WO2016011851A1 - 一种大型柴油机十字头组件 - Google Patents

一种大型柴油机十字头组件 Download PDF

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Publication number
WO2016011851A1
WO2016011851A1 PCT/CN2015/080455 CN2015080455W WO2016011851A1 WO 2016011851 A1 WO2016011851 A1 WO 2016011851A1 CN 2015080455 W CN2015080455 W CN 2015080455W WO 2016011851 A1 WO2016011851 A1 WO 2016011851A1
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WIPO (PCT)
Prior art keywords
hole
crosshead
crosshead pin
pin
oil
Prior art date
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Ceased
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PCT/CN2015/080455
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English (en)
French (fr)
Inventor
唐文献
潘志刚
张建
吴朝晖
李大宝
王筱蓉
苏世杰
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Jiangsu University of Science and Technology
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Jiangsu University of Science and Technology
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Priority to US15/316,749 priority Critical patent/US9885380B2/en
Publication of WO2016011851A1 publication Critical patent/WO2016011851A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C5/00—Crossheads; Constructions of connecting-rod heads or piston-rod connections rigid with crossheads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/1085—Channels or passages to recirculate the liquid in the bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/22—Internal combustion engines

Definitions

  • the invention belongs to the field of mechanical design and relates to the structure of a crosshead assembly of a large low-speed two-stroke diesel engine.
  • Crosshead assemblies are commonly used in large low-speed two-stroke diesel engines. It is fixed at the lower end of the piston rod, and is connected with the small end bearing of the connecting rod through the crosshead pin in the crosshead assembly, and can effectively transmit the power received by the piston to the connecting rod and the crankshaft. At the same time, the side thrust generated during the working process of the crank link mechanism is also transmitted to the guide plates fixed on both sides of the frame by the sliders on both sides of the crosshead pin in the crosshead assembly, thereby improving the working conditions of the piston and the cylinder liner, and ensuring the working condition of the piston and the cylinder liner.
  • the center of the piston maintains a good coaxiality with the center of the cylinder.
  • the crosshead assembly in the prior design has the following disadvantages: (1) the crosshead pin has a large weight, and the reciprocating inertia force generated when reciprocating up and down is large, which increases the load on the crankshaft linkage mechanism, and also gives The assembly increases the difficulty; (2) the friction between the parts with relative motion in the crosshead assembly is large, generating more heat, but the heat dissipation effect is poor, and the parts are prone to thermal fatigue and then failure; (3) existing In the design, the sliding surfaces of the two sliding surfaces of the slider are used to relieve friction and wear, but in the event of severe wear, the entire slider needs to be replaced, which greatly wastes materials and increases maintenance costs.
  • the object of the present invention is to overcome the defects and deficiencies of the crosshead assembly in the above prior art, and to provide a cross which is light in structure, sufficient in oil supply, good in heat dissipation, easy to wear and wear, and suitable for a large low-speed two-stroke diesel engine. Head assembly.
  • a large diesel crosshead assembly comprising a crosshead pin 1, a slider 2, a wear plate 3, a sealing cover 4 and a sleeve 5 forming an "H" shaped longitudinal cross section
  • said Cross pin 1 is a cylinder having a petal-shaped through hole 112
  • the left and right outer ends of the crosshead pin 1 are respectively provided with a connecting slider 2
  • the petal-shaped through hole 112 of the crosshead pin 1 is inserted into the connecting sleeve 5 to form a back.
  • a lubricating oil passage cavity the left and right end faces of the crosshead pin 1 are respectively connected with a sealing cover 4 for sealing the oil passage cavity, and the front and rear ends of the slider 2 are respectively connected with a wear plate 3;
  • the crosshead pin 1 is a cylinder having a petal-shaped through hole 112, and the front and rear outer circumferential surfaces of the crosshead pin 1 are symmetrically opened with a plane 101 matching the slider 2, each plane
  • the oil hole 102 is connected to the petal-shaped through hole 112 of the crosshead pin 1.
  • the upper outer circumferential surface of the crosshead pin 1 is provided with a rectangular plane 103 for positioning the piston rod, and the rectangular plane 103 is provided with two sides on the center of the rectangular plane 103.
  • a piston rod threaded hole 104 connecting the piston rod and four piston rod oil return holes 106 communicating with the petal-shaped through hole 112 of the crosshead pin 1 and a piston rod oil inlet hole 105 at the center of the rectangular plane 103, the crosshead pin 1 a crosshead pin oil inlet 107 and a crosshead oil drain hole 108 having a direction perpendicular to the rectangular plane 103 and communicating with the petal shaped through hole 112 of the crosshead pin 1 are provided on the outer circumferential surface of the left and right ends;
  • the left end end surface of the crosshead pin 1 is provided with an axial deep hole 109 parallel to the axis and communicating with the piston rod oil return hole 106 from the upper portion of the shaft center, and is disposed on the outer circumferential surface of the starting end of the axial deep hole 109.
  • the petal-shaped through hole 112 opened in the crosshead pin 1 is in the shape of a plum blossom, and the petal-shaped through holes 112 are communicated by the open spiral through groove 115, and are evenly arranged on the central circumferential surface of the crosshead pin 1 a bearing oil inlet hole 114 connecting the petal-shaped through hole 112 for lubricating and cooling the bearing pad between the crosshead pin 1 and the small end of the connecting rod;
  • the slider 2 is composed of a thin waist plate in the middle and a long strip at the front and rear ends.
  • the long waist plate is provided with a long hole 201 matching the two ends of the cross pin 1 and the long hole 201
  • Four trapezoidal weight reducing holes 202 are uniformly arranged around the circumference, and the width of the elongated strip is larger than the thickness of the thin waist plate;
  • a slider-side oil hole 203 communicating with the long hole 201 is defined in a middle portion of the long strip-shaped plate at the rear end, and a slider oil hole communicating with the long hole 201 is formed on the upper waist-shaped curved surface of the thin waist plate. 204;
  • the wear plate 3 is in the shape of a channel steel, fits on the long strip plate, and is connected with the long strip plate through the wear plate screw 7 and the four counterbore 301 uniformly disposed on the working surface thereof.
  • the working surface of the grinding plate 3 is also cast with a wear-resistant alloy, and the wear plate 3 is provided with a wear plate oil inlet hole 302 in the center thereof, and the working surface of the wear plate 3 is opened with an oil groove 303 communicating with the wear plate oil inlet hole 302.
  • the sealing cover is provided with a central hole 401 having the same diameter as the inner diameter of the sleeve 5, and four sealing cover screw positioning holes 402 are evenly disposed on the circumference of the central hole 401, and the sealing cover screw 6 passes through the four sealing cover screws.
  • the positioning hole 402 fixes the sealing cover 4 to the left and right end faces of the crosshead pin 1 for sealing the oil hole inside the crosshead pin 1, preventing leakage of the cooling oil, and at the same time not closing the sleeve 5, ensuring that the through hole of the sleeve 5 can be Air contact for improved cooling.
  • the length of the sleeve 5 is the same as the length of the crosshead pin 1, and the outer diameter thereof is slightly larger than the inner diameter of the petal-shaped through hole 112 of the crosshead pin 1.
  • the crosshead pin has a petal-shaped through hole which communicates with each other by a spiral passage groove, and the pin shaft is lightened, which reduces the influence on the load of the crank link mechanism and reduces the assembly difficulty.
  • the crosshead pin adopts the sleeve and the petal-shaped through hole interference fit structure, the contact area between the internal lubricating oil and the pin shaft increases, and the sleeve is directly in contact with the air, and the cooling and heat dissipation effect is better.
  • the outer side of the slider can be replaced with a wearable plate. Once the serious wear occurs, the entire slider can be replaced, and the wear plate can be replaced. It has good interchangeability, economy and convenience.
  • Figure 1 is a schematic view of the structure of the present invention
  • Figure 2 is a front elevational view of the present invention of Figure 1;
  • Figure 3 is a left side view of the present invention of Figure 1;
  • Figure 4 is a plan view of the present invention of Figure 1;
  • Figure 5 is a cross-sectional view taken along line A-A of Figure 2;
  • Figure 6 is a cross-sectional view taken along line B-B of Figure 4.
  • Figure 7 is a schematic structural view of a crosshead pin
  • Figure 8 is a front elevational view of the crosshead pin of Figure 7;
  • Figure 9 is a plan view of the crosshead pin of Figure 7.
  • Figure 10 is a left side view of the crosshead pin of Figure 7;
  • Figure 11 is a cross-sectional view taken along line C-C of Figure 9;
  • Figure 12 is a schematic view of the structure of the slider
  • Figure 13 is a front elevational view of the slider of Figure 12;
  • Figure 14 is a left side view of the slider of Figure 12;
  • Figure 15 is a plan view of the slider of Figure 12;
  • Figure 16 is a schematic view showing the structure of the wear plate
  • Figure 17 is a front elevational view of the wear plate of Figure 16;
  • Figure 18 is a cross-sectional view taken along line D-D of Figure 17;
  • Figure 19 is a front view of the sealing cover
  • 1 - cross pin 101 - plane, 102 - oil hole, 103 - rectangular plane, 104 - piston rod threaded hole, 105 - piston rod oil inlet, 106 - piston rod oil return hole, 107 - cross pin Oil inlet hole, 108—cross head pin drain hole, 109—axial deep hole, 110—shallow hole, 111—through hole, 112—petal shaped through hole, 113—sealing cap screw threaded hole, 114—bearing bush oil Hole, 115—spiral channel, 2—slider, 201—long hole, 202—weight reduction hole, 203—slider side oil hole, 204—slider oil hole, 3—wear plate, 301—sink hole, 302—wear plate oil inlet hole, 303—oil groove 4—sealing cap, 401—central hole, 402—sealing cap screw positioning hole, 5-sleeve, 6—seal cap screw, 7—wear plate screw.
  • inside and outside means that the orientation toward the inside of the component is internal with respect to the component itself, and vice versa, rather than the specific definition of the components of the present invention.
  • left and right as used in the present invention means that when the reader is facing the drawing, the left side of the reader is left and the right side of the reader is right instead of the specific definition of the components of the present invention.
  • connection may be a direct connection between components or an indirect connection between components through other components.
  • FIG. 1 to FIG. 6 are respectively a structural and structural view of a large diesel crosshead assembly according to the present invention.
  • the crosshead assembly comprises a crosshead pin 1, a slider 2, a wear plate 3, and a sealing cover 4.
  • the sleeve 5 constitutes an "H"-shaped structure with a longitudinal cross-section
  • the crosshead pin 1 is a cylinder having a petal-shaped through hole 112, and the left and right ends of the crosshead pin 1 are respectively sleeved and connected.
  • Block 2 the petal-shaped through hole 112 of the crosshead pin 1 is inserted into the connecting sleeve 5 to form an oil return passage cavity, and the left and right end faces of the crosshead pin 1 are respectively connected with a sealing cover 4 for sealing the oil passage cavity.
  • the front and rear ends of the slider 2 are respectively connected There are wear plates 3.
  • the crosshead pin 1 is a cylinder having a petal-shaped through hole 112, and the left and right ends of the crosshead pin 1 are front and rear outer circumferential surfaces.
  • a plane 101 matching the slider 2 is symmetrically opened at the center, and each of the planes 101 is provided with an oil hole 102 communicating with the petal-shaped through hole 112 of the crosshead pin 1.
  • the upper outer circumferential surface of the crosshead pin 1 is provided for a rectangular plane 103 on which the piston rod is positioned.
  • the rectangular plane 103 is provided with two piston rod threaded holes 104 for connecting the piston rod and four piston rod oil return holes 106 for communicating the crosshead 112 of the crosshead pin 1 and a piston rod oil inlet hole 105 located at the center of the rectangular plane 103, and a crosshead pin having a direction perpendicular to the rectangular plane 103 and communicating with the petal-shaped through hole 112 of the crosshead pin 1 on the outer circumferential surface of the left and right ends of the crosshead pin 1 Oil inlet hole 107 and crosshead pin drain hole 108.
  • the left end surface of the crosshead pin 1 is provided with an axial deep hole 109 parallel to the axis and communicating with the piston rod oil return hole 106 from the upper portion of the shaft center, and is perpendicular to the outer circumferential surface of the starting end of the axial deep hole 109.
  • a shallow hole 110 that communicates with each other.
  • the corresponding shallow hole 110 rotates counterclockwise about the axis, and a through hole 111 that radially penetrates the crosshead pin 1 and communicates with the shallow hole 110 is defined at a position away from the shallow hole 110.
  • the petal-shaped through hole 112 provided in the crosshead pin 1 is in the shape of a plum blossom, and the petal-shaped through holes 112 are communicated by the opened spiral through groove 115, and three connected petals are evenly arranged on the central circumferential surface of the crosshead pin 1.
  • the bushing inlet hole 112 has an oil inlet hole 114 for lubricating and cooling the bearing pad between the crosshead pin 1 and the small end of the connecting rod.
  • the slider 2 is composed of a middle thin waist plate and a longitudinal strip at the front and rear ends, and a thin waist plate is arranged in the middle.
  • An oblong hole 201 matched with both ends of the cross pin 1 , and four trapezoidal weight reducing holes 202 are uniformly formed around the oblong hole 201 , the width of the elongated plate is larger than the thickness of the thin waist plate;
  • the middle portion of the long strip plate is provided with a slider side oil hole 203 communicating with the oblong hole 201, and the upper waist portion of the thin waist plate is opened and long.
  • the oil hole 204 of the slider communicating with the circular hole 201.
  • the wear plate 3 is in the shape of a channel steel, fits on the long strip plate, and works through the wear plate screw 7 and the same.
  • the four counterbore 301 uniformly arranged on the surface are connected with the long strip plate, and the working surface of the wear plate 3 is also cast with a wear-resistant alloy, and the wear plate 3 is provided with a wear plate oil inlet hole 302 in the center, and the wear plate 3
  • the working surface is provided with an oil groove 303 communicating with the wear plate oil inlet hole 302 for lubricating the working surface of the sliding plate wear plate 3 to reduce friction and wear.
  • FIG. 19 which is a schematic structural view of the sealing cover 4, the sealing cover 4 is provided with a central hole 401 having the same diameter as the inner diameter of the sleeve 5, and four sealing cap screws are evenly disposed on the circumference of the central hole 401.
  • the positioning hole 402 the sealing cover screw 6 passes through the four sealing cover screw positioning holes 402 to fix the sealing cover 4 to the left and right end faces of the crosshead pin 1, for sealing the oil hole inside the crosshead pin 1, preventing the leakage of the cooling oil, and at the same time
  • the sleeve 5 is not closed, and the through hole inside the sleeve 5 is ensured to be in contact with the air to enhance the cooling effect.
  • the length of the sleeve 5 is the same as the length of the crosshead pin 1, and the outer diameter thereof is slightly larger than the inner diameter of the petal-shaped through hole 112 of the crosshead pin 1.
  • the sleeve 5 and the petal-shaped through hole 112 of the crosshead pin 1 are matched by a red sleeve process kit, and the left and right end faces of the sleeve 5 and the crosshead pin are ensured after being inserted. 1 The left and right ends are flush, and then the slider 2 is installed at the left and right ends of the cross pin 1.
  • the oil hole 204 of the slider 2 and the cross pin on the cross pin 1 are respectively ensured.
  • the oil inlet hole 107 and the crosshead pin drain hole 108 are aligned to ensure the smooth flow of the oil passage.
  • the sealing cover 4 is fixed to the end faces of the crosshead pin 1 by using the sealing cover screw 6.
  • the fixing rod 2 and the sealing crosshead pin 1 have an oil hole inside, and the wear plate 3 is fixedly connected to the outer side of the long strip of the slider 2 by the wear plate screw 7, and the assembly process of the crosshead assembly is completed.
  • the upper rectangular plane 103 of the crosshead pin 1 is engaged with the bottom surface of the piston rod, and the piston rod is fixed by screws to the screw hole 104 of the piston rod on the upper rectangular plane 103 of the crosshead pin 1, the middle arc of the crosshead pin 1
  • the surface is matched with the small end of the connecting rod, and the working surface of the wear plate 3 at the front and rear ends of the sliding block 2 cooperates with the crosshead guide plate in the diesel engine frame, and the wear plate 3 has a relative slip with the guide plate in the guiding direction of the crosshead guide plate. .
  • a large amount of heat will be generated between the relatively moving parts due to friction. If it cannot be cooled in time, the parts will be damaged, which may affect the normal operation of the diesel engine.
  • the oil circuit system of the present invention can effectively cool and lubricate the above components. As shown in FIG. 7 to FIG. 18, the lubricating oil enters the oil hole 204 of the slider on the upper part of the slider 2 on the right side of the crosshead assembly, and slides along the slide.
  • the block oil hole 204 enters the crosshead pin oil inlet hole 107 at the right end of the crosshead pin 1, and then enters the petal-shaped through hole 112 inside the pin shaft, the petal-shaped through hole 112 and the sleeve 5, and the crosshead pin 1
  • the sealing cover 4 of the left and right end faces forms a closed oil passage space, and the lubricating oil fills the entire closed space through the spiral passage groove 115 between the petal-shaped through holes 112, and a part of the lubricating oil filled in the closed space is positioned by the upper end of the crosshead pin 1
  • the piston rod oil inlet 105 at the center of the face 103 enters the piston head to cool the piston head.
  • the lubricating oil in the axial deep hole 109 enters the shallow hole 110 perpendicularly intersecting the starting end thereof, and the lubricating oil entering the shallow hole 110 enters the through hole 111 which intersects the shallow hole 110 perpendicularly, the through hole 111 and the cross pin pin 1
  • the crosshead pin drain hole 108 on the left side is in communication, and the lubricating oil finally enters the oil hole 204 of the upper slider of the slider 2 through the crosshead drain port 108 of the crosshead pin 1 to release the lubricating oil.
  • the axial deep hole 109 formed on the crosshead, the shallow hole 110 intersecting the axial deep hole 109, and the through hole 111 intersecting the shallow hole 110 are sealed by a sealing plug to ensure the cross pin 1
  • the internal lubricating oil can only be vented from the crosshead pin drain hole 108 at the end of the crosshead pin 1.
  • the lubricating oil can be cooled and lubricated in time for each component having a relative motion relationship, and the inner wall of the sleeve 5 is directly in contact with the air, and the heat dissipation effect is better, effectively preventing the components from being caused by excessive temperature.
  • the connection between the inside of the crosshead pin 1 and the interference fit of the sleeve 5 can ensure the normal operation of the crosshead assembly under the condition of reducing the weight of the crosshead assembly, and fully reduce the transmission of the crankshaft mechanism. influences.
  • the slider 2 in the crosshead assembly continuously performs the sliding friction of the shifting during the working process, and the wear is more serious.
  • the slider 2 is seriously worn, it is only necessary to replace the wear plate 3 on the long strip of the slider 2, and it is not necessary to replace the entire slider 2, which has good interchangeability, economy and convenience.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Abstract

公开了一种大型柴油机十字头组件。十字头组件由十字头销（1），滑块（2），耐磨板（3），密封盖（4）和套筒（5）构成，其纵横截面均为"H"形结构；十字头销（1）为开设有花瓣形通孔的圆柱体；十字头销（1）的左右两端外圆上分别套装连接滑块（2）；十字头销（1）的花瓣形通孔（112）中穿插连接套筒（5）形成进回油油路腔体；十字头销（1）的左右两端面上分别连接有用于密封油路腔体的密封盖（4）；滑块（2）的前后两端分别连接有耐磨板（3）。该十字头组件具有良好互换性、经济性、便捷性。

Description

一种大型柴油机十字头组件 技术领域
本发明属于机械设计领域，涉及一种大型低速二冲程柴油机的十字头组件的结构。
背景技术
十字头组件常用于大型低速二冲程柴油机。它固定于活塞杆下端，通过十字头组件中的十字头销与连杆小端轴承连接起来，能够有效的将活塞所受的动力传递给连杆和曲轴。同时曲柄连杆机构工作过程中产生的侧推力也由十字头组件中的十字头销两侧的滑块传递给固定于机架两侧的导板，从而改善了活塞与气缸套的工作条件，保证了活塞中心与气缸中心保持良好同轴度。
现有设计中的十字头组件具有以下缺点：(1)十字头销重量较大，其在做上下往复运动时产生的往复惯性力较大，增加了曲轴连杆机构所受载荷，同时也给装配增加了难度；(2)十字头组件中具有相对运动的各零件之间摩擦较大，产生热量较多，但散热效果较差，零件容易产生热疲劳进而出现失效情况；(3)现有设计中滑块两个滑动表面均浇铸百合金用于缓解摩擦磨损，但是一旦出现严重磨损需要将整个滑块进行更换，大大浪费了材料，增加的维修成本。
发明内容
本发明的目的在于克服上述现有设计中的十字头组件存在的缺陷和不足，提供一种结构轻巧，供油充分，散热性好，磨损易更换，适用于大型低速二冲程柴油机的一种十字头组件。
为了达到上述目的，本发明解决问题所采取的技术方案是：
一种大型柴油机十字头组件，所述十字头组件由十字头销1、滑块2、耐磨板3、密封盖4和套筒5构成一纵横截面均为“H”形结构，所述的十字头销 1为开设有花瓣形通孔112的圆柱体，十字头销1的左右两端外圆上分别套装连接滑块2，十字头销1的花瓣形通孔112中穿插连接套筒5形成进回油油路腔体，十字头销1的左右两端面上分别连接有用于密封油路腔体的密封盖4，所述滑块2的前后两端分别连接有耐磨板3；
所述的十字头销1为开设有花瓣形通孔112的圆柱体，十字头销1的左右两端前后外圆周面过中心分别对称开设有与滑块2相配合的平面101，每个平面101上开有连通十字头销1花瓣形通孔112的油孔102，十字头销1中部上外圆周面设有用于活塞杆定位的矩形平面103，矩形平面103上过中心设有两个用于连接活塞杆的活塞杆螺纹孔104以及连通十字头销1花瓣形通孔112的4个活塞杆回油孔106和1个位于矩形平面103中心的活塞杆进油孔105，十字头销1左右两端外圆周面上部设有方向与矩形平面103相垂直且连通十字头销1花瓣形通孔112的十字头销进油孔107和十字头销泄油孔108；
所述的十字头销1的左端端面距离轴心上部开设有与轴线平行且与活塞杆回油孔106相连通的轴向深孔109，在轴向深孔109起始端的外圆周面上设有与其垂直相连通的一浅孔110；在对应浅孔110绕轴线逆时针旋转，距离浅孔110位置处开设有一径向贯穿十字头销1且与浅孔110相连通的贯穿孔111。
所述的十字头销1开设有的花瓣形通孔112为梅花形，花瓣形通孔112之间由开设有的螺旋通槽115相连通，在十字头销1中部圆周面上均匀设有3个连通花瓣形通孔112的轴瓦进油孔114，用于润滑和冷却十字头销1与连杆小头之间的轴瓦；
所述滑块2由中间为细腰形板与前后两端为长条形板相垂直连接组成，细腰形板中间设有与十字头销1两端相配合的长孔201，长孔201四周均匀开设有4个梯形减重孔202，所述长条形板的宽度大于所述细腰形板的厚度；前 后两端长条形板的中部开设有与长孔201相连通的滑块侧油孔203，细腰形板上部上腰型弧面上开设有与长孔201相连通的滑块上油孔204；
所述的耐磨板3为槽钢形，套装在所述长条形板上，并通过耐磨板螺钉7和其工作表面均匀设置的4个沉孔301与长条形板相连接，耐磨板3的工作表面还浇铸有耐磨合金，耐磨板3中心开设有耐磨板进油孔302，耐磨板3的工作表面开有与耐磨板进油孔302相连通的油槽303，用于润滑滑块耐磨板3的工作表面，减小摩擦和磨损；
所述的密封盖设有孔径与套筒5内径大小相同的中心孔401，距离中心孔401的圆周上均匀设置有4个密封盖螺钉定位孔402，密封盖螺钉6穿过4个密封盖螺钉定位孔402将密封盖4固定于十字头销1左右端面上，用于密封十字头销1内部油孔，防止冷却油泄漏，同时又不封闭套筒5，保证套筒5内部通孔能够与空气接触，提升冷却效果。
所述的套筒5的长度与十字头销1的长度相同，其外径略大于十字头销1花瓣形通孔112的内径，两者通过红套工艺紧配合连接，配合过盈量δ＝0.03～0.06mm之间。
本发明的一种大型柴油机十字头组件的优点和有益效果：
1、十字头销内部开有由螺旋通槽相互连通的花瓣形通孔，销轴重量减轻，减小其对曲柄连杆机构载荷影响并且降低了装配难度。
2、十字头销采用套筒和花瓣形通孔过盈配合结构，内部润滑油与销轴接触面积增大，并且套筒又直接与空气接触，其冷却散热效果更好。
3、滑块外侧安装可更换耐磨板，一旦发生严重磨损无须更换整个滑块，更换耐磨板即可，具有良好互换性、经济性、便捷性。
附图说明：
图1为本发明的结构示意图；
图2为图1本发明的主视图；
图3为图1本发明的左视图；
图4为图1本发明的俯视图；
图5为图2的A-A剖视图；
图6为图4的B-B剖视图；
图7为十字头销的结构示意图；
图8为图7十字头销的主视图；
图9为图7十字头销的俯视图；
图10为图7十字头销的左视图；
图11为图9的C-C剖视图；
图12为滑块结构示意图；
图13为图12滑块的主视图；
图14为图12滑块的左视图；
图15为图12滑块的俯视图；
图16为耐磨板结构示意图；
图17为图16耐磨板的主视图；
图18为图17的D-D剖视图；
图19为密封盖的主视图；
其中：1—十字头销，101—平面，102—油孔，103—矩形平面，104—活塞杆螺纹孔，105—活塞杆进油孔，106—活塞杆回油孔，107—十字头销进油孔，108—十字头销泄油孔，109—轴向深孔，110—浅孔，111—贯穿孔，112—花瓣形通孔，113—密封盖螺钉螺纹孔，114—轴瓦进油孔，115—螺旋通槽，2—滑块， 201—长孔，202—减重孔，203—滑块侧油孔，204—滑块上油孔，3—耐磨板，301—沉孔，302—耐磨板进油孔，303—油槽，4—密封盖，401—中心孔，402—密封盖螺钉定位孔，5—套筒，6—密封盖螺钉，7—耐磨板螺钉。
具体实施方式
为使本发明实施例的目的和技术方案更加清楚，下面将结合附图和实施例对本发明的技术方案进行清楚、完整地描述。
本技术领域技术人员可以理解，除非另外定义，这里使用的所有术语(包括技术术语和科学术语)具有与本发明所属领域中的普通技术人员的一般理解相同的意义。
本发明中所述的“内、外”的含义指的是相对于组件本身而言，指向组件内部的方向为内，反之为外，而非对本发明的组件的特定限定。
本发明中所述的“左、右”的含义指的是阅读者正对附图时，阅读者的左边即为左，阅读者的右边即为右，而非对本发明的组件的特定限定。
本发明中所述的“连接”的含义可以是部件之间的直接连接也可以是部件间通过其它部件的间接连接。
本发明中所述的“前、后”的含义指的是阅读者正对附图时，离阅读者近的即为前，离阅读者远的即为后，而非对本发明的组件的特定限定。
如图1至图6所示，分别为本发明的一种大型柴油机十字头组件的结构及构件图，所述十字头组件由十字头销1、滑块2、耐磨板3、密封盖4和套筒5构成一纵横截面均为“H”形结构，所述的十字头销1为开设有花瓣形通孔112的圆柱体，十字头销1的左右两端外圆上分别套装连接滑块2，十字头销1的花瓣形通孔112中穿插连接套筒5形成进回油油路腔体，十字头销1的左右两端面上分别连接有用于密封油路腔体的密封盖4，所述滑块2的前后两端分别连接 有耐磨板3。
如图7至图11所示，分别为十字头销1的构造示意图，所述的十字头销1为开设有花瓣形通孔112的圆柱体，十字头销1的左右两端前后外圆周面过中心分别对称开设有与滑块2相配合的平面101，每个平面101上开有连通十字头销1花瓣形通孔112的油孔102，十字头销1中部上外圆周面设有用于活塞杆定位的矩形平面103，矩形平面103上过中心设有两个用于连接活塞杆的活塞杆螺纹孔104以及连通十字头销1花瓣形通孔112的4个活塞杆回油孔106和1个位于矩形平面103中心的活塞杆进油孔105，十字头销1左右两端外圆周面上部设有方向与矩形平面103相垂直且连通十字头销1花瓣形通孔112的十字头销进油孔107和十字头销泄油孔108。十字头销1的左端端面距离轴心上部开设有与轴线平行且与活塞杆回油孔106相连通的轴向深孔109，在轴向深孔109起始端的外圆周面上设有与其垂直相连通的一浅孔110。对应浅孔110绕轴线逆时针旋转，距离浅孔110位置处开设有一径向贯穿十字头销1且与浅孔110相连通的贯穿孔111。
十字头销1开设有的花瓣形通孔112为梅花形，花瓣形通孔112之间由开设有的螺旋通槽115相连通，在十字头销1中部圆周面上均匀设有3个连通花瓣形通孔112的轴瓦进油孔114，用于润滑和冷却十字头销1与连杆小头之间的轴瓦。
如图12至图15所示，分别为滑块2的构造示意图，所述滑块2由中间细腰形板与前后两端为长条形板相垂直连接组成，细腰形板中间设有与十字头销1两端相配合的长圆孔201，长圆孔201四周均匀开设有4个梯形减重孔202，所述长条形板的宽度大于所述细腰形板的厚度；前后两端长条形板的中部开设有与长圆孔201相连通的滑块侧油孔203，细腰形板上部上腰型弧面上开设有与长 圆孔201相连通的滑块上油孔204。
如图16至图18所示，为耐磨板3的构造示意图，所述的耐磨板3为槽钢形，套装在所述长条形板上，并通过耐磨板螺钉7和其工作表面均匀设置的4个沉孔301与长条形板相连接，耐磨板3的工作表面还浇铸有耐磨合金，耐磨板3中心开设有耐磨板进油孔302，耐磨板3的工作表面开有与耐磨板进油孔302相连通的油槽303，用于润滑滑块耐磨板3的工作表面，减小摩擦和磨损。
如图19所示，为密封盖4的构造示意图，所述的密封盖4设有孔径与套筒5内径大小相同的中心孔401，距离中心孔401的圆周上均匀设置有4个密封盖螺钉定位孔402，密封盖螺钉6穿过4个密封盖螺钉定位孔402将密封盖4固定于十字头销1左右端面上，用于密封十字头销1内部油孔，防止冷却油泄漏，同时又不封闭套筒5，保证套筒5内部通孔能够与空气接触，提升冷却效果。
所述的套筒5的长度与十字头销1的长度相同，其外径略大于十字头销1花瓣形通孔112的内径，两者通过红套工艺紧配合连接，配合过盈量δ＝0.03～0.06mm之间。
工作原理：
如图1所示，装配十字头组件时，首先将套筒5与十字头销1内部花瓣形通孔112采用红套工艺套装配合，套入后须保证套筒5左右两端面与十字头销1左右两端面平齐，随后在十字头销1左右两端安装滑块2，安装滑块2时，需保证滑块2的滑块上油孔204分别与十字头销1上的十字头销进油孔107和十字头销泄油孔108位置对应一致，保证油路畅通，在滑块2套入十字头销1之后，使用密封盖螺钉6将密封盖4固定于十字头销1两端面上，起到固定滑块2和密封十字头销1内部油孔作用，耐磨板3通过耐磨板螺钉7固定连接于滑块2长条形板外侧，完成十字头组件的装配过程。
十字头组件工作时，十字头销1上部矩形平面103与活塞杆底面配合，活塞杆通过螺钉固定于十字头销1上部矩形平面103上的活塞杆螺纹孔104内，十字头销1中部圆弧面与连杆小头配合连接，滑块2前后两端的耐磨板3工作表面与柴油机机架内的十字头导板配合，耐磨板3在十字头导板的导向方向上与导板存在相对滑移。工作过程中，各相对运动部件之间由于摩擦将产生大量热量，如果不能及时冷却，将会损坏各零部件，严重时可能影响到柴油机的正常工作。
本发明的油路系统能够有效对上述各零部件进行冷却和润滑，如图7至图18所示，润滑油进入十字头组件右侧滑块2上部的滑块上油孔204，顺着滑块上油孔204进入十字头销1右侧端部的十字头销进油孔107，随后进入销轴内部花瓣形通孔112，花瓣形通孔112与套筒5以及固定在十字头销1左右端面的密封盖4形成封闭的油路空间，润滑油通过各花瓣形通孔112之间的螺旋通槽115充满整个封闭空间，充满封闭空间的润滑油一部分通过十字头销1上端活塞杆定位面103中心部位的活塞杆进油孔105进入活塞头，对活塞头进行冷却。润滑油冷却活塞头之后通过活塞杆内部回油管路回到十字头销1上端活塞杆定位面103上的4个活塞杆回油孔106，活塞杆回油孔106内的润滑油进入与回油孔垂直相交的轴向深孔109。轴向深孔109中的润滑油又进入与其起始端垂直相交的浅孔110，进入浅孔110中的润滑油又进入方向与浅孔110垂直相交的贯穿孔111，贯穿孔111与十字头销1左侧的十字头销泄油孔108相连通，润滑油最后通过十字头销1左侧十字头销泄油孔108进入滑块2上部滑块上油孔204将润滑油泄出。其中十字头上所开设的轴向深孔109，与轴向深孔109相交的浅孔110，以及与浅孔110相交的贯穿孔111都需使用密封塞对其端口进行密封，保证十字头销1内部润滑油只能从十字头销1端部的十字头销泄油孔108泄出， 同时另一部分润滑油通过十字头销1中部圆周面上的轴瓦进油孔114润滑和冷却与其相连的连杆小头上的轴承，还有一部分润滑油通过十字头销1左右两端台阶平面101上油孔102和与之配合的滑块2左右两侧的滑块侧油孔203进入耐磨板3的工作表面，对耐磨板3工作表面进行润滑和冷却。通过上述油路的布置润滑油能够及时对具有相对运动关系的各个零部件进行冷却和润滑，并且套筒5内壁直接与空气接触，散热效果更好，有效的防止零部件由于温度过高而发生失效的情况，同时十字头销1内部与套筒5的过盈配合的连接方式，在减轻十字头组件自重的情况下能够保证十字头组件正常工作，充分减小其对曲柄连杆机构传动的影响。
十字头组件中的滑块2在工作过程中不断地作变速的滑动摩擦，磨损较为严重。当滑块2磨损严重时，只需更换滑块2长条形板上的耐磨板3即可，不需要更换整个滑块2，具有良好互换性、经济性、便捷性。

Claims (6)

  1. 一种大型柴油机十字头组件，其特征在于，所述十字头组件由十字头销(1)、滑块(2)、耐磨板(3)、密封盖(4)和套筒(5)构成一纵横截面均为“H”形结构，所述的十字头销(1)为开设有花瓣形通孔(112)的圆柱体，十字头销(1)的左右两端外圆上分别套装连接滑块(2)，十字头销(1)的花瓣形通孔(112)中穿插连接套筒(5)形成进回油油路腔体，十字头销(1)的左右两端面上分别连接有用于密封油路腔体的密封盖(4)，所述滑块(2)的前后两端分别连接有耐磨板(3)；
    所述的十字头销(1)的左右两端前后外圆周面过中心分别对称开设有与滑块(2)相配合的平面(101)，每个平面(101)上开有连通十字头销1花瓣形通孔(112)的油孔(102)，十字头销(1)中部上外圆周面设有用于活塞杆定位的矩形平面(103)，矩形平面(103)上过中心设有两个用于连接活塞杆的活塞杆螺纹孔(104)以及连通十字头销(1)花瓣形通孔(112)的4个活塞杆回油孔(106)和1个位于矩形平面(103)中心的活塞杆进油孔(105)，十字头销(1)左右两端外圆周面上部设有方向与矩形平面(103)相垂直且连通十字头销(1)花瓣形通孔(112)的十字头销进油孔(107)和十字头销泄油孔(108)；
    所述的十字头销(1)的左端端面距离轴心上部开设有与轴线平行且与活塞杆回油孔(106)相连通的轴向深孔(109)，在轴向深孔(109)起始端的外圆周面上设有与其垂直相连通的一浅孔(110)；在对应浅孔(110)绕轴线逆时针旋转，距离浅孔(110)位置处开设有一径向贯穿十字头销(1)且与浅孔(110)相连通的贯穿孔(111)；
    所述的十字头销(1)开设有的花瓣形通孔(112)之间由开设有的螺旋通槽(115)相连通，在十字头销(1)中部圆周面上均匀设有3个连通花瓣形通孔(112)的轴瓦进油孔(114)，用于润滑和冷却十字头销(1)与连杆小头之 间的轴瓦；
    所述滑块(2)由中间为细腰形板与前后两端为长条形板相垂直连接组成，细腰形板中间设有与十字头销(1)两端相配合的长孔(201)，前后两端长条形板的中部开设有与长孔(201)相连通的滑块侧油孔(203)，细腰形板上部上腰型弧面上开设有与长孔(201)相连通的滑块上油孔(204)；
    所述的耐磨板(3)为槽钢形，套装在所述长条形板上，并通过耐磨板螺钉(7)和其工作表面均匀设置的4个沉孔(301)与长条形板相连接，耐磨板(3)中心开设有耐磨板进油孔(302)，耐磨板(3)的工作表面开有与耐磨板进油孔(302)相连通的油槽(303)，用于润滑滑块耐磨板(3)的工作表面，减小摩擦和磨损；
    所述的密封盖(4)设有孔径与套筒(5)内径大小相同的中心孔(401)，距离中心孔(401)的圆周上均匀设置有4个密封盖螺钉定位孔(402)，密封盖螺钉(6)穿过4个密封盖螺钉定位孔(402)将密封盖4固定于十字头销(1)左右端面上，用于密封十字头销(1)内部油孔，同时又不封闭套筒(5)，保证套筒(5)通孔与空气接触。
  2. 根据权利要求1所述的一种大型柴油机十字头组件，其特征在于，所述的十字头销(1)的长度与套筒(5)的长度相同，其外径大于十字头销(1)花瓣形通孔(112)的内径，配合过盈量为δ＝0.03～0.06mm。
  3. 根据权利要求1所述的一种大型柴油机十字头组件，其特征在于，所述的十字头销(1)开设有的花瓣形通孔(112)为梅花形通孔。
  4. 根据权利要求1所述的一种大型柴油机十字头组件，其特征在于，所述耐磨板(3)的工作表面还浇铸有耐磨合金。
  5. 根据权利要求1所述的一种大型柴油机十字头组件，其特征在于，所 述的滑块(2)还均匀开设有4个梯形减重孔(202)。
  6. 根据权利要求1或5所述的一种大型柴油机十字头组件，其特征在于，所述的滑块(2)上的长条形板的宽度大于所述细腰形板的厚度。
PCT/CN2015/080455 2014-07-24 2015-06-01 一种大型柴油机十字头组件 Ceased WO2016011851A1 (zh)

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