RU2627236C2 - Gasket, engine (versions) and automobile - Google Patents

Abstract

FIELD: automotive industry.

SUBSTANCE: gasket (105, 2100, 3100, 4100) is an integral part of a round ring shape (101). One gasket surface is provided with lubricating grooves (104, 2130, 3130, 4130), and the central axis of the lubricating groove (104, 2130, 3130, 4130) is a curve (103) or a straight line (102). The engine and the automobile, wherein the gasket is used (105, 2100, 3100, 4100) are also proposed.

EFFECT: improved device reliability.

26 cl, 12 dwg

Description

Technical field

The invention relates to the field of mechanics and automotive, in particular to gasket, engine and car.

State of the art

The main function of the gear liner is to limit the axial movement of the gear to ensure stable and reliable gear operation. Currently, the intermediate gear gasket has a circular annular design, in the center of which there is a hole for installing the bolt, and its supporting side has a flat surface.

The intermediate gear gasket is firmly pressed against the intermediate gear shaft with a locking bolt. Between the intermediate gear and the intermediate gear gasket there is a certain axial clearance. Currently, the axial clearance is 0.1-0.2 mm. Axial clearance ensures normal rotation of the intermediate gear. When the intermediate gear rotates, the gasket is able to prevent axial movement of the intermediate gear, thus ensuring its stable and reliable rotation.

During rotation of the idler gear, friction can occur between the idler gear and the idler gear gasket. To prevent abrasion of the idler gear and the idler gear gasket on surfaces with which the idler gear and the idler gear liner are in contact with each other, lubricating oil is used to create greater sliding to reduce friction.

On the one hand, the surfaces by which the intermediate gear washer and the intermediate gear are in contact with each other are planes in the prior art. With such a flat design, the lubricating oil is difficult to penetrate into the space between the two surfaces, which leads to insufficient lubricating effect.

On the other hand, since the shaft is a rotating part, the gasket mounted on the shaft may experience friction with the parts in contact with and moving relative to the latter during operation. Therefore, the gasket must be lubricated. Under current conditions, one way to do this is to create through holes in the gasket: the more such holes, the larger the lubrication area and the higher the lubrication efficiency. However, the larger the holes, the less rigidity and effectiveness of the gasket and, accordingly, its lower ability to withstand axial force. A known method, providing for the presence of lubricating grooves on the gasket, which are usually located radially and have exits on the inner or outer circles, which ensures the effectiveness of the gasket and facilitates the application and addition of lubricating oil. However, when the lubricating grooves are spaced apart from each other at a certain distance, then, firstly, the lubricating oil is not best distributed over the rubbing surface, and secondly, under the influence of friction forces on the surface of parts in contact with the gasket and moving relative to her, the oil during a rotational movement can be ejected outward in the radial direction under the action of centrifugal force, while the radially lubricating grooves located become channels for the release of oil, which leads to its expense. Obviously, this reduces the lubrication of the gasket with oil and shortens its service life. In addition, for conventional gaskets, lubricating oil is applied only once (during installation) or is periodically refilled. The possibility of continuous lubrication is not considered.

Conventional gaskets are inexpensive parts that are used in large quantities and which are difficult to remove since they are installed in hard-to-reach places. Maintenance technicians have to periodically replenish lubricant oil or replace gaskets, which entails labor costs that significantly exceed the cost of gaskets. In practice, service technicians are usually passive about replacing gaskets before problems such as increased engine noise or other malfunctions caused by excessive friction of the gasket. Thus, the direction of a more economical solution to the problem is to ensure the longest possible action of lubricating oil on the gasket to reduce abrasion and extend its service life.

Summary of the invention

The first objective of the invention is to eliminate the above disadvantages to create a gasket having the best lubricating effect, and, as a result, increase its efficiency and reduce the cost of maintenance.

This goal in one embodiment of the invention is achieved due to the fact that the gasket, which is a solid ring-shaped part, has at least one flat surface provided with a lubricating groove, the central axis of which has the form of a curved or straight line, while if the central Since the axis of the lubrication groove is a straight line, the internal angle between this central axis and the radial line coming from the center of the gasket is greater than zero.

Preferably, the lubrication grooves are evenly distributed over the annular surface of the gasket.

In a preferred case, both surfaces of the gasket are provided with lubricating grooves that are arranged in alternating order on both surfaces.

In a preferred case, both surfaces of the gasket are provided with lubrication grooves, the shapes of which on different surfaces may be the same or different.

Preferably, the lubrication groove is a through lubrication groove, the two open ends of which extend to the outer circumference of the gasket.

In the preferred case, the number of lubrication grooves is at least two.

In the preferred case, the number of lubrication grooves on different surfaces of the gasket is the same or different.

In a preferred case, the cross-sectional shape of the lubrication groove is an isosceles trapezoid with no upper base.

In the preferred case, the internal angle between two lines extending the sides of the isosceles trapezoid is from 30 ° to 90 °.

In a preferred case, at the intersection of two inclined planes of the sides of the lubricating groove with the plane of its base, pairing is performed along an arc of a circle.

In the preferred case, the lubricating groove is in the form of a flat spiral, exits to the inner and outer circles, and makes at least one revolution around the inner circle.

In the preferred case, the width of the lubrication groove gradually increases in the direction from the exit to the inner circumference.

In the preferred case, the width of the lubrication groove increases gradually and smoothly.

In a preferred case, the depth of the lubrication groove gradually increases in the direction from the outlet on the inner circumference.

In a preferred case, the depth increases gradually and smoothly.

Preferably, both surfaces of the gasket are provided with lubricating grooves in the form of spirals having the same or opposite directions.

In the preferred case, the lubrication groove is in the form of a flat spiral, one end of which extends on the outer or inner circumferences of the gasket, and the other is closed, and the lubrication groove makes at least one revolution around the inner circumference.

In the preferred case, the width of the lubrication groove decreases gradually from the open end to the closed.

In a preferred case, the width decreases gradually and smoothly.

In a preferred case, the depth of the lubrication groove decreases gradually from the open end to the closed.

In a preferred case, the depth decreases gradually and smoothly.

In a preferred case, both surfaces of the gasket are provided with lubricating grooves, each in the form of a spiral, having the same or opposite directions.

In a preferred case, the gasket is solid and stamped.

A second object of the invention is to provide an engine requiring less frequent maintenance.

The specified goal according to one of the embodiments of the invention is achieved due to the fact that the engine contains a distribution gear; camshaft drive circuit; fuel injector and gasket of the claimed design.

The camshaft drive chain drives the distribution gear, which is in contact with the gasket and rotates relative to the gasket in the direction opposite to the spiral direction of the lubrication groove of the gasket, while the fuel nozzle supplies oil to the camshaft drive chain and gasket at the same time.

The engine comprises a shaft that has a channel for supplying oil to the outlet of the lubricating groove made in the form of a spiral located at the inner circumference of the gasket, while the gear rotates in the direction corresponding to the direction of the gasket spiral.

In a preferred case, a helical gear is used as the gear.

An engine characterized in that the gasket described is used on its spindle.

The third objective of the invention is to provide a car that requires less frequent maintenance and allows longer intervals between maintenance work.

This goal is achieved due to the fact that the gasket described above is used in the car.

When using a gasket in accordance with embodiments of the invention, the lubrication grooves always have an outlet located at some angle to the direction of rotation of the intermediate gear so that the exit of the oil film due to rotation of the intermediate gear cannot close the outlet at the exit of the lubricant grooves on the surface of the gasket and that the lubricating oil can penetrate to the contacting surfaces of the intermediate gear and the gasket, which increases the lubrication efficiency. If only one surface of the gasket is provided with a lubricating groove, this reduces the manufacturing process and reduces production costs.

It should be noted that the presence of a lubricating groove on the gasket ensures its rigidity and effectiveness of the gasket. When the lubricating groove is in the form of a flat spiral, after the lubricating oil penetrates into the lubricating groove from its outlet on the inner circumference, the rubbing surface of an adjacent element (for example, gears), acting similarly to the impeller of the water pump, “pumps” the oil through the lubricating grooves in this way so that it makes at least one revolution in a spiral around the inner circumference and, thus, provides lubrication of the entire surface of the gasket around the circumference without directly expelling the oils and from the lubricating groove of the gasket in the radial direction, which provides better lubricating action and extends the life of the gasket.

Lubrication of the surrounding parts can also be achieved when the outlets of the lubrication groove are present on both the inner and outer circles.

When the grease groove has exits on the outer and inner circles, the width or depth of the grease groove increases gradually in the direction from the outlet on the inner circumference in the direction of oil flow, which is similar to the gradual increase in the diameter of the pipe formed between the grease groove and the adjacent part so that the adjacent part ( for example, gear) is farther from the oil inlet channel after turning relative to the gasket under friction against the gasket, and the farther from the oil inlet channel, the slower its oil flows and the higher static pressure oil. Similarly to the principle of operation of a spiral water pump, oil is pumped out of the lubrication groove evenly, after which it enters the next stage of the machine, circulating through the lubricated system - for example, it enters the oil sump of the engine. In addition, a gradual increase in the width of the lubrication groove also meets the requirement that the farther from the inner circumference, the more lubricating oil is required.

In addition, the constant and gradual change in the width and depth of the lubrication groove, as well as the manufacture of gaskets by stamping in the form of an integral part, facilitate the production process.

In addition, the presence of a lubricating groove on both surfaces of the gasket prevents its incorrect installation if the spirals have the same direction, and allows the gasket to rotate in different directions if the spirals have the opposite direction.

If there is a channel for supplying oil to the engine shaft, oil can flow to the outlet of the lubrication groove located on the inner circumference of the gasket. The direction of rotation of the gear corresponds to the direction of the gasket spiral, i.e. the gear and gasket form a spiral oil pump that provides continuous lubrication of the gasket.

In the case where the lubrication groove has an outlet on the outer circumference of the gasket, while the other end [grooves] is closed, oil enters the lubrication groove from this outlet and flows by gravity along the spiral of the lubrication groove under the action of gravity. The fact that the other end of the lubrication groove is closed prevents oil leakage, thereby extending the residence time of the oil in the lubrication groove while maintaining the amount of oil to be added per unit time, which means that the oil is held longer in the lubrication groove and the lubricating effect is also longer ; accordingly, the frequency of adding lubricant is reduced, which reduces the costs associated with oil loss and maintenance. The fact that the spiral makes one revolution around the inner circumference provides lubrication of the entire surface of the gasket around the circumference, thereby providing the best lubricating effect and prolonging the life of the gasket. In the case where the lubrication groove has an outlet on the inner circumference of the gasket while the other end of the [lubrication groove] is closed, most of the centrifugal force acting on the oil in the lubrication groove is compensated by the counteracting force created by the wall of the lubrication groove; the oil can only move in the direction of the spiral of the lubricating groove, reaching the closed end of the spiral under the action of a part experiencing friction against the gasket, which prevents the radial discharge of oil and accelerates the spreading of oil. The fact that the spiral makes at least one revolution around the inner circumference provides lubrication of the entire surface of the gasket around the circumference, thereby providing better lubricating action and prolonging the life of the gasket.

A gradual decrease in the width or depth of the lubricating groove in the direction from the open end to the closed end reduces the diameter of the oil channel formed between the lubricating groove and the adjacent part. After adding the lubricating oil enters the lubricating groove through the outlet on the outer circumference, when starting the engine, the adjacent part rotates in the direction opposite to the direction of the spiral of the lubricating groove, and under the action of this part, which experiences friction against the gasket, the flow velocity is moving away from the oil inlet oil rises, and the static oil pressure decreases, which ensures a quick distribution of oil over the entire surface of the gasket and contributes to its retention.

The constant and gradual change in the width and depth of the lubricating groove, as well as the method of manufacturing the gasket by stamping in the form of an integral part, facilitate the production process.

In addition, the presence of a lubricating groove on both surfaces of the gasket prevents its incorrect installation if the spirals have the same direction, and allows the gasket to rotate in different directions if the spirals have the opposite direction.

Installing a gasket in accordance with embodiments of the invention reduces the level of noise generated and reduces the frequency of maintenance.

The gasket according to the claimed embodiments of the invention is provided with a lubricating groove to provide rigidity and effectiveness.

Moreover, if the width or depth of the lubrication groove is gradually reduced in the direction of the oil flow, then after adding the lubricating oil, when the equipment is already running and the shaft rotates, under the action of the part experiencing friction against the gasket, the oil flow velocity as it moves away from the oil inlet channel increases, and the static pressure of the oil decreases, which ensures a quick distribution of oil over the entire surface of the gasket without flowing out from the closed end.

In addition, the constant and gradual change in the width and depth of the lubrication groove, as well as the method of manufacturing the gasket as a solid part by stamping, facilitate the production process.

At the same time, the presence of a lubricating groove on both surfaces of the gasket prevents its incorrect installation if the spirals have the same direction and allows rotation in different directions if the spirals have the opposite direction.

Installing a gasket in accordance with the claimed variants of the invention in the engine or on the spindle of the car reduces the level of noise and reduces the frequency of maintenance.

Brief Description of the Drawings

In the drawings below, an additional detailed explanation of the embodiments is given.

FIG. 1 is a gasket design with lubricating grooves placed on its surface according to a scheme according to a first embodiment of the invention;

FIG. 2 is a gasket design with lubricating grooves placed on its surface according to a scheme according to a second embodiment of the invention;

FIG. 3 is a cross-section of a lubricating groove of a gasket according to the first and second embodiments of the invention;

FIG. 4 is a schematic illustration of a gasket according to the first and second embodiments of the invention;

FIG. 5 is a sectional view of a drive mechanism of a fuel pump of an engine according to a third embodiment of the invention;

FIG. 6 is a gasket view from the side indicated by the direction R in FIG. 5, according to a third embodiment;

FIG. 7 is a sectional view of the gasket along line BB of FIG. 6;

FIG. 8 is a front view of a gasket according to a fourth embodiment of the invention;

FIG. 9 is a section along line CC of FIG. 8;

FIG. 10 is a schematic diagram of an engine operating principle using a gasket according to a fourth embodiment of the invention;

FIG. 11 is a front view of a gasket according to a fifth embodiment of the invention; and

FIG. 12 is a schematic diagram of an engine operating principle using a gasket according to a fifth embodiment of the invention.

Detailed Description of Embodiments

The following is a detailed description of embodiments of the invention. Illustrations of embodiments are shown in the drawings, in which the same or similar positions correspond to the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the drawings are exemplary and are not intended to limit the invention, but to explain it.

In the present description it is necessary to understand that the directions and indications of position indicated by the concepts of center, length, width, thickness, up, down, front, rear, left, right, vertical, horizontal, top, bottom, inner, outer, clockwise, counterclockwise, etc., are based on the directions and indications of the position shown in the drawings, and are provided solely to facilitate understanding, and not to indicate or imply that the corresponding device or its elements should have a certain direction, as well as be placed and operated in certain directions. Thus, they should not be construed as limiting the invention.

In addition, the concepts of the first and second are given solely for understanding, and not for indicating or implying the relative importance or indirect indication of the numbers of a designated technical feature. In the present description, the term set means two or more than two, unless explicitly defined otherwise.

In embodiments of the invention, unless expressly defined and otherwise established, the concepts of installation, connection, communication, mounting, etc. should be understood in a broad sense. So, we can talk about a fixed connection, detachable connection or one-piece connection; the connection may be mechanical or electrical; the connection may be direct or indirect through an intermediate medium; there may also be a connection of the inner sides of the two elements. Specialists in the relevant field understand the specific meanings of the above concepts, which are used in the description examples depending on specific situations.

Example 1

As shown in FIG. 2-4, the gasket is pressed firmly against the shaft 107 of the intermediate gear 106 by a fixing bolt. A certain axial clearance is provided between the intermediate gear 106 and the gasket 105 to ensure the normal rotation of the intermediate gear 106. The gasket 105 is an annular solid piece 101 with an outer circumference of 38.5 mm, an inner circumference of 12 mm and a thickness of 2.5 mm. Intermediate gear gasket specifications may vary as required; while constructive solutions in embodiments of the invention remain unchanged. The surface of the gasket in contact with the intermediate gear is a plane with a lubricating groove 104 made on it, while the surface of the gasket opposite to it, remote from the intermediate gear, is flat. The central axis of the lubrication groove 104 is a curved line 103. In this embodiment, the selected gasket material is known from the prior art, but the choice of material does not affect the technical solution in the proposed embodiments of the invention. The central axis of the lubrication groove can be any type of curved line: the curved design of the lubrication groove has a positive effect on the preservation of the lubricating oil. There may be at least two lubrication grooves, preferably three or four, and these three or four lubrication grooves are evenly located on the gasket plane. With the curved shape of the lubricating groove, the lubricating oil in it experiences resistance from the lubricating groove side, which is in a non-linear relationship with the radially directed centrifugal force acting on the intermediate gear. In this case, the resistance and centrifugal force form the total force, the direction of which is an acute angle with the direction of rotation of the intermediate gear. Thus, the outward release of lubricating oil is excluded, which affects the lubricating effect. Preferably, both surfaces of the gasket are provided with lubrication grooves. The lubricating groove on the surface of the gasket remote from the intermediate gear has the same shape as the lubricating groove on the surface in contact with the intermediate gear, or a shape different from it. The expression “same” refers to the case where the lubrication grooves on the two surfaces of the gasket have an identical shape; and the expression “other than ...” implies that if the shape of the lubrication groove on either of the two surfaces of the gasket is curved, then the shape of the lubrication groove on the other surface of the gasket may be straight. Obviously, the lubrication grooves on different surfaces can have different shapes from each other.

The lubricating grooves on the annular surface of the gasket are evenly spaced, while the lubricating grooves on the surface of the gasket remote from the intermediate gear are arranged in alternating order with respect to the location of the lubricating grooves on the surface in contact with the intermediate gear. Preferably, each lubrication groove is a through lubrication groove, both ends of which extend to the outer circumference of the gasket.

The cross-sectional shape of the lubrication groove is an isosceles trapezoid with no upper base, the internal angle between two lines extending the sides of the isosceles trapezoid is from 30 ° to 90 °, preferably from 30 ° to 60 °, and at the intersection of two inclined the planes of the sides of the lubricating groove with the plane of its base, pairing is performed along an arc of a circle. Radial mating reduces friction between the intermediate gear and the gasket, and also reduces the release of lubricating oil to the contacting surfaces.

Example 2

As shown in FIG. 1, 3 and 4, the gasket is pressed firmly against the shaft 107 of the intermediate gear 106 by a fixing bolt. A certain axial clearance is provided between the intermediate gear 106 and the gasket 105 to ensure the normal rotation of the intermediate gear 106. The gasket 105 is an annular one-piece piece 101 whose surface remote from the intermediate gear is flat and the surface in contact with the intermediate gear is a plane with a lubrication groove 104 made thereon. In the embodiment under consideration, the selected gasket material is known in the art, but the choice of material is not It affects the technical solution in the embodiments of the invention. The central axis of the lubricating groove 104 is a straight line 102. The acute angle between the central axis of the lubricating groove and the radius of the annular gasket is greater than zero, but not equal to zero. There are at least two lubrication grooves, preferably three or four, arranged uniformly on the gasket plane. The lubricating grooves on the annular surface of the gasket are evenly spaced, while the lubricating grooves on the surface of the gasket remote from the intermediate gear are arranged in alternating order with respect to the location of the lubricating grooves on the surface in contact with the intermediate gear. Preferably, each lubrication groove is a through lubrication groove, both ends of which extend to the outer circumference of the gasket. The cross-sectional shape of the lubrication groove is an isosceles trapezoid with no upper base, the internal angle between two lines extending the sides of the isosceles trapezoid is from 30 ° to 90 °, preferably from 30 ° to 60 °, and at the intersection of two inclined the planes of the sides of the lubrication groove with the plane of its base, mating is provided along an arc of a circle. Radius mating reduces friction between the intermediate gear and the gasket, and also reduces the release of lubricating oil to the contacting surfaces.

Example 3

In FIG. 5 illustrates, by way of illustration, a fuel pump drive mechanism in an engine camshaft drive circuit. The gasket 2100 is used in the mechanism. Of course, it will be understood by those skilled in the art that the gasket 2100 can also be used in other distribution circuits, such as a motor drive mechanism, or in a place having a shaft and gear in the engine or other places in the car. Through gear 2500, the drive force from the crankshaft is transmitted to the drive axis 2200, which rotates in the hole of the flange 2400, which is fixedly mounted on the cylinder block 2300. A gasket 2100 is put on the shaft 2200 and is located between the gear 2500 and the flange 2400. An oil channel 2410 is provided on the flange 2400 to supply oil to the annular lubricating groove 2210 on the shaft 2200, which acts as an oil channel through which oil is supplied to the gasket.

As shown in FIG. 6, the gasket 2100 has an annular shape with an inner circumference 2110 and an outer circumference 2120. The inner circumference 2110 is for putting the gasket 2100 on the shaft. On the surface where the gasket 2100 and gear 2500 are in contact with each other and friction is created, a spiral groove 2130 is provided. The first end 2131 of the lubricating groove 2130 extends to the inner circumference 2110, and the second end 2132 extends to the outer circumference 2120 of the gasket. The lubricating groove 2130 crosses the line BB or reaches this line, the outer diameter of the gasket 2100 being at least twice the distance from the first end 2131 to the second end 2132 of the lubricating channel, i.e. the lubricating groove 2130 makes at least one revolution around the inner circumference 2110 of the gasket.

Assume that the gear 2500 rotates at this time clockwise in the direction corresponding to the direction of the spiral of the lubricating groove 2130 from its first end 2131 to the second end 2132. At this time, the oil in the lubricating groove 2130 tends to make a circular motion in the direction of rotation of the adjacent part due to friction of the adjacent part, inertia and viscosity of the oil. Thus, centrifugal and tangential forces acting on the oil are created. Since the lubricating groove 2130 is in the form of a flat spiral, at any point on the wall of the lubricating groove 2130, the centrifugal force is mainly compensated by the oppositely directed force created by the wall at the corresponding point and acting tangentially, i.e. in the direction indicated by the dotted arrow in FIG. 6. In this direction, the width W of the lubricating groove 2130 gradually increases, the contacting surfaces of the lubricating groove 2130 and the gears 2500 together form a water chamber, the action of which is similar to a spiral water pump, and the friction surface of the gear 2500 acts like an impeller, “pumping” the oil uniformly that the gasket 2100 is located in the circulating lubrication system of the machine and is lubricated continuously. When the 2500 gear is intermediate and used in conjunction with a roller bearing, it is inconvenient to lubricate the roller, but the oil pumped from the 2100 gasket provides continuous lubrication, after which it enters the oil sump to participate in the next circulation lubrication cycle, which is an advantage. A gradual increase in the width of the lubrication groove 2130 may be stepped or smooth. Gasket 2100 can be made by stamping, milling, etc. From the point of view of production efficiency, it is advantageous for the gasket to be produced by a single stamping method with a gradually increasing width.

In FIG. 7 shows a change in the depth of the lubrication groove 2130 in the direction of oil flow. Depth H1 is greatest at the second end — exit 2132, and depth H3 is smallest at the first end — exit 2131, depth H2 between the first end 2131 and second end 2132 is intermediate between H1 and H3; however, the change in depth occurs similarly to the change in width, that is, gradually, and can be stepwise or smooth, in the preferred case, the change is gradual and smooth. Changes in depth and width produce the same positive effect, so there is no need to re-describe it here.

Example 4

As shown in FIG. 8, the gasket 3100 has an annular shape with an inner circumference 3110 and an outer circumference 3120. Friction can occur between the surface of the gasket and an adjacent part tightly in contact with the gasket 3100 and rotating relative to the gasket 3100. On the surface of the gasket 3100, which is in contact with such a part and which is subjected to friction, a lubricating groove 3130 in the form of a spiral is provided. The first end 3131 of the lubricating groove 3130 is closed, and the second end 3132 has an exit to the outer circumference 3120. The lubricating groove 3130 crosses the line CC or reaches this line (along the line CC shows the cross section in Fig. 9), while the outer diameter of the gasket 3100 is at least twice the distance from the first end 3131 of the lubrication groove to its second end 3132, i.e. the lubricating groove 3130 makes at least one revolution around the inner circumference 3110. Due to the fact that the lubricating groove 3130 makes at least one revolution around the inner circumference 3110, the surface of the gasket 3110 is lubricated over the entire circumference. Assume that the adjacent part that experiences friction against the gasket rotates clockwise, the engine oil enters the lubrication groove through the outlet on the outer circumference of the gasket 3120, after the start of the equipment starts, the neighboring part rotates faster, while the oil in the lubrication groove 3130 tends to make a circular movement in the direction of rotation of the adjacent part due to friction, inertia and viscosity of the oil itself. Thus, centrifugal and tangential forces acting on the oil from the center of the inner circle 3110 are created. Since the lubricating groove 3130 has the shape of a spiral, at any point on the wall of the lubricating groove 3130 a large part of the centrifugal force is compensated by the opposing force created at the corresponding wall point, which is tangential, i.e. in the direction of the dashed arrow in FIG. 8, i.e. in the direction from the second end 3132 to the first end 3131. In this direction, the width W of the lubricating groove 3130 decreases gradually, after adding lubricating oil and starting the equipment while rotating the shaft with the rubbing part against the gasket, the oil flow rate increases with increasing distance from the oil inlet channel and the static oil pressure is reduced, which ensures quick spreading of oil over the entire surface of the gasket and facilitates the retention of oil on the gasket. From the above description it is clear that the principle of operation of the lubricating groove 3130 in the form of a spiral gasket 3100 is directly opposite to the principle of operation of a spiral water pump. The principle of operation of the spiral water pump is to pump water out of the water pump uniformly and with high static pressure, while the principle of operation of the spiral-shaped lubricating groove 3130 is to force the oil to move forward uniformly along the oil channel 3130 , spreading and reducing the statistical pressure, while the adjacent part of the gasket 3100 can be considered as the impeller of the water pump. A gradual decrease in the width of the lubrication groove 3130 may be stepped or smooth. Gasket 3100 can be made by stamping, milling, etc. From the point of view of production efficiency, it is recommended that the gasket is made by a single stamping method, with a gradual reduction in width. Since the first end 3131 of the gasket 3100 is closed, reaching the first end 3131, the oil cannot move further to flow out of the lubrication groove 3130, which is an advantage when adding oil from the outside.

In FIG. 9 shows a change in the depth of the lubrication groove 3130 in the direction of oil flow. Depth H1 is the greatest depth located at the second exit end 3132, and depth H3 is the smallest depth at the first exit end 3131, depth H2 between the first end 3131 and the second end 3132 is intermediate between H1 and H3; the change in depth is similar to the change in width, that is, the change in depth occurs gradually and can be stepwise or smooth; gradual, gradual change is preferred. Changes in depth and width produce the same positive effect, so there is no need to re-describe it here.

In FIG. 10 shows an engine that uses gasket 3100, where its interaction with the distribution gear is shown as an example. Gear 3500 is a distribution gear such as a fuel pump gear, a water pump gear, a generator gear, and the like. in the distribution mechanism system. The gear 3500 is driven by the crankshaft through a camshaft drive chain (not shown) and transmits torque to the 3200 shaft for rotation in the bore of the 3400 flange. The 3400 flange is fixed to the 3300 cylinder block. The 3100 gasket is worn on the 3200 shaft and is located between the gear 3500 and flange 3400. The distribution gear 3500 rotates clockwise when viewed in the R direction, respectively, it is a part that experiences friction against the gasket 3100, and the direction of rotation of the distribution gear is opposite to board spiral from the first end 3131 to the second end 3132 of the lubricating groove 3130 gaskets. With a camshaft drive circuit, a fuel injector (not shown) is typically used to supply engine oil to it. Since the outlet of the lubrication groove of the gasket 3100 is located at the outer circumference 3120, engine oil from the fuel nozzle flows into the lubrication groove 3130 from the side of the second exit end 3132 by gravity or moves along the channel for the lubricating oil.

It will be understood by those skilled in the art that the gasket 3100 according to this embodiment of the invention can also be used elsewhere in the engine or in another location, such as a shaft of a wheel or other mechanical device. If both surfaces of the gasket 3100 are equipped with lubricating grooves 3130, this eliminates the incorrect (reverse) installation of the gasket 3100 if the directions of the spirals of the lubricating grooves on both surfaces are the same (for example, a left-side or right-hand spiral is provided on both surfaces); if the directions of the spirals of the lubricating grooves on different surfaces are opposite, the gasket 3100 has great versatility, since it is possible to choose the contacting friction surface of the gasket 3100 about the neighboring part in accordance with the relative direction of rotation of the neighboring part (for example, clockwise or counterclockwise). Thus, it is preferable to have lubrication grooves on both surfaces of the gasket.

Example 5

As shown in FIG. 11, the gasket 4100 has an annular shape with an inner circumference 4110 and an outer circumference 4120. An adjacent part adjacent to the gasket 4100 rotates relative to the gasket 4100, while experiencing friction against the surface of the gasket 4100. On the surface of the gasket 4100, which is in contact with an adjacent part and which experiences friction, a spiral groove 4130 is provided. The first end 4131 of the lubrication groove 4130 has an outlet at the inner circumference 4110, and the second end 4132 is closed near the outer circumference 4120. The lubrication groove 4130 makes at least one revolution around the inner circumference 4110. The purpose of the output of the lubricating groove 4130 is to supply lubricating oil to the gasket 4100. The fact that the lubricating groove 4130 makes at least one revolution around the inner circumference 4110 provides lubrication of the surface of the gasket 4110 around the entire circumference. Assume that an adjacent part that experiences friction against the gasket 4100 rotates counterclockwise and the oil passes from the first end 4131 of the lubricating groove, the oil in the lubricating groove 4130 tends to make a circular motion in the direction of rotation of the neighboring part due to friction, inertia and viscosity of the oil itself . Thus, centrifugal and tangential forces act on the oil. Since the lubricating groove 4130 is in the form of a flat spiral, at any point on the wall of the lubricating groove 4130, the centrifugal force is mainly compensated by the opposing force created by the wall at the corresponding point, and the oil can only move tangentially, i.e. in the direction shown by the dotted arrow in FIG. 11, i.e. in the direction from the first end 4131 to the second end 4132. In the preferred case, the width of the lubrication groove 4130 gradually decreases in the above direction, after the lubricating oil is added under the action of a part experiencing friction against the gasket, when the equipment is started and the shaft rotates as it moves away from the channel for oil inlet, the oil flow rate increases, and the static oil pressure decreases. From the above description, it is understood that the principle of operation of the lubricating groove 4130 of the gasket 4100, which is in the form of a flat spiral, is directly opposite to the principle of operation of a spiral water pump. The principle of operation of a spiral water pump is to pump water out of the water pump uniformly and with high static pressure, while the principle of operation of a lubricating groove 4130, having the shape of a flat spiral, is to force the oil to move forward uniformly along the oil channel 4130, spreading and gradually reducing static pressure, where the adjacent part of the gasket 4100 can be considered as the impeller of the water pump. A gradual decrease in the width of the lubrication groove 4130 may be stepped or smooth. Gasket 4100 can be made by stamping, milling, etc. From the point of view of production efficiency, it is recommended that the gasket is made by a single stamping method with a gradual reduction in width. In addition, those skilled in the art can expect that the depth of the lubrication groove 4130 may decrease gradually in the direction from the first end 4131 to the second end 4132. The gradual decrease can be stepped or smooth and, in the preferred case, is gradual and smooth. Changes in depth and width produce the same positive effect, so there is no need to re-describe it here.

In FIG. 12 shows an engine that uses gasket 4100, where, as an example, a system interacting with a distribution gear is shown. Gear 4500 is a gear that is driven by the drive shaft 4200, rotating in the bore of the axis of the flange 4400. The flange 4400 is fixedly mounted on the cylinder block 4300. The gasket 4100 is worn on the shaft 4200, located between the gear 4500 and the flange 4400 and provides oil supply to the first end 4132 from the bore of the axis (not shown) of the shaft 4200. Suppose that the drive gear 4500 rotates counterclockwise when viewed in the R direction and is a part that experiences friction against the gasket 4100. The friction surface of the drive gear is 4500 and cm dressing groove 4130 to form a structure which is analogous to the action of the spiral water pump. However, the principle of operation of this design is the opposite of the principle of operation of a spiral water pump, since changes in the width and depth of the lubrication groove 4130 are directly opposite to the corresponding changes in the water chamber of the spiral water pump. The 4100 gasket has greater durability compared to other forms of gasket lubrication grooves used in the prior art.

It will be understood by those skilled in the art that the gasket 4100 according to this embodiment of the invention can also be used elsewhere in the engine or in another location, such as a shaft of a wheel or other mechanical device. In addition, any combination of changes in the width and depth and direction of the spiral, for example, a left-handed spiral and a right-handed spiral, can be used in accordance with the direction of rotation of an adjacent part of the gasket 4100. If both surfaces of the gasket 4100 are provided with lubricating grooves 4130, this eliminates the wrong (reverse) installation of a gasket 4100 if the directions of the spirals of the lubricating grooves on both surfaces are the same (for example, a left-side or right-side spiral is provided on both surfaces); if the directions of the spirals of the lubricating grooves on different surfaces are opposite, the gasket 4100 is more versatile, since it is possible to choose the contacting friction surface of the gasket 4100 about the neighboring part in accordance with the relative direction of rotation of the neighboring part (for example, clockwise or counterclockwise). Thus, it is preferable to have lubrication grooves on both surfaces of the gasket.

It will be apparent to those skilled in the art that all gaskets shown in Examples 1-5 of this application can be used in an engine or automobile, or in another mechanical device.

Some exemplary embodiments of the invention have been described above, given for illustrative purposes only. Of course, specialists in the relevant field can make changes to the described embodiments in different ways without departing from the essence and scope of the invention. Thus, the drawings and description in question are mainly demonstrative in nature and should not be interpreted as limiting the scope of protection of the present invention.

Claims (34)

1. A gasket, characterized in that it is an integral part of a circular annular shape, at least one surface of which is provided with a lubricating groove in the form of a flat spiral, which makes at least one revolution around the inner circumference of the gasket. 2. The gasket according to claim 1, characterized in that it contains at least two lubrication grooves. 3. The gasket according to claim 1, characterized in that both surfaces of the gasket are provided with lubricating grooves that are located on different surfaces of the gasket. 4. The gasket according to claim 1, characterized in that both surfaces of the gasket are provided with lubricating grooves, the shapes of which are identical or different on different surfaces. 5. The gasket according to any one of paragraphs. 3 or 4, characterized in that the number of lubrication grooves on different surfaces of the gasket is the same or different. 6. Gasket according to claim 1, characterized in that the lubricating groove is a through lubricating groove with two open ends facing the outer circumference of the gasket. 7. Gasket according to any one of paragraphs. 1-4, characterized in that the cross-sectional shape of the lubricating groove is an isosceles trapezoid with a missing upper base. 8. The gasket according to claim 7, characterized in that the internal angle between two lines extending the sides of the isosceles trapezoid is from 30 ° to 90 °. 9. The gasket according to claim 7, characterized in that at the intersection of two inclined planes of the sides of the lubricating groove with the plane of its base, mating is performed along an arc of a circle. 10. Gasket according to any one of paragraphs. 1-4, characterized in that the lubricating groove has exits on the inner and outer circumferences of the gasket. 11. The gasket according to claim 10, characterized in that the width of the lubricating groove increases gradually in the direction from the exit to the inner circumference. 12. The gasket according to claim 11, characterized in that the width of the lubricating groove increases gradually and smoothly. 13. Gasket according to claim 10, characterized in that the depth of the lubricating groove increases gradually in the direction from the exit to the inner circle. 14. The gasket according to claim 13, characterized in that the depth of the lubricating groove increases gradually and smoothly. 15. Gasket according to any one of paragraphs. 1-4, characterized in that one end of the lubricating groove extends to the outer or inner circumference of the gasket, and the other end is closed. 16. The gasket according to claim 15, characterized in that the width of the lubricating groove decreases gradually in the direction from the exit to the inner circumference. 17. Gasket according to claim 16, characterized in that the width of the lubricating groove decreases gradually and smoothly. 18. Gasket according to claim 15, characterized in that the depth of the lubrication groove decreases gradually from the open end to the closed. 19. The gasket according to claim 18, characterized in that the depth of the lubrication groove decreases gradually and smoothly. 20. The gasket according to claim 1, characterized in that it is made by a single stamping method. 21. The engine, characterized in that it consists of: distribution gear; camshaft drive circuit; fuel burner; gasket according to any one of paragraphs. 1-20; where the camshaft drive chain drives the distribution gear, which is in contact with the gasket and rotates relative to the gasket in the direction opposite to the direction of the spiral lubrication grooves of the gasket, and the fuel injector provides oil to the camshaft drive chain and gasket at the same time. 22. The engine according to claim 21, characterized in that a helical gear is used as a gear. 23. The engine, characterized in that it consists of: gear; gasket according to any one of paragraphs. 1-20; and a shaft with a channel for supplying oil to the outlet of the lubricating groove made in the form of a spiral located at the inner circumference of the gasket, while the gear rotates in the direction corresponding to the direction of the gasket spiral. 24. The engine according to p. 23, characterized in that the helical gear is used as a gear. 25. The engine, characterized in that it contains a gasket according to any one of paragraphs. 1-20 mounted on its spindle. 26. A car, characterized in that it contains a gasket according to any one of paragraphs. 1-20.

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