of the roller saddle owing to its deformability and its structure advantageously fulfils the function of a sealing means, both in radial and in axial direction of the high-pressure pump. The sealing lip is therefore able to adapt very well to the adjacent components.
This form of the sealing lip in a particularly advantageous manner simplifies the manufacture of the roller saddle because the tool is of a very simple construction and hence economical.
In a further advantageous form of the invention the roller saddle is configured in such a way that the roller may be clipped and/or inserted into the recess. Given a symmetrical connection, the result is advantageously not only a uniform load transmission but also a good positional stability of the roller in the roller saddle. Of particular advantage here is the positive connection of the roller to the roller saddle that therefore enables a tilt-resistant rotatable bearing arrangement and a mounting of the roller in the roller saddle that saves installation space. By virtue of the compact style of construction a reliable connection and functioning of the drive unit is guaranteed. What is more, an axially effective force may be transmitted directly. Clipping of the roller into the roller saddle moreover enables rapid and easy assembly while dispensing with additional fastening means.
It is further proposed that the recess of the roller saddle is configured in such a way that it receives the roller with an angle of wrap a of at least 180° in relation to the cross section of the roller. This advantageously results in a large-area positive connection between the roller and the roller saddle, in which connection the roller saddle is supported in a stable manner. This guarantees reliable functioning during operation of the high-pressure pump.
The roller saddle preferably takes the form of an injection-moulded part. This method advantageously allows cost-effective large-scale precision manufacture of the roller saddle as a directly usable injection-moulded part within a short time. In particular, the injection-moulding method allows components to be manufactured with different wall thicknesses and/or from different plastics materials in order to produce components with application-specific properties. Furthermore, because of the high accuracy of manufacture of the roller saddle using the injection-moulding method, excellent guidance of the roller saddle in the piston bore is possible, with the result that the integral high-pressure sealing ring that is moulded on with positional accuracy fulfils its sealing function always in a reliable and trouble-free manner.
It is further proposed that the transmission means takes the form of a cam and/or eccentric. Because of the particularly advantageous structural arrangement of the components of the drive unit for a high-pressure pump, besides an eccentric as a transmission means use of an alternative transmission means, such as for example a cam, as a drive is also possible. By means of a cam differing speeds of motion of the high-pressure pump may be realized in an advantageous manner. This advantageous use of the cam may help to improve the efficiency of the high-pressure pump and to reduce the friction at the high-pressure sealing ring.
According to the invention a high-pressure pump for a vehicJe comprises such a drive unit. Embodiments of the high-pressure pump according to the invention are used for example in safety systems, such as for example an electronic stability program (ESP) or an antilock braking system (ABS) of vehicles. An important advantage of the drive unit for the high-pressure pump is that even under particularly high loading it presents reduced wear and functions in a particularly reliable manner. As a result of the compact style of construction this high-pressure pump is therefore ideally suited for use in hydraulic systems that are subject to extreme stress and for implementing various safety functions in the vehicle, such as for example (ESP) or (ABS).
Advantageous embodiments of the invention are represented in the drawings and described below. In the drawings identical reference characters denote components and/or elements that perform identical and/or analogous functions.
Brief description of the drawings
Fig. I shows a diagrammatic sectional view of a detail of an embodiment of a drive unit according to the invention for a high-pressure pump, comprising a roller saddle and a roller, which is accommodated in the roller saddle and interacts with a transmission means, wherein a high-pressure sealing ring is integrated into the roller saddle.
Fig. 2 shows a perspective view of the drive unit of Fig. I with the roller saddle, which accommodates the roller and has the integrated high-pressure sealing ring, wherein the roller is clipped into a recess of the roller saddle.
S Fig. 3 shows a perspective sectional view of the roller saddle with the recess for the roller and with the high-pressure sealing ring configured as a circumferential sealing lip.
Fig. 1 shows a detail of an embodiment of a drive unit 10 according to the invention for a high-pressure pump, which is driven by means of a drive, for example an electric motor1 which is not represented here. In the present embodiment the high-pressure pump is provided for a vehicle, which is not represented here. In particular an application of the drive unit 10 preferably in a high-pressure pump for motor scooters and/or motorcycles is provided. Such high-pressure pumps are used for example in hydraulic systems for safety technologies in a vehicle, such as an antilock braking system (ABS), an electronic stability program (ESP), an electrohydraulic brake (EHB), a traction control system (TCS) and/or acceleration spin regulation (ASR).
The drive unit 10 comprises a cylindrical roller saddle 12 made of plastics material and a roller 16, which is accommodated in a recess 14 of the roller saddle 12 and interacts with a transmission means 18. The transmission means 18 in the present case may take the form of a cam and/or eccentric.
In order to guarantee ease of manufacture combined with an optimum sealing function of the roller saddle 12 in the drive unit 10 for the high-pressure pump, according to the invention the roller saddle 12 has an integrated high-pressure sealing ring 20.
As may be seen in Figs. 1 to 3, the high-pressure sealing ring 20 is disposed on an opposite end face 22 of the roller saddle 12 to the recess 14. According to the invention the high-pressure sealing ring 20 takes the form of an element that is moulded onto the roller saddle 12 and in the present example seals off a piston element 26, which is guided in a piston bore 32, from the transmission means 18. This means that the integral high-pressure sealing ring 20 in the present embodiment effectively seals off the region of the piston element 26 and the region of the transmission means 18 from one another in axial direction 32 and hence ensures trouble-free operation of the high-pressure pump.
The high-pressure sealing ring 20 in the present embodiment is configured as a circumferential sealing lip. The sealing lip 20 in axial direction 32 is preferably flush with a lateral surface 30 of the roller saddle 12, wherein adjoining the sealing lip 20 in radial direction 34 is a groove 24 that is designed to be open in the direction of the piston element 26. The sealing lip 20 in the illustrated embodiment advantageously terminates flush with the end face 22 of the roller saddle 12. However, in alternative embodiments that are not represented, the sealing lip 20 may be configured so as to project and/or be recessed in relation to the end face 22. The sealing lip 20 is preferably of a flexible configuration and in the event of a pressure variation changes its diameter and/or in the event of pressure loading increases its diameter up to the adjacent wall of the piston bore 32. During the build-up of the pressure there is a uniform distribution of the pressure load upon the roller saddle 12 and hence upon the sealing lip 20 of the roller saddle 12. This occurs during the compression phase of the high-pressure pump, wherein the entire area of the groove 24 of the roller saddle 12 is loaded with pressure, as is the sealing lip too, which is pressed in radial direction 34 against the wall of the piston bore 28, thereby effectively preventing the fluid from flowing from a discharge end back into an interior of the high-pressure pump.
In the present embodiment the roller saddle 12 is configured in such a way that the roller 16 may be clipped and/or inserted into the recess 14. The roller saddle 12 therefore forms for the roller 16 an open journal bearing, in which the roller 16 is rotatably coupled and/or accommodated. Both components 12, 16 are guided jointly as a unit in the piston bore 28 and necessarily together exert the lifting motions initiated by the transmission means 18.
A further optimization of the connection of the roller saddle 12 to the roller 16 is shown in Figs. I and 2, wherein the recess 14 of the roller saddle 12 is configured in such a way that it accommodates the roller 16 with an angle of wrap a of at least 180° in relation to the cross section of the roller 16. This form enables an adequate positive connection between roller saddle 12 and roller 16. and hence a secure bearing arrangement of the roller 16 in the roller saddle 12.
In an advantageous manner the roller saddle 12 according to the invention is S constructed from plastics material in the form of an injection-moulded part and may therefore be manufactured particularly easily and precisely. In particular, the manufacture of the roller saddle 12 in an injection moulding method enables a particularly advantageous construction of the roller saddle 12 as a partner in a clip-type connection to the roller 16.
As already mentioned, the transmission means 18 of the drive unit 10 for the high-pressure pump may take the form of a cam and/or eccentric. In the present embodiment in a preferred manner eccentrics 18 are used. Given the use of cams 18 as a transmission means 18 in high-pressure pumps differing speeds of motion may be realized, with the result that the efficiency and the frictional properties of a high-pressure pump may be further improved.
Claims (12)
- Claims 1. Drive unit for a high-pressure pump comprising a cylindrical roller saddle (12) made of plastics material and a roller (16), which is accommodated in a recess (14) of the roller saddle (12) and interacts with a transmission means (18), characterized in that the roller saddle (12) has an integrated high-pressure sealing ring (20).
- 2. Drive unit according to claim 1, characterized in that the high-pressure sealing ring (20) is disposed on an opposite end face (22) of the roller saddle (12) to the recess (14).
- 3. Drive unit according to claim 1 or 2, characterized in that the high-pressure sealing ring (20) is configured as a circumferential sealing lip.
- 4. Drive unit according to one of claims 1 to 3, characterized in that the circumferential sealing lip (20) terminates flush and/or in a projecting and/or recessed manner with the end face (22) of the roller saddle (12).
- 5. Drive unit according to one of claims 1 to 4, characterized in that the roller saddle (12) is configured in such a way that the roller (16) may be clipped and/or inserted into the recess (14).
- 6. Drive unit according to one of claims I to 5, characterized in that the recess (14) of the roller saddle (12) is configured in such a way that it accommodates the roller (16) with an angle of wrap (a) of at least 180° in relation to the cross section of the roller (16).
- 7. Drive unit according to one of claims 1 to 6, characterized in that the roller saddle (12) takes the form of an injection-moulded part.
- 8. Drive unit according to one of claims 1 to 7, characterized in that the transmission means (18) takes the form of a cam and/or eccentric.
- 9. High-pressure pump for a vehicle, characterized by a drive unit (10) according to one of claims 1 to 8.
- 10. High-pressure pump according to claim 9, characterized by a use in a safety system (ESP, ABS) of the vehide.
- 11. Drive unit for a high-pressure pump, substantially as hereinbefore described with reference to the accompanying drawings.
- 12. High-pressure pump substantially as hereinbefore described with reference to the accompanying drawings.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102010063317A DE102010063317A1 (en) | 2010-12-17 | 2010-12-17 | Drive unit for a high pressure pump and high pressure pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| GB201120607D0 GB201120607D0 (en) | 2012-01-11 |
| GB2486532A true GB2486532A (en) | 2012-06-20 |
Family
ID=45508951
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB1120607.5A Withdrawn GB2486532A (en) | 2010-12-17 | 2011-11-29 | Drive unit of pump with integrated seal |
Country Status (3)
| Country | Link |
|---|---|
| DE (1) | DE102010063317A1 (en) |
| FR (1) | FR2969225A1 (en) |
| GB (1) | GB2486532A (en) |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0462927A1 (en) * | 1990-06-18 | 1991-12-27 | Maschinenfabrik Sulzer-Burckhardt AG | Piston compressor for an oilfree gas compression |
| DE102004027506A1 (en) * | 2004-06-04 | 2005-12-22 | Robert Bosch Gmbh | Piston pump with spherical piston |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10242116B3 (en) | 2002-09-11 | 2004-04-29 | Robert Bosch Gmbh | Drive device for a pump element, especially for hydraulic units in motor vehicle braking systems, comprises a driven shaft, an eccentric element connected to the shaft, and a roll element |
| DE102005025869B4 (en) | 2005-06-06 | 2017-04-06 | Robert Bosch Gmbh | Low noise piston pump |
-
2010
- 2010-12-17 DE DE102010063317A patent/DE102010063317A1/en not_active Ceased
-
2011
- 2011-11-29 GB GB1120607.5A patent/GB2486532A/en not_active Withdrawn
- 2011-12-15 FR FR1103852A patent/FR2969225A1/en not_active Withdrawn
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0462927A1 (en) * | 1990-06-18 | 1991-12-27 | Maschinenfabrik Sulzer-Burckhardt AG | Piston compressor for an oilfree gas compression |
| DE102004027506A1 (en) * | 2004-06-04 | 2005-12-22 | Robert Bosch Gmbh | Piston pump with spherical piston |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102010063317A1 (en) | 2012-06-21 |
| GB201120607D0 (en) | 2012-01-11 |
| FR2969225A1 (en) | 2012-06-22 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| WAP | Application withdrawn, taken to be withdrawn or refused ** after publication under section 16(1) |