WO1997005393A1 - Peripheralpumpe, insbesondere zum fördern von kraftstoff aus einem vorratstank zur brennkraftmaschine eines kraftfahrzeuges - Google Patents
Peripheralpumpe, insbesondere zum fördern von kraftstoff aus einem vorratstank zur brennkraftmaschine eines kraftfahrzeuges Download PDFInfo
- Publication number
- WO1997005393A1 WO1997005393A1 PCT/DE1996/000919 DE9600919W WO9705393A1 WO 1997005393 A1 WO1997005393 A1 WO 1997005393A1 DE 9600919 W DE9600919 W DE 9600919W WO 9705393 A1 WO9705393 A1 WO 9705393A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- peripheral pump
- pressure
- channel
- pump according
- impeller
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D5/00—Pumps with circumferential or transverse flow
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D5/00—Pumps with circumferential or transverse flow
- F04D5/002—Regenerative pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/041—Axial thrust balancing
- F04D29/0416—Axial thrust balancing balancing pistons
Definitions
- Peripheral pump in particular for delivering fuel from a storage tank to the internal combustion engine of a motor vehicle
- the invention relates to a peripheral pump according to the features of the preamble of patent claim 1.
- a peripheral pump which comprises a circular cylindrical impeller rotating in a pump chamber, which has at least one of its two end faces a ring of vanes spaced apart in the circumferential direction of the impeller and seen in longitudinal section through the pump one Because of the groove-like gap between two adjacent vanes forms a circular section, the center of which is almost identical to the center of another circular section, which is formed by the bottom of an annular delivery channel, which is arranged opposite the wing rim in each wall of the pump chamber.
- peripheral pumps already show after a relatively short operating time that the impeller is subject to considerable wear, which is due to an axial force building up in the peripheral pump, which acts on the impeller and, in particular, against an impeller wall on the intake side of an intake cover. Furthermore, such a peripheral pump has poor starting behavior. In addition, the axial force building up in the fuel delivery unit leads to poor noise behavior.
- the peripheral pump according to the invention with the characterizing features of the main claim has the advantage that a pressure force counteracting the axial force can be formed in the pressure area on the impeller, so that the sum of the axial forces acting on the impeller is almost zero. This allows the impeller to rotate freely in the pump chamber, so that an almost wear-free rotation between the impeller and the walls forming the pump chamber is made possible, whereby the noise behavior can also be significantly improved.
- the operating pressure prevailing in the pressure range can be determined by changing the angle between a connecting channel and the suction opening of the delivery channel. With increasing angle or increasing distance, a higher pressure builds up in the conveying channel, which at the end of the conveying channel at the outlet opening can be up to 3 bar, for example.
- the connecting channel By arranging the connecting channel at a certain angle between the suction opening and the outlet opening, the pressure which is transferred to and prevails in the pressure region and which counteracts the axial force acting on the impeller can be adjustable.
- Fig. 1 is a fuel delivery unit with a
- FIG. 2 shows a schematic sectional illustration along the line II-II in FIG. 1 and
- FIG. 3 shows a schematic sectional illustration along the line III-III in FIG. 1.
- a unit 10 shown in FIG. 1 is used to convey fuel from a storage tank (not shown) to the fuel machine (also not shown) Motor vehicles.
- the fuel delivery unit 10 has a flow pump 11, the impeller 12 of which is connected in a rotationally locking manner by a shaft 13 driven by an electric drive motor (not shown).
- the shaft 13 penetrates the impeller 12 and bears on a bearing pin 14 which is arranged on a suction cover 16.
- the suction cover 16 closes off the fuel delivery unit 10 on its end face on the suction side.
- the impeller 12 is arranged in a pump chamber 17 which, viewed in the longitudinal direction of the impeller 12, is delimited on both sides by walls 18 and 19.
- the wall 18 is formed by the surface of the suction cover 16 facing the impeller 12.
- An intermediate housing 21 opposite the suction cover 16 has the second wall 19 forming the pump chamber 17.
- the wall 19 has a bearing 22 for the shaft 13.
- the flow pump 11 draws fuel through an intake port 26 and presses this medium via a pump outlet 28 in the intermediate housing 21 into a space 29 in which the electric motor (not shown) is accommodated. From there, the fuel is supplied to the internal combustion engine via an outlet or pressure connection 31. Since both the flow pump 11 and the electric motor (not shown) are housed in a common housing 32, which is provided with a suction port 26 and an outlet port 31, and the fuel thus flows through the fuel delivery unit 10, the fuel delivery unit 10 forms part of the delivery line from, as it were Storage tank for the internal combustion engine.
- the impeller 12 of the flow pump 11 has a disk-shaped, central region 34 which is connected directly to the shaft 13, it being possible advantageously to provide a central bearing bush.
- the impeller 12 or its central region 34 has a plurality of radial ones Wings that are connected to each other at their free ends facing away from the central area 34 by a circumferential ring 36, which is not absolutely necessary.
- the blades ⁇ are formed by the fact that 12 webs remain between openings on the impeller which are arranged on a common pitch circle and limit the openings in the circumferential direction.
- the axis of each opening runs parallel to the axis of rotation of the impeller 12.
- the bottom of the groove between the blades is advantageously formed by two circular sections 37, 38 which merge into one another in the central region of the impeller 12 without jolts.
- a circular ring-shaped feed channel 41, 42 is arranged in the chamber walls 18, 19, a circular ring-shaped feed channel 41, 42 is arranged.
- the bottom 43 of the conveying channel 41, 42 is also shaped in the form of a circular section.
- the circular section 37 in the circular section of the conveying channel 41 and the circular section 38 in the circular section of the conveying channel 42 advantageously merge smoothly into one another by being formed by a common center with the same radius.
- FIG. 2 shows a schematic sectional illustration along the line II-II on the suction-side wall 18 of the suction cover 16.
- the conveyor channel 41 is designed as a circular ring section which spans an angle of approximately 270 ° to 340 °.
- the beginning of the conveying channel 41 which in the embodiment is shown in a 6 o'clock position and is opposite an intake opening 46 of the intake port 26, extends in the counterclockwise direction to approximately an 8 o'clock position. With increasing progression from the 6 o'clock position to the approximately 8 o'clock position, there is a constant pressure build-up in the delivery channel 41, which at the end of the delivery channel 41 is in a range of approximately 3 bar. With this pressure, the medium is supplied to the space 29 via an outlet opening 47.
- the pressure region 34 is essentially circular as a pressure surface 48, which is designed as a depression in the wall 18. This pressure surface 48 extends radially advantageously over the largest possible area that is delimited by the conveying channel 41.
- a connection channel 49 is provided between the pressure surface 48 and the conveying channel 41, which is designed to run radially between the conveying channel 41 and the pressure surface 48.
- the connecting channel 49 is arranged approximately in a 9 o'clock position, which corresponds to an angle ⁇ of 270 °, as a result of which the pressure of the delivery channel 41 prevailing in the 9 o'clock position is transferred to the pressure surface 48 and thus to the impeller 12 acting axial force is determinable.
- the connecting channel 49 can also be arranged in a different position between the suction opening 46 and the outlet opening 47, an angle ⁇ between 180 ° and 300 ° preferably being provided. The positioning can be selected depending on the size of the peripheral pump, the delivery line of the flow pump, the electric motor or the like.
- the cross-section of the connecting duct 49 has a cross section that is so large that a flow cross section required for the pressure build-up in the pressure region 34 is created.
- FIG. 3 shows a top view of the wall 19 of the intermediate housing 21 along the line III-III in FIG. 1.
- the conveying channel 42 corresponds to the conveying channel 41.
- the medium to be conveyed flows in and runs clockwise to the exit opening 47, via which the medium is discharged into the space 29.
- the pressure in the delivery channel 42 builds up in a clockwise direction.
- a connecting channel 51 extends radially from the delivery channel 42 inwards and communicates with a pressure area 35. This pressure area is arranged essentially opposite the pressure area 34.
- the connecting duct 51 is advantageously arranged at the same angle as the connecting duct 49 in the intake cover 16. In this way, the same force relationships can be created on the impeller 12.
- the pressure area 35 of the intermediate housing 21 is cylindrical and has a diameter D1, which essentially corresponds to the cylindrical section 53 of the suction cover 16, which is deep compared to the pressure area 34.
- the pressure region 34 includes both the cylindrical section 52 and the disk-shaped pressure surface 48, which extends over the impeller 12 over a relatively large circular area and can transmit a uniform surface force to the impeller 12.
- the pressure area 34 is advantageously large, so that due to the positioning of the connection channel 49, 51 to the suction opening 46 at an angle ⁇ , the pressure prevailing in the pressure area 34, 35 can be adjusted.
- the connecting channels 49, 51 can be optimally arranged at an angle ⁇ to the suction opening 46 in a simple measurement or empirical manner.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1019970701765A KR970706457A (ko) | 1995-08-01 | 1996-05-28 | 원주류식 펌프(Peripheral pump) |
EP96919586A EP0783632A1 (de) | 1995-08-01 | 1996-05-28 | Peripheralpumpe, insbesondere zum fördern von kraftstoff aus einem vorratstank zur brennkraftmaschine eines kraftfahrzeuges |
JP9507065A JPH10507244A (ja) | 1995-08-01 | 1996-05-28 | 円周流式ポンプ、特に、燃料を自動車の蓄えタンクから内燃機関に圧送する円周流式ポンプ |
US08/804,943 US5980200A (en) | 1995-08-01 | 1996-05-28 | Peripheral pump, in particular for feeding fuel from feed tank to internal combustion engine of motor vehicle |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19528181.0 | 1995-08-01 | ||
DE19528181A DE19528181A1 (de) | 1995-08-01 | 1995-08-01 | Peripheralpumpe, insbesondere zum Fördern von Kraftstoff aus einem Vorratstank zur Brennkraftmaschine eines Kraftfahrzeuges |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1997005393A1 true WO1997005393A1 (de) | 1997-02-13 |
Family
ID=7768377
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE1996/000919 WO1997005393A1 (de) | 1995-08-01 | 1996-05-28 | Peripheralpumpe, insbesondere zum fördern von kraftstoff aus einem vorratstank zur brennkraftmaschine eines kraftfahrzeuges |
Country Status (7)
Country | Link |
---|---|
US (1) | US5980200A (de) |
EP (1) | EP0783632A1 (de) |
JP (1) | JPH10507244A (de) |
KR (1) | KR970706457A (de) |
CN (1) | CN1083946C (de) |
DE (1) | DE19528181A1 (de) |
WO (1) | WO1997005393A1 (de) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6019570A (en) * | 1998-01-06 | 2000-02-01 | Walbro Corporation | Pressure balanced fuel pump impeller |
CN100392251C (zh) * | 2004-07-05 | 2008-06-04 | 薛肇江 | 电动燃油双槽叶轮泵 |
KR101177293B1 (ko) * | 2011-04-05 | 2012-08-30 | 주식회사 코아비스 | 자동차용 터빈형 연료펌프 |
CN102758797A (zh) * | 2012-07-11 | 2012-10-31 | 孙立生 | 一种电动燃油泵 |
DE102012222336B4 (de) | 2012-12-05 | 2018-02-08 | Continental Automotive Gmbh | Strömungsmaschine |
DE102016207598A1 (de) | 2016-05-03 | 2017-11-09 | Robert Bosch Gmbh | Förderaggregat |
DE102016207595A1 (de) | 2016-05-03 | 2017-11-09 | Robert Bosch Gmbh | Förderaggregat |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3118533A1 (de) * | 1981-05-09 | 1982-12-02 | Robert Bosch Gmbh, 7000 Stuttgart | Aggregat zum foerdern von fluessigkeiten |
DE3118534A1 (de) * | 1981-05-09 | 1983-02-24 | Robert Bosch Gmbh, 7000 Stuttgart | Pumpe zum foerdern von kraftstoff aus einem vorratstank zu einer brennkraftmaschine |
DE3226325A1 (de) * | 1981-08-11 | 1983-03-03 | Nippondenso Co., Ltd., Kariya, Aichi | Elektrische kraftstoffpumpe |
JPS58197495A (ja) * | 1982-05-13 | 1983-11-17 | Nippon Denso Co Ltd | ポンプ装置 |
WO1993006372A1 (en) * | 1991-09-27 | 1993-04-01 | Foras Pumps S.R.L. | Improved pump casing for centrifugal pump and method for producing said casing |
DE9218042U1 (de) * | 1992-12-19 | 1993-06-09 | Pierburg GmbH, 4040 Neuss | Brennstoffpumpe |
DE4243544A1 (de) * | 1992-12-22 | 1994-06-23 | Bosch Gmbh Robert | Kraftstofförderpumpe |
DE4341563A1 (de) * | 1993-12-07 | 1995-06-08 | Bosch Gmbh Robert | Aggregat zum Fördern von Kraftstoff aus einem Vorratstank zur Brennkraftmaschine eines Kraftfahrzeuges |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4692092A (en) * | 1983-11-25 | 1987-09-08 | Nippondenso Co., Ltd. | Fuel pump apparatus for internal combustion engine |
DE3424520C2 (de) * | 1984-07-04 | 1986-07-10 | SWF Auto-Electric GmbH, 7120 Bietigheim-Bissingen | Kraftstofförderpumpe |
US4844621A (en) * | 1985-08-10 | 1989-07-04 | Nippondenso Co., Ltd. | Fuel pump with passage for attenuating noise generated by impeller |
CN2068609U (zh) * | 1990-03-19 | 1991-01-02 | 陆守余 | 液环式氯气泵 |
KR960001631B1 (ko) * | 1991-05-14 | 1996-02-03 | 미쓰비시덴키가부시키가이샤 | 원주류식(圓周流式) 액체펌프 |
-
1995
- 1995-08-01 DE DE19528181A patent/DE19528181A1/de not_active Withdrawn
-
1996
- 1996-05-28 US US08/804,943 patent/US5980200A/en not_active Expired - Fee Related
- 1996-05-28 WO PCT/DE1996/000919 patent/WO1997005393A1/de not_active Application Discontinuation
- 1996-05-28 EP EP96919586A patent/EP0783632A1/de not_active Withdrawn
- 1996-05-28 JP JP9507065A patent/JPH10507244A/ja active Pending
- 1996-05-28 KR KR1019970701765A patent/KR970706457A/ko not_active Application Discontinuation
- 1996-05-28 CN CN96190849A patent/CN1083946C/zh not_active Expired - Fee Related
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3118533A1 (de) * | 1981-05-09 | 1982-12-02 | Robert Bosch Gmbh, 7000 Stuttgart | Aggregat zum foerdern von fluessigkeiten |
DE3118534A1 (de) * | 1981-05-09 | 1983-02-24 | Robert Bosch Gmbh, 7000 Stuttgart | Pumpe zum foerdern von kraftstoff aus einem vorratstank zu einer brennkraftmaschine |
DE3226325A1 (de) * | 1981-08-11 | 1983-03-03 | Nippondenso Co., Ltd., Kariya, Aichi | Elektrische kraftstoffpumpe |
JPS58197495A (ja) * | 1982-05-13 | 1983-11-17 | Nippon Denso Co Ltd | ポンプ装置 |
WO1993006372A1 (en) * | 1991-09-27 | 1993-04-01 | Foras Pumps S.R.L. | Improved pump casing for centrifugal pump and method for producing said casing |
DE9218042U1 (de) * | 1992-12-19 | 1993-06-09 | Pierburg GmbH, 4040 Neuss | Brennstoffpumpe |
DE4243544A1 (de) * | 1992-12-22 | 1994-06-23 | Bosch Gmbh Robert | Kraftstofförderpumpe |
DE4341563A1 (de) * | 1993-12-07 | 1995-06-08 | Bosch Gmbh Robert | Aggregat zum Fördern von Kraftstoff aus einem Vorratstank zur Brennkraftmaschine eines Kraftfahrzeuges |
Non-Patent Citations (1)
Title |
---|
PATENT ABSTRACTS OF JAPAN vol. 008, no. 043 (M - 279) 24 February 1984 (1984-02-24) * |
Also Published As
Publication number | Publication date |
---|---|
CN1083946C (zh) | 2002-05-01 |
US5980200A (en) | 1999-11-09 |
EP0783632A1 (de) | 1997-07-16 |
JPH10507244A (ja) | 1998-07-14 |
DE19528181A1 (de) | 1997-02-06 |
CN1161078A (zh) | 1997-10-01 |
KR970706457A (ko) | 1997-11-03 |
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