CN216841948U - Quick oil return cylinder sleeve - Google Patents

Abstract

The utility model provides a quick oil return cylinder liner of automobile engine's accessory strengthens the endurance reliability of high explosion pressure and high power engine. The utility model discloses there is the oil groove design at the following cylinder liner inside diameter face design of oil ring lower dead center position, and the machine oil that the oil ring was scraped can fall along the quick release of the oil groove on the cylinder liner, greatly reduced remain the machine oil on the cylinder liner by the risk of scraping. The design of oil groove is preferred to be concentrated on the pinhole direction of piston, rather than the design that all the overall arrangement oil groove of a week, prevents that the piston from when moving bottom dead center position, because the area of contact of piston skirt portion and oil groove position oil groove department reduces, and the skirt portion contact surface that causes increases, and piston skirt portion wearing and tearing are inhomogeneous, and the wearing and tearing increase draws the jar even. The design does not influence the performance of the piston, and is favorable for the oil return effect of engine oil.

Description

Quick oil return cylinder sleeve

Technical Field

The utility model relates to an engine fitting technical field especially relates to an engine cylinder liner of quick oil gallery in area.

Background

In recent years, high explosion pressure and high power, which place more stringent demands on engine durability, will be one of the main features of the next generation of engine technology upgrades. The engine cylinder liner as one of the core engine parts will be challenged by the requirement of higher endurance reliability, as shown in fig. 1, which is the current cylinder liner design. The inner diameter of the cylinder sleeve is designed to be smooth and is provided with a certain honing reticulation. The disadvantages of this design are: when the oil ring scrapes oil to the bottom dead center position, the oil accumulated below the oil ring is not well released, and there is a risk that the oil further remaining on the cylinder liner is scraped up. As an improvement, in the prior art, an oil return groove is provided below the bottom dead center position of the cylinder liner, as shown in fig. 2, when the engine oil is scraped to the bottom dead center position, the engine oil flows into the oil return groove, and is prevented from being brought back to the combustion chamber by the piston.

SUMMERY OF THE UTILITY MODEL

In view of the above-mentioned problems, the present invention is directed to solving, at least to some extent, one of the technical problems in the related art. Therefore, the utility model provides a quick oil return cylinder liner can solve the machine oil that exists among the prior art and be scraped to the lower dead center position and store up the back, can not in time flow back to technical problem such as oil bath.

In order to solve the technical problem, the utility model adopts the following technical scheme:

the quick oil return cylinder liner is provided as an elongated cylinder having a liner outer surface and a liner inner surface, a liner central axis defined by the liner inner surface extends between a first liner axial end and a second liner axial end, the liner inner surface is configured to form a combustion chamber together with a piston and an engine housing, the piston is located in the cylinder liner and is movable relative to the cylinder liner between a top dead center position and a bottom dead center position, a quick oil return portion is provided on the liner inner surface corresponding to a non-skirt portion of the piston, that is, an oil return groove is provided only on the inner surface of the cylinder liner on the corresponding side of a piston pin axis, and no oil return groove is provided on the liner inner surface corresponding to the piston skirt portion, and further, the oil return portion is located: when the piston is at the bottom dead center position, the oil blade of the piston oil is positioned below the position of the inner surface of the cylinder sleeve corresponding to the oil blade; and the quick oil return portion extends to the second cylinder liner axial end and forms an opening at the second cylinder liner axial end. Therefore, the problem that in the prior art, the piston skirt is abraded due to the fact that the swinging piston collides with the oil return groove can be effectively avoided.

Further, the oil return portions are provided as a plurality of oil return grooves extending to the axial end of the second cylinder liner along the central axis of the cylinder liner. This is the main manifestation of the oil return.

Further, the main body cross-section of oil return groove sets up to the degree of depth be an, and the width is the rectangle of b, and two adjacent oil return groove intervals are c, as preferred, the degree of depth a of oil return groove >0.050mm, width b >1.0mm, two adjacent oil return groove intervals c set up to:

1.0mm<c<4.3mm。

further, the cross-sectional shape of the oil return groove in front view on the side close to the combustion chamber should be set to be semicircular, square, elliptical, or other shapes that facilitate the stored lubricant to be more easily collapsed into the oil return groove.

Furthermore, in order to make the lubricating oil flow into the oil return groove immediately when the lubricating oil drops or flows in a strand, it is particularly important to set the distance d between the corresponding position of the lower oil blade line of the oil scraper ring oil blade (i.e. the lowermost side ring line formed by the contact of the oil blade and the cylinder liner) and the vertex of the oil return groove at the bottom dead center, and after repeated verification, the d is set as: 1.75mm < d <4.3mm, is most favorable for lubricating oil backflow.

Furthermore, the distribution of the oil return part is limited in a numerical mode, the axial direction of the piston pin is set to be 0-180 degrees, the distribution range of the oil return part or the oil return groove is 0-45 degrees, 135-225 degrees, 315-360 degrees according to the distribution of the piston skirt part, and the number of the oil grooves is more than or equal to 2.

Yet further, it may relate to a cylinder liner and piston assembly, said assembly comprising:

a quick return oil cylinder liner as previously described;

a piston located in the cylinder casing and movable relative to the cylinder casing between a top-dead-center position and a bottom-dead-center position and including an upper piston face, a lower piston face, and a lower piston face forming a combustion surface.

Implement the technical scheme of the utility model, following beneficial effect has at least:

1) below the oil ring lower dead center position, the oil groove design of cylinder liner internal surface makes the quick backward flow of oil edge oil groove of oil ring scraping, and greatly reduced remains the risk of scraping on the machine oil on the cylinder liner by last.

2) The oil groove sets up the pinhole direction at the piston, because the piston is contactless with the cylinder liner on the pinhole direction, when the piston moved to the lower dead center position, the design of piston pinhole direction fretwork, can not have piston and cylinder liner contact in this side, does not have the influence to the piston performance, and on the other hand also is favorable to the oil return effect of machine oil.

3) The oil groove overall arrangement is sheathe in the cylinder on the round pin accuse direction, when having avoided whole week circle department oil groove, piston skirt portion and oil groove contact, because the area of contact of oil groove department reduces, can make the piston increase at the lower extreme point department skirt portion contact surface pressure, piston skirt portion wearing and tearing are inhomogeneous, to the fish tail of piston skirt, has the risk of drawing the jar in the time.

4) The oil groove is run through to the bottom of cylinder liner, can release the interior oil of oil groove to the crankcase in, can not accumulate in the oil groove, has avoided piston and bent axle to the oil of accumulation bottom the oil groove to scurry the risk.

Additional aspects and advantages of the present application will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.

Drawings

FIG. 1 is a side cross-sectional view of a prior cylinder liner design.

FIG. 2 is a side cross-sectional view of an embodiment of the present invention.

FIG. 3 is a layout of the cylinder liner oil grooves.

Fig. 4 is a diagram of oil groove dimensions.

Fig. 5(a) shows a state of the lubricating oil without the provision of the oil returning groove in the prior art.

Fig. 5(b) shows the state of the lubricating oil after the non-opening oil return groove is provided.

Fig. 5(c) shows the state of the lubricating oil after the oil return grooves of the present embodiment are provided.

Description of reference numerals:

1-cylinder liner; 10-the central axis of the cylinder sleeve; 11-the outer surface of the cylinder sleeve; 12-cylinder liner inner surface; 13-first axial liner end; 14-second axial liner end; 15 a flange;

2-an oil return groove; 3-a piston; 4-an oil ring; 5-piston pin;

a-the depth of the section of the oil return groove main body; b-the width of the section of the oil return groove main body;

c-the distance between two adjacent oil return grooves; d is the distance between the oil blade of the oil ring and the contact lower side ring line of the cylinder sleeve and the vertex of the oil return groove.

Detailed Description

To make the purpose, technical solution and advantages of the embodiments of the present invention clearer, the technical solution in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention, and obviously, the described embodiments are some, but not all, embodiments of the present invention. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative efforts belong to the protection scope of the present invention.

Those skilled in the art will appreciate that in a cylinder liner and piston assembly, the cylinder liner is an elongated cylindrical body having a liner outer surface and a liner inner surface defining a liner central axis extending between first and second axial liner ends, the piston moves between a Bottom Dead Center (BDC) position and a Top Dead Center (TDC) position in the engine liner to provide lubrication, avoid dry-out, form an oil intake gap between the top ring and the liner, and to avoid oil from entering the combustion chamber and causing carbon deposits, an oil ring is provided on the piston to scrape lubricating oil back into the crankcase sump when the piston is operating toward bottom dead center to thereby limit oil migration from the gap to the combustion chamber.

As noted in the background, the prior art cylinder liners and piston assemblies also suffer from certain drawbacks. For example, after the piston oil ring scrapes the lubricating oil back to the bottom dead center position, the lubricating oil flows back by gravity, but at the stage when the engine is just started or the temperature of the cylinder liner and the lubricating oil is not high, the flowing performance of the lubricating oil is poor, and the lubricating oil is accumulated on the cylinder liner at the bottom dead center position and is easily sucked back to the combustion chamber.

In the prior art, there is the cylinder liner structure as in fig. 1, wherein, although it is the improvement to the lubricating oil film, in fact also produced certain influence to the oil return effect, like fig. 5(b), lubricating oil flows back into the recess, the recess stores lubricating oil, for the fig. 5(a) that does not have the oil return tank among the prior art, the risk of suck-back has been avoided to a certain extent, however, because the machine oil quantity that the recess holds is limited, after the groove structure is full of oil, oil drips gather outstanding cylinder liner internal surface again, at this moment, when the piston rises from the bottom dead center, oil drips outstanding at the oil groove bottom are taken back to the cylinder liner inner wall very easily, be unfavorable for lubricating oil backward flow crankcase oil bath.

The utility model discloses to above-mentioned problem, improve the cylinder liner structure, under the circumstances of guaranteeing lubricated effect, make smooth and easy oil return in the cylinder liner, avoid lubricating oil to leap up to the purpose of the effect such as the problem that the combustion chamber leads to the carbon deposit. See below for a description of specific solutions.

Referring to fig. 1-2, in some embodiments of the present application, a cylinder liner with fast oil return is provided for use in a cylinder liner and piston assembly of an engine to further improve oil return to the cylinder liner of the engine.

The cylinder liner 1 includes an elongated cylindrical body having a liner outer surface 11 and a liner inner surface 12, the liner inner surface 12 defining a liner central axis 10 extending between a first axial liner end 13 and a second axial liner end 14. The elongated cylinder further comprises a flange 15 protruding radially outwards on the first axial liner end 13. In figure 1 the inner surface 12 of the cylinder liner 1 provides a surface supporting the reciprocating movement of the piston, the upper limit of piston movement being the Top Dead Centre (TDC) position and the lower limit being the Bottom Dead Centre (BDC) position, an oil intake gap being formed between the piston and the liner, and an oil ring being provided on the piston for scraping lubricating oil back to the crankcase oil sump.

In the process of piston operation, the lubricating oil is scraped to the position of the lower dead point, the lubricating oil flows back to the oil pool of the crank case along the wall of the cylinder sleeve by means of gravity, however, the fluidity of the lubricating oil at low temperature is not enough to flow and drip back to the oil pool completely and smoothly.

As a solution, in order to smoothly guide the scraped lubricating oil to the oil return pool, as shown in fig. 1, the oil return groove 2 with a groove structure is provided at the bottom of the cylinder liner in the present embodiment. The highest point of the oil return groove 2 in the direction of the central axis 10 is located at a position which is a distance d below a lower circular line where an oil edge of the oil ring contacts the inner surface 12 of the cylinder liner when the piston is at the bottom dead center position, that is, the highest point of the oil return groove 2 is just capable of receiving lubricating oil scraped from the inner surface 12 of the cylinder liner by the oil ring.

According to this, can effectual solution lubricating oil resorption's technical problem, however, need emphasize, the oil gallery of ring cloth on the cylinder liner, because it has reduced the area of contact of piston skirt portion and cylinder liner in the piston reciprocating motion process, and when the piston was swung in service, piston skirt and rough surface contact led to the fact piston skirt portion damage easily, led to the coating to drop, impaired piston skirt and cylinder liner contact further fish tail cylinder liner, serious lead to drawing the jar. Therefore, in the solution of the present embodiment, a quick oil return portion is provided on the inner surface of the cylinder liner corresponding to the non-skirt portion of the piston, that is, the oil return groove 2 is only provided on the inner surface 12 of the cylinder liner on the corresponding side of the piston pin, and the oil return groove 2 is not provided on the inner surface of the cylinder liner corresponding to the skirt portion of the piston, and is directly communicated with the second axial cylinder liner end surface 14 of the cylinder liner, so as to guide the lubricating oil to smoothly drop into the crankcase oil sump.

For better understanding of the distribution of the sumps 2, the range of the sumps is described in terms of angles, as shown in fig. 4: the direction of the pin shaft of the piston is 0-180 degrees, and the preferable distribution range of the oil return grooves 2 is 0-45 degrees, 135-225 degrees and 315-360 degrees according to the distribution of the piston skirt. The range can be properly adjusted according to different designs of the piston skirt, for example, the sizes of the main thrust surface and the auxiliary thrust surface of some pistons are different, so that the size design of the piston skirt is different, that is, the position range of the oil return groove can be flexibly adjusted according to the size of the piston skirt, and is, for example, 0-55 degrees, 125 degrees, 215 degrees, 325 degrees and 360 degrees. The maximum extent is limited by the absence of wear on the piston skirt.

In order to obtain more reasonable parameter data, reasonable experimental verification is indispensable, in this embodiment, the distance between the lower circular line of the contact between the oil blade of the oil ring and the inner surface 12 of the cylinder sleeve and the top end of the oil return groove 2 is d when the bottom dead center is set, and the front-view cross-sectional shape of the oil return groove close to the combustion chamber side is semicircular, square or oval, so as to form a shape setting which easily guides the backflow of the lubricating oil, and the experimental verification is performed on the size of d and the shape of the top of the oil return groove. In consideration of low-temperature fluidity and high-temperature viscosity of the lubricating oil, the most commonly used engine oil 5W-30 in automobiles is taken as the experimental lubricating oil. According to the fluidity research of the strand and drop of the lubricating oil at low temperature and high temperature, further, according to the thickness of the lubricating oil film and the thickness experiment result (the experiment process is not repeated) which can be influenced by the reciprocating motion process of the piston, the size of d is set to be in the range of 1.75mm-4.3mm, under the condition that d is 1.75mm, the lubricating oil is scraped and accumulated by an oil ring, after the oil film is formed, redundant height forms flowing liquid flow, the strand and drop of the lubricating oil flow is timely collapsed into the groove 2, meanwhile, when the piston moves towards the upper dead center, because the distance between 1.75mm and the oil ring and the residual ring bank is set reasonable, when the scraped lubricating oil forms oil drops or strands, namely when the piston stops at the lower dead center, the scraped lubricating oil flows into the oil return groove, the accumulated or accumulated height does not touch the side face of the piston, therefore, the generated return air flow, the lubricating oil is sucked back and brought back in a very small amount. However, when the distance between the oil return groove 2 and the oil ring is less than 1.75mm, because the oil return groove 2 is closer to the oil ring and farther from the edge of the residual ring land, although the scraped lubricating oil flows into the oil return groove 2, the phenomenon of belt return is obvious due to the belt return air flow generated by the piston and the negative pressure generated by the oil ring, and the belt return phenomenon is more serious the closer the position is to the oil ring at the lower dead point.

When the oil is continuously moved downwards to the upper top point of the oil return groove 2 to the position 4.3mm away from the oil ring at the bottom dead center of the inner surface of the cylinder sleeve, because the scraped lubricating oil forms oil drops higher than the oil film on the inner surface 12 of the cylinder sleeve or the flowing lubricating oil is highly contacted with the surface of the piston, the lubricating oil is accumulated on the cylinder sleeve in the two states, and the machine is easily brought back to the top dead center or even sucked back to a combustion chamber by the negative pressure generated by the sealing of the oil ring.

In order to further facilitate the flow of the lubricating oil into the oil return grooves 2 in consideration of the oil film forming and dripping properties of the lubricating oil, it should be clear that the depth a and the width b of the oil return grooves 2 and the distance c between two adjacent oil grooves are further set. The arrangement of the oil groove parameters of depth a and width b and the oil groove distance c is mainly based on the means that the accumulation of the lubricating oil into drops is still controlled, so that the lubricating oil can be timely collapsed and converged into a strand to flow down from the oil return groove 2 before the lubricating oil is accumulated into drops. Fig. 4 shows a cross-sectional view of the oil return groove 2, wherein the dimensions of the oil groove are defined as follows:

a>0.050mm；

b>1.0mm。

the distance c between the two adjacent oil return grooves is set as follows:

1.0mm<c<4.3mm。

< Industrial Applicability >

Experimental comparison referring generally to fig. 5(a), 5(b) and 5(c), fig. 5(a) shows the prior art arrangement without oil return grooves, it can be seen that the lubricating oil scraped back from the inner surface of the cylinder liner is accumulated on the lower side of the bottom dead center oil ring, and is easily subjected to suck back and carry back when the oil ring moves upward.

Fig. 5(b) shows the state of the lubricating oil after the non-opening oil return groove is arranged, after the engine is operated, the oil ring scrapes the lubricating oil to the position below the position of the oil ring of the piston bottom dead center, and due to the oil return groove, the lubricating oil flows back to the oil return groove when being accumulated to drop or flow in a strand, and is accumulated in the oil return groove, and when the fluidity of the lubricating oil does not meet the expected requirement, the accumulation protrudes out of the cylinder sleeve. The lubricating oil droplets in such a suspended state are inevitably scraped and rewound by the negative pressure generated by the rising of the piston and the oil scraper ring.

Fig. 5(c) shows the state of the lubricating oil after the oil return groove is set in this embodiment, after the engine is operated, the oil ring scrapes the lubricating oil down to the lower side of the oil ring position of the piston bottom dead center, because the setting is reasonable, when the lubricating oil is stored up to be a drop or a strand and flows, the volume of the lubricating oil covers the oil return groove, so that the oil drops collapse to enter the oil return groove, smoothly flow into the oil return groove after being accumulated, and flow back to the crankcase along the oil return groove by gravity. This arrangement also avoids the back-scraping and back-banding that occurs in the arrangement of figure 5 (b).

The detailed description of the present invention is the technology known to those skilled in the art. Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit the same; although the present invention has been described in detail with reference to the foregoing embodiments, it should be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; such modifications and substitutions do not depart from the spirit and scope of the present invention in its corresponding aspects.

Claims (7)

1. A quick return oil cylinder liner, the cylinder liner (1) being an elongated cylindrical body having a liner outer surface (11) and a liner inner surface (12), the liner inner surface (12) defining a liner central axis (10) extending between a first liner axial end (13) and a second liner axial end (14), the liner inner surface (12) being configured to form a combustion chamber with a piston (3) and an engine housing, the piston (3) being located in the cylinder liner (1) and being movable relative to the liner between a top dead center position and a bottom dead center position, the piston (3) being provided with an oil ring (4), characterized in that:

a quick oil return part is arranged on the inner surface of the cylinder sleeve corresponding to the non-skirt part of the piston, and the oil return part is positioned below the position of the inner surface of the cylinder sleeve corresponding to the oil blade of the piston oil ring (4) when the piston (3) is positioned at the bottom dead center position;

and the quick oil return portion extends to the second cylinder liner axial end (14) and forms an opening at the second cylinder liner axial end (14).

2. The quick oil return cylinder liner according to claim 1, characterized in that the oil return portion is a plurality of oil return grooves (2) extending along the central axis (10) of the cylinder liner to the axial end (14) of the second cylinder liner.

3. The cylinder liner with quick oil return function as claimed in claim 2, wherein the cross section of the main body of the oil return groove (2) is a rectangle with a depth a and a width b, and two adjacent oil return grooves have a distance c.

4. The quick oil return cylinder liner according to claim 3, wherein the depth a of the oil return groove (2) is more than 0.050mm, the width b is more than 1.0mm, and the distance c between two adjacent oil return grooves is set as follows:

1.0mm<c<4.3mm。

5. the quick oil return cylinder liner according to claim 3, characterized in that the oil return groove (2) has a semicircular, square, oval cross-sectional shape in front view close to the combustion chamber side.

6. The cylinder liner with quick oil return according to claim 3, characterized in that the distance between the vertex of the oil return groove (2) and the lower circular line of the oil cutting edge of the oil ring contacting with the inner surface (12) of the cylinder liner at the bottom dead center of the piston is d, and the d is set as:

1.75mm<d<4.3mm。

7. the cylinder liner for rapid oil return according to any one of claims 2-6, wherein the direction of the pin shaft of the piston is 0-180 °, and the distribution range of the oil return grooves (2) or the oil return parts is 0-45 °, 135 ° -225 °, 315 ° -360 °, and the number of the oil grooves is more than or equal to 2 according to the distribution of the skirt part of the piston.

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