CN218235289U - Piston ring group structure and diesel engine - Google Patents

Abstract

The utility model discloses a piston ring group structure and diesel engine belongs to piston equipment technical field, has solved the phenomenon that the present gaseous power of being used in on the piston ring and the resultant force of elasticity can cause the piston ring to produce radially collapsing, and the piston ring takes place for a long time and radially collapses the problem that makes the air leakage increase of piston easily, and when having improved the piston ring and collapsing, the air leakage that collapses reduces by a wide margin, has reduced the beneficial effect of terminal surface local contact stress under the first piston ring simultaneously, and the concrete scheme is as follows: the utility model provides a piston ring group structure, includes the piston body, and in the cylinder liner was located to the piston body, the week side of piston body was equipped with first piston ring groove and the second piston ring groove that sets gradually along its axial, and first piston ring groove is trapezoidal annular, and first piston ring is located in the first piston ring groove, and the second piston ring groove is the rectangle annular of up-warping setting angle formation inclination of up end, and the second piston ring is located in the second piston ring groove.

Description

Piston ring group structure and diesel engine

Technical Field

The utility model belongs to the technical field of piston equipment technique and specifically relates to a piston ring group structure and diesel engine.

Background

The statements in this section merely provide background information related to the present disclosure and may not constitute prior art.

At the present stage, the strengthening degree of the strengthening machine type of the diesel engine is high, the heat load is high, the piston adopts a rectangular groove, the engine oil is easy to coke, the carbon deposition is generated, and the lower end surface of the rectangular piston ring groove is in a horizontal state, the carbon deposition is difficult to be discharged in time, so that the consumption of the engine oil is increased, and the gas sealing effect of the piston ring is poor;

in addition, the motion law of the piston ring influences air leakage, the upper end face of the existing rectangular piston ring groove is in a horizontal state, the matched piston ring can be distorted in the working process, the piston is deformed by the heated ring groove and inclines, particularly, the resultant force of gas force and elastic force acting on the piston ring can cause the piston ring to generate a radial collapse phenomenon, the contact stress point of the distorted piston ring and the upper end face of the horizontal rectangular piston ring groove is close to the periphery of the piston body, so that the floating time of the piston ring is long, and meanwhile, the air leakage of the piston is easily increased due to the fact that the piston ring radially collapses for a long time.

SUMMERY OF THE UTILITY MODEL

The utility model aims at providing a not enough to prior art exists, the utility model aims at providing a piston ring group structure and diesel engine, the resultant force of having solved gas power and elasticity that is used in on the piston ring can cause the piston ring to produce radially to sink, causes the big problem of air leakage, has reduced terminal surface local contact stress under the first piston ring simultaneously, has avoided the interior carbon deposition jamming risk of annular of the rectangular ring scheme of no declination angle again.

In order to achieve the above purpose, the present invention is realized by the following technical solution:

the utility model provides a piston ring group structure, includes the piston body, and in the cylinder liner was located to the piston body, the week side of piston body was equipped with first piston ring groove and second piston ring groove that set gradually along its axial, and first piston ring groove is trapezoidal annular, and first piston ring is located in the first piston ring groove, and the second piston ring groove is the rectangle annular that the up-warping angle setting formed the inclination for the up end, and the second piston ring is located in the second piston ring groove.

In the above-mentioned piston ring set structure, the size of the inclination angle is between 10 'and 40'.

In the above piston ring set structure, the first piston ring is a ladder-shaped ring, and the diameter of the first piston ring in a natural state is larger than the inner diameter of the cylinder liner.

In one piston ring set structure as described above, the downward inclination angle of the first ring groove ranges from 0 ° to 7 ° 36'.

In the above-described piston ring set structure, the downward inclination angle of the first piston ring is greater than the downward inclination angle of the first piston ring groove.

According to the piston ring set structure, the periphery of the piston body is provided with the insert ring.

According to the piston ring group structure, the first piston ring groove is formed in the inlaid ring, and the second piston ring groove is formed in the bottom of the inlaid ring.

In the above piston ring set structure, the first piston ring and the second piston ring are provided with the notches, and the notches on the first piston ring and the second piston ring are arranged in a staggered manner.

In the above piston ring set structure, the first piston ring is arranged between the second piston ring and the piston crown.

A diesel engine comprises a cylinder and a piston ring set structure, wherein the piston ring set structure is the piston ring set structure.

Above-mentioned the utility model has the advantages as follows:

1. the utility model discloses an increase the inclination design at the second piston ring groove up end of rectangle, under the condition that does not increase piston ring elasticity, solve the problem of collapsing of the local time domain of piston ring, make the second piston ring stage of admitting air jump the in-process, change the inboard contact into with the annular contact point by the outside contact with cyclic ring, second piston ring up end and gas contact area have been increased, and then second piston ring side pressure has been increased, make the dwell time of second piston ring come-up in second piston ring groove reduce, the long time that the second piston ring collapses obviously improves, the air leakage volume of collapsing reduces by a wide margin, and simple structure, low cost, the effect is showing, convenient and feasible.

2. The first piston ring groove is matched with a trapezoidal first piston ring downtilt angle, the first piston ring downtilt angle is larger than the first piston ring groove downtilt angle, the downtilt angle range of the first piston ring groove is 0-7 degrees 36', the lower end face of the first piston ring is contacted uniformly as much as possible, the local contact stress of the lower end face of the first piston ring is reduced, the risk of carbon stagnation in the ring groove of a rectangular ring scheme without the downtilt angle is avoided, and the sealing performance, the reliability and the carbon removal performance of the piston and the piston ring are considered.

Drawings

The accompanying drawings, which form a part of the specification, are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention and not to constitute a limitation on the invention.

Fig. 1 is a schematic view of the second piston ring and the second piston ring groove in the embodiment of the present invention.

Fig. 2 is a schematic view of a second piston ring engaged with a second ring groove in the prior art.

Fig. 3 is a schematic view of the first piston ring and the first ring groove of the embodiment of the present invention.

Fig. 4 is a schematic view of the amount of air leakage due to collapse of a second piston ring in the prior art.

Fig. 5 is a schematic view of the second piston ring collapse air leakage after the inclination angle of the second piston ring groove is increased.

In the figure: the spacing or dimensions between each other are exaggerated to show the location of the various parts, and the schematic is shown only schematically.

Wherein: 1. the piston comprises a piston body, 2, a first piston ring groove, 3, a first piston ring, 4, a second piston ring groove, 5, a cylinder sleeve and 6, a second piston ring.

Detailed Description

It should be noted that the following detailed description is exemplary and is intended to provide further explanation of the invention. Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs.

Just as the background art introduces, the gaseous power and the resultant force of elasticity on the piston ring can cause the piston ring to produce radially collapsing among the prior art, causes the problem of air leakage increase, in order to solve above-mentioned technical problem, the utility model provides a piston ring group structure and diesel engine.

Example one

The utility model discloses an in the typical embodiment, refer to fig. 1-3, a piston ring group structure, including piston body 1, piston body 1 locates in cylinder liner 5 and along 5 axial motion of cylinder liner, and the week side of piston body 1 is equipped with the inlay circle, is equipped with the first piston ring groove that sets up along its axial on the inlay circle, and the second piston ring groove is located the inlay circle bottom.

The ring carrier and the piston body are made into an integrated structure, so that the problem of abrasion of the piston ring is solved.

First piston ring groove 2 adopts trapezoidal annular, and first piston ring 3 adopts trapezoidal ring in locating first piston ring groove 2, first piston ring 3 between first piston ring groove 2 and cylinder liner 5 in order to realize sealed.

The second piston ring groove 4 is a rectangular ring groove with an inclined angle formed by the upwarping of the upper end face, the second piston ring is arranged in the second piston ring groove, a piston ring with a rectangular cross section is adopted, and the first piston ring 3 is arranged between the second piston ring 6 and the top of the piston.

The motion law of piston ring influences the gas leakage of piston, especially the piston ring that combined action is caused to gas force and elasticity on the piston ring radially sinks, lead to the gas leakage increase, radial collapse to the gas leakage increase's that leads to of air intake phase second way rectangle piston ring problem, the up-warping of the up end that sets up second piston ring groove 4 sets up the angle and forms the inclination, make second piston ring 6 in the in-process of admitting air phase jump, the contact point of piston ring and piston ring groove becomes inboard contact, thereby the up end of piston ring and gaseous area of contact have been increased, under gaseous effect, the upside pressure of piston ring has been increased, make the dwell time of second piston ring 6 come-up in second piston ring groove 4 reduce, reduce the length of time that the second piston ring sinks, the gas leakage that sinks reduces by a wide margin.

Radial collapse of the second piston ring: the resultant force of gas force and elastic force acting on the piston ring at a certain moment is directed to the inner side of the piston ring, so that the outer circular surface of the second piston ring is not in contact with the cylinder sleeve locally, and air leakage is increased.

As shown in fig. 2, the existing rectangular second piston ring groove 4 is matched with the rectangular second piston ring 6, the second piston ring 6 is twisted during the working process, and the piston is deformed by the heated ring groove and declines, so that the contact stress point between the second piston ring 6 and the second piston ring groove 4 is mostly positioned on the outer peripheral side of the second piston ring groove 4, after the inclination angle is increased on the upper side surface of the second piston ring groove 4, the original contact stress point moves to the bottom close to the second piston ring groove 4, so that the gas contact area between the upper side surface and the upper side of the second piston ring 6 is increased, the residence time of the second piston ring 6 floating in the second piston ring groove 4 is reduced, and the gas leakage is improved.

The magnitude of the upward inclination of the second ring groove 4 is 10' to 40', and the preferred inclination in this embodiment is 25', and the upward inclination of the second ring groove 4 refers to the inclination of the upper end surface of the second ring groove 4 from the inner end point of the groove.

As shown in fig. 4 and 5, in order to compare the blow-by amount after the increase of the inclination angle of the second ring groove 4, it was found that the blow-by amount of the piston ring was remarkably improved after the increase of the inclination angle of the second ring groove 4.

The main effect of first piston ring 3 and second piston ring 6 is high temperature high pressure gas in the sealed jar, prevents gaseous entering crankcase, and in first piston ring, current first piston ring 3 cooperates with the rectangle structure of piston groove, and ring and annular declination angle are 0, and lower terminal surface contact is even relatively, though avoided the big problem of terminal surface local contact stress under the piston ring, nevertheless be unfavorable for the discharge of annular interior carbon deposit, cause the jamming of piston ring easily.

As shown in fig. 3, the first piston ring 3 groove of the present embodiment is a trapezoid ring groove, and when the first piston ring 3 is actually assembled with the first piston ring groove 2, the downward inclination angle of the first piston ring 3 is greater than the downward inclination angle of the first piston ring groove 2, the downward inclination angle of the first piston ring groove 2 ranges from 0 ° to 7 ° 36', and in the present embodiment, it is preferable that the first piston ring with a downward inclination angle of 3 ° 6' is matched with the first piston ring groove with a downward inclination angle of 3 °.

First piston ring down-rake: refers to the included angle (acute angle) between the lower end surface of the first piston ring and the horizontal direction.

First ring groove downward inclination angle: the included angle (acute angle) between the lower end surface of the first piston ring groove and the horizontal direction is indicated.

It should be noted that the downward inclination angle of the first piston ring is greater than the downward inclination angle of the first piston ring groove.

In the course of the work of piston, piston body 1 is heated the inflation, and the terminal surface has declined under the annular, and the annular total inclination increases, makes terminal surface and the first piston ring slot downside contact as far as possible even under the first piston ring 3, guarantees the face contact of ideal, has both reduced terminal surface local contact stress under the first piston ring 3, has avoided the interior carbon deposition jamming risk of annular again, has compromise leakproofness, reliability, the row carbon nature of piston and piston ring.

The diameter of the first piston ring 3 in a natural state is larger than the inner diameter of the cylinder sleeve, so that the second piston ring can be conveniently installed on the cylinder sleeve along with the piston body and then generates elastic force to cling to the cylinder sleeve.

The diameter of second piston ring 6 under the natural state also is greater than the internal diameter of cylinder liner to produce elasticity and cylinder liner adaptation during the installation, thereby prevent that twice piston ring elasticity from increasing the increase work of friction at present, reduce the overall efficiency of engine, consequently the mode that this embodiment adopted to set up second piston ring groove upper inclination solves the radial problem of collapsing of second piston ring, guarantees that the overall efficiency of engine does not reduce. And the structure is simple, the cost is low, the effect is obvious, and the method is feasible.

First piston ring 3 and second piston ring 6 are equipped with the incision, and the setting of staggering of incision on first piston ring and the second piston ring carries out effectual sealing to the high-pressure gas in the cylinder.

Example two

A diesel engine comprises a cylinder and a piston ring set structure, wherein the piston ring set structure adopts the piston ring set structure in the first embodiment, and the diesel engine in the embodiment also has the technical effects in the first embodiment, which are not repeated herein.

The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (10)

1. The utility model provides a piston ring group structure, its characterized in that includes the piston body, and in the cylinder liner was located to the piston body, the week side of piston body was equipped with first piston ring groove and the second piston ring groove that sets gradually along its axial, and first piston ring groove is trapezoidal annular, and first piston ring is located in the first piston ring groove, and the second piston ring groove is the rectangle annular of up-warping setting angle formation inclination for the up end, and the second piston ring is located in the second piston ring groove.

2. A piston ring set structure according to claim 1, wherein said inclination angle is in the range of 10 'to 40'.

3. The piston ring set structure as claimed in claim 1, wherein said first piston ring is a stepped ring, and a natural diameter of said first piston ring is larger than an inner diameter of said cylinder liner.

4. A piston ring set structure according to claim 3, wherein said first ring groove has a downward inclination in a range of 0 ° to 7 ° 36'.

5. The piston ring set structure as claimed in claim 4, wherein said first piston ring has a downward inclination larger than that of said first ring groove.

6. The piston ring assembly according to claim 1, wherein said piston body is provided with a ring insert on a peripheral side thereof.

7. The piston ring set structure as claimed in claim 6, wherein the first ring groove is formed in the insert ring, and the second ring groove is formed in a bottom portion of the insert ring.

8. The piston ring set structure as claimed in claim 1, wherein said first piston ring and said second piston ring are provided with cutouts, and the cutouts of the first piston ring and the second piston ring are offset.

9. The piston ring set structure as claimed in claim 1, wherein said first piston ring is disposed between said second piston ring and said piston crown.

10. A diesel engine comprising a cylinder and a piston ring assembly structure, wherein the piston ring assembly structure is according to any one of claims 1 to 9.

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