CN213574389U - Piston with special-shaped inner cooling oil cavity adapting to eccentricity of combustion chamber - Google Patents
Piston with special-shaped inner cooling oil cavity adapting to eccentricity of combustion chamber Download PDFInfo
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- CN213574389U CN213574389U CN202022801975.8U CN202022801975U CN213574389U CN 213574389 U CN213574389 U CN 213574389U CN 202022801975 U CN202022801975 U CN 202022801975U CN 213574389 U CN213574389 U CN 213574389U
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Abstract
The utility model relates to a piston with a special-shaped inner cooling oil cavity adapting to the eccentricity of a combustion chamber, which belongs to the technical field of internal combustion engine pistons.A combustion chamber is arranged at the top of the piston, an inlay ring and a ring groove are arranged on the side surface of the piston, and the eccentric distance between the central line of the combustion chamber and the central line of the piston is L; the inner cooling oil cavity is eccentric and consistent with the combustion chamber, so that the temperature of the eccentric side firepower bank is effectively reduced, the whole firepower bank of the piston is uniformly heated, and carbon deposit of the firepower bank is reduced.
Description
Technical Field
The utility model relates to a piston with cold oil pocket in eccentric dysmorphism of adaptation combustion chamber belongs to internal-combustion engine piston technical field.
Background
Since the heat generated by the combustion process is very high, forced cooling of the piston must be applied. In general, the power per unit area of the engine exceeds 0.29kW/cm2The unit piston area power of the medium-power marine diesel engine exceeds 0.15kW/cm2Cooling of the piston is required. In this case, the piston needs to be cooled in an oscillating manner to ensure that the heat to which the piston is subjected is removed.
The oscillating cooling is to arrange a cooling oil cavity at the head of the piston, cooling engine oil is injected from an oil inlet hole at one side of the oil cavity and is discharged from an oil return hole at the other side of the oil cavity, the cooling engine oil oscillates in the cooling oil cavity in the piston under the action of inertia force, the relative speed of the engine oil and the inner wall surface of the oil cavity is high, turbulence is formed, the heat exchange between a cooling medium and the inner wall surface is improved, and the heat dissipation area is one of factors influencing the heat exchange.
Along with the improvement of the strengthening degree of the diesel engine, the heat load and the mechanical load borne by the piston are also greatly increased, so that the temperature of the head of the piston is increased, the top surface of the piston, particularly the edge of a throat of a combustion chamber is ablated, and when the temperature of a first ring groove of the piston is too high, lubricating oil is caked and carbonized, and a clamping ring pulls a cylinder.
The piston without the oil cavity adopts free jet cooling, oil in a circulating lubrication system can be utilized to carry out oil injection cooling on the bottom of the piston, and the mode has simple structure and low cost, but large temperature difference is easy to cause between the inner surface and the outer surface of the head of the piston, heat generated by combustion is difficult to rapidly discharge, and risks such as piston ring groove carbon deposition, throat fatigue cracking and the like are easy to cause.
Most internal combustion engine aluminum alloy pistons in the current market have the inner cooling oil cavity with the equal section, although the cooling effect is better compared with the piston without the cooling oil cavity, along with the further improvement of detonation pressure and power, the heat dissipation area of the inner cooling oil cavity with the equal section is small, the heat dissipation effect is limited, the heat generated by combustion cannot be rapidly taken away by cooling oil, and the heat influence on the ring groove, the top and the throat of the piston is larger.
For the piston with a larger eccentric combustion chamber, the heat quantity of a firepower bank of the piston is different, the deformation and the carbon deposit generated by heating are different, and the firepower bank on the eccentric side has high heat quantity and is easier to generate carbon deposit.
SUMMERY OF THE UTILITY MODEL
To the not enough of prior art, the utility model provides a piston with cold oil pocket in eccentric dysmorphism of adaptation combustion chamber. The eccentric of the combustion chamber is adapted to the maximum extent, the cooling effect of the inner cooling oil cavity is ensured, the surface area of the inner cooling oil cavity is increased, and the heat dissipation area is enlarged.
The technical scheme of the utility model as follows:
a piston with a special-shaped inner cooling oil cavity adapting to eccentricity of a combustion chamber is provided, the top of the piston is provided with the combustion chamber, the side surface of the piston is provided with an inlay ring and a ring groove, and the eccentric distance between the central line of the combustion chamber and the central line of the piston is L;
the inner cooling oil cavity is annularly arranged around the bottom of the combustion chamber, the eccentric direction of the inner cooling oil cavity is the same as the eccentric direction of the combustion chamber, the distance from the inner diameter of the inner cooling oil cavity on the eccentric side to the center of the piston is L1, the distance from the inner diameter of the inner cooling oil cavity on the eccentric side to the center of the piston is L2, the distance from the outer diameter of the inner cooling oil cavity on the eccentric side to the center of the piston is L3, the distance from the outer diameter of the inner cooling oil cavity on the eccentric side to the center of the piston is L4, the distance from the inner cooling oil cavity on the eccentric side to the combustion chamber is L5, the distance from the inner cooling oil cavity on the eccentric side to the combustion chamber is L6, the distance from the inner cooling oil cavity on the eccentric side to the insert ring is H567, the distance from the inner cooling oil cavity on the;
wherein L1 is more than L2, L3 is more than L4, H1 is less than H2, R1 is less than R2, and L5 is less than L6.
Preferably, L1-L2-L, L3-L4-L, H2-H1-L, R2-R1-L, L6-L5-L, namely, the eccentricity of the internal cooling oil chamber is less than or equal to the eccentricity of a piston combustion chamber, and H1 and H2 are more than or equal to 3% D and D is the diameter of the piston, R1 and R2 are more than or equal to 4% D and L5 and L6 are more than or equal to 4% D to meet the structural strength of the piston. The value of the eccentricity L of the combustion chamber depends on the design requirements of the engine and is not within the scope of the present application.
The inner cooling oil cavity is eccentric and consistent with the combustion chamber, so that the temperature of the eccentric side firepower bank is effectively reduced, the whole firepower bank of the piston is uniformly heated, and carbon deposit of the firepower bank is reduced.
Preferably, the inner cooling oil cavity is formed by a special-shaped salt core, one side of the inner cooling oil cavity, which is close to the combustion chamber, protrudes inwards, the protruding arc angle of the side of the combustion chamber is R5, one side of the inner cooling oil cavity, which is close to the ring groove, protrudes inwards, the protruding arc angle of the side of the ring groove is R4, one side of the inner cooling oil cavity, which is close to the combustion chamber, is provided with a tooth-shaped cooling fin protrusion, the protruding fillet of the tooth-shaped cooling fin is R3, the tooth-shaped cooling fin can be designed to be singular or even, the number of teeth is determined according to the product requirements, and the appropriate tooth. All teeth are in fillet transition, so that stress concentration is prevented.
Further preferably, R3 < R5, R4. gtoreq.R 1, R4. gtoreq.R 2, i.e. values within the range satisfying the structural strength of the piston, are within the scope of the present application.
The structural design of an internal cooling oil cavity with a toothed sheet is added, so that the heat dissipation area is further increased. Through the design of the special-shaped inner cooling oil cavity for increasing the heat dissipation area, heat generated by combustion can be quickly taken away by cooling oil.
The tooth-shaped structure can be used as a reinforcing rib of the salt core, and compared with the salt core with the equal section, the tooth-shaped structure has higher strength and is not easy to damage in the casting process. Compared with the piston with the inner cooling oil cavity with the equal section, the piston with the tooth-shaped inner cooling oil cavity has higher strength on the piston with the same cylinder diameter.
Compared with an equal-section internal cooling oil cavity, the salt core has a relatively complex shape, and although the salt core is difficult to manufacture, the manufacturing difficulty caused by the complex shape can be ignored compared with the heat dissipation effect of the internal cooling oil channel.
The beneficial effects of the utility model reside in that:
the application provides a piston with special-shaped inner cooling oil cavity adapting to the eccentricity of a combustion chamber, the adaptation of the eccentricity of the combustion chamber to the maximum extent or no eccentricity of the combustion chamber is realized, the cooling effect of the inner cooling oil cavity is guaranteed, the surface area of the inner cooling oil cavity is increased, and the heat dissipation area is increased.
One side of the inner cooling oil cavity, which is close to the ring groove, protrudes inwards, the design of the piston ring groove is avoided, and the top of the inner cooling oil cavity is closer to the inlaid ring, so that the structural strength of the piston is ensured.
The inner cooling oil cavity designed eccentrically relative to the center of the piston enables the cooling oil to fully cool the eccentric side and to be consistent with the eccentricity of the combustion chamber, thereby effectively reducing the temperature of the firepower bank side and lightening the carbon deposit of the firepower bank.
The structural design of the inner cooling oil cavity with the additional tooth-shaped heat dissipation sheet type further increases the heat dissipation area through the design of the special-shaped inner cooling oil cavity with the increased heat dissipation area, and heat generated by combustion can be quickly taken away by cooling oil, so that the influence of high temperature on the top surface of the piston, the throat and the firepower bank part is reduced.
Drawings
FIG. 1 is a conventional internal cooling oil passage when a combustion chamber is eccentric;
in fig. 1: the eccentric distance of the L combustion chamber, the distance from the inner side of the La inner cooling oil duct to the center of the piston, the distance from the outer side of the Lb inner cooling oil duct to the center of the piston, the distance from the H inner cooling oil duct to the insert ring, the distance from the Lc eccentric side inner cooling oil duct to the combustion chamber, the distance from the Ld eccentric side inner cooling oil duct to the combustion chamber and the distance from the R inner cooling oil duct to the ring groove;
FIG. 2 is a piston of a special-shaped internal cooling oil cavity adapting to eccentricity of a combustion chamber;
in fig. 2: 1 special-shaped internal cooling oil cavity, 2 inlay ring, 3 eccentric side fire bank, 4 piston top surface, 5 throat, 6 combustion chamber, 7 eccentric opposite side fire bank, 8 ring groove, eccentric distance of L combustion chamber, distance of L1 eccentric side internal cooling oil cavity inner diameter to piston center, distance of L2 eccentric opposite side internal cooling oil cavity inner diameter to piston center, distance of L3 eccentric side internal cooling oil cavity outer diameter to piston center, distance of L4 eccentric opposite side internal cooling oil cavity outer diameter to piston center, distance of L5 eccentric side internal cooling oil cavity to combustion chamber, distance of L6 eccentric opposite side internal cooling oil cavity to combustion chamber, distance of H1 eccentric side internal cooling oil cavity to inlay ring, distance of H2 opposite side internal cooling oil cavity to inlay ring, distance of R1 eccentric side internal cooling oil cavity to ring groove, and distance of R2 eccentric opposite side internal cooling oil cavity to ring groove;
FIG. 3a is a schematic top view of a profiled salt core structure;
FIG. 3b is a view from A-A in FIG. 3 a;
FIG. 3c is a view from B-B in FIG. 3B;
in fig. 3 a-3 c: the engine comprises a R3 internal cooling oil cavity tooth-shaped fillet, a R4 avoiding piston ring groove fillet, a R5 combustion chamber conformal fillet, 9 and salt core internal teeth.
Detailed Description
The present invention will be further described, but not limited to, by the following examples in conjunction with the accompanying drawings.
Example 1:
a piston with a special-shaped internal cooling oil cavity adapting to eccentricity of a combustion chamber is characterized in that the top of the piston is provided with the combustion chamber, the side surface of the piston is provided with an inlaid ring and a ring groove, and the eccentric distance between the central line of the combustion chamber and the central line of the piston is L.
The inner cooling oil cavity is annularly arranged around the bottom of the combustion chamber, the eccentric direction of the inner cooling oil cavity is the same as the eccentric direction of the combustion chamber, the distance from the inner diameter of the inner cooling oil cavity on the eccentric side to the center of the piston is L1, the distance from the inner diameter of the inner cooling oil passage on the eccentric side to the center of the piston is L2, the distance from the outer diameter of the inner cooling oil passage on the eccentric side to the center of the piston is L3, the distance from the outer diameter of the inner cooling oil passage on the eccentric side to the center of the piston is L4, the distance from the inner cooling oil passage on the eccentric side to the combustion chamber is L5, the distance from the inner cooling oil passage on the eccentric side to the combustion chamber is L6, the distance from the inner cooling oil passage on the eccentric side to the insert ring is H567, the distance from the inner cooling oil passage on the;
wherein L1 is more than L2, L3 is more than L4, H1 is less than H2, R1 is less than R2, and L5 is less than L6. L1-L2 is not less than L, L3-L4 is not less than L, H2-H1 is not less than L, R2-R1 is not less than L, L6-L5 is not less than L, namely the eccentricity of the internal cooling oil chamber is not less than the eccentricity of a piston combustion chamber, and H1 and H2 are not less than 3% D to meet the structural strength of the piston, D is the diameter of the piston, R1 and R2 are not less than 4% D, and L5 and L6 are not less than 4% D. The value of the eccentricity L of the combustion chamber depends on the design requirements of the engine and is not within the scope of the present application.
Example 2:
the structure of the piston is as described in embodiment 1, except that the inner cooling oil cavity is formed by a special-shaped salt core, one side of the inner cooling oil cavity, which is close to the combustion chamber, protrudes inwards, the side of the combustion chamber protrudes with an arc angle R5, namely the arc angle at the R5 is actually conformal with the combustion chamber, one side of the inner cooling oil cavity, which is close to the ring groove, protrudes inwards to avoid a piston ring groove, the side of the ring groove protrudes with an arc angle R4, one side of the inner cooling oil cavity, which is close to the combustion chamber, is provided with a tooth-shaped cooling fin protrusion, the protruding fillet of the tooth-shaped cooling fin is R3, the tooth-shaped cooling fin can be designed to be singular or even, the number of teeth is determined according to the product requirement, and the volume fraction of the cooling oil is analyzed by finite elements to determine. All the teeth 9 are in round transition with the teeth 9, so that stress concentration is prevented. R3 is the tooth-shaped fillet of the inner cooling oil chamber, R4 is the fillet of avoiding the piston ring groove, R5 is the fillet following the shape of the combustion chamber, wherein R3 is more than R5, R4 is more than or equal to R1, R4 is more than or equal to R2, namely the numerical value in the structural strength range of the piston is within the protection range of the application. FIG. 1 shows a piston structure with eccentric combustion chamber and non-eccentric inner cooling oil passage. For a piston with a larger eccentric combustion chamber, the heat quantity of a firepower bank of the piston is different, the deformation caused by heating and the carbon deposit caused by heating are different, the firepower bank on one eccentric side has high heat quantity, the carbon deposit is more easily generated, the abrasion of the piston and a cylinder sleeve is easily generated, and even the risk of cylinder pulling is caused. In view of the problems presented in fig. 1, the present application proposes a piston with a profiled internal cooling gallery that accommodates combustion chamber eccentricity.
FIG. 2 is a schematic diagram of piston structure of a profiled internal cooling oil cavity adapted to eccentricity of a combustion chamber. According to the figure, due to the existence of the eccentricity L of the combustion chamber, the distance between the outer circle of the piston and the center of the combustion chamber on the top surface 4 of the piston is different, after the heat generated by fuel combustion is transferred to the piston, the heat of the eccentric side fire bank 3 is different from that of the eccentric side fire bank 7, the temperature of the eccentric side fire bank 3 is higher than that of the eccentric side fire bank 7, and the eccentric side fire bank 3 is more prone to thermal fatigue and carbon deposition. The center of the special-shaped internal cooling oil cavity 1 is not concentric with the center of a piston and is biased towards the direction of eccentricity H, according to the drawing, L1 & gt L2, L3 & gt L4, H1 & lt H2, R1 & lt R2 and L5 & lt L6 are arranged, and the cooling oil in the internal cooling oil passage achieves the best cooling effect through the matching change of the sizes of L1, L2, L3, L4, H1, H2, R1 and R2.
3 a-3 c are special-shaped salt cores for forming the cooling oil cavities in the pistons, R3 is a tooth-shaped cooling fin fillet, R4 is an avoiding ring groove fillet, 9 is a salt core tooth-shaped cooling fin, the tooth shapes of the salt core tooth-shaped cooling fin can be designed to be singular or even, the number of the teeth is determined according to the product requirements, and the volume fraction of the cooling oil is analyzed through finite elements to determine the appropriate tooth shape number. All the teeth 9 are in round transition with the teeth 9, so that stress concentration is prevented. All numbers of tooth profiles are within the scope of the present application.
The salt core R4 is to the piston excircle bulge fillet, dodges the piston ring groove, is closer to the ring carrier, compares with the oil duct excircle in the conventional interior cooling oil duct shape (fig. 1), has further increased the oil duct surface area, improves the cooling effect.
The salt core is manufactured by adopting a pressing and sintering method, and the fillet transition at the tooth-shaped radiating fin is smooth, so that the salt core is convenient to press, sinter and form.
The special-shaped inner cooling oil cavity 1 is positioned in the piston, the inner teeth 9 are close to the combustion chamber 6, the throat opening 5, the insert ring 2, the top surface 4 of the piston and the firepower banks 3 and 7, and due to the adoption of a tooth-shaped heat dissipation structure, the surface area of the inner cooling oil cavity 1 is increased, more heat caused by combustion in the combustion chamber 6, the throat opening 5, the insert ring 2, the top surface 4 of the piston and the firepower banks 3 and 7 can be taken away, and the temperature of the places is effectively reduced.
Claims (4)
1. A piston with a special-shaped inner cooling oil cavity adapting to eccentricity of a combustion chamber is provided, the top of the piston is provided with the combustion chamber, and the side surface of the piston is provided with an inlay ring and a ring groove;
the inner cooling oil cavity is annularly arranged around the bottom of the combustion chamber, the eccentric direction of the inner cooling oil cavity is the same as the eccentric direction of the combustion chamber, the distance from the inner diameter of the inner cooling oil cavity on the eccentric side to the center of the piston is L1, the distance from the inner diameter of the inner cooling oil passage on the eccentric side to the center of the piston is L2, the distance from the outer diameter of the inner cooling oil passage on the eccentric side to the center of the piston is L3, the distance from the outer diameter of the inner cooling oil passage on the eccentric side to the center of the piston is L4, the distance from the inner cooling oil passage on the eccentric side to the combustion chamber is L5, the distance from the inner cooling oil passage on the eccentric side to the combustion chamber is L6, the distance from the inner cooling oil passage on the eccentric side to the insert ring is H567, the distance from the inner cooling oil passage on the;
wherein L1 is more than L2, L3 is more than L4, H1 is less than H2, R1 is less than R2, and L5 is less than L6.
2. The piston with the special-shaped inner-cooling oil chamber adapting to the eccentricity of the combustion chamber as claimed in claim 1, wherein L1-L2-L, L3-L4-L, H2-H1-L, R2-R1-L, L6-L5-L, H1 and H2 are greater than or equal to 3% of D, D is the diameter of the piston, R1 and R2 are greater than or equal to 4% of D, and L5 and L6 are greater than or equal to 4% of D.
3. The piston as claimed in claim 2, wherein said cavity is formed by a profiled salt core, the cavity is inwardly convex on the side adjacent to said combustion chamber, the convex arc angle on the combustion chamber side is R5, the cavity is inwardly convex on the side adjacent to said ring groove, the convex arc angle on the ring groove side is R4, and the cavity is provided with a tooth-shaped fin bulge on the side adjacent to said combustion chamber, the convex fillet of said fin is R3.
4. The piston with the shaped inner cooling gallery accommodating eccentricity of the combustion chamber as claimed in claim 3, wherein R3 is more than R5, R4 is more than or equal to R1, and R4 is more than or equal to R2.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022801975.8U CN213574389U (en) | 2020-11-27 | 2020-11-27 | Piston with special-shaped inner cooling oil cavity adapting to eccentricity of combustion chamber |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022801975.8U CN213574389U (en) | 2020-11-27 | 2020-11-27 | Piston with special-shaped inner cooling oil cavity adapting to eccentricity of combustion chamber |
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| Publication Number | Publication Date |
|---|---|
| CN213574389U true CN213574389U (en) | 2021-06-29 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202022801975.8U Active CN213574389U (en) | 2020-11-27 | 2020-11-27 | Piston with special-shaped inner cooling oil cavity adapting to eccentricity of combustion chamber |
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| CN (1) | CN213574389U (en) |
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- 2020-11-27 CN CN202022801975.8U patent/CN213574389U/en active Active
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