CN111425314A - Horizontal opposed engine piston - Google Patents
Horizontal opposed engine piston Download PDFInfo
- Publication number
- CN111425314A CN111425314A CN202010322191.9A CN202010322191A CN111425314A CN 111425314 A CN111425314 A CN 111425314A CN 202010322191 A CN202010322191 A CN 202010322191A CN 111425314 A CN111425314 A CN 111425314A
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- Prior art keywords
- piston
- cooling
- engine
- piston rod
- lubricating
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- 238000001816 cooling Methods 0.000 claims abstract description 83
- 230000001050 lubricating effect Effects 0.000 claims abstract description 45
- 239000010705 motor oil Substances 0.000 claims abstract description 24
- 239000003921 oil Substances 0.000 claims description 32
- 238000000034 method Methods 0.000 claims description 13
- 238000005461 lubrication Methods 0.000 claims description 9
- 230000002093 peripheral effect Effects 0.000 claims description 3
- 238000007789 sealing Methods 0.000 abstract description 33
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Chemical compound O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 9
- 230000006835 compression Effects 0.000 abstract description 6
- 238000007906 compression Methods 0.000 abstract description 6
- 238000006073 displacement reaction Methods 0.000 description 26
- 238000004088 simulation Methods 0.000 description 24
- 238000010586 diagram Methods 0.000 description 13
- 239000000463 material Substances 0.000 description 10
- 238000004364 calculation method Methods 0.000 description 5
- 230000001133 acceleration Effects 0.000 description 3
- 238000009434 installation Methods 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000002485 combustion reaction Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000000295 fuel oil Substances 0.000 description 2
- 230000000452 restraining effect Effects 0.000 description 2
- 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
- 238000007599 discharging Methods 0.000 description 1
- 230000035515 penetration Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- 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 horizontally opposed engine piston, which is arranged in a cylinder body of a horizontally opposed engine and is connected with a crankshaft of the horizontally opposed engine through a connecting rod, and comprises a piston guide, a piston rod and a piston head which are symmetrically arranged at two ends of the piston guide, wherein 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 circuit and the lubricating circuit lead in the engine oil from the piston guide position, and the engine oil flows back to the cylinder body again after passing through the piston rod and the piston head. The invention 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 the piston rod, 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, a traditional engine is powered by a crankshaft driven by a piston to rotate, a compression ratio parameter exists on the engine, the compression ratio is higher than the performance of the engine, but the high compression ratio can bring about the problem of knocking, so that the piston needs to be cooled, and compared with the traditional crank block engine, the traditional crank block engine is influenced by the structure of the engine, the cooling mode is generally that a nozzle is additionally arranged on a cylinder body, the piston is cooled from the outside, and the cooling from the inside of the piston is difficult to realize, so that the efficiency of the cooling mode is lower; in addition, in the conventional engine, a connecting rod generates a lateral force on a piston due to swinging motion, so that the piston slightly swings in a direction perpendicular to a moving direction in a linear reciprocating motion process, and the piston actually swings, and in addition, although the piston head and the cylinder are sealed, a small gap exists between the piston head and the cylinder in an actual assembly manner and the piston ring cannot be sealed by hundreds of percent in consideration of thermal expansion and cold contraction, so that water vapor generated in a combustion process of the conventional engine enters a crankcase, and further influences engine oil and other parts.
Disclosure of Invention
In view of 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 an engine, change the traditional piston movement mode, increase a sealing structure on a piston rod and further prevent water vapor from entering a crankcase.
In order to solve the technical problems, the invention adopts the following technical scheme:
the invention provides a horizontally opposed engine piston, which is arranged in a cylinder body of a horizontally opposed engine and is connected with a crankshaft of the horizontally opposed engine through a connecting rod, and is characterized in that the piston comprises a piston guide, a piston rod and a piston head which 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 guide 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 circuit and the lubricating circuit lead in the engine oil from the piston guide position, and the engine oil flows back to the cylinder body again 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 guide, of the piston rod, the cavity is of a blind hole structure, the hole bottom of the blind hole is communicated with the cylinder body, the end, close to the piston head, of the cavity is connected with the piston head in a sealing mode, a cooling ring cavity is formed between the end, far away from the piston guide, of the piston rod and the piston head, and the cooling ring cavity is communicated with the cooling loop.
Preferably, the oil in the cooling circuit 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 circulation; the lubricating circuit is communicated with the cooling circuit, the engine oil in the cooling circuit flows into the lubricating circuit and flows into the sliding contact surface between the piston head and the cylinder in the circulating process, and 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 in the movement process of the piston.
Preferably, the cooling loop comprises a plurality of cooling inlet channels and a plurality of cooling return channels, the cooling inlet channels are arranged on the piston rod, one end of each cooling inlet channel is communicated with the cylinder body through piston guiding, the other ends of the cooling inlet channels are communicated with the cooling ring cavity, one end of each cooling return channel is communicated with the cooling ring cavity, and the other ends of the cooling return channels are communicated with the sliding end of the piston rod;
the lubricating loop comprises a plurality of lubricating inlet channels and a plurality of lubricating return channels which are arranged on the piston rod and the piston head, one end of each lubricating inlet channel is communicated with the cooling return channel, and the other end of each lubricating inlet channel is communicated with the cylinder; one end of the lubricating return passage is communicated with the cylinder, and the other end of the lubricating return passage 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 lubricating inlet channel and the lubricating return channel extend into one of the ring grooves.
Preferably, the piston guide is provided with a closed annular through groove for the connecting rod to pass through, and the connecting rod is connected with the sliding end of the piston rod arranged on the piston guide in a sliding manner; 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 at two ends of the piston guide and are communicated with the through grooves.
Preferably, the sliding end is an installation groove formed at the end 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 in a reciprocating manner relative to the oil seal, and the sliding end is an installation groove formed in the end portion, located at the piston guide, of the piston rod.
Preferably, the end surface of the piston away from the piston guide is a circular arc concave surface.
The invention has the beneficial effects that:
(1) the working mode of a traditional crank connecting rod type engine is changed, so that the motion mode of a piston is linear reciprocating motion, and because the traditional engine generates lateral force on the piston due to the swinging motion of a connecting rod, the piston slightly swings in the direction vertical to the motion direction in the linear reciprocating motion process, and a piston head cannot be completely sealed, the traditional engine cannot be provided with a sealing structure, but the sealing structure can be arranged on the piston in the application, so that water vapor generated after fuel oil is combusted is prevented from entering a cylinder body;
(2) the structure of the piston is improved, and the cooling of the piston can be carried out from the inside by utilizing the cooling loop, so that the cooling effect of the piston is greatly improved, and the compression ratio of an engine is improved; while the motion of the piston can be lubricated by means of a 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, a closed slotting mode is adopted on the piston guide, the processing precision is improved, compared with an open design, the open design can cause necking, so that one side of the excircle of the piston guide is large, and the other side is small, so that the precision is influenced.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
FIG. 1 is a perspective view of a piston and connecting rod of the present invention;
FIG. 2 is a perspective view of the piston of the present invention;
FIG. 3 is a first plan view of the piston of the present invention;
FIG. 4 is a cross-sectional view taken along line A-A of 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 line B-B of 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 line C-C of FIG. 7;
FIG. 9 is a fourth plan view of the piston of the present invention;
FIG. 10 is a cross-sectional view taken along line D-D of 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 in the cylinder;
FIG. 15 is a schematic diagram of a finite element simulation of the piston in a first condition;
FIG. 16 is a first schematic diagram of a finite element simulation of piston guidance in a first case;
FIG. 17 is a second schematic diagram of a finite element simulation of piston guidance in a first case;
FIG. 18 is a first schematic diagram of a finite element simulation of a piston rod in a first case;
FIG. 19 is a second schematic view of a finite element simulation of a piston rod in a first case;
FIG. 20 is a schematic diagram of a finite element simulation of a piston in a second condition;
FIG. 21 is a first schematic diagram of a finite element simulation of piston guidance in a second case;
FIG. 22 is a second schematic diagram of a finite element simulation of piston guidance in a second case;
FIG. 23 is a first schematic diagram of a finite element simulation of a piston rod in a second case;
FIG. 24 is a second schematic view of a finite element simulation of a piston rod in a second case;
FIG. 25 is a schematic diagram of a finite element simulation of a piston in a third case;
FIG. 26 is a schematic diagram of a finite element simulation of a piston in a fourth case.
Description of reference numerals: 1-piston guide, 11-through groove, 12-oil groove, 2-piston rod, 21-cavity, 22-cooling inlet channel, 23-cooling return channel, 24-lubricating inlet channel, 25-lubricating 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 technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present 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, namely, the connecting rod is provided with two connecting parts which are respectively connected with the crankshafts, namely, the connecting rod comprises a connecting rod body 71 and a sliding ring 73, the sliding ring 73 is connected with the connecting rod body 71 in a sliding way to form a sliding pair, the connecting rod body 71 is provided with a rotating pair 74, meanwhile, the sliding ring 73 is a rotating pair, the sliding ring 73 and the rotating pair 74 are respectively connected with a crankshaft of the engine, guide rails 72 are arranged at two sides of the connecting rod body 71 and are integrally formed with the connecting rod body 71, and then reduce the two and adopt the split type to cause the heavy problem of machine operation because of the material changes when being heated, two guide rails 72 are connected with piston rod 2 sliding respectively, namely with the sliding end sliding connection described below, and then realize that the piston drives the rotation of double-crankshaft.
Further, with reference to fig. 2, the piston includes a piston guide 1, a piston rod 2 and a piston head 3 symmetrically disposed at two ends of the piston guide 1, the piston guide 1 is detachably connected to the piston rod 2, that is, the two can be separated, so as to form a three-stage structure, that is, two piston rods 2 and one piston guide 1, thereby facilitating processing and assembling; referring to fig. 12, the piston rod 2 is connected to the 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, and 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 by 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 9, and the piston guide 1 is used as a guide end matched with the cylinder body 8, namely, the motion direction of the whole piston is in linear reciprocating motion by utilizing the matching limit function of the piston guide 1 and the cylinder body 8, therefore, a piston guide groove for the piston guide 1 to move is arranged in the cylinder body 8 of the engine in a matched manner;
the outer contour of the piston rod 2 is a rotating body, the end of the piston rod 2 far away from the piston guide 1 is provided with a cavity 21, the cavity 21 is a blind hole structure, the bottom of the blind hole is communicated with the cylinder body 8, in combination with fig. 2 and 12, one end of the piston rod 2 close to the piston guide 1 is provided with a through hole 27, because the piston rod 2 is fixed with the piston guide 1, the piston guide 1 is also provided with the through hole 27 corresponding to the piston rod 2, further the cavity 21 is communicated with the cylinder body 8, the end of the cavity 21 close to the piston head 3 is hermetically connected with the piston head 3, in combination with fig. 4 and 13, because the cavity 21 is a blind hole structure, the end of the cavity 21 is sealed by a sealing plate 4; a cooling ring cavity 32 is arranged between the end of the piston rod 2 far away from the piston guide 1 and the piston head 3, and the cooling ring cavity 32 is communicated with a cooling circuit which is described below; because the piston rod 2 is a rotating body, and according to the structure of the piston, the motion of the piston is linear reciprocating motion, an oil seal 6 (which is an existing structure) can be arranged on the piston rod, so as to realize sealing, the oil seal 6 can be fixed on a cylinder body 8, the oil seal 6 is used for sealing a cylinder 9 and is dynamically sealed with the piston rod 2, the oil seal 6 can prevent water vapor generated after fuel oil is combusted from entering a crankcase (namely the cylinder body 8), because a traditional engine generates lateral force on the piston due to the swinging motion of a connecting rod, the piston has slight swinging in the direction vertical to the motion direction in the linear reciprocating motion process, and the piston head can not be completely sealed, so that the oil seal 6 can not be additionally arranged on the piston rod to seal in the operation process of the traditional engine, and the piston in the application can be used for sealing the inner cylinder 9 of the cylinder body 8 and the outer side of the oil seal 6, the gap formed between the piston rod 2 and the cylinder 9 is used for storing water vapor, and the cylinder 8 is provided with a vent passage 10 for discharging water vapor, and it should be noted that the vent passage 10 is positioned outside the position limit of the piston head 3, i.e. the piston head 3 does not move to the vent passage 10, as shown in fig. 14, for which purpose, we give a schematic view, and it can be seen that the oil seal 6 can prevent water vapor from entering the cylinder 8.
Furthermore, a cooling circuit and a lubricating circuit for engine 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 introduce the engine oil from the piston guide 1, the engine oil flows back into the cylinder body 8 again after passing through the piston rod 2 and the piston head 3, and the piston rod 2 is provided with a sliding end in sliding connection with the connecting rod;
that is, the engine oil in the cooling circuit flows into the piston rod 2 from the piston guide 1, flows back into the piston rod 2 via the cooling ring cavity 32, and flows into the sliding end of the piston rod to form a circulation, and forms lubrication for the connecting rod at the sliding end, referring to fig. 4 and 6, the sliding end is the mounting groove 26 opened at the end of the piston rod 2 located at the piston guide 1, and the connecting rod is slidably connected with the mounting groove 26, that is, the two guide rails 72 of the connecting rod are slidably connected with the mounting groove 26; the lubricating circuit is communicated with the cooling circuit, the oil in the cooling circuit flows into the lubricating circuit and flows into the sliding contact surface (namely the cylinder wall) of the piston head 3 and the cylinder 9 during circulation, and the oil flows back into the cavity 21 of the piston rod 2 through the lubricating circuit and flows into the cylinder body 8 through the cavity 21 to form circulation during the movement of the piston.
Further, in order to realize the above-mentioned circulation of cooling and lubrication, as shown in fig. 4, 6, 8, and 10:
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 each cooling inlet channel 22 is communicated with the cylinder body 8 through the piston guide 1, the other end of each cooling inlet channel 22 is communicated with the cooling ring cavity 32, one end of each cooling return channel 23 is communicated with the cooling ring cavity 32, and the other end of each cooling return channel 23 is communicated with the cylinder body 8 through the piston guide 1;
the lubricating loop comprises a plurality of lubricating inlet channels 24 and a plurality of lubricating return channels 25 which are arranged on the piston rod 2 and the piston head 3, one end of each lubricating inlet channel 24 is communicated with the cooling return channel 23, and the other end of each lubricating inlet channel 25 is communicated with the cylinder 9; one end of the lubricating return passage 25 is communicated with the cylinder 9, and the other end of the lubricating return passage 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 with reference to fig. 4, it can be seen that the number of the ring grooves 31 is 3, the two at the bottom are used for mounting the gas ring, the uppermost one is used for mounting the oil ring, and one end of the lubrication inlet channel 24 and one end of the lubrication return channel 25 extend into the ring groove 31 at the uppermost one for mounting the oil ring.
With reference to fig. 1 and 2, in order to cooperate with the use of the connecting rod, a closed annular through groove 11 is formed in the piston guide 1, the connecting rod is slidably connected with a sliding end of a piston rod 2 mounted on the piston guide 1, and the closed through groove 11 is easier to ensure the precision in processing, so that compared with the opening form of a piston (CN 205744177U) of the previous generation (the opening design causes the shrinkage, so that the outer circle side of the piston guide 1 is large and the side is small), the processing precision is easier to improve, because the through groove 11 is formed, the piston guide 1 forms a thin-wall feature, the deformation of the open through groove is large in processing, and the deformation is large in addition to the thermal expansion, so that the precision is poor relative to the closed through groove; as shown in fig. 4, a cooling inlet 22 of the cooling circuit is communicated with one of the oil grooves 12 to introduce the engine oil, and a through hole communicated with the oil groove 12 is correspondingly formed in a piston guide groove which is matched in the engine cylinder body 8 and used for the piston guide 1 to move, and the through hole penetrates through the cylinder body 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 far away from the piston guide 1 is a circular arc concave surface 33, the arrangement of the circular arc surface enables the gas to rotate, the gas and the oil are mixed more sufficiently, a high tumble ratio is formed, and high-speed combustion is realized.
According to the structure of the piston, finite element simulation is carried out for proving feasibility, wherein simulation software and processing software used in the method are ansa, hyperworks and abaqus, and the method comprises the following specific steps:
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 240 Mpa; 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 700 Mpa;
the simulation is to simulate the situation that a piston reaches a bottom dead center in a cylinder in reality, and for the simulation in the situation, a connecting rod is required to be incapable of moving and rotating at all, so that the freedom degrees of 1-6 are restricted; if the contact part is not in contact with the contact part, the part-to-part penetration can occur in the simulation calculation process, and even some parts fly away; 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 that point; in fact, the action connecting rod is arranged at one end which is far away from the sliding block, and the action connecting rod is arranged in the middle, so that the practical situation is not problematic if the condition can be met under the worse working condition.
In the first case: f acts on the middle of the connecting rod and the inertia force in the-Y direction;
parts: the piston comprises a piston head, a sealing plate, a connecting rod, a piston guide and a fixing pin;
boundary conditions: the restraining connecting rod (dof12356) is in contact with the contact part, and each part exerts node force F/node number which is equal to ma/node number which is equal to 19785N/node number;
acceleration: a ═ rw2＝(146.5/2)/1000*(4000*2π/60)212856N/kg (146.5/2 is radius of gyration, 146.5 is design size, 4000 is rotation speed)
Piston mass: m 1.539kg (for design mass)
F ═ ma ═ 1.539 ═ 12856 ═ 19785N
The following results are obtained through simulation: (for simplicity of explanation, we only show a part of the simulation diagram)
Dis (maximum total displacement before and after calculation): 0.26mm, as shown in FIG. 15;
z displacement (maximum Z-displacement before and after calculation): 0.11 mm;
maximum tensile stress of sealing plate: 9.7 Mpa;
maximum compressive stress of sealing plate: -26.3 Mpa;
maximum tensile stress of the connecting rod: 148.6 MPa;
maximum compressive stress of the connecting rod: -174.7 MPa;
piston guided maximum tensile stress: 58.7MPa, as shown in FIG. 16;
piston-guided maximum compressive stress: 107.7MPa, as shown in FIG. 17;
maximum tensile stress of the piston rod: 56.7MPa, as shown in FIG. 18;
maximum compressive stress of the piston rod: 148.4MPa, as shown in FIG. 19;
maximum tensile stress of piston head: 129.0 MPa;
maximum compressive stress of piston head: -38.2 Mpa;
and (4) conclusion:
1. maximum displacement when a total node force of 19785N is applied to Y-direction: 0.26 mm; the Z-direction displacement 11 wire is smaller than the reserved 25 wire (namely 0.025mm, and the reserved distance is the design size), so that the piston head cannot collide with the cylinder wall;
2. when a total node force of 19785N is applied to the Y direction, the piston head sealing plate, 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 120 MPa;
3. when a total node force of 19785N is applied to the Y direction, the piston head sealing plate, the piston body, the connecting rod, the piston guide, the slide block and the pin all meet the following conditions: the compressive stress is less than or equal to 240 MPa;
4. when a total node force of 19785N is applied to the Y direction, the maximum tensile stress of the piston head is 129.0MPa > 120MPa, which is slightly beyond the ideal range. The actual yield value of the material is 480MPa, and the material can be accepted as far as the yield value is not reached.
In the second case: f acts on the middle of the connecting rod and is an inertia force in the direction of + Y;
parts: the piston comprises a piston head, a sealing plate, a connecting rod, a piston guide and a fixing pin;
boundary conditions: the restraining connecting rod (dof12356) is in contact with the contact part, and each part exerts node force F/node number which is equal to ma/node number which is equal to 19785N/node number;
acceleration: a ═ rw2＝(146.5/2)/1000*(4000*2π/60)2＝12856N/kg
Piston mass: m 1.539kg
F ═ ma ═ 1.539 ═ 12856 ═ 19785N
The following results are obtained through simulation: (for simplicity of explanation, we only show a part of the simulation diagram)
Dis (maximum total displacement before and after calculation): 0.26mm, as shown in FIG. 20;
z displacement (maximum Z-displacement before and after calculation): 0.10 mm;
maximum tensile stress of sealing plate: 9.0 Mpa;
maximum compressive stress of sealing plate: -27.0 Mpa;
maximum tensile stress of the connecting rod: 158.4 MPa;
maximum compressive stress of the connecting rod: 169.7 MPa;
piston guided maximum tensile stress: 59.1MPa, as shown in FIG. 21;
piston-guided maximum compressive stress: 107.2MPa, as shown in FIG. 22;
maximum tensile stress of the piston rod: 57.4Mpa, as shown in FIG. 23;
maximum compressive stress of the piston rod: 150.4MPa, as shown in FIG. 24;
maximum tensile stress of piston head: 129.1 MPa;
maximum compressive stress of piston head: -38.2 Mpa;
and (4) conclusion:
1. maximum displacement when a total node force of 19785N is applied to Y-direction: 0.26 mm; the Z-direction displacement 10 wires are smaller than the reserved 25 wires, and the piston head cannot collide with the cylinder wall;
2. when a total node force of 19785N is applied to the Y direction, the piston head sealing plate, 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 120 MPa;
3. when a total node force of 19785N is applied to the Y direction, the piston head sealing plate, the piston body, the connecting rod, the piston guide, the slide block and the pin all meet the following conditions: the compressive stress is less than or equal to 240 MPa;
4. when a total node force of 19785N is applied to the Y direction, the maximum tensile stress of the piston head is 129.1MPa > 120MPa, which is slightly beyond the ideal range. The actual yield value of the material is 480MPa, and the material can be accepted as far as the yield value is not reached.
In the third case: the surface of a piston head of the cylinder applies 10 MPa pressure and transmits the pressure 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: constraining link (dof12356), the contact portion makes contact,
force applied: fz 10 × pi (43.38)2 59119N
An air inlet side: fz in 32644N;
an exhaust side: row Fz 26470N;
59114N.
The following results are obtained through simulation: (for simplicity of explanation, we only show a part of the simulation diagram)
As shown in fig. 25:
maximum displacement: 0.65mm
Displacement at the air inlet side: 0.65mm
Displacement on the exhaust side: 0.60mm
Z displacement: the diameter of the hole is 0.20mm,
initial groove height at the inlet side of the groove: 1.220mm (one groove means the lowest ring groove in figure 4)
One slot inlet side final slot height: 1.204mm
Inlet side one slot height variation: 1.220-1.204 mm ═ 0.016mm
Initial cell height on the exhaust side of the cell: 1.220mm
One cell exhaust side final cell height: 1.205mm
Exhaust side-groove height variation: 1.220-1.205-0.015 mm
Maximum tensile stress of sealing plate: 94.4MPa
Maximum compressive stress of sealing plate: -73.3MPa
Maximum tensile stress of the connecting rod: 398.9MPa
Maximum compressive stress of the connecting rod: 501.1MPa
Piston guided maximum tensile stress: 97.8MPa
Piston-guided maximum compressive stress: 135.3MPa
Maximum tensile stress of the piston rod: 100.2MPa
Maximum compressive stress of the piston rod: -236.8MPa
Maximum tensile stress of the slider: 48.4MPa
Maximum compressive stress of the slider: -146.8MPa
Maximum tensile stress of piston head: 105.8MPa
Maximum compressive stress of piston head: -140.9MPa
And (4) conclusion:
1. intake side displacement (maximum displacement) when pressure of 59119N is applied to the cylinder end: 0.65mm, exhaust side displacement: 0.60 mm; the Z-direction displacement of 20 wires is less than the reserved 25 wires, and the piston head cannot collide with the cylinder wall;
2. when 59119N pressure is applied to the cylinder end, 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 59119N pressure is applied to the cylinder end, the piston head sealing plate, the piston body, the piston guide and the sliding block all satisfy the following conditions: the tensile stress is less than or equal to 120MPa, and the compressive stress is less than or equal to 240 MPa;
4. when the pressure of 59119N is applied to the inner cylinder end, the connecting rod satisfies the following conditions: the compressive stress is less than or equal to 700 MPa;
5. when 59119N pressure is applied to the inner cylinder end, the maximum tensile stress of the connecting rod is 398.9MPa which is more than 350MPa,
out of the desired range. The actual yield value of the material is 900MPa, and the material can not reach the yield value and is acceptable.
In a fourth case: the surface of the piston head of the cylinder applies 10 MPa pressure and transmits the pressure to the part with 25mm lateral deviation of the middle part of the connecting rod,
parts: piston head, piston head sealing plate, piston rod, connecting rod, piston guide and stator
Force applied: fz 10 × pi (43.38)2 59119N
An air inlet side: fz in 32644N;
an exhaust side: row Fz 26470N;
59114N (F ═ F-
Obtained by simulation (omitted here with respect to the simulation screen shot)
As shown in fig. 25
Maximum displacement: 0.55mm
Displacement at the air inlet side: 0.55mm
Displacement on the exhaust side: 0.51mm
Z displacement: 0.05mm
Initial groove height at the inlet side of the groove: 1.220mm (one groove means the lowest ring groove in figure 4)
One slot inlet side final slot height: 1.205mm
Inlet side one slot height variation: 1.220-1.205-0.015 mm
Initial cell height on the exhaust side of the cell: 1.220mm
One cell exhaust side final cell height: 1.204mm
Exhaust side-groove height variation: 1.220-1.204 mm-0.014 mm
Maximum tensile stress of sealing plate: 94.4MPa
Maximum compressive stress of sealing plate: -73.3MPa
Maximum tensile stress of the connecting rod: 268.4MPa
Maximum compressive stress of the connecting rod: -328.8MPa
Piston guided maximum tensile stress: 65.9MPa
Piston-guided maximum compressive stress: 97.3MPa to
Maximum tensile stress of the piston rod: 95.6MPa
Maximum compressive stress of the piston rod: -236.8MPa
Maximum tensile stress of piston head: 105.6MPa
Maximum compressive stress of piston head: -141.1MPa
And (4) conclusion:
1. intake side displacement (maximum displacement) when pressure of 59119N is applied to the cylinder end: 0.55mm, exhaust side displacement: 0.51 mm; the Z-direction displacement 5 wires are smaller than the reserved 25 wires, and the piston head cannot collide with the cylinder wall;
2. when 59119N pressure is applied to the cylinder end, the air inlet side of one groove contracts 1.5 filaments, and the air outlet side of the other groove contracts 1.4 filaments which are smaller than the reserved 3-4 filament space;
3. when 59119N pressure is applied to the cylinder end, the piston head sealing plate, the piston body, the piston guide and the sliding block all satisfy the following conditions: the tensile stress is less than or equal to 120MPa, and the compressive stress is less than or equal to 240 MPa;
4. when 59119N pressure is applied by the gas end, the connecting rod satisfies the following conditions: the tensile stress is less than or equal to 350MPa, and the compressive stress is less than or equal to 700 MPa.
When the piston is used, the piston is arranged in a horizontally opposite double-crankshaft engine and is connected with double crankshafts through a connecting rod, namely a rotating pair 74 and a sliding ring 73 on the connecting rod are respectively connected with the crankshafts, the piston guide 1 is used as a guide end of the piston so that the motion mode of the piston is linear reciprocating motion, and the piston head 3 is used as a sealing end of the piston and is in dynamic sealing with the cylinder 9; the mixed oil gas is combusted in the cylinder 9, the arc concave surface 33 of the piston head 3 accelerates the mixing effect, further power is generated to drive the crankshaft to rotate, and the oil seal 6 plays a role in sealing in the process of piston movement and prevents generated water vapor from entering the cylinder body 8; meanwhile, the engine oil in the cooling circuit and the lubricating circuit flows, in the cooling circuit, the engine oil enters the cooling inlet channel 22 through the oil groove 12 of the piston guide 1, flows through the cooling ring cavity 32 to enter the cooling return channel 23, and flows into the sliding end of the piston rod 2 from the cooling return channel 23 to form a circulation, and meanwhile, the sliding of the connecting rod is lubricated; the engine oil in the lubricating circuit flows out of the piston head 3 from the cooling return passage 23 through the lubricating inlet passage 24 and enters the wall of the cylinder 9, scrapes the engine oil back in the process of piston movement, then enters the cavity 21 through the lubricating return passage 25, and flows into the cylinder body 8 through the cavity 21 and a through hole 27 formed in the piston guide 1 to form a circulation.
It will be apparent to those skilled in the art that various changes and modifications may be made in the present invention without departing from the spirit and scope of the invention. Thus, if such modifications and variations of the present invention fall within the scope of the claims of the present invention and their equivalents, the present invention is also intended to include such modifications and variations.
Claims (9)
1. A piston of a horizontally opposed engine 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 the horizontally opposed engine 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 lead in the engine oil from the piston guide position, and the engine oil flows back to the cylinder body again after passing through the piston rod and the piston head.
2. The horizontally opposed engine piston as claimed in claim 1, wherein the outer profile of the piston rod is a rotating body, the end of the piston rod away from the piston guide is provided with a cavity, the cavity is a blind hole structure, the bottom of the blind hole is communicated with the cylinder body, the end of the cavity close to the piston head is hermetically connected with the piston head, and a cooling ring cavity is arranged between the end of the piston rod away from the piston guide and the piston head and is communicated with the cooling circuit.
3. The opposed horizontal engine piston of claim 2, wherein oil in said cooling circuit flows from the piston guide into the piston rod, back into the piston rod through said cooling ring cavity and into the sliding end of the piston rod for a cycle; the lubricating circuit is communicated with the cooling circuit, the engine oil in the cooling circuit flows into the lubricating circuit and flows into the sliding contact surface between the piston head and the cylinder in the circulating process, and 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 in the movement process of the piston.
4. The horizontally opposed engine piston as set forth in claim 2 or 3, wherein said cooling circuit includes a plurality of cooling intake passages and a plurality of cooling return passages provided in said piston rod, one end of said cooling intake passage communicating with the cylinder block through the piston guide, the other end of said cooling intake passage communicating with said cooling ring chamber, one end of said cooling return passage communicating with said cooling ring chamber, the other end of said cooling return passage communicating with the sliding end of the piston rod;
the lubricating loop comprises a plurality of lubricating inlet channels and a plurality of lubricating return channels which are arranged on the piston rod and the piston head, one end of each lubricating inlet channel is communicated with the cooling return channel, and the other end of each lubricating inlet channel is communicated with the cylinder; one end of the lubricating return passage is communicated with the cylinder, and the other end of the lubricating return passage is communicated with the cavity.
5. The opposed, horizontally disposed engine piston of claim 4, wherein said piston head defines a plurality of circumferential grooves in a peripheral wall thereof, one end of said lubrication inlet and said lubrication return extending into one of said grooves.
6. The horizontally opposed engine piston as set forth in claim 1, wherein said piston guide has a closed annular through slot formed therein for the passage of said connecting rod, said connecting rod being slidably connected to a sliding end of a piston rod mounted on said 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 at two ends of the piston guide and are communicated with the through grooves.
7. The opposed horizontal engine piston of claim 6, wherein said sliding end is a mounting slot formed in the end of the piston rod at the piston guide.
8. The horizontally opposed engine piston of claim 2, wherein said piston rod is nested with an oil seal fixed within said cylinder, said piston rod being sealed from said oil seal and linearly sliding back and forth relative to said oil seal.
9. A horizontally opposed engine piston as set forth in claim 1 wherein said piston end surface directed away from said piston is concave.
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