CN115126621A - Partitioned micro-modeling cylinder sleeve and area division and partitioned micro-modeling design method thereof - Google Patents
Partitioned micro-modeling cylinder sleeve and area division and partitioned micro-modeling design method thereof Download PDFInfo
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- CN115126621A CN115126621A CN202210652625.0A CN202210652625A CN115126621A CN 115126621 A CN115126621 A CN 115126621A CN 202210652625 A CN202210652625 A CN 202210652625A CN 115126621 A CN115126621 A CN 115126621A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/004—Cylinder liners
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/18—Other cylinders
- F02F1/20—Other cylinders characterised by constructional features providing for lubrication
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Abstract
The invention discloses a partitioned micro-modeling cylinder sleeve, which comprises a cylinder sleeve, wherein the cylinder sleeve is sequentially divided into a boundary lubrication area I, a mixed lubrication area I, a fluid lubrication area, a mixed lubrication area II and a boundary lubrication area II from top to bottom along the axial direction of the cylinder sleeve, and a cylinder sleeve area division and partitioned micro-modeling design method is disclosed, and comprises the steps of 1) determining the model and the basic parameters of an engine. 2) And determining the working speed, the crank length and the connecting rod length of the engine. 3) And analyzing the radial load of the piston ring. 4) And performing a friction test according to the speed and the load of different cylinder sleeve positions of the cylinder sleeve-piston ring working stroke to obtain the friction coefficients of different positions of the working stroke. 5) And determining the positions of the boundary lubrication area, the mixed lubrication area and the fluid lubrication area according to the friction coefficient, and performing partition micro-molding. The invention divides the lubrication state area of the cylinder sleeve position in the working stroke, and adopts different micro-modeling parameters in different lubrication areas, thereby obviously improving the friction performance of the cylinder sleeve-piston ring.
Description
Technical Field
The invention relates to the field of micro-forming antifriction, in particular to a cylinder sleeve with micro-forming in subareas and a method for dividing the cylinder sleeve into areas and designing the micro-forming in subareas.
Background
Piston ring-to-cylinder liner frictional wear is the most common phenomenon of industrial equipment wear in internal combustion engines and also determines the life of the internal combustion engine. The researchers point out that the friction work consumed by the piston ring-cylinder sleeve friction pair accounts for 25% -50% of the total friction work of the internal combustion engine. Abnormal abrasion of a piston ring-cylinder sleeve friction pair can cause the phenomena of noise and vibration increase of an internal combustion engine, serious gas leakage, lubricating oil consumption increase, power reduction, fuel oil consumption increase and the like.
The surface micro-modeling technology is that micro-modeling patterns such as micro grooves or pits distributed in a certain array are processed on one surface of the friction pair, and abrasive dust can be contained under the condition of dry friction; the lubricating oil can be stored under lean lubrication conditions; hydrodynamic lubrication pressure can be generated under fluid lubrication and mixed lubrication conditions. The slight contouring can reduce friction and increase the life of the internal combustion engine. The cylinder sleeve is large in area and easy to machine, so that the cylinder sleeve is selected as a slightly-shaped machining object.
The micro-molding cylinder sleeve in the prior art does not consider the influence of the lubricating state, for example, the micro-molding type of the cylinder sleeve of the internal combustion engine with the composite lubricating structure of patent 202023015076.1 is that circular pits are uniformly distributed, the influence of the lubricating state is ignored by the uniform micro-molding, and the resistance reducing effect is poor.
Disclosure of Invention
The invention aims to: in view of the above problems, the present invention provides a cylinder liner with a micro-partitioned design, and provides a design method for partitioning and micro-partitioned design to reduce the frictional resistance between piston rings of the cylinder liner, achieve the effect of drag reduction, and improve the characteristics of the diesel engine such as friction and lubrication.
The technical scheme is as follows: the cylinder sleeve is sequentially divided into a boundary lubricating area I, a mixed lubricating area I, a fluid lubricating area, a mixed lubricating area II and a boundary lubricating area II from top to bottom along the circumferential direction of the cylinder sleeve, the boundaries in front of the two adjacent areas are a boundary S1, a boundary S2, a boundary S3 and a boundary S4 respectively, a plurality of circular micro-molding blind holes I are distributed on the boundary lubricating area I and the boundary lubricating area II respectively, a plurality of circular micro-molding blind holes II are distributed on the mixed lubricating area I and the mixed lubricating area II respectively, and a plurality of oval micro-molding blind holes are arranged on the fluid lubricating area respectively.
Furthermore, the distances between the boundary S1, the boundary S2, the boundary S3, the boundary S4 and the upper boundary of the first boundary lubrication area are respectively 0.4-1.5 mm, 2-5 mm, 122-124 mm and 124.5-125 mm.
Further, the radius R of the first round micro-molding blind hole 1 0.005 mm-0.125 mm, depth HP 1 The diameter of the first round micro-molding blind hole is 0.005 mm-0.04 mm, and the area ratio of the first round micro-molding blind hole in the first boundary lubrication area to the second boundary lubrication area is 10% -25%.
Preferably, the first plurality of circular micro-molding blind holes are distributed in an equidistant matrix type, and the distance between the two transversely adjacent first circular micro-molding blind holes is equal to the distance between the two longitudinally adjacent first circular micro-molding blind holes.
Further, the radius R of the second round micro-modeling blind hole 2 0.05 mm-0.125 mm, depth HP 2 The diameter of the first round micro-molding blind hole is 0.005 mm-0.04 mm, and the area of the second round micro-molding blind hole accounts for 10% -25% of the first mixed lubrication area and the second mixed lubrication area.
Preferably, the plurality of second circular micro-molding blind holes are distributed in an equidistant matrix type, and the distance between two horizontally adjacent second circular micro-molding blind holes is equal to the distance between two vertically adjacent second circular micro-molding blind holes.
Furthermore, the inclination angle theta of the oval micro-modeling blind hole is 0-90 degrees, the ratio of the oval minor axis a to the oval major axis b is 1 (1-4), and the depth HP 3 0.005 mm-0.04 mm, and the area of the plurality of oval micro-molded blind holes in the fluid lubrication area accounts for 10% -25%.
Optimally, a plurality of oval micro-molded blind holes are distributed in an array shape, and a straight line between every two adjacent oval micro-molded blind holes is arranged transverselyThe distance is equal to the linear distance between two longitudinally adjacent elliptical micro-modeling blind holes and is L 3 The inclination angle theta of each row of the oval micro-molded blind holes is inclined in the same direction, and the inclination angles theta of two adjacent rows of the oval micro-molded blind holes are inclined oppositely.
A cylinder sleeve surface lubrication state area division and partition micro-modeling design method comprises the following steps:
the first step is as follows: determining basic parameters of the engine, and determining the model and the basic parameters of the engine;
the second step is that: determination of engine operating conditions: determining the normal working rotating speed, the length of a crank and the length of a connecting rod of the engine; determining the change rule of the position of a cylinder sleeve in a power stroke and the speed of a piston ring:
the relation of the displacement of the piston ring of the engine along with the crank angle is as follows:
wherein S is the displacement of the piston in m; r is the crank radius in m, and L is the link length in m; alpha is the included angle between the crank and the center line of the cylinder, and the unit is an angle;
engine piston ring speed as a function of crank angle:
wherein v is the piston movement speed in m/s; omega is the engine idle speed, rad/s;
the third step: radial load analysis of an engine piston ring: determining the radial stress change of the engine under different strokes, and determining the radial load change rule of the piston ring under the power stroke:
establishing a balance equation according to the stress condition:
F Z +F a +F r ＝F e +F g ；
wherein, F Z A radial force generated for oil pressure; fa is the radial pressure generated by the contact of the cylinder sleeve and the piston ring, and Fr is the static friction force between the lower surface of the piston ring and the groove; fe is the radial elastic force of the piston ring, and Fg is the back pressure gas acting force of the piston ring;
the elastic force calculation formula of the piston ring is as follows:
wherein S is 0 The opening end distance of the piston ring, D the radius of the piston ring, T the radial thickness of the piston ring and E the elastic modulus of the piston ring.
The calculation formula of the piston ring surface pressure is as follows:
wherein H is the ring height of the piston;
the fourth step: performing a friction test according to the speed and the load of the working stroke of the cylinder sleeve-piston ring at different cylinder sleeve positions to obtain friction coefficients of different positions of the working stroke;
the fifth step: determining an engine cylinder sleeve lubrication state area based on a pin disc friction wear experiment: and determining the positions of the boundary lubrication area, the mixed lubrication area and the fluid lubrication area according to the friction coefficient, and performing partition micro-modeling.
Has the advantages that: compared with the prior art, the invention has the advantages that: the friction wear machine is utilized to find the critical positions of areas in different lubricating states, different micro-modeling dimensions are adopted in different lubricating states, micro-modeling is processed on the surface of the cylinder sleeve through the laser impact technology, and the purpose of reducing drag is achieved by storing abrasive dust and lubricating oil through pits or generating a dynamic pressure lubricating effect. The micron-sized micro-sculpt is processed on the surface of the lean lubricating area of the cylinder sleeve, so that the hardness and the strength of the surface of the material can be improved, and the abrasive dust and the lubricating oil can be stored to the maximum extent. The micron-sized micro-sculpt is processed on the surface of the mixed lubrication area, so that the dynamic pressure lubrication performance of the surface can be enhanced. The millimeter-scale micro-sculpt is processed on the surface of the fluid lubrication area, so that the dynamic pressure lubrication performance of the surface can be enhanced, and the abrasion between a piston ring and a cylinder sleeve can be effectively reduced. After the partition cylinder sleeve is slightly molded, the frictional wear performance between the piston rings of the cylinder sleeve can be greatly improved.
Drawings
FIG. 1 is a flow chart of the present invention;
FIG. 2 is a ring profile (top ring, second ring, oil ring);
FIG. 3 is a schematic diagram of cylinder liner axial position division;
FIG. 4 is a graph of engine piston ring displacement;
FIG. 5 is a graph of engine piston ring velocity;
FIG. 6 is a graph of the relationship between the speed of the power stroke and the position of the cylinder liner;
FIG. 7 is an analysis graph of radial force of a piston ring;
FIG. 8 is a schematic diagram of engine combustion chamber pressure;
FIG. 9 is a graph of the relationship between the radial load of the power stroke and the position of the cylinder liner;
FIG. 10 is a schematic view of a pin disc friction pair;
FIG. 11 is a schematic view of a disk sample;
FIG. 12 is a schematic view of a pin sample;
FIG. 13 is a graph of the change in coefficient of friction for S-0.24 mm;
FIG. 14 is a schematic diagram of the division criteria of the lubrication status;
FIG. 15 is a friction coefficient diagram under the working stroke condition;
FIG. 16 is a sectional view of a cylinder liner surface in different lubrication zones;
FIG. 17 is a schematic view of a boundary lubrication status zone parameter of a cylinder liner;
FIG. 18 is a schematic view of a parameter map of a cylinder liner in a mixed lubrication state;
FIG. 19 is a schematic view of a zone parameter of the liner in a fluid lubrication condition;
FIG. 20 is a plot of the optimum parametric coefficient of friction for the no micro-texture versus the micro-texture.
Detailed Description
The present invention is further illustrated by the following examples in conjunction with the accompanying drawings, it being understood that these examples are intended to illustrate the present invention and are not intended to limit the scope of the present invention.
A cylinder sleeve with a partitioned micro-molding function is shown in figures 2, 3 and 16 and comprises the cylinder sleeve, a friction area of the cylinder sleeve and a first piston ring (top ring) on a piston is sequentially divided into five areas from top to bottom, namely a boundary lubrication area I1, a mixed lubrication area I2, a fluid lubrication area 3, a mixed lubrication area II 4 and a boundary lubrication area II 5, the boundaries in front of the two adjacent areas are a boundary S1, a boundary S2, a boundary S3 and a boundary S4 respectively, a plurality of circular micro-molding blind holes I are distributed in the boundary lubrication area I1 and the boundary lubrication area II 5 respectively, a plurality of circular micro-molding blind holes II are distributed in the mixed lubrication area I2 and the mixed lubrication area II 4 respectively, and a plurality of oval micro-molding blind holes are arranged in the fluid lubrication area 3 respectively.
The distances between the boundary S1, the boundary S2, the boundary S3, the boundary S4 and the upper boundary of the boundary lubrication area I1 are 0.4-1.5 mm, 2-5 mm, 122-124 mm and 124.5-125 mm respectively.
As shown in FIGS. 17-19, wherein V is the moving speed of the piston ring, as shown in FIG. 17, the radius R of the first round micro-formed blind hole 1 0.005 mm-0.125 mm, depth HP 1 0.005 mm-0.04 mm, and the area of the first plurality of round micro-molded blind holes in the first boundary lubrication area and the second boundary lubrication area accounts for 10% -25%. The first round micro-modeling blind holes are distributed in an equidistant matrix manner, the distance between the first two transversely adjacent round micro-modeling blind holes is equal to the distance between the first two longitudinally adjacent round micro-modeling blind holes, and the distances are L 1 。
As shown in FIG. 18, the radius R of the second round micro-blind hole 2 0.05 mm-0.125 mm, depth HP 2 The diameter of the first round micro-molding blind hole is 0.005 mm-0.04 mm, and the area of the second round micro-molding blind hole accounts for 10% -25% of the first mixed lubrication area and the second mixed lubrication area. The second circular micro-molding blind holes are distributed in an equidistant matrix manner, the distance between every two adjacent horizontal circular micro-molding blind holes is equal to the distance between every two adjacent vertical circular micro-molding blind holes, and the distances are L 2 。
As shown in the figure19, the inclination angle theta of the oval micro-modeling blind hole is 0-90 degrees, the ratio of the oval minor axis a to the oval major axis b is 1 (1-4), and the depth HP 3 0.005 mm-0.04 mm, and the area of the plurality of oval micro-molded blind holes in the fluid lubrication area accounts for 10% -25%.
The plurality of oval micro-modeling blind holes are distributed in an array, the linear distance between two transversely adjacent oval micro-modeling blind holes is equal to the linear distance between two longitudinally adjacent oval micro-modeling blind holes, and the linear distances are L 3 The inclination angle theta of each row of the oval micro-molded blind holes is inclined in the same direction, and the inclination angles theta of two adjacent rows of the oval micro-molded blind holes are inclined oppositely.
A method for designing the regional division and the regional micro-modeling of the lubricating state of the sectional micro-modeling cylinder sleeve is shown in figure 1 and comprises the following steps:
the first step is as follows: and determining various parameters of the engine. Taking the engine YTRC2110D as an example, the idle speed of the engine is 1500rpm, the crank length is 0.0625m, and the connecting rod length is 0.1912 m. The opening end distance of the piston ring is 0.525mm, the radius of the piston ring is 49.25mm, the radial thickness of the piston ring is 4.525mm, and the elastic modulus of the piston ring is 200 GPa. The stroke is 125mm, and the cylinder diameter is 110 mm. Fig. 2 is a schematic profile view of three piston rings of a diesel engine, and the invention is used for researching the friction between a top ring and a cylinder sleeve. The position of the top dead center of the piston ring at the working stroke stage is defined as 0, the position of the bottom dead center is defined as 125mm, and the schematic diagram of the position of the cylinder sleeve is shown in fig. 3.
The second step is that: determination of engine operating conditions. The relation of the displacement of the piston ring of the engine along with the crank angle is as follows:
wherein S is the position of the piston in m; r is the crank radius in m, and L is the link length in m;
alpha is the angle between the crank and the cylinder centerline in degrees. The image of which is shown in fig. 4.
Engine piston ring speed as a function of crank angle:
v is the piston movement velocity in m/s; ω is the engine idle speed, rad/s. The image of which is shown in fig. 5. The relation graph of the position and the speed of the cylinder sleeve in the power stroke stage obtained by the formula (2) is shown in fig. 6.
The third step: and analyzing the radial load of the piston ring. The radial load stress analysis of the engine piston ring is shown in figure 7, the research object of the invention is a top ring, the bottom of the top ring is supposed to be always contacted with a groove, the analysis process is simplified, only main factors are considered, the stress condition is shown in the figure, and a balance equation is established:
F Z +F a +F r ＝F e +F g (3)
in formula (3): f Z A radial force generated for oil pressure; fa is the radial pressure generated by the contact of the cylinder sleeve and the piston ring, and Fr is the static friction force between the lower surface of the piston ring and the groove, and can be ignored due to the small value; fe is the radial spring force of the piston ring, Fg is the gas force of the piston ring back pressure, which is determined from the piston ring back ring pressure Pg, Pg is generally 0.7 times the combustion chamber pressure, and the combustion chamber pressure change diagram is shown in fig. 8.
Formula for calculating elasticity of piston ring
In the formula, S 0 The opening end distance of the piston ring, D the radius of the piston ring, T the radial thickness of the piston ring and E the elastic modulus of the piston ring.
Calculation of piston ring face pressure
Wherein H is the ring height of the piston; the rule of the change of the radial load along with the position of the cylinder sleeve under the working stroke can be finally obtained by the formulas (3), (4) and (5) and is shown in figure 9.
The fourth step: and performing a friction test by comparing the speeds and loads of different cylinder sleeve positions of the working stroke of the cylinder sleeve-piston ring to obtain the friction coefficients of different positions of the working stroke, dividing the working stroke of the engine according to the speeds, loads and positions based on the pin disc friction form of the friction wear machine, and performing the pin disc friction test, wherein the test scheme is shown in table 1.
TABLE 1 lubricating State zone partitioning test protocol
A schematic illustration 10 of a pin-disk friction pair is shown. Wherein F is the normal loading force and R is the radius of gyration. When the test is performed, the pin is stationary and the disc performs a gyratory motion. The disk sample had a radius of 80mm and a thickness of 8mm, as shown in FIG. 11. The pin sample had a radius of 6mm and a length of 16mm as shown in FIG. 12. The pin coupon was the piston ring material of engine YTRC2110D, which was stainless steel. The disk sample was the material used for the cylinder liner of engine YTRC2110D, which was ductile iron.
And fifthly, determining the positions of the boundary lubrication area, the mixed lubrication area and the fluid lubrication area according to the friction coefficient and performing partition micro-modeling.
FIG. 13 shows a 0.24mm friction coefficient time-varying curve for a liner position condition, with a steady-state average friction coefficient of 0.135. The lubrication condition criteria are shown in fig. 14, where the abscissa is the operating condition, U is the slip speed, P is the load, and μ is the fluid viscosity. The ordinate represents the friction coefficient, wherein the maximum value and the minimum value of the average friction coefficient obtained by fmax and fmin tests are shown. Therefore, the ab-segment region with a friction coefficient greater than 0.1 is defined as a boundary lubrication state, the bc-segment region between fmin and 0.1 is a mixed lubrication state, and the region after point c is a fluid lubrication state. The change rule of the friction coefficient at the stable stage under the working stroke working condition is observed as shown in fig. 15, wherein fmax of an area near the top dead center is 0.152, and fmin is 0.032; the area fmax near bottom dead center is 0.13 and fmin is 0.051. Fig. 16 is a schematic diagram illustrating the division of the lubrication state regions, where the boundary lubrication region 1, the mixed lubrication region 2, the fluid lubrication region 3, the mixed lubrication region two 4, and the boundary lubrication region two 5 are critical positions of the sliding state in S1, S2, S3, and S4. According to the divided cylinder liner schematic diagram, S1 is 0.48mm, S2 is 4.08mm, S3 is 124.61mm, and S4 is 122.69 mm.
In the fifth step, the design method of the divisional micro-molding is as follows:
different micro-modeling types are selected in different lubrication state areas, the micro-modeling dimensions of the boundary lubrication area and the mixed lubrication area are micron-sized circles, and the influence rule of the area rate, the radius and the depth of the circles on the friction coefficient is explored to obtain the optimal parameters. The scale of the fluid lubrication area is millimeter-scale ellipse, and the influence rule of the inclination angle, the ratio of the major axis to the minor axis, the area rate and the depth of the ellipse micro-structure on the friction coefficient is researched to obtain the optimal parameters.
The sectional development of the boundary lubrication region is shown in FIG. 17, where V is the moving speed of the piston ring and R is the moving speed of the piston ring 1 Is a micro-molding radius, L 1 For micro-moulding pitch, HP 1 Is the micro-molding depth. The cross-sectional development of the micro-molding of the mixed lubrication area is shown in FIG. 18, where V is the moving speed of the piston ring, and R is 2 Is a micro-molding radius, L 2 At a micro-molding pitch, HP 2 Is the micro-molding depth. The developed view of the micro-molding section of the fluid lubrication area is shown in fig. 19, wherein V is the motion speed of the piston ring, theta is the included angle between the micro-molding and the opposite speed direction, the inclination angle theta of each row of the elliptical micro-molding blind holes is in the same direction, the inclination angles theta of two adjacent rows of the elliptical micro-molding blind holes are opposite, a is the long axis of the ellipse, b is the short axis of the ellipse, and L is the minor axis of the ellipse 3 For micro-moulding pitch, HP 3 Is the micro-molding depth. Wherein the area ratio is defined as:
wherein each parameter has a range of R 1 In the range of 0.05mm to 0.125mm, S p1 5% to 25%, HP 1 Is 0.005mm to 0.04 mm. R 2 In the range of 0.05mm to 0.125mm, S p2 5% to 25%, HP 2 Is 0.005 to 0.04 mm. Theta ranges from 0 DEG to 90 DEG, the ratio of a to b is from 1 to 4, S p3 10% to 30%, HP 3 From 0.005mm to 0.04 mm.
Through test, the optimal parameter S of the boundary lubrication state is found p1 20% of R 1 Is 125um, HP 1 Is 20 um; optimum parameter S of mixed lubrication state p2 20% of R 2 Is 100um, HP 2 Is 20 um; the optimal parameter of the fluid lubrication state is that theta is 30 degrees, a: b is 3: 1, S p3 20% of HP 3 Is 20 um.
FIG. 20 is a plot of the average coefficient of friction versus the optimum micro-parameter for the micro-texture without the micro-texture and for the micro-texture at different lubrication conditions. As can be seen from the figure, the optimum micro-sculpted friction coefficient for the boundary lubrication regime is reduced by 46.2% compared to no micro-sculpting; the friction coefficient of the optimal micro-structure in the boundary lubrication state is reduced by 43.8 percent; the optimum micro-sculpted friction coefficient for boundary lubrication conditions was reduced by 32.1%.
Claims (10)
1. The utility model provides a subregion micro-structure cylinder liner, includes the cylinder liner, its characterized in that: the cylinder sleeve is sequentially divided into a boundary lubrication area I (1), a mixed lubrication area I (2), a fluid lubrication area (3), a mixed lubrication area II (4) and a boundary lubrication area II (5) from top to bottom along the circumferential direction of the cylinder sleeve, the boundary between the two adjacent areas is a boundary S1, a boundary S2, a boundary S3 and a boundary S4, a plurality of circular micro-molding blind holes I are distributed on the boundary lubrication area I (1) and the boundary lubrication area II (5), a plurality of circular micro-molding blind holes II are distributed on the mixed lubrication area I (2) and the mixed lubrication area II (4), and a plurality of oval micro-molding blind holes are formed in the fluid lubrication area (3).
2. The cylinder liner of claim 1, wherein: the distances between the boundary S1, the boundary S2, the boundary S3, the boundary S4 and the upper boundary of the boundary lubrication area I (1) are respectively 0.4-1.5 mm, 2-5 mm, 122-124 mm and 124.5-125 mm.
3. The cylinder liner of claim 1, wherein: radius R of first round micro-modeling blind hole 1 0.005 mm-0.125 mm, depth HP 1 The diameter of the first round micro-molding blind hole is 0.005 mm-0.04 mm, and the area ratio of the first round micro-molding blind hole to the first boundary lubrication area (1) and the second boundary lubrication area (5) is 10% -25%.
4. The cylinder liner of claim 3, wherein: the first round micro-modeling blind holes are distributed in an equidistant matrix mode, and the distance between every two transversely adjacent first round micro-modeling blind holes is equal to the distance between every two longitudinally adjacent first round micro-modeling blind holes.
5. The cylinder liner of claim 1, wherein: radius R of second round micro-molding blind hole 2 0.05 mm-0.125 mm, depth HP 2 The diameter of the circular micro-molding blind hole II is 0.005 mm-0.04 mm, and the area ratio of the circular micro-molding blind hole II in the first mixed lubrication area (2) to the second mixed lubrication area (4) is 10% -25%.
6. The cylinder liner of claim 5, wherein: the plurality of second circular micro-molding blind holes are distributed in an equidistant matrix type, and the distance between every two adjacent horizontal second circular micro-molding blind holes is equal to the distance between every two adjacent vertical second circular micro-molding blind holes.
7. The cylinder liner according to claim 1, wherein: the dip angle theta of the elliptic micro-modeling blind hole is 0-90 degrees, and the elliptic minor axis a and the ellipseThe ratio of the long axis b is 1 (1-4), the depth HP 3 Is 0.005 mm-0.04 mm, and the area of the plurality of oval micro-molded blind holes in the fluid lubrication area (3) accounts for 10% -25%.
8. The cylinder liner of claim 7, wherein: the plurality of oval micro-modeling blind holes are distributed in an array form, the linear distance between every two transversely adjacent oval micro-modeling blind holes is equal to the linear distance between every two longitudinally adjacent oval micro-modeling blind holes, and the linear distances are L 3 The inclination angles theta of each row of the oval micro-molded blind holes are in the same direction, and the inclination angles theta of two adjacent rows of the oval micro-molded blind holes are opposite.
9. The cylinder liner according to claim 1, wherein: the first boundary lubrication area (1), the first mixed lubrication area (2), the fluid lubrication area (3), the second mixed lubrication area (4) and the second boundary lubrication area (5) are located in a friction area of the cylinder sleeve and the piston top ring.
10. The method for designing the cylinder liner by the regional division and the regional micro-modeling according to any one of claims 1 to 9, characterized by comprising the following steps:
the first step is as follows: determining basic parameters of the engine, and determining the model and the basic parameters of the engine;
the second step: determination of engine operating conditions: determining the normal working speed, the crank length and the connecting rod length of the engine; determining the change rule of the position of the cylinder sleeve in the power stroke and the speed of the piston ring:
the relation of the displacement of the piston ring of the engine along with the crank angle is as follows:
wherein S is the displacement of the piston in m; r is the crank radius in m, and L is the connecting rod length in m; alpha is the included angle between the crank and the center line of the cylinder, and the unit is an angle;
engine piston ring speed as a function of crank angle:
wherein v is the piston movement speed in m/s; omega is the idle speed of the engine, rad/s;
the third step: radial load analysis of an engine piston ring: determining the radial stress change of the engine under different strokes, and determining the radial load change rule of the piston ring under the power stroke:
establishing a balance equation according to the stress condition:
F Z +F a +F r ＝F e +F g ；
wherein, F Z A radial force generated for oil pressure; fa is the radial pressure generated by the contact of the cylinder sleeve and the piston ring, and Fr is the static friction force between the lower surface of the piston ring and the groove; fe is the radial elastic force of the piston ring, and Fg is the back pressure gas acting force of the piston ring;
the elastic force calculation formula of the piston ring is as follows:
wherein S is 0 The opening end distance of the piston ring, D the radius of the piston ring, T the radial thickness of the piston ring and E the elastic modulus of the piston ring.
The calculation formula of the piston ring surface pressure is as follows:
wherein H is the ring height of the piston;
the fourth step: performing a friction test according to the speed and the load of the working stroke of the cylinder sleeve-piston ring at different cylinder sleeve positions to obtain the friction coefficients of the working stroke at different positions;
the fifth step: determining the lubricating state area of an engine cylinder sleeve based on a pin disc friction and wear experiment: and determining the positions of the boundary lubrication area, the mixed lubrication area and the fluid lubrication area according to the friction coefficient, and performing partition micro-modeling.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210652625.0A CN115126621A (en) | 2022-06-07 | 2022-06-07 | Partitioned micro-modeling cylinder sleeve and area division and partitioned micro-modeling design method thereof |
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|---|---|---|---|
| CN202210652625.0A CN115126621A (en) | 2022-06-07 | 2022-06-07 | Partitioned micro-modeling cylinder sleeve and area division and partitioned micro-modeling design method thereof |
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Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2021060048A (en) * | 2019-10-03 | 2021-04-15 | 日本ピストンリング株式会社 | Internal combustion engine sliding structure and method for creating the same |
| CN113323764A (en) * | 2021-06-24 | 2021-08-31 | 潍柴动力股份有限公司 | Cylinder sleeve, cylinder and engine |
| CN214384176U (en) * | 2020-12-14 | 2021-10-12 | 兰州交通大学 | Internal combustion engine cylinder sleeve with composite lubricating structure |
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Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2021060048A (en) * | 2019-10-03 | 2021-04-15 | 日本ピストンリング株式会社 | Internal combustion engine sliding structure and method for creating the same |
| CN214384176U (en) * | 2020-12-14 | 2021-10-12 | 兰州交通大学 | Internal combustion engine cylinder sleeve with composite lubricating structure |
| CN113323764A (en) * | 2021-06-24 | 2021-08-31 | 潍柴动力股份有限公司 | Cylinder sleeve, cylinder and engine |
Non-Patent Citations (4)
| Title |
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| "油润滑条件下减摩织构表面的优化设计", 中国博士学位论文全文数据库, pages 45 - 49 * |
| MENG F: "A Lubricant transport across the pistion ring with flat and triangular lubrication injection profiles on the liner in lage two-storke marine diesel engine s", PROCEEDINGS OF THE INSITITUION OF MECHANICAL ENGINEERS, PART J:JOURNAL OF ENGINEERING TRIBOLOGY, pages 1 - 3 * |
| N WBOLANDER等: "Lubrication regime transition at piston ring-cylinder liner interface", PROCEEDINGS OF INSTITUTION OF MECHANICAL ENGINEERS, PART J:JOURNAL OF ENGINEER TRIBOLOGY, pages 19 - 25 * |
| 于海武: "基于流体动压润滑效应的表面织构优化设计", 中国博士学位论文全文库, pages 51 - 55 * |
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