CN102753826B - Pump-unit - Google Patents
Pump-unit Download PDFInfo
- Publication number
- CN102753826B CN102753826B CN201080063197.3A CN201080063197A CN102753826B CN 102753826 B CN102753826 B CN 102753826B CN 201080063197 A CN201080063197 A CN 201080063197A CN 102753826 B CN102753826 B CN 102753826B
- Authority
- CN
- China
- Prior art keywords
- pump
- gear
- face
- pump shaft
- shaft
- 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.)
- Expired - Fee Related
Links
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
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/08—Combinations of two or more pumps the pumps being of different types
- F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
- F04B23/103—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type being a radial piston pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
- F02M39/005—Arrangements of fuel feed-pumps with respect to fuel injection apparatus
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
- F04C11/005—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of dissimilar working principle
- F04C11/006—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of dissimilar working principle having complementary function
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
- F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
- F04C15/0073—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/10—Fluid working
- F04C2210/1044—Fuel
Abstract
The present invention relates to a kind of pump-unit (1), it is particularly useful for the fuel injection system of internal-combustion engine of air compressing, self ignition, described pump-unit comprises high-pressure service pump (2) and gear pump (3), described high-pressure service pump has high pressure pump shaft (7), and described gear pump has gear pump shaft (8).The invention still further relates to one and be arranged on clutch (12) between described high pressure pump shaft (7) and gear pump shaft (8), described clutch has at least one and consumes surface (21,22).
Description
Technical field
The present invention relates to a kind of pump-unit, especially a kind of pump-unit with high-pressure service pump and external gear pump.The present invention is specifically related to the fuel injection system field of a kind of air compressing, auto-ignition internal combustion engines.
Background technique
From DE 197 36 160 A1 known a kind of internal combustion engine injection system for the pump-unit of high voltage supply fuel.Described known pump-unit has a kind of pump case for radial piston pump, for housing parts and the end plate of gear pump.At this moment, arrange intersection plate clutch, it drives and connects the live axle of radial piston pump and an axle of gear pump.
Be from the shortcoming of the known pump-unit of DE 197 36 160 A1, in described clutch, occur the wearing and tearing of denuding.Also improve friction pair imaginabale, in the friction pair of especially live axle material or clutch material, in another situation, especially reach on the gear-bearing of described gear pump and bear high load.
Summary of the invention
The advantage with the pump-unit of the feature of claim 1 according to the present invention is, can ensure the longitudinal balance of the clutch between described high pressure pump shaft and gear pump shaft or gear in described length of life.
The favourable improvement project of the pump-unit given by claim 1 can be described by the measure listed in the dependent claims.
Especially, in the high-pressure service pump being used as common rail, its advantage is that described gear pump is driven by described high pressure pump shaft by described clutch.Described high pressure pump shaft is used as live axle here.When described driving moment is delivered to described gear pump shaft from described high pressure pump shaft, because described clutch to produce the wearing and tearing of abrasion relative to the relative movement of described live axle.These wearing and tearing are enhanced because lubricating bad fuel, and thus cause described pump-unit to lose efficacy.Especially when by hard metal normal clutch design proposal, because it is inserted in described high pressure pump shaft fiercely, the axial motion of the clutch thus required for described backlash compensation is no longer provided, and thus causes breaking or the member bursts of jointing place between described high-pressure service pump and gear pump of described clutch.Especially, in the fuel of high rotating speed and insufficient lubrication, the wearing and tearing of this abrasion are very large, so that normal clutch is seriously walked to be incorporated in described live axle, and there is the danger that described clutch breaks.By improving described friction pair, especially the improvement of live axle material or clutch material and the reduction therefore occurred by the wearing and tearing of described abrasion, the load of the gear-bearing of described gear pump is too large, so that the rest pin of the such as primary pinion of described gear pump is too seriously bending.Here, described gear can be walked to be incorporated in the housing parts of described gear pump.Therefore, when reducing the wearing and tearing of described abrasion, in another situation, described problem is transferred in the structure of described pump-unit.
The wearing and tearing of denuding can be realized because of the consumption face of described clutch.Therefore first stop high pressure pump shaft to come across in described clutch, and stop on the other position of described pump-unit, the load that especially described gear-bearing is increased.
Therefore advantageously, described clutch can make to there is axial clearance between described high pressure pump shaft and gear pump shaft.But also advantageously, described high pressure pump shaft has two-sided, described two-sided the second end face having the first end face and deviate from the first end face, described first end mask has an exhaustion layer, and described second end face has an exhaustion layer.Formed one here by described exhaustion layer and consume surface.The thickness of described exhaustion layer and the expected service life of described pump-unit predetermined relatively.If therefore described exhaustion layer is enough large, on described working life, do not worn and torn completely in described consumption surface.Because described clutch can not bite described two-sided on, on the working life of described pump-unit, thus keep the longitudinal balance of described clutch (especially described gear pump).Here, described consumption surface can realize the structure keeping described pump-unit further.Especially, the change parts of described pump-unit needed reduces and is thus restricted on the region of described clutch.Therefore little construction expenditure is used just can to extend the working life of described pump-unit.
The two-sided of described high pressure pump shaft is engaged in the groove of described gear pump shaft in a preferred manner at least in part.Described clutch certainly also can be provided with at least one driving section consuming the other formation in face by one and realize.
Therefore, also in high-revolving high-pressure service pump and in the fuel of insufficient lubrication, such as, for the lubrication in described clutch region, ensure the axial clearance in described clutch region on the working life of described pump-unit.
Accompanying drawing explanation
Describe the preferred embodiments of the present invention in detail with reference to accompanying drawing in the following description, wherein the corresponding identical reference character of element represents.In the accompanying drawings:
Fig. 1 shows the pump-unit of corresponding one embodiment of the present of invention with schematic, brief axial sectional view;
Fig. 2 shows the high pressure pump shaft of the high-pressure service pump of the pump-unit shown in Fig. 1 with brief view.
Embodiment
Fig. 1 shows the pump-unit 1 of corresponding one embodiment of the present of invention with schematic, brief axial sectional view.Pump-unit 1 can be particularly useful for fuel injection system that is compressed-air actuated, auto-ignition internal combustion engines.A preferable use of pump-unit 1 is the fuel injection system storing high-pressure diesel, have fuel distributor press strip.Pump-unit 1 in this case for transfer the fuel to this fuel distributor press strip.But pump in accordance with the present invention device 1 is also applicable to other applicable cases.
Pump-unit 1 has high-pressure service pump 2 and gear pump 3.High-pressure service pump 2 has housing 4.Gear pump 3 has the housing parts 5 being such as designed to lid 5.Housing parts 5 connects the housing 4 of high-pressure service pump 2 by rights.Here make to separate between the region of high-pressure service pump 2 with the region of gear pump 3 by the part 6 of housing 4.
High-pressure service pump 2 has high pressure pump shaft 7, and high pressure pump shaft 7 is bearing in housing 4 by rights.In addition, gear pump 3 has gear pump shaft 8, and gear pump shaft 8 is bearing in the hole 9 of housing parts 5.Here arrange on gear pump shaft 8 and fix the gear 10 that is designed to actuation gear 10.Such as gear 10 can be pressed on gear pump shaft 8.Gear pump 3 has other gear 11, and gear 11 works with gear 10 and is connected.Two gears 10,11 here engage in the mode obtaining pumping effect.High pressure pump shaft 7 is used as live axle here, and except the pump element of high-pressure service pump 2, it goes back actuation gear pump shaft 8, and then driving gear pump 3.Gear pump 3 is used as the transfer pump of high-pressure service pump 2.
Clutch 12 is set between high pressure pump shaft 7 and gear pump shaft 8.Clutch 12 comprises clutch part 13 and clutch part 14.Clutch part 14 is in this embodiment to drive the form of section 14 to be formed on high pressure pump shaft 7.Clutch part 14 is designed to two-sided form here.Clutch part 14 certainly also can work by rights with high pressure pump shaft 7 and be connected, especially with high pressure pump shaft 7 form fit or material fit be connected.Clutch part 13 can be designed to a part for gear pump shaft 8.Certainly, clutch part 13 also can be designed to independently clutch block 13, and it works by rights and connects gear pump shaft 8, and especially form fit or material fit ground connect gear pump shaft 8.Clutch block 13 also can directly be arranged on gear 10, thus can save described gear pump shaft 8, and can replace with supporting stub 8.Here advantageously, gear 10 is bearing in the hole 9 of the housing parts 5 of gear pump 3 by supporting stub 8, and the housing parts 5 of gear pump 3 connects the housing 4 of high-pressure service pump 2 at least indirectly.In this embodiment, clutch part 13 has groove 15, and the longitudinal axis 16 perpendicular to pump-unit 1 under the assembling condition of clutch part 13 carries out orientation.High pressure pump shaft 7 and gear pump shaft 8 align with the longitudinal axis 16, and are in operation and at least approximately rotate around the longitudinal axis 16.
In this embodiment exhaustion layer 17 is set in clutch part 14,18.Exhaustion layer 17 is here applied on the first end face 19 of clutch part 14.Exhaustion layer 18 is applied on the second end face 20 of clutch part 14.Two end faces 19,20 here deviate from mutually.Exhaustion layer 17,18 partly cover end face 19,20 here respectively.Exhaustion layer 17 forms consumption face 21.Exhaustion layer 18 also forms consumption face 22.In this embodiment, thus clutch 12 comprises the exhaustion layer 17,18 with consumption face 21,22.
Clutch 12 makes can there is certain axial clearance between high pressure pump shaft 7 and gear pump shaft 8.Be in operation, the clutch part 13 of clutch 12, thus causes relative movement between 14.Exhaustion layer 17, the raw materials of 18 adaptive clutch part 13.The wearing and tearing at least substantially consuming face 21,22 are caused relating to because of described relative movement.
Fig. 2 shows the high pressure pump shaft 7 of the high-pressure service pump 2 of the pump-unit 1 shown in Fig. 1 with brief illustrative diagram.The size of the thickness 23 of exhaustion layer 17 is arranged in length of life consumption face 21 and is not exclusively worn.Correspondingly, the size of the thickness 24 of exhaustion layer 18 is set to not be worn away completely in length of life consumption face 22.Thus the longitudinal balance of clutch 12 is kept in the length of life of gear pump 3.The parts of gear pump 3 here can reach and at least substantially be used unchangeably.Therefore, do not have or only there is the working life that little structural change just can extend the pump-unit 1 with high-pressure service pump 2 and gear pump 3.
The invention is not restricted to described embodiment.
Claims (11)
1. a pump-unit (1), described pump-unit has high-pressure service pump (2) and gear pump (3), and wherein, described high-pressure service pump has high pressure pump shaft (7), it is characterized in that,
Clutch (12) is arranged between the gear pump shaft (8) of described high pressure pump shaft (7) and described gear pump (3) or the gear (10) of described gear pump (3), described clutch has at least one consumption face (21,22) and described consumption face (21,22) are formed on exhaustion layer (17,18).
2. pump-unit according to claim 1, is characterized in that,
Axial clearance can be there is in described clutch (12) between high pressure pump shaft (7) described in useful life period chien shih and gear pump shaft (8) or gear (10).
3. pump-unit according to claim 1 and 2, is characterized in that,
Described high pressure pump shaft (7) has two-sided (14), the second end face (20) that described two-sided (14) have the first end face (19) and deviate from mutually with described first end face (19), described first end face (19) has exhaustion layer (17), and described second end face (20) has exhaustion layer (18).
4. pump-unit according to claim 3, is characterized in that,
Described gear pump shaft (8) or gear (10) have groove (15) and two-sided (14) of described high pressure pump shaft (7) are engaged in the groove (15) of described gear pump shaft (8) or gear (10) at least in part.
5. pump-unit according to claim 3, is characterized in that,
Described first end face (19) and described second end face (20) be coating exhaustion layer (17,18) partly.
6. pump-unit according to claim 1 and 2, is characterized in that,
The thickness (23,24) of described exhaustion layer (17,18) is predetermined relatively with working life.
7. pump-unit according to claim 1 and 2, is characterized in that,
Described consumption face (21,22) is arranged in the driving section (13) of high pressure pump shaft (7).
8. pump-unit according to claim 1 and 2, is characterized in that,
Described gear pump shaft (8) arranges a gear (10), described gear pump shaft (8) is bearing in the housing parts (5) of described gear pump (3), and the housing parts (5) of described gear pump (3) connects the housing (4) of described high-pressure service pump (2) at least indirectly.
9. pump-unit according to claim 1 and 2, is characterized in that,
Described gear (10) is bearing in the housing parts (5) of described gear pump (3), and the housing parts (5) of described gear pump (3) connects the housing (4) of described high-pressure service pump (2) at least indirectly.
10. pump-unit according to claim 1 and 2, is characterized in that,
Described high-pressure service pump (2) is designed to high-revolving high-pressure service pump (2).
11. pump-units according to claim 1 and 2, is characterized in that, described pump-unit is used for the fuel injection system of air compressing, auto-ignition internal combustion engines.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102009047576.1 | 2009-12-07 | ||
| DE102009047576A DE102009047576A1 (en) | 2009-12-07 | 2009-12-07 | pump assembly |
| PCT/EP2010/064972 WO2011069708A1 (en) | 2009-12-07 | 2010-10-07 | Pump arrangement |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102753826A CN102753826A (en) | 2012-10-24 |
| CN102753826B true CN102753826B (en) | 2015-10-21 |
Family
ID=43086287
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201080063197.3A Expired - Fee Related CN102753826B (en) | 2009-12-07 | 2010-10-07 | Pump-unit |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP2510235B1 (en) |
| CN (1) | CN102753826B (en) |
| DE (1) | DE102009047576A1 (en) |
| IN (1) | IN2012DN05042A (en) |
| WO (1) | WO2011069708A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2559148B (en) * | 2017-01-26 | 2019-06-05 | Delphi Tech Ip Ltd | Driveshaft with transfer pump adapter |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5542832A (en) * | 1994-03-31 | 1996-08-06 | Kabushiki Kaisha Toshiba | Rotary fluid compressor having an oldham mechanism |
| DE19736160A1 (en) * | 1997-08-20 | 1999-02-25 | Bosch Gmbh Robert | High pressure fuel pump for IC engine in common rail systems |
| EP1803939A1 (en) * | 2004-09-28 | 2007-07-04 | Daikin Industries, Ltd. | Slide member and fluid machine |
| CN101025204A (en) * | 2007-03-21 | 2007-08-29 | 太原市通泽成套设备有限公司 | Universal-joint-pin type universal coupling |
| CN101368600A (en) * | 2007-08-15 | 2009-02-18 | 胡厚飞 | High-torsion universal joint structure |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4289460B2 (en) * | 2004-12-28 | 2009-07-01 | 株式会社山田製作所 | Electric oil pump |
-
2009
- 2009-12-07 DE DE102009047576A patent/DE102009047576A1/en not_active Withdrawn
-
2010
- 2010-10-07 EP EP10767994.6A patent/EP2510235B1/en not_active Not-in-force
- 2010-10-07 WO PCT/EP2010/064972 patent/WO2011069708A1/en active Application Filing
- 2010-10-07 CN CN201080063197.3A patent/CN102753826B/en not_active Expired - Fee Related
- 2010-10-07 IN IN5042DEN2012 patent/IN2012DN05042A/en unknown
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5542832A (en) * | 1994-03-31 | 1996-08-06 | Kabushiki Kaisha Toshiba | Rotary fluid compressor having an oldham mechanism |
| DE19736160A1 (en) * | 1997-08-20 | 1999-02-25 | Bosch Gmbh Robert | High pressure fuel pump for IC engine in common rail systems |
| EP1803939A1 (en) * | 2004-09-28 | 2007-07-04 | Daikin Industries, Ltd. | Slide member and fluid machine |
| CN101025204A (en) * | 2007-03-21 | 2007-08-29 | 太原市通泽成套设备有限公司 | Universal-joint-pin type universal coupling |
| CN101368600A (en) * | 2007-08-15 | 2009-02-18 | 胡厚飞 | High-torsion universal joint structure |
Also Published As
| Publication number | Publication date |
|---|---|
| IN2012DN05042A (en) | 2015-10-09 |
| EP2510235B1 (en) | 2013-08-07 |
| WO2011069708A1 (en) | 2011-06-16 |
| CN102753826A (en) | 2012-10-24 |
| DE102009047576A1 (en) | 2011-06-09 |
| EP2510235A1 (en) | 2012-10-17 |
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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: 20151021 |
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| CF01 | Termination of patent right due to non-payment of annual fee |