AU2013391197A1 - High-pressure fuel pump driving structure - Google Patents
High-pressure fuel pump driving structure Download PDFInfo
- Publication number
- AU2013391197A1 AU2013391197A1 AU2013391197A AU2013391197A AU2013391197A1 AU 2013391197 A1 AU2013391197 A1 AU 2013391197A1 AU 2013391197 A AU2013391197 A AU 2013391197A AU 2013391197 A AU2013391197 A AU 2013391197A AU 2013391197 A1 AU2013391197 A1 AU 2013391197A1
- Authority
- AU
- Australia
- Prior art keywords
- sleeve
- pressure fuel
- fuel pump
- high pressure
- skew gear
- 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
Classifications
-
- 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
- F02M39/02—Arrangements of fuel-injection apparatus to facilitate the driving of pumps; Arrangements of fuel-injection pumps; Pump drives
-
- 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
-
- 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
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
Abstract
A high-pressure fuel pump driving structure for an engine, comprising: a skew gear (5) with an internal spline; a sleeve (4) with an external spline; a sliding sleeve (7); and a fixed sleeve (9); the sleeve (4) is mounted fixedly on a pump shaft of the high-pressure fuel pump, and the fitting clearance of the external spline of the sleeve (4) and the internal spline of the skew gear (5) enables the skew gear (5) to slide relative to the sleeve (4) along axial direction. The sliding sleeve (7) and the fixed sleeve (9) are coaxially sleeved together and can slide relative to each other axially. One end of the sliding sleeve (7) is propped against the skew gear (5). A pre-compressed spring (8) is provided between the sliding sleeve (7) and the fixed sleeve (9). The structure is capable of avoiding the axial force produced by driving the skew gear, thereby being more applicable for high-pressure fuel pump and reducing noise.
Description
High Pressure Fuel Pump Driving Structure Technical Field 5 The present application relates to the field of engine, specifically to a high pressure fuel pump driving structure driven by skew gear. Background 10 Engine is used widely in various technical fields, especially in automobile field. High pressure co-rail fuel system is widely used in diesel engine for vehicles along with the more restrictive exhaust regulations both at home and abroad. High pressure fuel pump is driven through timing system gear or chain wheel, belt. In recent years, there has tends to change to skew gear from 15 the original spur gear for driving the timing system of an engine for reducing noise effectively. For example, the Chinese patent application of the application NO. 201210078678.2, the application date 2012-03-22, and the title "Diesel Engine Oil Pump Transmission System" uses skew gear in the timing system. 20 Since the pump shaft of high pressure fuel pump cannot bear axial force in general, the axial force generated during transmission needs to be offset or compensated. The Chinese patent of the application NO. 200810107974.4, the application date 2008-05-06, and the title "A novel High Pressure Fuel Pump Transmission Mechanism" uses a crosshead shoe between drive shaft and 25 pump shaft of the fuel pump thereby to eliminate the impact of axial force and normal force of the timing chain and to improve the compensation ability to the relative shift between transmission shaft and pump shaft, and the connecting structure is simple. However, if the timing system uses skew gear, the skew gear has to bear larger axial component relative to spur gear, and therefore, the 1 WP150783AU elimination and shift compensation of axial force has become the primary problem in design. If crosshead shoe is still in use for connection, at the time of mutation of loading caused by engine speeding up or slowing down the rotation, or changes of other situation such as bumping road, the axial force 5 will bring more significant impact. And at the time of frequent mutation of loading, the axial shuttle of crosshead shoe between the pump shaft and the drive shaft is larger and more frequent, which not only causes abrasion and shortens lifetime, but also generates impact between the pump shaft and the drive shaft, reducing the noise-decrease effect of the skew gear. 10 The Chinese patent application of the application NO. 201210042389.7, the application date 2012-02-23, and the title "A Fuel Injection Pump for Engine and Engine" discloses processing internal spline on axis hole of the fuel injection pump gear and mounting external spline on cam shaft for delivery torque through cooperation of the internal and external splines, and positioning 15 on axial direction needs positioning member (specifically a positioning bolt or a positioning pin) to pass through gear base and bearing bush and then cooperate with groove on circumferential direction of the fuel injection pump gear. It is to say that if skew gear is used, the axial component may be delivered to the positioning member, and then delivered to gear base and offset 20 by it. Since the positioning member and the groove on circumferential direction of the fuel injection pump gear are in rigid contact, as time goes on, it will generate abrasion between the positioning member and the groove, results in axial shuttle of the fuel injection pump gear and generates noise. 25 Content of the Invention The object of the present application is to provide a structure that can bear and avoid effectively axial force generated when skew gear is used to drive a high pressure fuel pump, such that the skew gear is more adaptable for driving 2 WP150783AU engine of high pressure fuel pump whereby reducing engine noise. For achieving the above object, the present application provides the following technical solutions: An engine high pressure fuel pump driving structure, comprising: a skew 5 gear with internal spline; a sleeve with external spline; a sliding sleeve; and a fixed sleeve; the sleeve is fixedly mounted on pump shaft of the high pressure fuel pump, the external spline of the sleeve and the internal spline of the skew gear are in clearance fit so that the skew gear can slide relative to the sleeve in axial direction, the sliding sleeve and the fixed sleeve are sleeved together 10 coaxially and can slide axially relative to each other, one end of the sliding sleeve is propped against the skew gear, and a pre-compressed spring is provided between the sliding sleeve and the fixed sleeve. Preferably, the fixed sleeve is fixed on a casing for closing the chain wheel chamber. 15 Preferably, the fixed sleeve is a single member. Preferably, the spring is pre-compressed when the fixed sleeve is mounted. Preferably, the sleeve is fixedly mounted on the pump shaft through a nut. Preferably, a diameter of skirt of the nut is larger than outer diameter of the sleeve. 20 Preferably, a thrust pad is provided between the skew gear and a flange plate, the thrust pad and the flange plate are positioned through a positioning pin. Preferably, there opens an oil groove on end face of the sliding sleeve propping against the skew gear. 25 Preferably, there opens a vent hole on the sliding sleeve. Preferably, there opens a circular hole on the sliding sleeve and a waist-round hole on the fixed sleeve, a limit pin passing through the circular hole and the waist-round hole is provided in the circular hole and the waist-round hole. 3 WP150783AU In the present application, the pump shaft transmission to the high pressure fuel pump is accomplished through cooperation of the inner splines of the skew gear and the external splines of the sleeve; when mutation of loading occurs on skew gear, the axial force towards cylinder is delivered to flange plate and 5 further delivered to the cylinder, while the axial force towards chain wheel chamber tends to make the skew gear and sleeve sliding relatively in axial direction, when the axial force is smaller, the axial force is offset by pretightening force of the spring, while when the axial force is larger, kinetic energy generated by the relative sliding is converted to potential energy of the 10 spring through the sliding sleeve, which reduces effectively impact and vibration generated from the relative sliding. Therefore, the axial force cannot be applied to the pump shaft no matter which direction axial force is oriented, and the high pressure fuel pump can accommodate the cooperation with the skew gear. At the same time, the structure of the present application 15 does not cause impact and vibration generated for the need of offset axial force in most cases, and therefore, can fully develop the advantages of smooth transmission and low noise of the skew gear. Further, the fixed sleeve is fixed to a casing used for closing chain wheel chamber, and as the structure is distributed along the pump shaft in axial 20 direction as a whole, it is ensured that no interfering with the timing chain can be generated, and the entire structure can fully use small room of the chain wheel chamber. Further, the fixed sleeve is a single member, then when maintenance is necessary, the sliding sleeve and spring can be taken out only by dissembling 25 the fixed sleeve from the casing without dissembling the casing, which facilitates maintenance. Further, the spring is pre-compressed by the fixed sleeve at the same time mounting the casing to close the chain wheel chamber, the mounting is simple. Further, a nut is used to fix the sleeve to the pump shaft, which simplifies 4 WP150783AU dissembling of the entire structure. Further, the diameter of skirt of the nut is larger than the outer diameter of the sleeve, which makes the skirt of the nut become a limit structure of the skew gear to prevent the skew gear from sliding off the sleeve when the axial 5 force is too large. Further, the thrust pad can provide buffer to axial force towards the cylinder and can improve abrasion performance, and using positioning pin for positioning facilitates dissembling. Further, to open an oil groove on end face of the sliding sleeve propping 10 against the skew gear can provide lubricating oil to the gap between the skew gear and the sliding sleeve, which makes the gap between the skew gear and the sliding sleeve more abrasion resistance. Further, the vent hole on the sliding sleeve can balance air pressure inside and outside the sliding sleeve when the sliding sleeve moves due to relative 15 sliding of the skew gear and the sleeve. Further, inserting a pin to the circular hole on the sliding sleeve and the waist-round hole on the fixed sleeve can limit a journey of the sliding sleeve (further a journey of the skew gear), and the waist-round hole can also be used as an inlet hole of oil to provide lubricating oil between the sliding sleeve and 20 the fixed sleeve. Description of Figures Fig. 1 is a front sectional view of the engine high pressure fuel pump 25 driving structure of a embodiment of the present application; Fig. 2 is a front sectional view similar to that in Fig. 1 with ignoring surrounding members such as cylinder, casing, etc. for the purpose of clear; Fig 3 is an explosive view of the engine high pressure fuel pump driving structure of the embodiment of the present application; 5 WP150783AU Fig. 4 is a partial enlarged view of part I in Fig. 2. Reference signs in the above Figs are: cylinder 1, high pressure fuel pump 2, pump shaft 21, flange plate 3, axle hole 31, sleeve 4, skew gear 5, nut 6, skirt 5 61, sliding sleeve 7, end 71, oil groove 711, vent hole 72, circular hole 73, spring 8, fixed sleeve 9, waist-round hole 91, casing 10, thrust pad 11, positioning pin 12, limit pin 13. Mode of Carrying out the Invention 10 Specific embodiments of the present application are further described in conjunction with the drawings. Combing Fig. 1 to Fig. 3, the high pressure fuel pump 2 is mounted on cylinder 1 through flange plate 3, there is an axle hole 31 on the flange plate 3, pump shaft 21 of the high pressure fuel pump 2 passes through the axle hole 31 15 to extend to the chain wheel chamber (not marked) of the engine, and there is a timing wheel system held in the chain wheel chamber. In the chain wheel chamber, sleeve 4 is sleeved on pump shaft 21 and tightened through a nut 6 for fixedly mounting the sleeve 4 and the pump shaft 21. It is easy for a person skilled in the art to image that the sleeve 4 can also be sleeved on pump shaft 20 21 through interference fit, but using a nut has advantage from the view of easy dismounting. The sleeve 4 has external spline and the skew gear 5 has internal spline, the external spline of the sleeve 4 and the internal spline of the skew gear 5 are in clearance fit. The timing chain (not shown) in the chain wheel chamber delivers driving force to pump shaft 21 through spline fit 25 between the skew gear 5 and the sleeve 4 thereby driving the high pressure fuel pump 2 to work. Further, as the sleeve 4 and the skew gear 5 are in clearance fit, the skew gear 5 can slide relative to the sleeve 4 in the axial direction. In the Figs, on the right side of the skew gear 5, end 71 of the sliding sleeve 7 props against the skew gear 5. The fixed sleeve 9 can be a single member 6 WP150783AU fixed to casing 10 (such as chain wheel shell, fly wheel shell, etc.) for enclosing chain wheel chamber through adapting piece such as bolt, rivet, etc., or is not a single member but fixed on casing 10 through a manner of unibody such as casting. Preferably the fixed sleeve 9 is a single member fixed on the casing 5 10 with manners such as a bolt, or, to process external thread on the fixed sleeve 9 and threaded hole on casing 10, the fixed sleeve 9 is screwed into the chain wheel chamber from outside, and the fixed sleeve 9 pre-compresses the spring 8 at the same time. When the driving structure needs maintenance, sliding sleeve 7 and spring 8 in the chain wheel chamber can be taken out only 10 by unscrewing the bolt or the fixed sleeve 9 and disassembling the fix between the sleeve 9 and the casing 10, or unscrewing nut 6 to replace or adjust other parts without disassembling the casing 10, which facilitates maintenance. Of cause when the fixed sleeve 9 is a single member, there should be a seal ring between the fixed sleeve 9 and the casing 10. The sliding sleeve 7 and the fixed 15 sleeve 9 are sleeved together coaxially and both are in clearance fit, so the sliding sleeve 7 can slide relative to the fixed sleeve 9 in axial direction. And there is a pre-compressed spring 8 between the sliding sleeve 7 and the fixed sleeve 9. Referring to Fig. 2, under normal operation, the skew gear 5 also bears 20 axial force, and the axial force changes when mutation of the loading on the skew gear 5 occurs because of cases such as engine speed up, speed down, bump road, etc. The axial force is directed to two directions, one is directed to axial force F1 towards the cylinder and the other is directed to axial force F2 towards the chain wheel chamber. In the present application, since spring 8 is 25 pre-compressed, the pretightening force of the spring 8 pushes the sliding sleeve 7 towards the skew gear 5 under initial circumstance, and then the skew gear 5 tends to props against the flange plate 3, when the axial force is directed to force F1 towards the cylinder 1, F1 is delivered to cylinder 1 without having impact on the pump shaft 21. Since skew gear 5 rotates under operation, 7 WP150783AU preferably there provides a thrust pad 11 between the flange plate 3 and the skew gear 5. And in conjunction with Fig. 3, it can be seen that the thrust pad 11 and the flange plate 3 are positioned through the positioning pin 12 to prevent thrust pad 11 from rotating. When the skew gear 5 undergoes the 5 impact of the axial force F2 towards the chain wheel chamber, F2 can be offset by pretightening force of the spring 8 when F2 is smaller, and therefore, the skew gear 5 does not have axial slide. Even if F2 is larger that exceeds the pretightening force of the spring 8, since the skew gear 5 and the sleeve 4 are in clearance fit, the skew gear 5 can slide slightly towards the direction of the 10 casing 10, push the sliding sleeve 7 further pressing the spring 8, the kinetic energy of skew gear 5 is converted to potential energy of the spring 8, and no noise generated from impact in the entire structure. And since the sliding sleeve 7 may move towards the fixed sleeve 9, preferably there opens vent hole 72 on the sliding sleeve 7 to keep the air pressure inside and outside of the 15 sliding sleeve 7 being consistent. Referring to Fig. 3, there opens several oil grooves 711 on the end surface of the end 71 of the sliding sleeve 7 propping against the skew gear 5 for lubrication between the end surface and the skew gear 5. Combining Fig. 3 and Fig. 4, it can be seen that there opens a circular hole 73 on the sliding 20 sleeve 7 and a waist-round hole 91 on the fixed sleeve 9, and limit pin 13 passes through the circular hole 73 and the waist-round hole 91. When the skew gear 5 slides, the limit pin 13 can slide only within the waist-round hole 91, which limits the sliding journey of the skew gear 5, prevents strong impact caused by the excessive axial force F2 and sliding down of the skew gear 5 25 from the sleeve 4, and the waist-round hole 91 can also be an inlet of oil to provide lubricating oil to the contact face between the sliding sleeve 7 and the fixed sleeve 9. Referring to Fig. 4, diameter D1 of skirt 61 of the nut 6 is larger than outer diameter D2 of the sleeve 4, so that the skirt 61 can also serve to limit the 8 WP150783AU sliding journey of the skew gear 5 and prevent sliding down of skew gear 5 from the sleeve 4. Returning to Fig. 3 again, when mounting, at the first, the high pressure fuel pump 2 is mounted onto the flange plate 3, the sleeved thrust pad 11 is 5 mounted on the pump shaft 21, the positioning pin 12 is inserted to fix the thrust pad 11 on the flange plate 3, and then the sleeve 4 is sleeved, the skew gear 5 is sleeved on the sleeve 4, then nut 6 is screwed to integrate the above mounted parts into a whole, and then fixed on cylinder 1 through the flange plate 3 to facilitate the following installing and adjusting. Then sliding sleeve 10 7 is mounted, the spring 8 is inserted, the fixed sleeve 9 is mounted onto casing 10, and the fixed sleeve 9 pre-compresses the spring 8 at the same time of mounting the fixed sleeve 9. When disassembling is necessary for maintenance, it only needs to unscrew fixed sleeve 9 and flange plate 3, then the flange plate 3, high pressure fuel pump 2, thrust pad 11, sleeve4, skew gear 5 and nut 6 can 15 be taken out as an integer from the chain wheel chamber without worrying that parts could fall into chain wheel chamber during the disassembling, and there is no need to disassembly the casing 10. If further disassembling is needed for replacing parts, disassembling the entire structure can be completed by unscrewing nut 6 and demounting flange plate 3, which is very convenient. 20 The present application is described with combination of the above embodiments, but is not limited by the embodiments and is only defined by the claims, A person skilled in the art can make modification and change easily without departing away from the substance design and scope of the present application. 25 9 WP150783AU
Claims (11)
1. An engine high pressure fuel pump driving structure, characterized in comprising: 5 a skew gear with internal spline; a sleeve with external spline; a sliding sleeve; a fixed sleeve; the sleeve is fixedly mounted on pump shaft of the high pressure fuel 10 pump, the external spline of the sleeve and the internal spline of the skew gear are in clearance fit so that the skew gear can slide relative to the sleeve in axial direction, the sliding sleeve and the fixed sleeve are sleeved together coaxially and can slide axially relative to each other, one end of the sliding sleeve props against the skew gear, and a pre-compressed spring is provided between the 15 sliding sleeve and the fixed sleeve.
2. An engine high pressure fuel pump driving structure according to claim 1, characterized in that the fixed sleeve is fixed on a casing for closing a chain wheel chamber.
3. An engine high pressure fuel pump driving structure according to claim 20 1, characterized in that the fixed sleeve is a single member.
4. An engine high pressure fuel pump driving structure according to claim 2, characterized in that the spring is pre-compressed when the fixed sleeve is mounted.
5. An engine high pressure fuel pump driving structure according to claim 25 1, characterized in that the sleeve is fixedly mounted on the pump shaft through a nut.
6. An engine high pressure fuel pump driving structure according to claim 5, characterized in that diameter of skirt of the nut is larger than outer diameter of the sleeve. 10 WP150783AU
7. An engine high pressure fuel pump driving structure according to any of claims 1-6, characterized in that a thrust pad is provided between the skew gear and the flange plate, the thrust pad and the flange plate are positioned through a positioning pin. 5
8. An engine high pressure fuel pump driving structure according to any of claims 1-6, characterized in that there opens an oil groove on end face of the sliding sleeve propping against the skew gear.
9. An engine high pressure fuel pump driving structure according to any of claims 1-6, characterized in that there opens a vent hole on the sliding 10 sleeve.
10. An engine high pressure fuel pump driving structure according to any of claims 1-6, characterized in that there opens a circular hole on the sliding sleeve and a waist-round hole on the fixed sleeve, a limit pin passing through the circular hole and the waist-round hole is provided in the circular hole and 15 the waist-round hole.
11 WP150783AU
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310200313.7 | 2013-05-27 | ||
| CN201310200313.7A CN103266972B (en) | 2013-05-27 | 2013-05-27 | High pressure fuel pump driving structure |
| PCT/CN2013/082616 WO2014190631A1 (en) | 2013-05-27 | 2013-08-30 | High-pressure fuel pump driving structure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| AU2013391197A1 true AU2013391197A1 (en) | 2015-09-10 |
| AU2013391197B2 AU2013391197B2 (en) | 2016-06-09 |
Family
ID=49010622
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| AU2013391197A Ceased AU2013391197B2 (en) | 2013-05-27 | 2013-08-30 | High-pressure fuel pump driving structure |
Country Status (6)
| Country | Link |
|---|---|
| CN (1) | CN103266972B (en) |
| AU (1) | AU2013391197B2 (en) |
| BR (1) | BR112015029593A2 (en) |
| CL (1) | CL2015003449A1 (en) |
| RU (1) | RU2618361C1 (en) |
| WO (1) | WO2014190631A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2017016787A1 (en) * | 2015-07-28 | 2017-02-02 | Delphi International Operations Luxembourg S.À R.L. | High pressure fuel pump |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103266972B (en) * | 2013-05-27 | 2015-03-25 | 安徽江淮汽车股份有限公司 | High pressure fuel pump driving structure |
| CN105909437B (en) * | 2016-05-06 | 2018-11-23 | 潍柴动力扬州柴油机有限责任公司 | A kind of fuel pump transmission device and the fuel injection system equipped with the device |
| CN106286054A (en) * | 2016-11-11 | 2017-01-04 | 安徽江淮汽车股份有限公司 | A kind of high-pressure oil pump mounting structure and electromotor |
| CN115853640A (en) | 2018-05-23 | 2023-03-28 | 康明斯公司 | Engine and method of removing fuel pump from engine |
| CN108979918A (en) * | 2018-09-04 | 2018-12-11 | 江苏农华智慧农业科技股份有限公司 | A kind of oil transfer pump oil transportation circulation mechanism based on crankshaft |
| JP7176307B2 (en) * | 2018-09-07 | 2022-11-22 | いすゞ自動車株式会社 | pump gear |
| RU187542U1 (en) * | 2018-10-11 | 2019-03-12 | Публичное акционерное общество "КАМАЗ" | HIGH PRESSURE FUEL PUMP DRIVE |
| US11698050B2 (en) | 2020-07-13 | 2023-07-11 | Powerhouse Engine Solutions Switzerland IP Holding GmbH | System and method for oil supply to pump |
| RU202530U1 (en) * | 2020-09-14 | 2021-02-24 | Публичное акционерное общество "КАМАЗ" | HIGH PRESSURE FUEL PUMP DRIVE |
Family Cites Families (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2021718A (en) * | 1931-11-12 | 1935-11-19 | Gustave Fast Engineering Corp | Torsionally resilient coupling |
| JPS59176424A (en) * | 1983-03-26 | 1984-10-05 | Nippon Denso Co Ltd | Fuel injection timing regulator of internal-combustion engine |
| JPS60216032A (en) * | 1984-04-11 | 1985-10-29 | Yanmar Diesel Engine Co Ltd | Auxiliary driving apparatus for internal-combustion engine |
| JPS6181574A (en) * | 1984-09-28 | 1986-04-25 | Hino Motors Ltd | Fuel injection pump driving device for diesel engine |
| DE3921245A1 (en) * | 1989-06-29 | 1991-01-03 | Kloeckner Humboldt Deutz Ag | FUEL PUMP PUMP DESIGNED AS A ROTOR PUMP |
| DE4430908A1 (en) * | 1994-08-31 | 1996-03-07 | Bosch Gmbh Robert | IC engine fuel injection pump |
| US5860328A (en) * | 1995-06-22 | 1999-01-19 | Chrysler Corporation | Shaft phase control mechanism with an axially shiftable splined member |
| JP2002227738A (en) * | 2001-01-31 | 2002-08-14 | Yanmar Diesel Engine Co Ltd | Fuel injection pump of engine |
| JP2003278886A (en) * | 2002-03-20 | 2003-10-02 | Ricoh Co Ltd | Drive transmission mechanism |
| JP3829824B2 (en) * | 2003-06-11 | 2006-10-04 | 株式会社デンソー | Fuel injection pump |
| CN1865680A (en) * | 2006-04-30 | 2006-11-22 | 无锡开普动力有限公司 | Oil-supply adjusting mechanism for injection pump of engine |
| CN101285440B (en) * | 2008-05-06 | 2011-05-11 | 奇瑞汽车股份有限公司 | High voltage oil fuel pump transmission mechanism |
| CN102465801B (en) * | 2010-11-18 | 2014-08-13 | 博世汽车柴油系统有限公司 | High-pressure fuel pump |
| RU109504U1 (en) * | 2011-04-25 | 2011-10-20 | Открытое акционерное общество "КАМАЗ" | HIGH PRESSURE FUEL PUMP DRIVE |
| CN102606255A (en) * | 2012-03-22 | 2012-07-25 | 东风朝阳朝柴动力有限公司 | Oil pump driving system for diesel engine |
| CN102606359A (en) * | 2012-03-22 | 2012-07-25 | 潍柴动力股份有限公司 | High-pressure oil pump transmission and assembling method thereof |
| CN103047169A (en) * | 2013-01-15 | 2013-04-17 | 中国兵器工业集团第七0研究所 | Adjustable thrust structure for balancing axial force of gear |
| CN103266972B (en) * | 2013-05-27 | 2015-03-25 | 安徽江淮汽车股份有限公司 | High pressure fuel pump driving structure |
-
2013
- 2013-05-27 CN CN201310200313.7A patent/CN103266972B/en active Active
- 2013-08-30 WO PCT/CN2013/082616 patent/WO2014190631A1/en active Application Filing
- 2013-08-30 AU AU2013391197A patent/AU2013391197B2/en not_active Ceased
- 2013-08-30 BR BR112015029593A patent/BR112015029593A2/en active Search and Examination
- 2013-08-30 RU RU2015154659A patent/RU2618361C1/en active
-
2015
- 2015-11-24 CL CL2015003449A patent/CL2015003449A1/en unknown
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2017016787A1 (en) * | 2015-07-28 | 2017-02-02 | Delphi International Operations Luxembourg S.À R.L. | High pressure fuel pump |
Also Published As
| Publication number | Publication date |
|---|---|
| BR112015029593A2 (en) | 2017-07-25 |
| CL2015003449A1 (en) | 2016-09-30 |
| AU2013391197B2 (en) | 2016-06-09 |
| WO2014190631A1 (en) | 2014-12-04 |
| RU2618361C1 (en) | 2017-05-03 |
| CN103266972B (en) | 2015-03-25 |
| CN103266972A (en) | 2013-08-28 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| AU2013391197B2 (en) | High-pressure fuel pump driving structure | |
| US8985293B2 (en) | Decoupler assembly with sliding interface between hub and pulley | |
| US9010209B2 (en) | Scissors gear assembly | |
| US9074497B2 (en) | Camshaft phaser having a spring attached to the pin of a screw | |
| US9200609B2 (en) | Torque transmission mechanism | |
| US20110146604A1 (en) | Valve train of internal combustion engine | |
| WO2011114052A3 (en) | Combustion engine starter with output pinion in the starter housing | |
| CN209483803U (en) | It is connected with the combined bias shaft of harmonic speed reducer | |
| JP5912308B2 (en) | Camshaft and combustion engine | |
| CN208431088U (en) | Engine foot starter and engine | |
| CN101285440B (en) | High voltage oil fuel pump transmission mechanism | |
| US20150014119A1 (en) | Torque Transmission Mechanism | |
| JP2016156430A (en) | Tensioner unit for auxiliary drive belt | |
| CN103982529B (en) | A kind of assembled crankshaft | |
| US20100154743A1 (en) | Hydraulic radial piston engine | |
| CN202251732U (en) | Planet wheel speed reducer provided with wear-resistant part | |
| CN201916356U (en) | Axial clearance adjusting structure of input shaft bearing | |
| CN103758952B (en) | A kind of chain tightener for tensioning engine timing chain | |
| TWM451425U (en) | Auxiliary device of engine crankshaft | |
| CN205172661U (en) | Engine air distribution mechanism ball tappet | |
| CN105545399B (en) | Engine valve actuating mechanism ball tappet | |
| CN204900708U (en) | Automobile engine uses automatic belt tensioner | |
| CN108005828B (en) | Engine foot starting device and engine | |
| CN209469465U (en) | A kind of automobile engine belt pulley friction shim | |
| CN105370392B (en) | mechanical supercharger |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FGA | Letters patent sealed or granted (standard patent) | ||
| HB | Alteration of name in register |
Owner name: ANHUI JIANGHUAI AUTOMOBILE GROUP CORP., LTD. Free format text: FORMER NAME(S): ANHUI JIANGHUAI AUTOMOBILE CO., LTD |
|
| MK14 | Patent ceased section 143(a) (annual fees not paid) or expired |