EP3572664B1 - High-pressure pump - Google Patents

High-pressure pump Download PDF

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Publication number
EP3572664B1
EP3572664B1 EP18741821.5A EP18741821A EP3572664B1 EP 3572664 B1 EP3572664 B1 EP 3572664B1 EP 18741821 A EP18741821 A EP 18741821A EP 3572664 B1 EP3572664 B1 EP 3572664B1
Authority
EP
European Patent Office
Prior art keywords
section
plunger
plunger sleeve
pressure
pressure chamber
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.)
Active
Application number
EP18741821.5A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3572664A4 (en
EP3572664A1 (en
Inventor
Qing Li
Zhongyu WU
Yin ZHU
Haoxun DONG
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
United Automotive Electronic Systems Co Ltd
Original Assignee
United Automotive Electronic Systems Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by United Automotive Electronic Systems Co Ltd filed Critical United Automotive Electronic Systems Co Ltd
Publication of EP3572664A1 publication Critical patent/EP3572664A1/en
Publication of EP3572664A4 publication Critical patent/EP3572664A4/en
Application granted granted Critical
Publication of EP3572664B1 publication Critical patent/EP3572664B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/442—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston means preventing fuel leakage around pump plunger, e.g. fluid barriers
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams

Definitions

  • the present invention relates to the technical field of fuel injection pumps, and in particular, to a high-pressure pump.
  • a high-pressure pump is a critical part of a direct fuel injection engine.
  • the high-pressure pump includes an inlet valve 5', an outlet valve 6', a pressure chamber 1' disposed between the inlet valve 5' and the outlet valve 6', a plunger sleeve 3' disposed in the pressure chamber 1', a protruding member 8' disposed at one end of the plunger sleeve and at its outer side, and in interference fit to the pressure chamber 1', and a plunger 4' disposed inside the plunger sleeve 3'.
  • Pressure is generated by the movement of the plunger 4' in the pressure chamber 1' to convert low-pressure fuel into high-pressure fuel (having a pressure up to 150 bar or higher).
  • the above schemes 1 and 2 are accompanied by the increase in weight and cost, and the above scheme 3 is accompanied by the risks of accelerated wear to the plunger set and a significant decrease in the service life, and it is required to use the material having better performance in wear resistance or to perform a surface treatment process to acquire a better wear resistance.
  • the cost will be increased.
  • WO2008086011 discloses a clamping and seal loading technique for securing the plunger sleeve to the pump housing of a single plunger fuel pump. This is achieved by providing a load ring between a sleeve retainer and the sleeve, such that the axial force applied by the retainer during installation and attachment to the plunger bore wall of the housing, is distributed more evenly on the sleeve and the sealing surface of the sleeve against the housing adjacent to the pumping chamber. The even distribution of force minimizes misalignment of the sleeve and thus maintains concentricity between the sleeve and the plunger.
  • An objective of the present invention is to provide a high-pressure pump to solve the problem in the prior art that in the fuel pumping stage of the high-pressure pump, the high-pressure fuel is likely to return to low-pressure areas through a plunger clearance, and the volumetric efficiency is reduced.
  • the present invention provides a high-pressure pump, comprising: a pressure chamber, a plunger sleeve disposed in the pressure chamber, a protruding member disposed at an outer side of the plunger sleeve and in interference fit to a wall of the pressure chamber, a plunger disposed in the plunger sleeve, an inlet valve, and an outlet valve, wherein the plunger sleeve comprises a first section and a second section connected to the first section; the protruding member is disposed on an outer side of the second section close to the first section; the protruding member divides the pressure chamber into a first pressure chamber and a second pressure chamber, the first section is located in the first pressure chamber, and the inlet valve and the outlet valve are disposed at the first pressure chamber.
  • the plunger moves from the second pressure chamber towards the first pressure chamber.
  • the first pressure chamber in the fuel pumping stage of the high-pressure pump, has a pressure higher than a pressure of the second pressure chamber.
  • the first section of the plunger sleeve deforms to contract inwards, and a clearance between the first section of the plunger sleeve and the plunger is smaller than a machining clearance of a plunger set.
  • the pressure in the first pressure chamber is progressively decreased along a direction towards the second pressure chamber.
  • the plunger moves from the first pressure chamber towards the second pressure chamber.
  • the first pressure chamber in the fuel sucking stage of the high-pressure pump, has a pressure equal to a pressure of the second pressure chamber.
  • a clearance between the first section of the plunger sleeve and the plunger is equal to a clearance between the second section of the plunger sleeve and the plunger, and the clearance between the second section of the plunger sleeve and the plunger is a machining clearance of a plunger set.
  • the first section of the plunger sleeve has an inner diameter same as an inner diameter of the second section of the plunger sleeve, and the first section of the plunger sleeve has an outer diameter same as an outer diameter of the second section of the plunger sleeve.
  • the first section of the plunger sleeve has an inner diameter same as an inner diameter of the second section of the plunger sleeve, and the first section of the plunger sleeve has an outer diameter different from an outer diameter of the second section of the plunger sleeve.
  • the first section of the plunger sleeve has a length satisfying a relationship with a total length of the plunger sleeve as follows: 3 ⁇ L 2 L 1 ⁇ 8 wherein L2 represents the total length of the plunger sleeve, and L1 represents the length of the first section of the plunger sleeve.
  • the inner diameter of the first section of the plunger sleeve, the outer diameter of the first section of the plunger sleeve, and the outer diameter of the second section of the plunger sleeve satisfy the following relationship: D 2 ⁇ D 1 D 3 ⁇ D 1 > 1.2 , wherein D1 represents the inner diameter of the first section of the plunger sleeve, D2 represents the outer diameter of the second section of the plunger sleeve, and D3 represents the outer diameter of the first section of the plunger sleeve.
  • the first section is connected to the second section through a transition section, and a cross section of the transition section is shaped with any one of a round corner, a right angle, a chamfer, a multi-section curve, and a multi-section line, or a combination of the multi-section curve and the multi-section line.
  • the plunger sleeve of the high-pressure pump includes a first section and a second section connected to the first section, the protruding member is disposed on the outer side of the second section close to the first section, and the first section is located in the first pressure chamber.
  • the position at which the protruding member is in interference fit to the pressure chamber is lower.
  • the first section is deformed and shrunk inwards due to the pressure difference between the inside and the outside of the first section, and the clearance between the first section and the plunger is reduced, which effectively reduces the likelihood of backflow through the clearance.
  • the high-pressure pump of the present invention has a larger plunger clearance in the fuel sucking stage, less wear to the plunger set, and a longer service life than the existing high-pressure pump. Therefore, it is possible to further reduce the machining clearance in the plunger set to increase the volumetric efficiency, without increasing the weight or using more expensive materials.
  • 1' denotes a pressure chamber; 3' denotes a plunger sleeve; 4' denotes a plunger; 5' denotes an inlet valve; 6' denotes an outlet valve; 7' denotes a machining clearance in a plunger set; 8' denotes a protruding member.
  • 1 denotes a first pressure chamber
  • 2 denotes a second pressure chamber
  • 3 denotes a plunger sleeve
  • 31 denotes a first section
  • 32 denotes a second section
  • 4 denotes a plunger
  • 5 denotes an inlet valve
  • 6 denotes an outlet valve
  • 7 denotes a machining clearance in a plunger set
  • 8 denotes a protruding member.
  • FIGs. 2 and 4 are schematic structural diagrams of a high-pressure pump according to the present invention.
  • the high-pressure pump comprises a pressure chamber, a plunger sleeve 3 disposed in the pressure chamber, a protruding member 8 disposed at an outer side of the plunger sleeve 3 and in interference fit to the wall of the pressure chamber, a plunger 4 disposed in the plunger sleeve 3, an inlet valve 5, and an outlet valve 6.
  • the plunger sleeve 3 comprises a first section 31 and a second section 32 connected to the first section 31.
  • the protruding member 8 is disposed on the outer side of the second section 32 close to the first section 31.
  • the protruding member 8 divides the pressure chamber into a first pressure chamber 1 and a second pressure chamber 2.
  • the first section 31 is located in the first pressure chamber 1, and the inlet valve 5 and the outlet valve 6 are disposed at the first pressure chamber 1.
  • the protruding member serves as a boundary point which divides the pressure chamber into a first pressure chamber 1 and a second pressure chamber 2.
  • the protruding member 8 shown in FIG. 2 is at a lower position than the protruding member 8' shown in FIG 1 , so that the plunger sleeve 3 is received in the first pressure chamber with a defined length (i.e., the first section).
  • the length of the plunger sleeve received in the first pressure chamber is increased in FIG. 2 , to solve the problem that in the fuel pumping stage of the high-pressure pump, the high-pressure fuel is likely to return to the low-pressure area through the plunger clearance, and the volumetric efficiency is reduced.
  • Two stages including a fuel pumping stage and a fuel sucking stage are involved in the operation of the high-pressure pump, which are specified as follows: As shown in FIG. 2 , in the fuel pumping stage, the plunger 4 moves from the second pressure chamber 2 towards the first pressure chamber 1, so that the pressure in the first pressure chamber 1 is higher than that in the second pressure chamber 2. In this case, a pressure difference is generated between the inside and the outside of the first section 31, which means the pressure in the first pressure chamber 1 is progressively decreased along a direction towards the second pressure chamber 2.
  • the main reason is that the outer side of the first section 31 of the plunger sleeve 3 is affected by the high and constant pressure in the first pressure chamber 1, and the inner side of the first section 31 of the plunger sleeve 3 is in communication with the second pressure chamber 2, and thus, the pressure at the inner side of the first section 31 of the plunger sleeve 3 is progressively decreased along a direction from the first pressure chamber 1 towards the second pressure chamber 2 and is less than the pressure applied to the outer side of the first section 31.
  • the first section 31 is deformed and contracted inwards, so that the clearance between the first section 31 of the plunger sleeve 3 and the plunger 4 is smaller than the machining clearance 7 in the plunger set (i.e., the original machining clearance between the plunger 4 and the plunger sleeve 3).
  • the plunger 4 moves from the first pressure chamber 1 towards the second pressure chamber 2, so that the pressure in the first pressure chamber 1 becomes equal to that in the second pressure chamber 2. Therefore, no pressure difference is generated between the inside and the outside of the first section 31, and the first section 31 is recovered to the shape before deformation from the inwardly contracted configuration in the fuel pumping stage, and the clearance between the first section 31 of the plunger sleeve 3 and the plunger 4 is equal to the clearance between the second section 32 of the plunger sleeve 3 and the plunger 4 (i.e., the initial state of the plunger sleeve 3), which are equal to the machining clearance 7 in the plunger set.
  • the machining clearance 7 in the plunger set has a width ranging from 1 ⁇ m to 15 ⁇ m.
  • the high-pressure pump of the present invention can have a larger plunger clearance in the fuel sucking stage, a less wear to the plunger set, and a longer service life, and can further reduce the machining clearance 7 in the plunger set to increase the volumetric efficiency.
  • the machining clearance 7 in the plunger set can be further reduced, to reduce the likelihood of backflow through the clearance, without increasing the weight or using more expensive materials.
  • the greater the fuel pumping pressure is the larger the adaptive deformation is, and the more significant the beneficial effects to the volumetric efficiency is, thereby effectively improving the fuel combustion utilization rate and reducing fuel consumption.
  • the inner diameter of the first section 31 of the plunger sleeve 3 is the same as that of the second section 32 of the plunger sleeve 3, and the outer diameter of the first section 31 of the plunger sleeve 3 is the same as or different from that of the second section 32 of the plunger sleeve 3.
  • the outer diameter of the first section 31 of the plunger sleeve 3 is different from that of the second section 32 of the plunger sleeve 3, so that the first section 31 is more likely to be deformed to contract in the fuel pumping stage.
  • the first section is connected to the second section through a transition section which facilitates in mounting the plunger sleeve in the pressure chamber, and the cross section of the transition section is shaped with one of a round corner, a right angle, a chamfer, a multi-section curve, and a multi-section line, or a combination of the multi-section curve and the multi-section line.
  • the plunger sleeve of the high-pressure pump includes a first section and a second section connected to the first section, the protruding member is disposed on the outer side of the second section close to the first section, and the first section is located in the first pressure chamber.
  • the position at which the protruding member is in interference fit to the pressure chamber is lower.
  • the first section is deformed and contracted inwards due to the pressure difference between the inside and the outside of the first section, and the clearance between the first section and the plunger is reduced, which effectively reduces the likelihood of backflow through the clearance.
  • the high-pressure pump of the present invention has a larger plunger clearance in the fuel sucking stage, a less wear to the plunger set, and a longer service life than the existing high-pressure pump. Therefore, it is possible to further reduce the machining clearance in the plunger set to increase the volumetric efficiency, without increasing the weight or using more expensive materials.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Reciprocating Pumps (AREA)
EP18741821.5A 2017-01-23 2018-01-23 High-pressure pump Active EP3572664B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201710058832.2A CN106762299B (zh) 2017-01-23 2017-01-23 高压泵
PCT/CN2018/073787 WO2018133876A1 (zh) 2017-01-23 2018-01-23 高压泵

Publications (3)

Publication Number Publication Date
EP3572664A1 EP3572664A1 (en) 2019-11-27
EP3572664A4 EP3572664A4 (en) 2020-01-01
EP3572664B1 true EP3572664B1 (en) 2022-05-18

Family

ID=58941822

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18741821.5A Active EP3572664B1 (en) 2017-01-23 2018-01-23 High-pressure pump

Country Status (3)

Country Link
EP (1) EP3572664B1 (zh)
CN (1) CN106762299B (zh)
WO (1) WO2018133876A1 (zh)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106762299B (zh) * 2017-01-23 2023-06-20 联合汽车电子有限公司 高压泵

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008086011A2 (en) * 2007-01-10 2008-07-17 Stanadyne Corporation Load ring mounting of pumping plunger

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07217742A (ja) * 1993-12-10 1995-08-15 Kayaba Ind Co Ltd ブッシュの取り付け方法
JP3652005B2 (ja) * 1996-03-27 2005-05-25 カヤバ工業株式会社 ブッシュの取り付け方法
DE102004063074B4 (de) * 2004-12-28 2013-03-07 Robert Bosch Gmbh Kolbenpumpe, insbesondere Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine
DE102008040090A1 (de) * 2008-07-02 2010-01-07 Robert Bosch Gmbh Hochdruckpumpe
CN102619660B (zh) * 2011-01-28 2015-06-24 株式会社电装 高压泵
WO2015032558A1 (en) * 2013-09-04 2015-03-12 Continental Automotive Gmbh High pressure pump
JP6368517B2 (ja) * 2014-03-28 2018-08-01 Ｋｙｂ株式会社 液圧回転機
CN204458157U (zh) * 2015-03-02 2015-07-08 北京博曼迪汽车科技有限公司 高压共轨油泵及其柱塞偶件装置
CN205225549U (zh) * 2015-12-02 2016-05-11 无锡威孚马山油泵油嘴有限公司 一种新型柱塞偶件
CN206439132U (zh) * 2017-01-23 2017-08-25 联合汽车电子有限公司 高压泵
CN106762299B (zh) * 2017-01-23 2023-06-20 联合汽车电子有限公司 高压泵

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008086011A2 (en) * 2007-01-10 2008-07-17 Stanadyne Corporation Load ring mounting of pumping plunger

Also Published As

Publication number Publication date
EP3572664A4 (en) 2020-01-01
CN106762299A (zh) 2017-05-31
EP3572664A1 (en) 2019-11-27
WO2018133876A1 (zh) 2018-07-26
CN106762299B (zh) 2023-06-20

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