CN107687368B - Method for predicting friction loss of radial sealing sheet of microminiature rotor engine - Google Patents

Method for predicting friction loss of radial sealing sheet of microminiature rotor engine Download PDF

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CN107687368B
CN107687368B CN201710957030.5A CN201710957030A CN107687368B CN 107687368 B CN107687368 B CN 107687368B CN 201710957030 A CN201710957030 A CN 201710957030A CN 107687368 B CN107687368 B CN 107687368B
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oil film
sealing sheet
cylinder
normal force
radial sealing
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刘金祥
左正兴
张帅
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Beijing Institute of Technology BIT
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    • 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
    • F02B55/00—Internal-combustion aspects of rotary pistons; Outer members for co-operation with rotary pistons
    • 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
    • F02F11/00—Arrangements of sealings in combustion engines 
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Abstract

The invention discloses a method for predicting the friction loss of a radial sealing sheet of a micro-miniature rotor engine, belonging to the field of micro-miniature engines. The invention comprises the following steps: the method comprises the following steps: analyzing the plane composite motion track of the radial sealing plate, and establishing a static equilibrium equation between the normal force of an oil film between the sealing plate and the inner wall of the cylinder, the normal force of a micro convex body and other loads; step two: establishing a relation between an oil film normal force and the oil film thickness, and establishing a relation between a microprotrusion normal force and the oil film thickness; step three: adjusting the thickness of the oil film, and determining the normal force of the oil film and the normal force of the micro-convex body according to the thickness of the oil film; step four: determining the tangential force of an oil film and the tangential force of a micro convex body between the radial sealing plate and the inner wall of the cylinder; step five: determining the friction loss between the radial sealing sheet and the inner wall of the cylinder; and guiding the design and engineering application of the radial sealing sheet of the micro-miniature rotor engine according to the friction loss between the radial sealing sheet and the inner wall of the cylinder determined in the step five, and solving the problem of practical engineering.

Description

Method for predicting friction loss of radial sealing sheet of microminiature rotor engine
Technical Field
The invention relates to a prediction method of a radial sealing sheet of a micro-miniature rotor engine, belonging to the field of micro-miniature engines.
Background
With the rapid development of equipment such as portable equipment and small unmanned aerial vehicles, microminiature power and energy systems show huge market and application. The rotary engine has a simple structure, stable operation, small vibration, and easy miniaturization, and thus has received much attention.
The combustion of the microminiature rotor engine is difficult to organize due to the small combustion chamber. In addition, the surface-to-volume ratio is large, the temperature of the cylinder is easy to lose, the temperature of the cylinder is low, the flame is easy to quench, and the large surface-to-volume ratio can cause serious heat loss. The indicated power of the micro rotary engine is relatively low.
In order to reduce the physical quality and mass, micro-miniature rotary engines often omit a lubrication system. In this case, the lubricating oil must first be mixed into the fuel and then reach the combustion chamber by the intake of the fuel, which is generally less effective than the lubricating system with a lubricating system, but the mechanical losses between the radial sealing plate and the inner wall of the cylinder are difficult to measure and calculate in this case at present. Therefore, it is necessary to provide a method for predicting the friction loss between the radial sealing plate and the inner wall in the micro-rotor engine.
Disclosure of Invention
The invention discloses a method for predicting the friction loss of a radial sealing sheet of a micro-miniature rotor engine, which aims to realize the prediction of the friction loss of the radial sealing sheet of the micro-miniature rotor engine.
The purpose of the invention is realized by the following technical scheme:
the invention discloses a friction loss prediction method for radial sealing pieces of a microminiature rotor engine, which comprises the following steps:
the method comprises the following steps: analyzing the track of the radial sealing sheet doing plane compound motion to establish the normal force P of the oil film between the sealing sheet and the inner wall of the cylinderhMicro-convex normal force FaspAnd other loads, as shown in
Figure GDA0002371854210000021
Wherein, FsprPre-tightening the spring piece; fPbThe gas force is applied to the bottom of the sealing sheet; plaTo direct combustion chamber gas pressure; ptaTo follow the combustion chamber gas pressure; theta is a guide side oil film wetting angle; thetatThe following side oil film wetting angle is adopted; rsThe radius of curvature of the top end of the sealing sheet; phNormal pressure for oil film generation; faspNormal pressure generated for the microprotrusions; b is the thickness of the sealing sheet; m is the quality of the sealing sheet; rcη,RcξIs the centroid coordinate of the sealing piece. a isoxAnd aoyThe inertial force of the radial sealing piece, α, is expressed as the crank angle, α is three times that of β.
Solving the normal force P of the radial sealing piece for removing the oil film according to the static equilibrium equationhMicro-convex normal force FaspThe other loads are as follows
Figure GDA0002371854210000022
Step two: establishing oil film normal force PhThe relation between the oil film thickness h and the micro-convex body normal force F is establishedaspAnd the oil film thickness h.
Step 2.1: establishing oil film normal force PhAnd the oil film thickness h.
Considering the influence of roughness on the lubricating state between the sealing sheet and the cylinder, adopting an average Reynolds equation to establish a mixed lubricating model between the radial sealing sheet and the inner wall of the cylinder of the microminiature rotor engine, wherein the mixed lubricating model is an oil film normal force PhAnd the oil film thickness h.
Figure GDA0002371854210000023
Wherein phi isxIs a pressure flow factor phisIs a shear factor, phicIs the contact factor, h is the oil film thickness, μ is the lubricant viscosity, U is the velocity of the seal relative to the cylinder, and σ is the integrated roughness t is the time. PhIs the oil film pressure.
Step 2.2: establishing a microprotrusion normal force FaspAnd the oil film thickness h.
Microprotrusion normal force F between radial seal and cylinder inner wallaspIn order to realize the purpose,
Fasp＝KE′F2.5(H)
the above formula establishes the normal force F of the microprotrusion bodyaspAnd the oil film thickness h.
Wherein: k is a comprehensive parameter determined by roughness, E' is the sum elastic modulus of the two materials, and H is the ratio of the oil film thickness H to the comprehensive roughness sigma. F2.5(H) To describe the rough peak distribution between the radial seal plate and the cylinder,
Figure GDA0002371854210000031
wherein A is a coefficient and z is an index.
The overall parameter K determined by the roughness in step 2.2 is preferably 1.198 × 10-4The coefficient A is preferably 4.4068 × 10-5The index z is preferably 6.804.
Step three: oil film normal force P between realization by adjusting oil film thickness hhMicro-convex normal force FaspAnd the hydrostatic balance between the oil film and other borne loads, and further determining the normal force P of the oil film according to the thickness h of the oil filmhMicro-convex normal force Fasp。
Step four: determining the oil film tangential force tau between the radial sealing plate and the inner wall of the cylinderhAnd microprotrusion tangential force F0。
Step 4.1: determining the oil film tangential force tau between the radial sealing plate and the inner wall of the cylinderh。
The tangential force of an oil film between the radial sealing sheet and the inner wall of the cylinder is
Figure GDA0002371854210000032
Wherein: tau ishTangential force, phi, generated for the oil filmf、φfsAnd phifpRespectively, representing the relevant parameters. The formula is as follows:
φfp＝1.14e-0.66HH＞0075
Figure GDA0002371854210000033
Figure GDA0002371854210000034
wherein, z is H/3, H is z { z [132+ z (M +345) ] } -55, M is z { z [ z (60+147z) -405] -160}
Step 4.2: determining a microprotrusion tangential force F between a radial seal land and the cylinder inner wall0。
Microprotrusion tangential force F between radial seal and cylinder inner wall0Comprises the following steps:
F0＝τ0Ac+a0Fasp
wherein F0Tangential force, τ, generated by the sealing disc0Shear strength of the microprotrusions, AcIs the actual contact area, a0Is the boundary friction coefficient. Wherein the actual contact area is expressed as follows
Ac＝π2(ηβσ)2F2(H)
Step five: oil film tangential force tau determined according to step fourhAnd microprotrusion tangential force F0And determining the friction loss between the radial sealing sheet and the inner wall of the cylinder.
The friction loss between the radial seal piece and the inner wall of the cylinder is
Figure GDA0002371854210000041
Wherein: thetalLeading the oil film infiltration angle of the side; thetatThe following side oil film wetting angle is adopted; rsThe radius of curvature of the top end of the sealing sheet; and B is the thickness of the sealing sheet.
Step six: and guiding the design and engineering application of the radial sealing sheet of the micro-miniature rotor engine according to the friction loss between the radial sealing sheet and the inner wall of the cylinder determined in the step five, and solving the problem of practical engineering.
Has the advantages that:
the load that the radial sealing strip of microminiature rotor engine receives among the prior art is complicated, leads to the mechanical loss between radial sealing strip and the cylinder inner wall to the sealing strip and the cylinder inner wall contact state complicacy to be difficult to measure and calculate, and mechanical loss when radial sealing strip and cylinder inner wall between design improper probably brings following problem: (1) the service life of the radial sealing sheet and the inner wall of the cylinder in the microminiature rotor engine is short; (2) the microminiature rotor engine has high mechanical loss and low output power; the method for predicting the friction loss of the radial sealing sheet of the micro-miniature rotor engine can predict the friction loss of the radial sealing sheet of the micro-miniature rotor engine, guide the design and engineering application of the radial sealing sheet of the micro-miniature rotor engine and avoid the problem caused by improper design of mechanical loss between the radial sealing sheet and the inner wall of a cylinder.
Drawings
FIG. 1 is a flow chart of a method for predicting the friction loss of radial sealing pieces of a micro-miniature rotor engine, which is disclosed by the invention;
FIG. 2 is a schematic view of the contact between the radial seal piece and the cylinder inner wall;
FIG. 3 is a graph showing the oil film force and the microprotrusion contact force between the radial seal and the cylinder bore wall in an exemplary embodiment;
FIG. 4 is a diagram showing the friction force generated by the oil film and the micro-protrusions between the radial seal piece and the inner wall of the cylinder in the embodiment;
fig. 5 shows the mechanical losses between the radial sealing plate and the cylinder inner wall in the embodiment.
Detailed Description
For a better understanding of the objects and advantages of the present invention, reference should be made to the following detailed description taken in conjunction with the accompanying drawings and examples.
Example 1:
the present embodiment is designed to create a radius R of 21mm, an eccentricity E of 3mm, an offset distance of 1mm, a thickness l of 14.5mm, a roughness σ of the seal piece and the inner wall of the cylinder of 0.6um. elastic model E' ═ 21000MPa, a poisson ratio of 0.3, and a mass M of the radial seal piece of 8 × 10-4g, bottom spring force FsprIs 10N, and the oil film thickness is hc0.05mm, and the viscosity of the lubricating oil is 1.65 × 10-9MPa·s。
The purpose of the invention is realized by the following technical scheme:
as shown in fig. 1, the method for predicting the friction loss of the radial sealing plate of the micro-rotor engine disclosed in this embodiment includes the following specific steps:
the method comprises the following steps: analyzing the track of the radial sealing sheet doing plane compound motion to establish the normal force P of the oil film between the sealing sheet and the inner wall of the cylinderhMicro-convex normal force FaspAnd other loads, as shown in
Figure GDA0002371854210000051
Wherein, FsprIs a spring leafPre-tightening force; fPbThe gas force is applied to the bottom of the sealing sheet; plaTo direct combustion chamber gas pressure; ptaTo follow the combustion chamber gas pressure; theta is a guide side oil film wetting angle; thetatThe following side oil film wetting angle is adopted; rsThe radius of curvature of the top end of the sealing sheet; phNormal pressure for oil film generation; faspNormal pressure generated for the microprotrusions; b is the thickness of the sealing sheet; m is the quality of the sealing sheet; rcη,RcξIs the centroid coordinate of the sealing piece. a isoxAnd aoyThe inertial force of the radial sealing piece, α, is expressed as the crank angle, α is three times that of β.
The contact between the radial seal and the cylinder inner wall is shown in figure 2. Solving the normal force P of the radial sealing piece for removing the oil film according to the static equilibrium equationhMicro-convex normal force FaspThe other loads are as follows
Figure GDA0002371854210000052
Step two: establishing oil film normal force PhThe relation between the oil film thickness h and the micro-convex body normal force F is establishedaspAnd the oil film thickness h.
Step 2.1: establishing oil film normal force PhAnd the oil film thickness h.
Considering the influence of roughness on the lubricating state between the sealing sheet and the cylinder, adopting an average Reynolds equation to establish a mixed lubricating model between the radial sealing sheet and the inner wall of the cylinder of the microminiature rotor engine, wherein the mixed lubricating model is an oil film normal force PhAnd the oil film thickness h.
Figure GDA0002371854210000061
Wherein phi isxIs a pressure flow factor phisIs a shear factor, phicIs the contact factor, h is the oil film thickness, μ is the lubricant viscosity, and U is the velocity of the seal relative to the cylinderAnd sigma is the comprehensive roughness t and time. PhIs the oil film pressure.
Step 2.2: establishing a microprotrusion normal force FaspAnd the oil film thickness h.
Microprotrusion normal force F between radial seal and cylinder inner wallaspIn order to realize the purpose,
Fasp＝KE′F2.5(H)
the above formula establishes the normal force F of the microprotrusion bodyaspAnd the oil film thickness h.
Wherein: k is a comprehensive parameter determined by roughness, E' is the sum elastic modulus of the two materials, and H is the ratio of the oil film thickness H to the comprehensive roughness sigma. F2.5(H) To describe the rough peak distribution between the radial seal plate and the cylinder,
Figure GDA0002371854210000062
wherein A is a coefficient and z is an index.
The overall parameter K determined by the roughness in step 2.2 is preferably 1.198 × 10-4The coefficient A is preferably 4.4068 × 10-5The index z is preferably 6.804.
Step three: oil film normal force P between realization by adjusting oil film thickness hhMicro-convex normal force FaspAnd the hydrostatic balance between the oil film and other borne loads, and further determining the normal force P of the oil film according to the thickness h of the oil filmhMicro-convex normal force FaspAs shown in fig. 3.
Step four: determining the oil film tangential force tau between the radial sealing plate and the inner wall of the cylinderhAnd microprotrusion tangential force F0。
Step 4.1: determining the oil film tangential force tau between the radial sealing plate and the inner wall of the cylinderh。
The tangential force of an oil film between the radial sealing sheet and the inner wall of the cylinder is
Figure GDA0002371854210000063
Wherein: tau ishTangential force, phi, generated for the oil filmf、φfsAnd phifpRespectively, representing the relevant parameters. The formula is as follows:
φfp＝1.14e-0.66HH＞0.75
Figure GDA0002371854210000071
Figure GDA0002371854210000072
wherein, z is H/3, N is z { z [132+ z (M +345) ] } -55, M is z { z [ z (60+147z) -405] -160}
Step 4.2: determining a microprotrusion tangential force F between a radial seal land and the cylinder inner wall0。
Microprotrusion tangential force F between radial seal and cylinder inner wall0Comprises the following steps:
F0＝τ0Ac+a0Fasp
wherein F0Tangential force, τ, generated by the sealing disc0Shear strength of the microprotrusions, AcIs the actual contact area, a0Is the boundary friction coefficient. Wherein the actual contact area is expressed as follows
Ac＝π2(ηβσ)2F2(H)
The obtained oil film force tangential force tauhAnd microprotrusion tangential force F0As shown in fig. 4.
Step five: oil film tangential force tau determined according to step fourhAnd microprotrusion tangential force F0And determining the friction loss between the radial sealing sheet and the inner wall of the cylinder.
The friction loss between the radial seal piece and the inner wall of the cylinder is
Figure GDA0002371854210000073
Wherein: thetalLeading the oil film infiltration angle of the side; thetatThe following side oil film wetting angle is adopted; rsThe radius of curvature of the top end of the sealing sheet; and B is the thickness of the sealing sheet. Calculating the oil film force PhGentle convex force FaspThe resulting friction loss is shown in fig. 5.
Step six: and guiding the design and engineering application of the radial sealing sheet of the micro-miniature rotor engine according to the friction loss between the radial sealing sheet and the inner wall of the cylinder determined in the step five, and solving the problem of practical engineering.
The above detailed description is intended to illustrate the objects, aspects and advantages of the present invention, and it should be understood that the above detailed description is only exemplary of the present invention and is not intended to limit the scope of the present invention, and any modifications, equivalents, improvements and the like made within the spirit and principle of the present invention should be included in the scope of the present invention.

Claims (5)

1. A friction loss prediction method for radial sealing pieces of a microminiature rotor engine is characterized by comprising the following steps: the method comprises the following steps:
the method comprises the following steps: analyzing the track of the radial sealing sheet doing plane compound motion to establish the normal force P of the oil film between the sealing sheet and the inner wall of the cylinderhMicro-convex normal force FaspAnd other loads, as shown in
Figure FDA0002371854200000011
Wherein, FsprPre-tightening the spring piece; fPbThe gas force is applied to the bottom of the sealing sheet; plaTo direct combustion chamber gas pressure; ptaTo follow the combustion chamber gas pressure; theta is a guide side oil film wetting angle; thetatThe following side oil film wetting angle is adopted; rsThe radius of curvature of the top end of the sealing sheet; phNormal pressure for oil film generation; faspNormal pressure generated for the microprotrusions; b is the thickness of the sealing sheet; m is the quality of the sealing sheet; rcη,RcξIs the centroid coordinate of the sealing piece; a isoxAnd aoyThe inertial force of the radial sealing piece, α, expressed as crank angle, α is three times that of β;
solving the normal force P of the radial sealing piece for removing the oil film according to the static equilibrium equationhMicro-convex normal force FaspThe other loads are as follows
Figure FDA0002371854200000012
Step two: establishing oil film normal force PhThe relation between the oil film thickness h and the micro-convex body normal force F is establishedaspThe relation between the oil film thickness h;
step three: oil film normal force P between realization by adjusting oil film thickness hhMicro-convex normal force FaspAnd the hydrostatic balance between the oil film and other borne loads, and further determining the normal force P of the oil film according to the thickness h of the oil filmhMicro-convex normal force Fasp；
Step four: determining the oil film tangential force tau between the radial sealing plate and the inner wall of the cylinderhAnd microprotrusion tangential force F0；
Step five: oil film tangential force tau determined according to step fourhAnd microprotrusion tangential force F0Determining the friction loss between the radial sealing sheet and the inner wall of the cylinder;
the friction loss between the radial seal piece and the inner wall of the cylinder is
Figure FDA0002371854200000021
Wherein: thetalLeading the oil film infiltration angle of the side; thetatThe following side oil film wetting angle is adopted; rsThe radius of curvature of the top end of the sealing sheet; and B is the thickness of the sealing sheet.
2. The method for predicting the friction loss of the radial sealing sheet of the miniature rotor engine as set forth in claim 1, wherein: step six: and guiding the design and engineering application of the radial sealing sheet of the micro-miniature rotor engine according to the friction loss between the radial sealing sheet and the inner wall of the cylinder determined in the step five, and solving the problem of practical engineering.
3. The method for predicting the friction loss of the radial sealing sheet of the miniature rotor engine as set forth in claim 1 or 2, wherein: the concrete implementation method of the second step is that,
step 2.1: establishing oil film normal force PhThe relation between the oil film thickness h;
considering the influence of roughness on the lubricating state between the sealing sheet and the cylinder, adopting an average Reynolds equation to establish a mixed lubricating model between the radial sealing sheet and the inner wall of the cylinder of the microminiature rotor engine, wherein the mixed lubricating model is an oil film normal force PhThe relation between the oil film thickness h;
Figure FDA0002371854200000022
wherein phi isxIs a pressure flow factor phisIs a shear factor, phicIs a contact factor, h is the oil film thickness, mu is the lubricant viscosity, U is the velocity of the sealing sheet relative to the cylinder, and sigma is the comprehensive roughness t is the time; phOil film pressure;
step 2.2: establishing a microprotrusion normal force FaspThe relation between the oil film thickness h;
microprotrusion normal force F between radial seal and cylinder inner wallaspIn order to realize the purpose,
Fasp＝KE′F2.5(H)
the above formula establishes the normal force F of the microprotrusion bodyaspThe relation between the oil film thickness h;
wherein: k is a comprehensive parameter determined by roughness, E' is the sum elastic modulus of the two materials, and H is the ratio of the oil film thickness H to the comprehensive roughness sigma; f2.5(H) To describe the rough peak distribution between the radial seal plate and the cylinder,
Figure FDA0002371854200000023
wherein A is a coefficient and z is an index.
4. The method for predicting the friction loss of the radial sealing sheet of the miniature rotor engine as claimed in claim 3, wherein the comprehensive parameter K determined by the roughness in the step 2.2 is selected from 1.198 × 10-4Coefficient A of 4.4068 × 10-5And the index z is 6.804.
5. The method for predicting the friction loss of the radial sealing sheet of the miniature rotor engine as set forth in claim 1 or 2, wherein: the concrete implementation method of the step four is that,
step 4.1: determining the oil film tangential force tau between the radial sealing plate and the inner wall of the cylinderh；
The tangential force of an oil film between the radial sealing sheet and the inner wall of the cylinder is
Figure FDA0002371854200000031
Wherein: tau ishTangential force, phi, generated for the oil filmf、φfsAnd phifpRespectively representing relevant parameters; the formula is as follows:
φfp＝1.14e-0.66HH＞0.75
Figure FDA0002371854200000032
Figure FDA0002371854200000033
wherein, z is H/3, N is z { z [132+ z (M +345) ] } -55, M is z { z [ z (60+147z) -405] -160}
Step 4.2: determining a microprotrusion tangential force F between a radial seal land and the cylinder inner wall0；
Microprotrusion tangential force F between radial seal and cylinder inner wall0Comprises the following steps:
F0＝τ0Ac+a0Fasp
wherein F0Tangential force, τ, generated by the sealing disc0Shear strength of the microprotrusions, AcIs the actual contact area, a0Is the boundary friction coefficient; wherein the actual contact area formula is as follows:
Ac＝π2(ηβσ)2F2(H) 。
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