CN209444454U - A kind of large bore engine piston and engine - Google Patents
A kind of large bore engine piston and engine Download PDFInfo
- Publication number
- CN209444454U CN209444454U CN201821778391.XU CN201821778391U CN209444454U CN 209444454 U CN209444454 U CN 209444454U CN 201821778391 U CN201821778391 U CN 201821778391U CN 209444454 U CN209444454 U CN 209444454U
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- ring
- slot
- gas
- gas ring
- large bore
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Abstract
The utility model relates to Diesel Engine Technique Field, a kind of large bore engine piston and engine are disclosed.The large bore engine piston, piston include top compression ring slot, second gas ring slot and third road oil ring groove from top to bottom, and the lower groove face of the second gas ring slot of the piston tilts predetermined angle α from its slot bottom upwards；Periphery wall between the second gas ring slot and third road oil ring groove of piston is third ring bank C, and the third ring bank C is connect with the second gas ring slot through the recessed portion.The problem of the utility model can make large-diameter non-distorted second gas ring play the same effect of twist type ring, efficiently solve top compression ring pump oil.
Description
Technical field
The utility model relates to Diesel Engine Technique Field more particularly to a kind of large bore engine pistons and engine.
Background technique
Piston ring in engine is divided into compression ring and oil ring, and the effect of compression ring is the high-temperature fuel gas in sealing combustion room, makes
It is leaked into crankcase less as far as possible, and the effect of oil ring is to carry out scraping control to the lubricating oil on cylinder sleeve, will be extra
Lubricating oil scrapes in crankcase, while guaranteeing that suitable lubricating oil stays in inner surface of cylinder liner, it is made to lubricate the fortune of compression ring and cylinder sleeve
Row surface.
As depicted in figs. 1 and 2, piston 2 ' includes top compression ring slot, second gas ring slot and third road oil from top to bottom
Annular groove, the periphery wall between the top compression ring slot and second gas ring slot of piston are the second ring bank B', second gas ring slot
It is periphery wall between third road oil ring groove is third ring bank C'.
In order to make the gas pressure of the second ring bank B' be less than firepower bank A', light medium-sized high speed engine height of piston ring and diameter
Smaller to thickness, the piston ring excircle contact surface with distortion is influenced smaller by distortion inner chamfer E' scale error.Generally by second
Road compression ring 4' is designed as negative twist piston ring, the gas (gas pressure P2) of the second ring bank B' can be introduced second gas ring slot
Bottom, offset the gas at the top of a part of second gas ring 4' together with the gas pressure (P3, P3 < P2) of third ring bank C'
Pressure increases the unstability of second gas ring 4', acts on second gas ring when the upward reciprocal inertia force of piston ring is greater than
When the upper downward gas pressure of 4', second gas ring 4' beats upwards, and the gas of the second ring bank B' is let out crankshaft by bottom
In case, D ' is gas flow schematic diagram in Fig. 2.
At this stage, the high medium seed diesel engine of large-diameter develops towards directions such as high detonation pressure, high powers.If by second gas ring 4 '
It is designed as negative twist structure, because of the torsional deformation of the chamfering E' control piston ring of second gas ring 4 ', when diesel engine cylinder diameter is greater than
When 150mm or more, because the height and radial thickness of second gas ring 4 ' are excessive, cause chamfering E' machining accuracy to be difficult to ensure, lead
The outer circle twist angle of activation plug ring in a circumferential direction is different, and then the position for contacting piston ring excircle face with cylinder sleeve 1' does not connect
It is continuous, influence the sealing performance of piston ring excircle.
As shown in Figure 3 and Figure 4, if the second gas ring 4' of the high medium seed diesel engine of large-diameter is designed as non-distorted structure,
Such design causes the second ring bank B' gas to cannot be introduced into the bottom of second gas ring slot, can not offset at the top of the second ring bank B'
Gas pressure, second gas ring 4' are easily pressed in always second gas ring trench bottom by the gas of the second ring bank B', can not pass through second
The bounce of road compression ring 4' passes the gas through second gas ring slot slot bottom for gas and leaks into crankcase, makes second gas ring slot gas
Pressure (P2) is greater than the gas pressure (P1) of firepower bank A' in exhaust latter stage, and then top compression ring 3' is caused to move up and down.Together
When, because the gas pressure P2 of the second ring bank B' is greater than the gas pressure P1 of firepower bank A', therefore, the gas of the second ring bank B' can be anti-
Firepower bank A' is flowed to, while the machine oil of the second ring bank B' is pumped into the even combustion chamber firepower bank A', leads to firepower bank A' carbon distribution
Seriously, machine oil oil consumption increases, serious to lead to firepower bank A' scuffing of cylinder bore.
Utility model content
The purpose of this utility model is to provide a kind of large bore engine piston and engines, and large-diameter can be made non-
The problem of distortion second gas ring plays the same effect of twist type ring, efficiently solves top compression ring pump oil.
For this purpose, the utility model uses following technical scheme:
A kind of large bore engine piston is provided, piston includes top compression ring slot, second gas ring slot from top to bottom
Predetermined angle α is tilted upwards from its slot bottom with the lower groove face of third road oil ring groove, the second gas ring slot of the piston；
Periphery wall between the second gas ring slot and third road oil ring groove of piston is third ring bank C, the third ring bank C
It is connect with the second gas ring slot through recessed portion.
Preferably, the recessed portion is the right angle groove for being set to the upper end the third ring bank C, the slot of the right angle groove
Bottom is connect with the lower groove face of the second gas ring.
Preferably, the lower groove face fillet of the slot bottom of the right angle groove and the second gas ring seamlessly transits.
Preferably, the recessed portion is 0.5-1.5mm along the size range of the radial depth capacity D of the piston.
Preferably, the recessed portion is not less than 1mm along the height H of piston axial direction.
Preferably, the recessed portion is inner sunken face, and the both ends of the recessed portion are connected to the second gas ring
The lower groove face of slot and the third ring bank C.
Preferably, the recessed portion be convex outward, the both ends of the recessed portion respectively with the second gas ring slot
Lower groove face is connected with the third ring bank C.
Preferably, the upper groove surface of the second gas ring slot tilts predetermined angle β from its slot bottom upwards.
Preferably, the lower groove face of the upper groove surface of the second gas ring slot and the second gas ring slot is arranged in parallel.
Preferably, the range of the predetermined angle α and the predetermined angle β are 0.1 ° -0.4 °.
A kind of engine is additionally provided in the utility model, including the large bore engine piston.
The utility model has the beneficial effects that the lower groove face of second gas ring slot is designed to that inclination angle is upward in the utility model
Structure, so that second gas ring and second gas ring slot is formed a twist relative angle, increase the gas of second gas ring slot slot bottom
Body pressure increases the unstable of second gas ring to offset the gas pressure that a part acts on second gas ring periphery wall
Property.Meanwhile concave part is set on the bank in third ring, this structure is simple, and structural modification is small, special by the dynamics for improving piston ring
Property, to solve the exhausting problem of second gas ring, while the oil pump problem of top compression ring is also efficiently avoided, substantially
Ground improves the service life and reliability of engine.
It is improved by second gas ring slot and recessed portion is set on the bank in third ring, large-diameter non-distorted can be made
Two compression rings play the same effect of twist type ring.
Detailed description of the invention
Fig. 1 be second gas ring in the prior art be negative distorted-structure when, the partial structurtes of piston cylinder internal structure are shown
It is intended to；
Fig. 2 be second gas ring in the prior art be negative distorted-structure when, part when second gas ring exhaust condition
Structural schematic diagram；
Fig. 3 be second gas ring in the prior art be non-distorted structure when, the partial structurtes of piston cylinder internal structure are shown
It is intended to；
Fig. 4 is second gas ring in the prior art when being non-distorted structure, part when second gas ring exhaust condition
Structural schematic diagram；
Fig. 5 is the partial structural diagram of the internal structure of the piston cylinder of the utility model；
Fig. 6 is a kind of partial structural diagram of structure of the large bore engine piston of the utility model；
Fig. 7 is the partial structural diagram of another structure of the large bore engine piston of the utility model.
In figure:
1 ', cylinder sleeve；2 ', piston；3 ', top compression ring；4 ', second gas ring；
1, top compression ring slot；2, second gas ring slot；3, third road oil ring groove；21, lower groove face；22, upper groove surface；4, recessed
Concave portion；5, second gas ring；6, top compression ring；7, cylinder sleeve.
Specific embodiment
Further illustrate the technical solution of the utility model below with reference to the accompanying drawings and specific embodiments.
As shown in Figure 5 and Figure 6, a kind of large bore engine piston is provided in the present embodiment, is mainly used in large cylinder
Diameter engine mainly improves the second gas ring slot 2 of piston.
The lower groove face 21 of the second gas ring slot 2 of piston tilts predetermined angle α, and the model of predetermined angle α from slot bottom upwards
Enclose is 0.1 ° -0.4 °.Lower groove face 21 is set as tilting upwards, in order to make second gas ring 5 and the formation of second gas ring slot 2
One twist relative angle makes the gas of the second ring bank B introduce the slot bottom of second gas ring slot 2, offsets a part of second gas ring 5
The gas pressure of periphery wall increases the unstability of second gas ring 5, allows gas to enough through the discharge of 2 slot bottom of second gas ring slot
To crankcase.
The upper groove surface 22 of second gas ring slot 2 in the present embodiment tilts predetermined angle β, upper groove surface 22 from its slot bottom upwards
It is arranged in parallel with lower groove face 21.Predetermined angle α is identical with predetermined angle β angular range.In other embodiments, when upper groove surface 22
When being obliquely installed upwards, the specific angle of predetermined angle α and predetermined angle β selection can be identical, can also be different, specific inclination angle
Degree is determined according to actual needs.In addition, the upper groove surface 22 of second gas ring slot 2 can be with horizontally disposed.
Above-mentioned third ring bank C is connect with second gas ring slot 2 through recessed portion 4.Recessed portion 4 is not small along piston axial height H
In 1mm.Recessed portion 4 is set in order to avoid the interference of the generation to second gas ring 5.
Specifically, as shown in fig. 6, being the partial structural diagram of the radial section of piston and second gas ring 5, this implementation
Recessed portion 4 in example be the right angle groove for being set to the upper end third ring bank C, the slot bottom of right angle groove under second gas ring 5
Groove face 21 connects.The slot bottom of right angle groove forms the periphery centered on piston axis.The slot bottom and second of right angle groove
21 fillet of lower groove face of compression ring 5 seamlessly transits.Third ring bank C is step type, model of the above-mentioned right angle groove along piston radial depth D
It encloses for 0.5-1.5mm, i.e., right angle groove is in tricyclic ring radially contracted 0.5-1.5mm on the bank.
Because third ring bank C upper top is provided with right angle groove, therefore, the stream at the second ring bank B end-gaps can be increased
Logical area, further decreases the gas pressure P2 of the second ring bank B.In addition, the forge piece of step type structure of third ring bank C can be by second
Compression ring 5 is moved to left in the contact point E with lower groove face 21, is increased the overturning degreeof tortuosity of second gas ring 5, is further increased second
The unstability of compression ring 5 accelerates the gas leakage of the second ring bank B, avoids 6 pump oil of top compression ring.
In other embodiments as shown in fig. 7, above-mentioned recessed portion 4 can also be inner sunken face, one end of recessed portion 4 connects
It is connected to the lower groove face 21 of second gas ring slot 2, the other end is connect with third ring bank C, it is therefore preferable to which the two is smoothly connected.In setting
The purpose of concave curved surface is identical as the purpose of above-mentioned right angle groove, be for be second gas ring 5 Yu lower groove face 21 contact point E
It moves to left.
In addition, recessed portion 4 can also be convex outward, the both ends of recessed portion 4 respectively with the lower slot of second gas ring slot 2
Face 21 and the round and smooth connection of third ring bank C.It is herein round-corner transition, lower groove face 21 is avoided to contact with 5 wedge angle of second gas ring, to the
Two compression rings 5 cause to damage.
The upper groove surface 22 of second gas ring slot 2 and lower groove face 21 are designed to the upward structure in inclination angle in the present embodiment,
Meanwhile third ring bank C is designed as step type, this structure is simple, and structural modification is small, special by the dynamics for improving piston ring
Property, to solve 5 exhausting problem of second gas ring.
A kind of engine is additionally provided in the present embodiment, including above-mentioned large bore engine piston.It is lived by improving
The structure of the second gas ring slot 2 of plug solves piston in cylinder sleeve 7 when uplink, the exhausting problem of second gas ring 5.Simultaneously
Also it solves the oil pump problem of top compression ring 6, the service life and reliability of engine has been significantly increased.
Obviously, the above embodiments of the present invention is used for the purpose of clearly illustrating examples for clearly illustrating the present invention, and
It is not limitations of the embodiments of the present invention.For those of ordinary skill in the art, in above description
On the basis of can also make other variations or changes in different ways.There is no need and unable to give all embodiments
Exhaustion.Any modifications, equivalent replacements, and improvements made within the spirit and principle of the present invention etc., should be included in
Within the protection scope of the utility model claims.
Claims (11)
1. a kind of large bore engine piston, piston includes top compression ring slot (1), second gas ring slot (2) from top to bottom
With third road oil ring groove (3), which is characterized in that the lower groove face (21) of the second gas ring slot (2) of the piston from its slot bottom to
Upper inclination predetermined angle (α)；
Periphery wall between the second gas ring slot (2) and third road oil ring groove (3) of piston is third ring bank (C), the third
Ring bank (C) is connect with the second gas ring slot (2) through recessed portion (4).
2. large bore engine piston according to claim 1, which is characterized in that the recessed portion (4) is to be set to
The right angle groove of third ring bank (C) upper end, the lower groove face of the slot bottom of the right angle groove and the second gas ring (5)
(21) it connects.
3. large bore engine piston according to claim 2, which is characterized in that the slot bottom of the right angle groove and institute
State lower groove face (21) the fillet smooth transition of second gas ring (5).
4. large bore engine piston according to claim 1, which is characterized in that the recessed portion (4) is along the work
The size range of the radial depth capacity (D) of plug is 0.5-1.5mm.
5. large bore engine piston according to claim 1, which is characterized in that the recessed portion (4) is along piston shaft
To height (H) be not less than 1mm.
6. large bore engine piston according to claim 1, which is characterized in that the recessed portion (4) is interior concave curved
Face, the both ends of the recessed portion (4) are connected to the lower groove face (21) and the third ring bank of the second gas ring slot (2)
(C)。
7. large bore engine piston according to claim 1, which is characterized in that the recessed portion (4) is outer evagination
Face, the both ends of the recessed portion (4) respectively with the lower groove face (21) of the second gas ring slot (2) and the third ring bank (C)
Connection.
8. large bore engine piston according to claim 1, which is characterized in that the second gas ring slot (2)
Upper groove surface (22) tilts predetermined angle (β) from its slot bottom upwards.
9. large bore engine piston according to claim 1, which is characterized in that the second gas ring slot (2)
The lower groove face (21) of upper groove surface (22) and the second gas ring slot (2) is arranged in parallel.
10. large bore engine piston according to claim 8, which is characterized in that the predetermined angle (α) and described
The range of predetermined angle (β) is 0.1 ° -0.4 °.
11. a kind of engine, which is characterized in that including the described in any item large bore engine pistons of claim 1-10.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821778391.XU CN209444454U (en) | 2018-10-31 | 2018-10-31 | A kind of large bore engine piston and engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821778391.XU CN209444454U (en) | 2018-10-31 | 2018-10-31 | A kind of large bore engine piston and engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN209444454U true CN209444454U (en) | 2019-09-27 |
Family
ID=68010870
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201821778391.XU Active CN209444454U (en) | 2018-10-31 | 2018-10-31 | A kind of large bore engine piston and engine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN209444454U (en) |
-
2018
- 2018-10-31 CN CN201821778391.XU patent/CN209444454U/en active Active
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| GR01 | Patent grant |