CN111425314B - Horizontally opposed engine piston - Google Patents
Horizontally opposed engine piston Download PDFInfo
- Publication number
- CN111425314B CN111425314B CN202010322191.9A CN202010322191A CN111425314B CN 111425314 B CN111425314 B CN 111425314B CN 202010322191 A CN202010322191 A CN 202010322191A CN 111425314 B CN111425314 B CN 111425314B
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- Prior art keywords
- piston
- cooling
- piston rod
- rod
- guide
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- 238000001816 cooling Methods 0.000 claims abstract description 84
- 238000007789 sealing Methods 0.000 claims abstract description 34
- 230000001050 lubricating effect Effects 0.000 claims abstract description 30
- 239000010705 motor oil Substances 0.000 claims abstract description 21
- 239000003921 oil Substances 0.000 claims description 34
- 238000005461 lubrication Methods 0.000 claims description 29
- 238000000034 method Methods 0.000 claims description 10
- 230000002093 peripheral effect Effects 0.000 claims description 3
- 230000006835 compression Effects 0.000 abstract description 14
- 238000007906 compression Methods 0.000 abstract description 14
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Chemical compound O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 9
- 238000006073 displacement reaction Methods 0.000 description 26
- 238000004088 simulation Methods 0.000 description 24
- 238000010586 diagram Methods 0.000 description 10
- 239000000463 material Substances 0.000 description 10
- 238000002485 combustion reaction Methods 0.000 description 4
- 230000001133 acceleration Effects 0.000 description 3
- 238000004364 calculation method Methods 0.000 description 3
- 230000000452 restraining effect Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000004075 alteration Effects 0.000 description 1
- 229940037003 alum Drugs 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000000670 limiting effect Effects 0.000 description 1
- 230000035515 penetration Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
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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
- F02F3/00—Pistons
- F02F3/0015—Multi-part pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/06—Lubricating systems characterised by the provision therein of crankshafts or connecting rods with lubricant passageways, e.g. bores
-
- 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
-
- 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
-
- 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
- F02F3/00—Pistons
- F02F3/16—Pistons having cooling means
- F02F3/20—Pistons having cooling means the means being a fluid flowing through or along piston
- F02F3/22—Pistons having cooling means the means being a fluid flowing through or along piston the fluid being liquid
-
- 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
- F16C7/00—Connecting-rods or like links pivoted at both ends; Construction of connecting-rod heads
- F16C7/02—Constructions of connecting-rods with constant length
- F16C7/023—Constructions of connecting-rods with constant length for piston engines, pumps or the like
-
- 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
- F16N—LUBRICATING
- F16N1/00—Constructional modifications of parts of machines or apparatus for the purpose of lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/06—Lubricating systems characterised by the provision therein of crankshafts or connecting rods with lubricant passageways, e.g. bores
- F01M2001/066—Connecting rod with passageways
-
- 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
- F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
- F02B75/18—Multi-cylinder engines
- F02B75/24—Multi-cylinder engines with cylinders arranged oppositely relative to main shaft and of "flat" type
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
Abstract
The invention discloses a piston of a horizontally opposed engine, which is arranged in a cylinder body of the horizontally opposed engine and is connected with a crankshaft of the horizontally opposed engine through a connecting rod, wherein the piston comprises a piston guide, a piston rod and a piston head, wherein the piston rod and the piston head are symmetrically arranged at two ends of the piston guide, and a sliding end which is in sliding connection with the connecting rod is arranged on the piston rod; a cooling loop and a lubricating loop for engine oil circulation are arranged on the piston rod and the piston head; the cooling circuit and the lubricating circuit introduce engine oil from the guide position of the piston, and the engine oil flows back into the cylinder body after passing through the piston rod and the piston head. The invention can realize the internal cooling of the piston, improve the compression ratio of the engine, and change the traditional piston movement mode, so that the piston rod can be added with a sealing structure, thereby preventing water vapor from entering the crankcase.
Description
Technical Field
The invention relates to the technical field of engines, in particular to a horizontally opposed engine piston.
Background
At present, the traditional engine is powered by the rotation of a crankshaft driven by a piston, a compression ratio parameter exists on the engine, the performance of the engine is higher than that of the engine, but the high compression ratio can bring about the knocking problem, so that the piston needs to be cooled, the traditional crank block engine is influenced by the structure, the cooling mode is generally that a nozzle is added on a cylinder body, the piston is cooled from the outside, and the cooling is difficult to realize from the inside of the piston, so that the cooling mode has lower efficiency; in addition, in the traditional engine, lateral force is generated on the piston due to the swinging motion of the connecting rod, so that the piston swings slightly in the direction perpendicular to the motion direction in the linear reciprocating motion process, and the piston is swinging actually, in addition, although the piston head and the cylinder are sealed, in consideration of thermal expansion and contraction, a small gap exists between the piston head and the cylinder in the actual assembly process, the piston ring cannot achieve hundred percent sealing, so that water vapor generated in the combustion process of the traditional engine can enter a crankcase to further influence engine oil and other parts.
Disclosure of Invention
Aiming at the technical defects, the invention aims to provide a horizontally opposed engine piston, which can realize internal cooling of the piston, improve the compression ratio of the engine and change the traditional piston movement mode, so that a sealing structure can be added on a piston rod, and further, water vapor is prevented from entering a crankcase.
In order to solve the technical problems, the invention adopts the following technical scheme:
The invention provides a piston of a horizontally opposed engine, which is arranged in a cylinder body of the horizontally opposed engine and is connected with a crankshaft of the horizontally opposed engine through a connecting rod, and is characterized by comprising a piston guide, a piston rod and a piston head, wherein the piston rod and the piston head are symmetrically arranged at two ends of the piston guide;
a cooling loop and a lubricating loop for engine oil circulation are arranged on the piston rod and the piston head;
The cooling circuit and the lubricating circuit introduce engine oil from the guide position of the piston, and the engine oil flows back into the cylinder body after passing through the piston rod and the piston head.
Preferably, the outer contour of the piston rod is a rotating body, a cavity is formed in the end, far away from the piston, of the piston rod, the cavity is of a blind hole structure, the bottom of the blind hole is communicated with the cylinder body, the end, close to the piston head, of the cavity is in sealing connection with the piston head, a cooling ring cavity is formed between the end, far away from the piston, of the piston rod and the piston head, and the cooling ring cavity is communicated with the cooling loop.
Preferably, the engine oil in the cooling loop flows into the piston rod from the piston guide, flows back into the piston rod through the cooling ring cavity and flows into the sliding end of the piston rod to form a cycle; the lubricating circuit is communicated with the cooling circuit, engine oil in the cooling circuit flows into the lubricating circuit in the circulating process and flows into the sliding contact surface of the piston head and the cylinder, and during the movement of the piston, the engine oil flows back into the cavity of the piston rod through the lubricating circuit and flows into the cylinder body through the cavity to form a circulation.
Preferably, the cooling loop comprises a plurality of cooling channels and a plurality of cooling loops, wherein the cooling channels are formed in the piston rod, one end of each cooling channel is communicated with the cylinder body through a piston guide, the other end of each cooling channel is communicated with the cooling ring cavity, one end of each cooling loop is communicated with the cooling ring cavity, and the other end of each cooling loop is communicated with the sliding end of the piston rod;
The lubricating loop comprises a plurality of lubricating channels and a plurality of lubricating channels, the lubricating channels and the lubricating channels are formed in the piston rod and the piston head, one end of each lubricating channel is communicated with the cooling channel, and the other end of each lubricating channel is communicated with the cylinder; one end of the lubrication return channel is communicated with the air cylinder, and the other end of the lubrication return channel is communicated with the cavity.
Preferably, the outer peripheral wall of the piston head is provided with a plurality of ring grooves, and one ends of the lubrication inlet channel and the lubrication return channel extend into one of the ring grooves.
Preferably, a closed annular through groove for the connecting rod to pass through is formed in the piston guide, and the connecting rod is in sliding connection with the sliding end of a piston rod arranged on the piston guide; a plurality of oil grooves are symmetrically formed in two sides of the piston guide, and the cooling loop is communicated with one of the oil grooves; and mounting holes for mounting the piston rod are formed in the two ends of the piston guide, and are communicated with the through grooves.
Preferably, the sliding end is a mounting groove formed in the end portion of the piston rod located at the piston guide.
Preferably, the piston rod is nested with an oil seal fixed in the cylinder body, the piston rod is sealed with the oil seal and slides linearly and reciprocally relative to the oil seal, and the sliding end is a mounting groove formed in the end part of the piston rod, which is positioned at the piston guide.
Preferably, the end surface of the piston, which is far away from the piston, is a circular arc concave surface.
The invention has the beneficial effects that:
(1) The application changes the working mode of the traditional crank connecting rod type engine, so that the movement mode of the piston is linear reciprocating movement, and as the traditional engine can generate lateral force on the piston due to the swinging movement of the connecting rod, the piston has micro-swinging in the direction perpendicular to the movement direction in the linear reciprocating movement process, and the piston head can not be completely sealed, the traditional engine can not be provided with a sealing structure, and the application can be provided with the sealing structure on the piston, thereby preventing water vapor generated after fuel combustion from entering the cylinder body;
(2) According to the invention, the structure of the piston is improved, and the cooling circuit is utilized to cool the piston from the inside, so that the cooling effect of the piston is greatly improved, and the compression ratio of the engine is improved; and meanwhile, the motion of the piston can be lubricated by utilizing the lubrication circuit.
(3) The invention adopts a sectional structure, namely the piston rod and the piston guide are detachable, so that the processing and the assembly are convenient, meanwhile, the piston guide is suitable for the installation of the connecting rod, and a closed grooving mode is adopted on the piston guide, so that the processing precision is improved.
Drawings
In order to more clearly illustrate the embodiments of the invention or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, it being obvious that the drawings in the following description are only some embodiments of the invention, and that other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a perspective view of a piston and connecting rod of the present invention;
FIG. 2 is a perspective view of a piston of the present invention;
FIG. 3 is a plan view of a piston of the present invention;
FIG. 4 is a cross-sectional view taken along the direction A-A in FIG. 3;
FIG. 5 is a second plan view of the piston of the present invention;
FIG. 6 is a cross-sectional view taken along the direction B-B in FIG. 5;
FIG. 7 is a third plan view of the piston of the present invention;
FIG. 8 is a cross-sectional view taken along the direction C-C in FIG. 7;
FIG. 9 is a plan view of a piston of the present invention;
FIG. 10 is a cross-sectional view taken along the direction D-D in FIG. 9;
FIG. 11 is a plan view of the piston head;
FIG. 12 is an exploded view of the piston;
FIG. 13 is a partial exploded view of the piston;
FIG. 14 is a schematic view of the piston disposed within the cylinder;
FIG. 15 is a finite element simulation diagram of a piston of the first case;
FIG. 16 is a first finite element simulation diagram of piston steering for the first case;
FIG. 17 is a second finite element simulation diagram of piston guidance for the first case;
FIG. 18 is a first finite element simulation diagram of a piston rod of the first case;
FIG. 19 is a second finite element simulation of a piston rod of the first case;
FIG. 20 is a finite element simulation diagram of a piston of a second case;
FIG. 21 is a schematic diagram of a piston-guided finite element simulation of a second case;
FIG. 22 is a second finite element simulation diagram of piston steering for the second case;
FIG. 23 is a first finite element simulation diagram of a piston rod for a second case;
FIG. 24 is a second finite element simulation diagram of a piston rod for the second case;
FIG. 25 is a finite element simulation schematic of a piston of a third case;
Fig. 26 is a finite element simulation diagram of a piston of a fourth case.
Reference numerals illustrate: 1-piston guide, 11-through groove, 12-oil groove, 2-piston rod, 21-cavity, 22-cooling inlet channel, 23-cooling return channel, 24-lubrication inlet channel, 25-lubrication return channel, 26-mounting groove, 27-through hole, 3-piston head, 31-ring groove, 32-cooling ring cavity, 33-arc concave surface, 4-sealing plate, 5-fixing pin, 6-oil seal, 71-connecting rod body, 72-guide rail, 73-slip ring, 74-revolute pair, 8-cylinder body, 9-cylinder and 10-exhaust channel.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
Examples
As shown in fig. 1, the present invention provides a horizontally opposed engine piston, which is used in a horizontally opposed double-crankshaft engine and is connected to the double-crankshaft through a connecting rod, that is, two connecting portions are provided on the connecting rod and are respectively connected to the crankshafts, that is, the connecting rod includes a connecting rod body 71 and a slip ring 73, the slip ring 73 is slidably connected to the connecting rod body 71 to form a sliding pair, a rotating pair 74 is provided on the connecting rod body 71, meanwhile, the slip ring 73 is also a rotating pair, the slip ring 73 and the rotating pair 74 are respectively connected to the crankshafts of the engine, and both sides of the connecting rod body 71 are provided with guide rails 72 and are integrally formed with the connecting rod body 71, so that the problem that the two guide rails 72 are heavy due to different materials being heated is reduced, and the two guide rails 72 are slidably connected to the piston rod 2, that is slidably connected to the sliding ends described below, so that the piston drives the double-crankshaft to rotate.
Further, referring to fig. 2, the piston includes a piston guide 1, and a piston rod 2 and a piston head 3 symmetrically disposed at two ends of the piston guide 1, where the piston guide 1 and the piston rod 2 are detachably connected, i.e. can be separated, thereby forming a three-stage structure, i.e. two piston rods 2 and one piston guide 1, so as to facilitate processing and assembly; referring to fig. 12, a piston rod 2 is connected with a piston guide 1 by a fixing pin 5, and mounting holes for mounting the piston rod 2 are distributed at two ends of the piston guide 1, so that the piston rod 2 and the piston guide 1 are fixed together by the fixing pin 5;
The piston head 3 is fixedly connected with the piston rod 2, the piston head 3 is fixed on the piston rod 2 through welding, the piston head 3 is used as a sealing end matched with a cylinder 9 of an engine, namely the piston head 3 is sealed with the cylinder movement 9, the piston guide 1 is used as a guiding end matched with the cylinder body 8, namely the movement direction of the whole piston is in linear reciprocating movement by utilizing the matched limiting effect of the piston guide 1 and the cylinder body 8, and a piston guide groove for the movement of the piston guide 1 is arranged in the engine cylinder body 8 in a matched manner;
The outer contour of the piston rod 2 is a rotating body, the end part of the piston rod 2 far away from the piston guide 1 is provided with a cavity 21, the cavity 21 is of a blind hole structure, the bottom of the blind hole is communicated with the cylinder body 8, and as shown in fig. 2 and 12, one end of the piston rod 2 close to the piston guide 1 is provided with a through hole 27, and as the piston rod 2 is fixed with the piston guide 1, the piston guide 1 is also provided with a through hole 27 corresponding to the piston rod 2, so that the cavity 21 is communicated with the cylinder body 8, and the end part of the cavity 21 close to the piston head 3 is in sealing connection with the piston head 3, and as shown in fig. 4 and 13, the end part of the cavity 21 is sealed by adopting a sealing plate 4 as shown in the blind hole structure; the end of the piston rod 2 remote from the piston guide 1 and the piston head 3 have a cooling ring chamber 32, which cooling ring chamber 32 communicates with a cooling circuit described below; because the piston rod 2 is a rotating body and the piston moves in a straight reciprocating manner according to the structure of the piston, an oil seal 6 (which is an existing structure) can be arranged on the piston rod, so that sealing is realized, the oil seal 6 can be fixed on the cylinder body 8, the oil seal 6 is sealed with the cylinder 9 and also dynamically sealed with the piston rod 2, water vapor generated after fuel combustion can be prevented from entering a crankcase (namely the cylinder body 8) by the oil seal 6, and as the conventional engine generates lateral force on the piston due to swinging movement of a connecting rod, the piston swings slightly in the direction perpendicular to the moving direction in the straight reciprocating movement process, and the piston head cannot realize complete sealing, therefore, the conventional engine cannot be additionally provided with the oil seal 6 on the piston rod in the running process, so that the piston of the application can enable the inner cylinder 9 of the cylinder body 8 to be sealed with the outer side of the oil seal 6, the gap formed between the piston rod 2 and the cylinder 9 is utilized to store water vapor, and a water vapor discharge exhaust channel 10 is arranged on the cylinder body 8, and attention is required, namely the piston head 10 is required to be positioned on the outer side of the position limit of the piston head 3, namely the piston head 3 cannot move to the exhaust channel 10, as shown in fig. 6, so that the water vapor can be prevented from entering the cylinder 8.
Further, a cooling circuit and a lubricating circuit for oil circulation are arranged in the piston and are respectively used for cooling and lubricating the piston head 3, the cooling circuit and the lubricating circuit are used for introducing oil from the piston guide 1, the oil flows back into the cylinder body 8 again after passing through the piston rod 2 and the piston head 3, and a sliding end which is in sliding connection with the connecting rod is arranged on the piston rod 2;
I.e. the engine oil in the cooling circuit flows into the piston rod 2 from the position of the piston guide 1, flows back into the piston rod 2 through the cooling ring cavity 32 and flows into the sliding end of the piston rod to form a cycle, and simultaneously forms lubrication of the connecting rod at the sliding end, and as shown in fig. 4 and 6, the sliding end is provided with a mounting groove 26 at the end of the piston rod 2 positioned at the piston guide 1, the connecting rod is in sliding connection with the mounting groove 26, i.e. two guide rails 72 of the connecting rod are in sliding connection with the mounting groove 26; the lubrication circuit communicates with a cooling circuit, through which oil flows into the lubrication circuit during circulation and into the sliding contact surface of the piston head 3 and the cylinder 9 (i.e. the wall of the cylinder), and through which oil flows back into the cavity 21 of the piston rod 2 during movement of the piston and into the cylinder body 8 via the cavity 21 to form a cycle.
Further, in order to realize the above-described cycle of cooling and lubrication, fig. 4,6, 8, and 10 show:
The cooling loop comprises a plurality of cooling inlet channels 22 and a plurality of cooling return channels 23 which are arranged on the piston rod 2, one end of the cooling inlet channel 22 is communicated with the cylinder body 8 through the piston guide 1, the other end of the cooling inlet channel 22 is communicated with the cooling annular cavity 32, one end of the cooling return channel 23 is communicated with the cooling annular cavity 32, and the other end of the cooling return channel 23 is communicated with the cylinder body 8 through the piston guide 1;
The lubrication circuit comprises a plurality of lubrication channels 24 and a plurality of lubrication channels 25 which are arranged on the piston rod 2 and the piston head 3, one end of the lubrication channel 24 is communicated with the cooling channel 23, and the other end of the lubrication channel 25 is communicated with the cylinder 9; one end of the lubrication return channel 25 is communicated with the air cylinder 9, and the other end of the lubrication return channel 25 is communicated with the cavity 21; the outer peripheral wall of the piston head 3 is provided with a plurality of ring grooves 31, one end of the lubrication inlet channel 24 and one end of the lubrication return channel 25 extend into one of the ring grooves 31, and as can be seen in conjunction with fig. 4, the number of the ring grooves 31 is 3, the lowest two are used for installing gas rings, the uppermost one is used for installing oil rings, and one end of the lubrication inlet channel 24 and one end of the lubrication return channel 25 extend into the uppermost ring groove 31 for installing the oil rings.
In order to match with the use of the connecting rod, the piston guide 1 is provided with a closed annular through groove 11 for the connecting rod to pass through, the connecting rod is in sliding connection with the sliding end of the piston rod 2 arranged on the piston guide 1, the precision of the closed through groove 11 is easier to ensure in processing, and compared with the opening form of the piston (CN 205744177U) of the previous generation (the opening design can cause shrinkage, so that one side of the outer circle of the piston guide 1 is large and the other side is small), the processing precision is easier to improve, because the opening of the through groove 11 can lead the piston guide 1 to form a thin-wall characteristic, the open through groove is larger in processing, and the precision is poorer than that of the closed through groove due to thermal expansion and cold shrinkage; the two sides of the piston guide 1 are symmetrically provided with a plurality of oil grooves 12, the cooling circuit is communicated with one of the oil grooves 12, as shown in fig. 4, a cooling inlet 22 of the cooling circuit is communicated with one of the oil grooves 12 to introduce engine oil, and a through hole communicated with the oil groove 12 is correspondingly formed in a matched piston guide groove arranged in the engine cylinder 8 for the movement of the piston guide 1, and the through hole penetrates through the cylinder 8 to introduce the engine oil into the oil groove 12.
With reference to fig. 4 and 11, the end of the piston head 3 is structurally optimized, and the surface of the end of the piston head far away from the piston guide 1 is a circular arc concave surface 33, and the cambered surface is arranged to enable the gas to rotate, so that the gas and the air can be mixed more fully, a higher tumble ratio is formed, and high-speed combustion is realized.
According to the structure of the piston, we have made some finite element simulations to prove the feasibility, wherein the simulation software and the processing software used are ansa, hyperworks, abaqus, and the following is specific:
Materials: the piston material is alum (7075-T6), the tensile stress is less than or equal to 120Mpa, and the compressive stress is less than or equal to 240Mpa; link (connecting rod) materials are: 42CrMo, the tensile stress is less than or equal to 350Mpa, and the compressive stress is less than or equal to 700Mpa;
The simulation is to simulate the situation when the piston reaches the bottom dead center in the cylinder body in reality, and the simulation here requires that the connecting rod cannot move and rotate at all, so that 1-6 degrees of freedom are restrained; if the contact part is not contacted, penetration of parts can occur in the simulation calculation process, and even some parts fly away; the nodal forces applied at the nodes are inherent properties of the simulated object: inertia, the resulting inertial force, the value resulting from multiplying the mass of the entire piston by the acceleration reached by the piston rod at this point; the connecting rod is actually applied to the middle part of the connecting rod, which is far away from one end of the sliding block, because the condition can be met under more severe working conditions, and the actual situation is not problematic.
First case: f acts in the middle of the connecting rod, -the inertial force in the Y direction;
parts: the piston head, the sealing plate, the connecting rod, the piston guide and fixing pin;
Boundary conditions: restraining link (dof 12356), contact portion making contact, each member applying node force F/node number = ma/node number = 19785N/node number;
Acceleration: a=rw 2＝(146.5/2)/1000*(4000*2π/60)2 = 12856N/kg (where 146.5/2 is radius of gyration, 146.5 is design size, 4000 is rotational speed)
Piston mass: m=1.539 kg (for design quality)
Yielding f=ma=1.539×12856= 19785N
The simulation results are that: (for simplicity of illustration, we only give a partial simulation)
Dis (maximum total displacement before and after calculation): 0.26mm, as shown in FIG. 15;
z displacement (calculate maximum Z displacement before and after): 0.11mm;
maximum tensile stress of the sealing plate: 9.7Mpa;
Maximum compressive stress of the sealing plate: -26.3Mpa;
Maximum tensile stress of the connecting rod: 148.6Mpa;
maximum compression stress of connecting rod: -174.7Mpa;
Piston guiding maximum tensile stress: 58.7MPa, as shown in FIG. 16;
piston guiding maximum compressive stress: -107.7Mpa as shown in figure 17;
Maximum tensile stress of the piston rod: 56.7MPa, as shown in FIG. 18;
Maximum compression stress of piston rod: -148.4Mpa, as shown in figure 19;
Maximum tensile stress of piston head: 129.0Mpa;
Maximum compressive stress of piston head: -38.2Mpa;
Conclusion:
1. Maximum displacement when node force of 19785N total is applied in Y direction: 0.26mm; the Z-displacement 11 wire is smaller than the reserved 25 wires (namely 0.025mm, the reserved distance is designed size), and the piston head cannot collide with the cylinder wall;
2. When node force of 19785N is applied in the Y direction, the sealing plate of the piston head, the piston body, the connecting rod, the piston guide and the sliding block all meet the following conditions: the tensile stress is less than or equal to 120MPa;
3. when node force of 19785N is applied in the Y direction, the piston head sealing plate, the piston body, the connecting rod, the piston guide, the sliding block and the pin all meet the following conditions: the compressive stress is less than or equal to 240MPa;
4. when the total node force of 19785N is applied in the Y direction, the maximum tensile stress of the piston head= 129.0MPa > 120MPa, and the maximum tensile stress is slightly beyond the ideal range. The actual yield value of the material is 480MPa, and the yield value is far from being reached, so that the material is acceptable.
Second case: f acts in the middle of the connecting rod, +y inertial force;
parts: the piston head, the sealing plate, the connecting rod, the piston guide and fixing pin;
Boundary conditions: restraining link (dof 12356), contact portion making contact, each member applying node force F/node number = ma/node number = 19785N/node number;
acceleration: a=rw 2＝(146.5/2)/1000*(4000*2π/60)2 = 12856N/kg
Piston mass: m=1.539 kg
Yielding f=ma=1.539×12856= 19785N
The simulation results are that: (for simplicity of illustration, we only give a partial simulation)
Dis (maximum total displacement before and after calculation): 0.26mm, as shown in FIG. 20;
Z displacement (calculate maximum Z displacement before and after): 0.10mm;
Maximum tensile stress of the sealing plate: 9.0Mpa;
Maximum compressive stress of the sealing plate: -27.0Mpa;
maximum tensile stress of the connecting rod: 158.4Mpa;
maximum compression stress of connecting rod: 169.7MPa;
piston guiding maximum tensile stress: 59.1MPa, as shown in FIG. 21;
piston guiding maximum compressive stress: -107.2Mpa as shown in figure 22;
maximum tensile stress of the piston rod: 57.4MPa, as shown in FIG. 23;
Maximum compression stress of piston rod: -150.4Mpa as shown in figure 24;
maximum tensile stress of piston head: 129.1Mpa;
Maximum compressive stress of piston head: -38.2Mpa;
Conclusion:
1. maximum displacement when node force of 19785N total is applied in Y direction: 0.26mm; the Z-displacement 10 wire is smaller than the reserved 25 wires, and the piston head cannot collide with the cylinder wall;
2. When node force of 19785N is applied in the Y direction, the sealing plate of the piston head, the piston body, the connecting rod, the piston guide and the sliding block all meet the following conditions: the tensile stress is less than or equal to 120MPa;
3. when node force of 19785N is applied in the Y direction, the piston head sealing plate, the piston body, the connecting rod, the piston guide, the sliding block and the pin all meet the following conditions: the compressive stress is less than or equal to 240MPa;
4. When node force of 19785N is applied in the Y direction, the maximum tensile stress of the piston head=129.1MPa > 120MPa, and the maximum tensile stress is slightly beyond an ideal range. The actual yield value of the material is 480MPa, and the yield value is far from being reached, so that the material is acceptable.
Third case: the piston head surface of the cylinder applies 10 megapascals pressure and is transferred to the middle part of the connecting rod;
parts: piston head, piston head sealing plate, piston rod, connecting rod, piston guide and fixing pin
Boundary conditions: restraining link (dof 12356), contact portion to make contact,
Applied force: fz=10 pi (43.38) 2= 59119N
Intake side: fzfeed = 32644N;
Exhaust side: fz row = 26470N;
fsynthesis=59114N.
The simulation results are that: (for simplicity of illustration, we only give a partial simulation)
As shown in fig. 25:
maximum displacement: 0.65mm
Intake side displacement: 0.65mm
Exhaust side displacement: 0.60mm
Z displacement: the diameter of the air flow is 0.20mm,
Initial slot height of one slot intake side: 1.220mm (one groove refers to the lowest one in FIG. 4)
Final slot height of one slot intake side: 1.204mm
Air inlet side one-groove height variation: 1.220-1.204=0.016 mm
Initial slot height of one slot exhaust side: 1.220mm
Final slot height of one slot exhaust side: 1.205mm
Exhaust side one-slot height variation: 1.220-1.205=0.015 mm
Maximum tensile stress of the sealing plate: 94.4MPa
Maximum compressive stress of the sealing plate: -73.3MPa
Maximum tensile stress of the connecting rod: 398.9MPa
Maximum compression stress of connecting rod: -501.1MPa
Piston guiding maximum tensile stress: 97.8MPa
Piston guiding maximum compressive stress: -135.3MPa
Maximum tensile stress of the piston rod: 100.2MPa
Maximum compression stress of piston rod: -236.8MPa
Maximum tensile stress of the sliding block: 48.4MPa
Maximum compression stress of the sliding block: -146.8MPa
Maximum tensile stress of piston head: 105.8MPa
Maximum compressive stress of piston head: -140.9MPa
Conclusion:
1. intake side displacement (maximum displacement) when a cylinder end applies 59119N pressure: 0.65mm, exhaust side displacement: 0.60mm; the Z-displacement 20 wires are smaller than the reserved 25 wires, and the piston head cannot collide with the cylinder wall;
2. when the cylinder end applies 59119N pressure, the air inlet side of one groove contracts 1.6 wires, and the air outlet side of the other groove contracts 1.5 wires, which are smaller than the reserved 3-4 wire space;
3. When the cylinder end applies 59119N pressure, the piston head sealing plate, the piston body, the piston guide and the sliding block all meet the following conditions: the tensile stress is less than or equal to 120MPa, and the compressive stress is less than or equal to 240MPa;
4. When the cylinder end applies 59119N pressure, the connecting rod meets the following conditions: the compressive stress is less than or equal to 700MPa;
5. when the cylinder end applies 59119N pressure, the maximum tensile stress of the connecting rod= 398.9MPa > 350MPa,
Out of the ideal range. The actual yield value of the material is 900MPa, and the yield value is far from being reached, so that the material is acceptable.
Fourth case: the piston head surface of the cylinder applies 10 megapascals of pressure, which is transferred to the 25mm of connecting rod middle side deflection part,
Parts: piston head, piston head sealing plate, piston rod, connecting rod, piston guide and stator
Applied force: fz=10 pi (43.38) 2= 59119N
Intake side: fzfeed = 32644N;
Exhaust side: fz row = 26470N;
fclose=59114N
Obtained by simulation (omitted here also for simulation screenshots)
As shown in fig. 25
Maximum displacement: 0.55mm
Intake side displacement: 0.55mm
Exhaust side displacement: 0.51mm
Z displacement: 0.05mm
Initial slot height of one slot intake side: 1.220mm (one groove refers to the lowest one in FIG. 4)
Final slot height of one slot intake side: 1.205mm
Air inlet side one-groove height variation: 1.220-1.205=0.015 mm
Initial slot height of one slot exhaust side: 1.220mm
Final slot height of one slot exhaust side: 1.204mm
Exhaust side one-slot height variation: 1.220-1.204=0.014 mm
Maximum tensile stress of the sealing plate: 94.4MPa
Maximum compressive stress of the sealing plate: -73.3MPa
Maximum tensile stress of the connecting rod: 268.4MPa
Maximum compression stress of connecting rod: -328.8MPa
Piston guiding maximum tensile stress: 65.9MPa
Piston guiding maximum compressive stress: -97.3MPa
Maximum tensile stress of the piston rod: 95.6MPa
Maximum compression stress of piston rod: -236.8MPa
Maximum tensile stress of piston head: 105.6MPa
Maximum compressive stress of piston head: -141.1MPa
Conclusion:
1. intake side displacement (maximum displacement) when a cylinder end applies 59119N pressure: 0.55mm, exhaust side displacement: 0.51mm; the Z-displacement 5 wire is smaller than the reserved 25 wires, and the piston head cannot collide with the cylinder wall;
2. when the cylinder end applies 59119N pressure, the air inlet side of one groove contracts 1.5 wires, the air outlet side of the other groove contracts 1.4 wires, and the air inlet side of the other groove contracts less than the reserved 3-4 wire space;
3. When the cylinder end applies 59119N pressure, the piston head sealing plate, the piston body, the piston guide and the sliding block all meet the following conditions: the tensile stress is less than or equal to 120MPa, and the compressive stress is less than or equal to 240MPa;
4. when the pressure of 59119N is applied to the gas end, the connecting rod meets the following conditions: the tensile stress is less than or equal to 350MPa, and the compressive stress is less than or equal to 700MPa.
When the piston is used, the piston is arranged in a horizontally opposite double-crankshaft engine and is connected with the double crankshafts through a connecting rod, namely, a revolute pair 74 and a sliding ring 73 on the connecting rod are respectively connected with the crankshafts, a piston guide 1 is used as a guide end of the piston to enable the movement mode of the piston to be linear reciprocating movement, and a piston head 3 is used as a sealing end of the piston and is dynamically sealed with a cylinder 9; the mixed oil gas burns in the cylinder 9, the arc concave surface 33 of the piston head 3 accelerates the mixing effect, and then power is generated to drive the crankshaft to rotate, and in the process of the movement of the piston, the oil seal 6 plays a role in sealing, so that the generated water vapor is prevented from entering the cylinder body 8; the engine oil in the cooling loop and the lubricating loop flows simultaneously, in the cooling loop, the engine oil enters the cooling inlet channel 22 through the oil groove 12 of the piston guide 1, flows through the cooling annular cavity 32 and enters the cooling loop 23, flows into the sliding end of the piston rod 2 from the cooling loop 23, and further forms a cycle, and simultaneously lubricates the sliding of the connecting rod; the engine oil in the lubrication circuit flows out of the piston head 3 from the cooling circuit 23 through the lubrication inlet 24 and enters the wall of the cylinder 9, and is scraped back in the process of the movement of the piston, and then enters the cavity 21 through the lubrication circuit 25, and flows into the cylinder 8 through the cavity 21 and the through hole 27 formed in the piston guide 1, so that a cycle is formed.
It will be apparent to those skilled in the art that various modifications and variations can be made to the present invention without departing from the spirit or scope of the invention. Thus, it is intended that the present invention also include such modifications and alterations insofar as they come within the scope of the appended claims or the equivalents thereof.
Claims (6)
1. The piston of the horizontal opposed engine is arranged in a cylinder body of the horizontal opposed engine and is connected with a crankshaft of the horizontal opposed engine through a connecting rod, and is characterized by comprising a piston guide, a piston rod and a piston head, wherein the piston rod and the piston head are symmetrically arranged at two ends of the piston guide, the piston guide is detachably connected with the piston rod, the piston head is fixedly connected with the piston rod, the piston head is used as a sealing end matched with a cylinder of the engine, the piston guide is used as a guiding end matched with the cylinder body, and the piston rod is provided with a sliding end in sliding connection with the connecting rod;
a cooling loop and a lubricating loop for engine oil circulation are arranged on the piston rod and the piston head;
the cooling loop and the lubricating loop introduce engine oil from a guide position of the piston, and the engine oil flows back into the cylinder body again after passing through the piston rod and the piston head;
The outer contour of the piston rod is a rotating body, a cavity is formed in the end, far away from the piston, of the piston rod, the cavity is of a blind hole structure, the bottom of the blind hole is communicated with the cylinder body, the end, close to the piston head, of the cavity is in sealing connection with the piston head, a cooling ring cavity is formed between the end, far away from the piston, of the piston rod and the piston head, and the cooling ring cavity is communicated with the cooling loop;
The cooling loop comprises a plurality of cooling channels and a plurality of cooling loops, the cooling channels are formed in the piston rod, one end of each cooling channel is communicated with the cylinder body through piston guide, the other end of each cooling channel is communicated with the cooling annular cavity, one end of each cooling loop is communicated with the cooling annular cavity, and the other end of each cooling loop is communicated with the sliding end of the piston rod;
The lubricating loop comprises a plurality of lubricating channels and a plurality of lubricating channels, the lubricating channels and the lubricating channels are formed in the piston rod and the piston head, one end of each lubricating channel is communicated with the cooling channel, and the other end of each lubricating channel is communicated with the cylinder; one end of the lubrication return channel is communicated with the air cylinder, and the other end of the lubrication return channel is communicated with the cavity;
the piston rod is nested with an oil seal fixed in the cylinder body, and the piston rod is sealed with the oil seal and slides linearly and reciprocally relative to the oil seal.
2. A horizontally opposed engine piston as set forth in claim 1 wherein oil in said cooling circuit flows from the piston guide into the piston rod, back into the piston rod via said cooling ring cavity and into the sliding end of the piston rod to form a cycle; the lubricating circuit is communicated with the cooling circuit, engine oil in the cooling circuit flows into the lubricating circuit in the circulating process and flows into the sliding contact surface of the piston head and the cylinder, and during the movement of the piston, the engine oil flows back into the cavity of the piston rod through the lubricating circuit and flows into the cylinder body through the cavity to form a circulation.
3. A horizontally opposed engine piston as set forth in claim 1 wherein said piston head has a plurality of ring grooves formed in its peripheral wall, one end of said lubrication inlet and said lubrication return extending into one of said ring grooves.
4. A horizontally opposed engine piston as set forth in claim 1 wherein said piston guide defines a closed annular channel through which said connecting rod passes, said connecting rod being slidably connected to the sliding end of a piston rod mounted in the piston guide; a plurality of oil grooves are symmetrically formed in two sides of the piston guide, and the cooling loop is communicated with one of the oil grooves; and mounting holes for mounting the piston rod are formed in the two ends of the piston guide, and are communicated with the through grooves.
5. A horizontally opposed engine piston as set forth in claim 4 wherein the sliding end is a mounting groove formed in the end of the piston rod at the piston guide.
6. A horizontally opposed engine piston as set forth in claim 1 wherein the end of the piston directed away from the piston is a concave arcuate surface.
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| US20130186365A1 (en) * | 2011-09-06 | 2013-07-25 | Mahle Koenig Kommanditgesellschaft Gmbh & Co Kg | Piston, cylinder and engine with crown precision cooling |
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