WO2014190631A1 - 一种高压燃油泵驱动结构 - Google Patents

一种高压燃油泵驱动结构 Download PDF

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Publication number
WO2014190631A1
WO2014190631A1 PCT/CN2013/082616 CN2013082616W WO2014190631A1 WO 2014190631 A1 WO2014190631 A1 WO 2014190631A1 CN 2013082616 W CN2013082616 W CN 2013082616W WO 2014190631 A1 WO2014190631 A1 WO 2014190631A1
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WO
WIPO (PCT)
Prior art keywords
sleeve
pressure fuel
fuel pump
helical gear
pump drive
Prior art date
Application number
PCT/CN2013/082616
Other languages
English (en)
French (fr)
Inventor
胡志胜
靳素华
钱多德
胡必谦
孟祥山
祖炳峰
徐玉梁
徐勋
郑久林
Original Assignee
安徽江淮汽车股份有限公司
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 安徽江淮汽车股份有限公司 filed Critical 安徽江淮汽车股份有限公司
Priority to BR112015029593A priority Critical patent/BR112015029593A2/pt
Priority to RU2015154659A priority patent/RU2618361C1/ru
Priority to AU2013391197A priority patent/AU2013391197B2/en
Publication of WO2014190631A1 publication Critical patent/WO2014190631A1/zh

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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
    • 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

Definitions

  • the present invention relates to the field of engines, and more particularly to a high pressure fuel pump drive structure driven by a helical gear. Background technique
  • the timing system adopts helical gears
  • the helical gear receives a larger axial component than the spur gear, so the elimination of axial force and displacement compensation become the primary issues to be considered in the design, and if still With the cross-slider connection, the axial force is more pronounced when the engine accelerates, decelerates, or changes in load due to other conditions such as road bumps.
  • the cross slider is in the pump. The axial yaw between the shaft and the drive shaft is larger and more frequent, which not only makes it easier to wear and shortens the life, but also creates an impact between the pump shaft and the drive shaft, reducing the noise reduction effect of the helical gear.
  • An object of the present invention is to provide a structure capable of effectively withstanding and avoiding an axial force generated when a high pressure fuel pump is driven by a helical gear, and making the helical gear more suitable for driving an engine high pressure fuel pump, thereby reducing engine noise.
  • the present invention provides the following technical solutions:
  • An engine high-pressure fuel pump driving structure comprising: a helical gear with internal splines; a sleeve with external splines; a sliding sleeve; a fixing sleeve; the sleeve is fixedly mounted on a pump shaft of the high-pressure fuel pump,
  • An external spline of the sleeve cooperates with an internal spline of the helical gear to enable the helical gear to slide relative to the sleeve in an axial direction, and the sliding sleeve and the fixed sleeve are coaxially disposed
  • the first sliding sleeve is abutted against the helical gear, and a pre-compressed spring is disposed between the sliding sleeve and the fixed sleeve.
  • the fixing sleeve is fixed to a housing for closing the sprocket chamber.
  • the fixing sleeve is a separate member.
  • the spring is pre-compressed while the fixing sleeve is being mounted.
  • the sleeve is fixedly mounted to the pump shaft by a nut.
  • the diameter of the skirt of the nut is greater than the outer diameter of the sleeve.
  • a thrust piece is disposed between the helical gear and the flange, and the thrust piece and the flange are positioned by a positioning pin.
  • the sliding sleeve has an oil groove on an end surface of the helical gear.
  • the sliding sleeve is provided with a vent hole.
  • the sliding sleeve is provided with a circular hole
  • the fixing sleeve is provided with a waist hole
  • the circular hole and the waist hole have a limit extending through the circular hole and the waist hole pin.
  • the helical gear is driven to the pump shaft of the high pressure fuel pump by the spline coupling with the inner and outer sleeves of the sleeve.
  • the axial force toward the cylinder is transmitted to the flange and then transmitted.
  • the axial force toward the sprocket chamber tends to cause the helical gear to slide axially relative to the sleeve.
  • the axial force When the axial force is small, the axial force is offset by the spring preload, and when the axial force is compared When large, the kinetic energy generated by the relative sliding is converted into the potential energy of the spring by the sliding sleeve, which can effectively reduce the impact and vibration caused by the relative sliding. Therefore, no matter which side the axial force is directed, it will not act on the pump shaft, so that the high-pressure fuel pump can adapt to the cooperation with the helical gear, while the structure of the present invention does not substantially cause the impact due to the need to offset the axial force. And vibration, so that the advantages of stable helical gear transmission and low noise can be fully utilized.
  • the fixing sleeve is fixed to the casing for closing the sprocket chamber, and since the structure is integrally arranged along the axial direction of the pump shaft, it is ensured that the interference does not interfere with the timing chain, so that the entire structure can fully utilize the chain.
  • the fixing sleeve when used as a single component, when the maintenance is required, the fixing sleeve can be removed from the casing, that is, the sliding sleeve and the spring can be taken out without removing the casing, and the inspection is convenient.
  • the fixing sleeve pre-compacts the spring to mount the cartridge.
  • the nut is used to fix the sleeve to the pump shaft, so that the entire structure can be disassembled and assembled.
  • the diameter of the skirt of the nut is larger than the outer diameter of the sleeve, so that the skirt of the nut simultaneously serves as a limit structure of the helical gear to prevent the helical gear from slipping off the sleeve when the axial force is too large.
  • the thrust piece can provide cushioning to the axial force toward the cylinder and improve the wear resistance, and positioning by the positioning pin makes the disassembly and assembly more convenient.
  • the sliding sleeve has an oil groove on the end surface of the helical gear to supply lubricating oil between the helical gear and the sliding sleeve, so that the helical gear and the sliding sleeve are more wear-resistant.
  • vent hole on the sliding sleeve can ensure the balance of the air pressure inside and outside the sliding sleeve when the helical gear and the sleeve slide relative to each other to drive the sliding sleeve.
  • the stroke of the sliding sleeve (and thus the stroke of the helical gear) can be limited, and the waist hole can also serve as the oil inlet hole. Provides lubrication between the sleeve and the sleeve.
  • FIG. 1 is a front cross-sectional view showing a driving structure of an engine high pressure fuel pump according to an embodiment of the present invention
  • Fig. 2 is a front cross-sectional view similar to Fig. 1, and for clarity, peripheral components such as a cylinder and a casing are omitted;
  • Figure 3 is an exploded view of the engine high-pressure fuel pump drive structure of the embodiment of the present invention.
  • Figure 4 is a partial enlarged view of the portion I of Figure 2.
  • the high pressure fuel pump 2 is mounted to the cylinder 1 through a flange 3 having a shaft hole 31 through which the pump shaft 21 of the high pressure fuel pump 2 extends into the sprocket of the engine.
  • Room (unmarked), the timing wheel train is housed in the sprocket room.
  • the sleeve 4 is fitted over the pump shaft 21 and fastened by a nut 6 to achieve a fixed mounting of the sleeve 4 and the pump shaft 21.
  • the sleeve 4 can also be fitted over the pump shaft 21 by means of an interference fit, but from the standpoint of ease of assembly and disassembly, it is apparent that the nut is more advantageous.
  • the sleeve 4 has external splines
  • the helical gear 5 has internal splines
  • the outer splines of the sleeve 4 are in clearance fit with the internal splines of the bevel gear 5.
  • a timing chain (not shown) in the sprocket chamber transmits the driving force to the pump shaft 21 through the spline engagement between the helical gear 5 and the sleeve 4, thereby driving the high pressure fuel pump 2 to operate. Further, since the sleeve 4 and the helical gear 5 are clearance-fitted, the helical gear 5 can slide relative to the sleeve 4 in the axial direction.
  • the fixing sleeve 9 can be a separate member that is fixed to a housing 10 (for example, a sprocket housing, a flywheel housing, etc.) for closing the sprocket chamber by a screw, a rivet or the like, or is not a separate member but is cast, etc. It is fixed to the housing 10 in an integrally formed manner.
  • the fixing sleeve 9 is a separate member, which is fixed on the casing 10 by screws or the like, or an external thread is machined on the fixing sleeve 9.
  • a threaded hole is opened in the casing 10, and the fixing sleeve 9 is screwed into the sprocket chamber from the outside, and the fixing sleeve 9 pre-compresses the spring 8.
  • the fixing sleeve 9 needs to be unscrewed. 9 Unscrew, the fixing between the fixing sleeve 9 and the casing 10 is released, that is, the sliding sleeve 7 and the spring 8 in the sprocket chamber can be taken out, or the nut 6 can be unscrewed and replaced and adjusted, and the other parts are no longer needed.
  • the housing 10 is removed and the inspection is convenient.
  • the fixing sleeve 9 is a separate member, it is necessary to provide a sealing jaw between the fixing sleeve 9 and the housing 10.
  • the sliding sleeve 7 is coaxially fitted with the fixing sleeve 9, and the two are in a clearance fit so that the sliding sleeve 7 can slide axially relative to the fixing sleeve 9.
  • a pre-compressed spring 8 is arranged between the sliding sleeve 7 and the fixing sleeve 9.
  • the helical gear 5 will also bear axial force, and for example, when the engine is increasing speed, decelerating, bumping, etc., the helical gear 5 will change in axial force due to sudden load changes. .
  • axial force F1 towards the cylinder There are two directions of axial force, one is the axial force F1 towards the cylinder, and the other is the axial force F2 towards the sprocket chamber.
  • the spring 8 since the spring 8 is pre-compressed, in the initial state, the pre-tightening force of the spring 8 pushes the sliding sleeve 7 to the helical gear 5, and the helical gear 5 tends to abut against the flange 3 In the case where the axial force is the force F1 toward the cylinder 1, F1 is transmitted to the cylinder 1 without affecting the pump shaft 21. Since the helical gear 5 is rotated in the operating state, it is preferable to provide the thrust piece 11 between the flange 3 and the helical gear 5. Further, as can be seen in conjunction with Fig. 3, the thrust piece 11 and the flange 3 are positioned by the positioning pin 12 to prevent the thrust piece 11 from rotating.
  • the sliding sleeve 7 may move toward the fixing sleeve 9, it is preferable to open the vent hole 72 in the sliding sleeve 7 so that the internal air pressure of the sliding sleeve 7 is kept in line with the outside.
  • a plurality of oil grooves 711 are formed in the end surface of the sliding sleeve 7 against the end portion 71 of the helical gear 5 for lubrication between the end surface and the helical gear 5.
  • the sliding sleeve 7 is provided with a circular hole 73.
  • the fixing sleeve 9 is provided with a waist hole 91, and the limiting pin 13 penetrates the circular hole 73 and the waist hole 91, so that when the helical gear 5 slides
  • the limit pin 13 can only slide in the waist hole 91, thereby realizing the limit of the sliding stroke of the helical gear 5, preventing the violent impact when the axial force F2 is too large, and preventing
  • the helical gear 5 slides down on the sleeve 4, while the waist hole 91 can also serve as an oil inlet for providing lubrication to the contact surface between the sleeve 7 and the sleeve 9.
  • the diameter D1 of the skirt 61 of the nut 6 is larger than the outer diameter D2 of the sleeve 4, so that the skirt 61 can also play a defining role for the sliding stroke of the helical gear 5, preventing the helical gear 5 from being passed over the sleeve 4. The effect of slipping.
  • the high pressure fuel pump 2 is mounted on the flange 3
  • the thrust piece 11 is fitted on the pump shaft 21, and the positioning pin 12 is inserted to fix the thrust piece 11 to the flange.
  • the sleeve 4 is further assembled, the helical gear 5 is set on the sleeve 4, and then the nut 6 is tightened, and the assembled parts are taken as a whole, and are fixed to the cylinder 1 through the flange 3, which is convenient for subsequent Installation adjustments.
  • the sliding sleeve 7 is installed, the spring 8 is inserted, and the fixing sleeve 9 is attached to the casing 10, and the fixing sleeve 9 is simultaneously pre-compressed when the fixing sleeve 9 is mounted.
  • the flange 3, the high pressure fuel pump 2, the thrust piece 11, the sleeve 4, the helical gear 5, and the nut 6 can be used as long as the fixing sleeve 9 is loosened and the flange 3 is loosened.
  • One unit is removed and removed from the sprocket chamber without fear of dropping parts into the sprocket chamber during disassembly without disassembling the housing 10.
  • unscrew the nut 6. Remove the flange 3 to complete the disassembly of the entire structure, which is very convenient.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

一种发动机高压燃油泵驱动结构，包括：具有内花键的斜齿轮（5）；具有外花键的套管（4）；滑套（7）；固定套（9）；套管（4）固定安装在高压燃油泵的泵轴上，套管（4）的外花键与斜齿轮（5）的内花键间隙配合以使得斜齿轮（5）在轴向方向上能相对套管（4）滑动，滑套（7）与固定套（9）同轴套装在一起并能轴向相对滑动，滑套（7）的一端抵靠在斜齿轮（5）上，滑套（7）与固定套（9）之间设置预压紧的弹簧（8）。该结构能避免斜齿轮驱动所产生的轴向力，从而更适合于高压燃油泵，并降低噪音。

Description

一种高压燃油泵驱动结构
技术领域
本发明涉及发动机领域， 具体涉及一种通过斜齿轮驱动的高压燃油泵 驱动结构。 背景技术
发动机普遍应用于各种技术领域， 尤其是汽车领域。 随着国内外排放 法规的日益严格， 高压共轨燃油系统普遍应用于车用柴油发动机上。 高压 燃油泵通过正时系统齿轮或链轮、 皮带驱动。 近年来， 为了有效降低发动 机的噪音， 出现了将发动机的正时系统由原来的直齿轮改为斜齿轮驱动的 趋势， 例如在申请号： 201210078678.2、 申请日： 2012-03-22、 发明名称为
"柴油发动机机油泵传动系统" 的中国发明专利申请中， 在正时系统中就 采用了斜齿轮。
由于高压燃油泵的泵轴一般不能承受轴向力， 因此需要对传动过程中 产生的轴向力进行氏销或补偿。 在申请号： 200810107974.4、 申请曰： 2008-05-06、 发明名称为 "一种新型高压燃油泵传动机构" 的中国发明专利 中， 驱动轴与燃油泵的泵轴之间通过十字滑块传动， 从而消除了正时轮系 的轴向力和法向力的影响，提高了传动轴与泵轴之间的相对位移补偿能力， 且连接结构筒单。 但是， 如果正时系统采用斜齿轮的话， 相对于直齿轮， 斜齿轮所受到的轴向分力更大， 因此对轴向力的消除、 位移补偿成为设计 中需要考虑的首要问题， 而如果仍然采用十字滑块连接的话， 在发动机加 速运转、减速运转或由于其它情况的变化例如道路颠簸而引起载荷突变时， 轴向力的影响更加显著， 而在频繁载荷突变情况下， 十字滑块在泵轴和驱 动轴之间的轴向窜动量更大更频繁， 不仅更容易磨损而缩短寿命， 而且会 在泵轴与驱动轴之间产生撞击， 降低了斜齿轮的降噪效果。
在申请号： 201210042389.7、 申请日： 2012-02-23、 发明名称为 "一种 用于发动机的喷油泵及发动机" 的中国发明专利申请中， 通过在喷油泵齿 轮的轴心孔加工出内花键， 在凸轮轴上安装外花键， 利用内外花键的配合 来传递扭矩， 而轴向方向上的定位需要定位件 （具体地为定位螺釘或者定 位销） 穿过齿轮座和轴瓦后与喷油泵齿轮周向方向上的凹槽配合。 也就是 说， 如果采用斜齿轮的话， 则轴向分力会传递给定位件， 然后再传递给齿 轮座被其 4氏消， 而由于定位件与喷油泵齿轮周向方向上的凹槽之间为刚性 接触， 随着时间的推移， 定位件与凹槽之间会产生磨损， 从而造成喷油泵 齿轮的轴向窜动， 产生噪声。 发明内容
本发明的目的是提供一种能够有效承受、 避免高压燃油泵采用斜齿轮 驱动时产生的轴向力的结构，使斜齿轮更加适用于驱动发动机高压燃油泵， 从而降低发动机噪音。
为实现上述目的， 本发明提供了如下技术方案：
一种发动机高压燃油泵驱动结构， 包括： 具有内花键的斜齿轮； 具有 外花键的套管； 滑套； 固定套； 所述套管固定安装在所述高压燃油泵的泵 轴上， 所述套管的外花键与所述斜齿轮的内花键间隙配合以使所述斜齿轮 在轴向方向上能够相对所述套管滑动， 所述滑套与所述固定套同轴套装在 一起并能够轴向相对滑动， 所述滑套的一端抵靠在所述斜齿轮上， 所述滑 套与所述固定套之间设置有预压紧的弹簧。
优选地， 所述固定套固定在用于封闭所述链轮室的壳体上。
优选地， 所述固定套为一单独构件。
优选地， 在安装所述固定套的同时对所述弹簧进行预压紧。
优选地， 所述套管是通过螺母固定安装到所述泵轴上的。
优选地， 所述螺母的裙边的直径大于所述套管的外径。
优选地， 所述斜齿轮与所述法兰盘之间设置有止推片， 所述止推片与 所述法兰盘通过定位销定位。
优选地， 所述滑套抵靠所述斜齿轮的端面上开有油槽。
优选地， 所述滑套上开有通气孔。
优选地， 所述滑套上开有圓孔， 所述固定套上开有腰型孔， 所述圓孔 和所述腰型孔中具有贯穿所述圓孔和所述腰型孔的限位销。 在本发明中， 斜齿轮通过与套管的内、 外花键配合实现向高压燃油泵 的泵轴传动， 当斜齿轮发生载荷突变时， 朝向气缸的轴向力被传递到法兰 盘进而传递到气缸上， 而朝向链轮室的轴向力倾向于使斜齿轮与套管发生 轴向相对滑动， 轴向力较小时该轴向力被弹簧预紧力所抵消， 而当轴向力 较大时， 相对滑动所产生的动能通过滑套转化为弹簧的势能， 能够有效降 低由于相对滑动而产生的撞击、 振动。 因此无论轴向力朝向哪边， 均不会 作用到泵轴上， 使得高压燃油泵能够适应与斜齿轮的配合， 而同时本发明 的结构基本不会造成由于需要抵消轴向力而产生的撞击和振动， 因此能够 充分发挥斜齿轮传动平稳、 噪声低的优点。
进一步地， 固定套固定到用于封闭链轮室的壳体上， 而且由于该结构 整体沿着泵轴的轴向布置， 保证了不会与正时链条产生干涉， 使得整个结 构能够充分利用链轮室的狭小空间。
进一步地， 将固定套作为一个单独构件， 则需要检修时， 只需将固定 套从壳体上拆下， 即能够将滑套、 弹簧取出， 而不需要拆除壳体， 检修方 便。
进一步地， 在安装壳体对链轮室进行封闭的同时， 固定套对弹簧进行 预压紧， 安装筒单。
进一步地， 采用螺母将套管固定到泵轴上， 使得整个结构拆装筒单。 进一步地， 螺母的裙边的直径大于套管的外径， 使得螺母的裙边同时 作为斜齿轮的限位结构， 防止轴向力过大时斜齿轮从套管上滑落。
进一步地， 止推片能够对朝向气缸的轴向力提供緩沖， 并且提高耐磨 性能， 而采用定位销进行定位使得拆装更方便。
进一步地， 滑套抵靠斜齿轮的端面上开有油槽能够向斜齿轮与滑套之 间提供润滑油， 使得斜齿轮与滑套之间更耐磨。
进一步地， 滑套上的通气孔能够使得斜齿轮与套管发生相对滑动而带 动滑套运动时， 保证滑套内、 外气压平衡。
进一步地， 滑套上的圓孔与固定套上的腰型孔中插入销后， 能够对滑 套的行程 （进而对斜齿轮的行程） 进行限位， 同时腰型孔还能作为进油孔 为滑套和固定套之间提供润滑油。 附图说明
图 1是本发明的实施例的发动机高压燃油泵驱动结构的主视剖视图； 图 2是类似于图 1的主视剖视图， 为了清晰， 气缸、 壳体等周边部件 被省略；
图 3是本发明的实施例的发动机高压燃油泵驱动结构的爆炸图； 图 4是图 2中的 I部分的局部放大图。
上图中标记说明： 气缸 1、 高压燃油泵 2、 泵轴 21、 法兰盘 3、 轴孔 31、 套管 4、 斜齿轮 5、 螺母 6、 裙边 61、 滑套 7、 端部 71、 油槽 711、 通 气孔 72、 圓孔 73、 弹簧 8、 固定套 9、 腰型孔 91、 壳体 10、 止推片 11、 定位销 12、 限位销 13。 具体实施方式
接下来将结合附图对本发明的具体实施例作进一步详细描述。
结合图 1至图 3 , 高压燃油泵 2通过法兰盘 3安装到气缸 1上， 法兰 盘 3具有轴孔 31 , 高压燃油泵 2的泵轴 21穿过轴孔 31伸入发动机的链轮 室 （未标记） ， 链轮室中容纳有正时轮系。 在链轮室中， 套管 4套装在泵 轴 21上， 并通过螺母 6紧固， 实现套管 4与泵轴 21的固定安装。 本领域 普通技术人员能够很容易地想象， 套管 4还能够通过过盈配合的方式套装 在泵轴 21上， 但从拆装方便的角度看， 显然采用螺母更具优势。 套管 4具 有外花键， 斜齿轮 5具有内花键， 套管 4的外花键与斜齿轮 5的内花键间 隙配合。 链轮室中的正时链条 （未示出 ) 将驱动力通过斜齿轮 5、 套管 4 之间的花键配合传递给泵轴 21 , 从而驱动高压燃油泵 2工作。 并且， 由于 套管 4与斜齿轮 5为间隙配合， 因此在轴向方向上， 斜齿轮 5能够相对套 管 4滑动。在图示中斜齿轮 5的右侧，滑套 7的端部 71抵靠在斜齿轮 5上。 固定套 9能够是一个单独构件， 通过螺釘、 铆釘等连接件固定到用于封闭 链轮室的壳体 10 (例如链轮壳、 飞轮壳等） 上， 或者不是一个单独构件而 是通过铸造等一体成型的方式固定到壳体 10上。优选固定套 9为一单独构 件，采用螺釘等方式固定在壳体 10上，或者，在固定套 9上加工出外螺纹， 在壳体 10上开螺纹孔， 从外部将固定套 9拧入链轮室， 同时固定套 9对弹 簧 8进行预压紧， 需要对驱动结构进行检修时， 只需拧下螺釘或者将固定 套 9拧下， 解除固定套 9与壳体 10之间的固定， 即能够将链轮室内的滑套 7、 弹簧 8取出， 或者拧下螺母 6后对其它零件进行更换、 调整， 而不再需 要将壳体 10拆下， 检修方便。 当然， 当固定套 9为单独构件时， 需要在固 定套 9与壳体 10之间设置密封圏。 滑套 7与固定套 9同轴套装在一起， 并 且两者为间隙配合因而滑套 7能够相对固定套 9轴向滑动。 同时在滑套 7 与固定套 9之间设置有预压紧的弹簧 8。
参考图 2, 在正常工作状态下， 斜齿轮 5也会承受轴向力， 而例如当 发动机增速、 减速、 道路颠簸等情况下， 斜齿轮 5上会由于载荷突变而产 生轴向力的变化。 轴向力的方向有两个， 一个是朝向气缸的轴向力 F1 , — 个是朝向链轮室的轴向力 F2。 在本发明中， 由于弹簧 8是被预压紧的， 因 此在初始状态下， 弹簧 8的预紧力将滑套 7顶向斜齿轮 5 , 进而斜齿轮 5 倾向于抵靠在法兰盘 3上， 在轴向力为朝向气缸 1 的力 F1 的情况下， F1 被传递到气缸 1上， 而不会对泵轴 21造成影响。 由于斜齿轮 5在工作状态 下是转动的， 因此优选在法兰盘 3与斜齿轮 5之间设置止推片 11。 而且结 合图 3可见， 止推片 11与法兰盘 3通过定位销 12实现定位， 防止止推片 11旋转。 当斜齿轮 5受到朝向链轮室的轴向力 F2的作用时， 当 F2较小时， F2能够被弹簧 8的预紧力抵消， 因此斜齿轮 5轴向方向上不会发生滑动。 即使当 F2较大而超过弹簧 8的预紧力时，由于斜齿轮 5与套管 4之间是间 隙配合， 因此斜齿轮 5会稍稍向着壳体 10的方向滑动， 推动滑套 7进一步 压缩弹簧 8 , 斜齿轮 5的动能转化为弹簧 8的势能， 在整个结构中不会发 生撞击产生噪音。 并且， 由于滑套 7可能会向着固定套 9运动， 因此优选 在滑套 7上开通气孔 72, 以使滑套 7的内部气压与外部保持一致。
参考图 3 ,滑套 7抵靠斜齿轮 5的端部 71的端面上开有多个油槽 711 , 用于该端面与斜齿轮 5之间的润滑。 结合图 3和图 4, 可见滑套 7上开有 圓孔 73 , 固定套 9上开有腰型孔 91 , 限位销 13贯穿圓孔 73和腰型孔 91 , 因此在斜齿轮 5滑动时， 限位销 13只能在腰型孔 91 内滑动， 从而实现了 对斜齿轮 5的滑动行程的限位， 防止轴向力 F2过大时的猛烈撞击， 防止了 斜齿轮 5在套管 4上滑落， 同时腰型孔 91还能够作为进油孔为滑套 7与固 定套 9之间的接触面提供润滑。
参考图 4, 螺母 6的裙边 61的直径 D1大于套管 4的外径 D2 , 因此裙 边 61也能够起到对斜齿轮 5的滑动行程的限定作用， 防止斜齿轮 5从套管 4上滑落的作用。
再次回到图 3 , 在安装时， 首先， 将高压燃油泵 2安装到法兰盘 3上， 在泵轴 21上套装止推片 11 ,插入定位销 12以将止推片 11固定于法兰盘 3 上， 再套装套管 4, 在套管 4上套装斜齿轮 5 , 然后拧紧螺母 6, 将以上装 配好后的各零件作为一个整体， 通过法兰盘 3 固定在气缸 1上， 方便后续 安装调整。 然后， 安装滑套 7 , 插入弹簧 8 , 固定套 9安装到壳体 10上， 在安装固定套 9时固定套 9同时对弹簧 8进行预压紧。 在需要维修进行拆 卸时， 只要松开固定套 9、 松开法兰盘 3 , 就能够将法兰盘 3、 高压燃油泵 2、 止推片 11、 套管 4、 斜齿轮 5和螺母 6作为一个整体取下， 从链轮室中 取出而不必担心拆卸过程中零件掉落入链轮室， 同时不用拆卸壳体 10。 需 要进一步拆解、 更换零件时， 拧下螺母 6、 卸下法兰盘 3就能完成整个结 构的拆卸， 十分方便。
虽然本发明是结合以上实施例进行描述的， 但本发明并不限定于上述 实施例， 而只受权利要求的限定， 本领域普通技术人员能够容易地对其进 行修改和变化， 但并不离开本发明的实质构思和范围。

Claims

权 利 要 求
1. 一种发动机高压燃油泵驱动结构， 其特征在于， 包括：
具有内花键的斜齿轮；
具有外花键的套管；
滑套；
固定套；
所述套管固定安装在所述高压燃油泵的泵轴上， 所述套管的外花键与 所述斜齿轮的内花键间隙配合以使所述斜齿轮在轴向方向上能够相对所述 套管滑动， 所述滑套与所述固定套同轴套装在一起并能够轴向相对滑动， 所述滑套的一端抵靠在所述斜齿轮上， 所述滑套与所述固定套之间设置有 预压紧的弹簧。
2. 根据权利要求 1所述的发动机高压燃油泵驱动结构， 其特征在于， 所述固定套固定在用于封闭所述链轮室的壳体上。
3. 根据权利要求 1所述的发动机高压燃油泵驱动结构， 其特征在于， 所述固定套为一单独构件。
4. 根据权利要求 2所述的发动机高压燃油泵驱动结构， 其特征在于， 在安装所述固定套的同时对所述弹簧进行预压紧。
5. 根据权利要求 1所述的发动机高压燃油泵驱动结构， 其特征在于， 所述套管是通过螺母固定安装到所述泵轴上的。
6. 根据权利要求 5所述的发动机高压燃油泵驱动结构， 其特征在于， 所述螺母的裙边的直径大于所述套管的外径。
7. 根据权利要求 1 至 6 中的任一项所述的发动机高压燃油泵驱动结 构， 其特征在于， 所述斜齿轮与所述法兰盘之间设置有止推片， 所述止推 片与所述法兰盘通过定位销定位。
8. 根据权利要求 1 至 6 中的任一项所述的发动机高压燃油泵驱动结 构， 其特征在于， 所述滑套抵靠所述斜齿轮的端面上开有油槽。
9. 根据权利要求 1 至 6 中的任一项所述的发动机高压燃油泵驱动结 构， 其特征在于， 所述滑套上开有通气孔。
10. 根据权利要求 1 至 6 中的任一项所述的发动机高压燃油泵驱动结 构， 其特征在于， 所述滑套上开有圓孔， 所述固定套上开有腰型孔， 所述 圓孔和所述腰型孔中具有贯穿所述圓孔和所述腰型孔的限位销。
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