RU2397327C2 - Sealing system of rotary ice - Google Patents

Abstract

FIELD: engines and pumps.

SUBSTANCE: proposed system comprises radial, face and tangential seals. Radial seals are fitted in grooves of rotor vanes. Tangential seals represent rectangular plates fitted in rotor groove walls on both sides of the vanes. Radial seals represent "П"-like plates spring-loaded towards housing work surface. Each of said plates is coupled with counterweight by bell cranks fitted in pairs relative to feet of "П"-like plates. End of bell cranks share common axles fitted in blocks arranged in counterweight openings and feet of "П"-like plates. Aligned axles of bell cranks are fitted in vanes walls. Face seals represent plates fitted on both sides of the rotor, parallel to its rotational axis, and are furnished with adjustable thrusts.

EFFECT: efficient sealing.

1 cl, 7 dwg

Description

The invention relates to engine building, and in particular to sealing systems of internal combustion engines with rotating working bodies, which can be used in power engineering as a hydraulic motor, pump and internal combustion engine in land, sea and air transport.

A known sealing system of a rotary piston internal combustion engine containing radial, mechanical seals located in the grooves of the housing on both sides of the rotor, and tangential seals (see RU 2239703, C1, IPC 7F01C 19/00, F02B 55/02).

The sealing system according to patent No. 2239703 has sealing protrusions made on sealing strips connected by a sealing element mounted in the grooves of the piston blades, and the contact surface of the sealing protrusions with mechanical seals is made intermittent.

The sealing system described above has the following disadvantages. Radial seals are located in the grooves of the blades and are made in the form of a ring installed in the piston groove, interacting with both the working surface of the housing and the working surface of the slider.

Such a constructive solution of the radial seal does not allow reliable sealing of the working chamber of the engine due to the technical impossibility of simultaneously having constant contact with both the working surface of the housing and the surface of the slider. High precision of execution and dimensional stability of the working surface of the housing and the slider are required during the entire period of operation of the engine. In other words, it is necessary to guarantee the movement of the center of the piston along the contour forming the working surface of the engine, which is impossible, because surface wear occurs. There is a separation from the surface of the slide of the ring and loss of charge. The geometry of the working surface of the engine is difficult to manufacture and requires a piston pivotally connected to the slider, which complicates the design of the engine and the ring installed in the piston groove to ensure contact of the ring with the working surface of the housing.

The structural solution of mechanical seals does not provide a high degree of sealing due to the lack of sufficient length along the seal in the radial direction on the one hand and the linear nature of their interaction with the radial seal ring.

Tangential seals are complex in design and time-consuming to manufacture, as they require their location. There is a likelihood of shock when one of the protrusions meets the mechanical seals as a result of dimensional disruptions during surface wear.

Creating a reliable sealing system with a high degree of sealing is the task to which this invention is directed.

The essence of the invention lies in the fact that in the sealing system of a rotary internal combustion engine containing radial seals located in the grooves of the blades in contact with the working surface of the housing, mechanical and tangential seals, radial seals are made in the form of U-shaped plates spring-loaded to the working surface of the housing each of which is connected to the counterweight by means of two-arm levers, installed in pairs relative to the legs of the U-shaped plates, the ends of which have common axes, is installed in crackers located in the counterweight windows and legs of the U-shaped plates, and the axis of rotation of the two-arm levers are coaxial and installed in the walls of the blades, mechanical seals are made in the form of plates mounted on both sides of the rotor parallel to its rotation plane with adjustable stops, tangential seals - in the form of rectangular plates installed in the walls of the rotor groove on both sides of the blades.

The invention is illustrated by drawings, where in Fig.1 - shows a cross section bb of the engine in Fig.2 and radial seals;

figure 2 is a longitudinal section bB of the engine of figure 1, radial and mechanical seals;

figure 3 - section aa of the engine of figure 1, radial and mechanical seals;

figure 4 - section GG of the engine of figure 3, radial seals;

5 is a view along arrow D in figure 4, radial seals;

6 is a section EE of the engine of figure 2, radial and tangential seals;

Fig.7 is a sectional view of the II motor of Fig.6, tangential seals.

The sealing system of a rotary internal combustion engine contains radial seals 1, mechanical seals 2 and tangential seals 3. Radial seals 1 are made in the form of U-shaped plates 7, spring-loaded to the working surface of the housing 6. Each U-shaped plate 7 is connected to the counterweight 8 through two shoulders levers 9, installed in pairs relative to the legs 10 and 11 of the U-shaped plates 7. The ends of the two-arm levers 9 have common axes 12, mounted in crackers 15 located in the windows 14 of the counterweights 8 and the legs 10 and 11 of the U-shaped x plates 7. The axis of rotation of the two shoulders of the levers 9 are coaxial and mounted on the walls of the 16 blades 4. The mechanical seals 2 are made in the form of plates 17 mounted on both sides of the rotor 18 parallel to the plane of its rotation, located on the shaft 19 in the housing 6 with adjustable stops 20 Mechanical seals 2 are designed to seal the working chambers 21. The tangential seals 3 are made in the form of rectangular plates 22 mounted in the walls 23 of the grooves of the rotor 18 on both sides of the blades 4 and pressed by springs 24.

When the rotor 18 located on the shaft 19 rotates, inertial forces act on the radial seals 1 - on the U-shaped plates 7 and balances 8. The inertia forces acting on the U-shaped plates are transmitted by crackers 13 to the common axes 12. In turn, the inertial forces acting on the counterweights 8 by means of crackers 13 are also transmitted to the common axes 12 of the two-arm levers 9, which rotate relative to the axis 15. The inertia forces acting on the U-shaped plate 7 and the counterweight 8 relative to the axis of rotation of the two-arm lever 9 on the left leg 1 0 act in opposite directions, namely, the inertia forces of the left leg 10 of the U-shaped plate 7 will act clockwise, and the inertia forces of the counterweight 8 - counterclockwise. The inertia forces acting on the U-shaped plate 7 and the counterweight 8 relative to the axis of rotation 15 of the two shoulders of the lever 9 on the right leg 11 will act in opposite directions, namely, the inertia forces of the right leg 11 of the U-shaped plate 7 will act counterclockwise, and the forces counterweight inertia 8 - clockwise.

Thus, the U-shaped plates 7 are balanced by counterweights 8 by means of four two-arm levers 9, arranged in pairs relative to the legs 10 and 11 of the U-shaped plates 7 with the axes 15 of rotation of these levers installed in the walls 16 of the blades 4.

Balance is determined by the formulas:

Fj ₁ = m ₁ ω _ρ ² ρ ₁

Fj ₂ = m ₂ ω _ρ ² ρ ₂ , where

Fj ₁ and Fj ₂ - inertia forces acting respectively on the centers of gravity (CT) of the U-shaped plates 7 and balances 8.

m ₁ and m ₂ - the mass of the U-shaped plates 7 and balances 8.

ω _ρ is the rotor speed.

ρ ₁ and ρ ₂ are the distances from the centers of gravity (CT) of the U-shaped plates 7 and the balances 8 to the axis of rotation of the rotor, respectively.

Equilibrium condition for radial seals

Fj ₁ = fj ₂

If the inertial forces acting on the U-shaped plate 7 and the counterweight 8 are equal, equilibrium is established.

Therefore, the inertial pressing of the U-shaped plate 7 to the working surface 5 of the housing 6 will be zero and will be carried out by an elastic element, such as a spring, with an optimal design force. In this case, the degree of compression of the U-shaped plate 7 will not depend on the speed of the rotor 18, which leads to minimal wear of the radial seals and the working surface 5 of the motor housing 6.

To preserve the charge in the working chambers 21 and to obtain high engine parameters, it is necessary to seal them with mechanical seals 2. When the rotor 18 is rotated, the working chambers 21 are sealed by contacting the planes of the mechanical seals 2 with the surfaces of the rotor 18 and blades 4. Due to the fact that zones 6 with different pressures of the working fluid take place in the engine casing 6, the plates 17 of the mechanical seals 2 are pressed by means of adjustable stops 20, eliminating the distortions of the plates 17, providing sealing Yu.

When the blades 4 rotate, they move in the grooves of the rotor 18 in the radial direction. Between the walls of the blades 4 and the walls 23 of the grooves of the rotor 18, gaps are formed through which there is a leak of charge from the working chambers 21, which causes a loss of charge and a decrease in power and weight and size. In order to eliminate leaks through these gaps in the walls 23 of the grooves of the rotor 18, rectangular grooves through the length of the rotor 18 are made, in which tangential seals 3 are installed in the form of spring-loaded plates 22 installed in the walls 23 of the grooves of the rotor 18 on both sides of the blades 4 and interacting with them the outer surface when moving in the groove of the rotor 18.

The proposed sealing system of the working chambers is a combination of radial, mechanical and tangential seals, which provide effective sealing of the working chambers of the engine.

Radial seals provide constant contact stresses, optimal in magnitude due to balancing.

Mechanical seals ensure constant contact with the mechanical part of the rotor and the blades, eliminating the possible distortion of the adjustable stops.

Tangential seals eliminate charge leakage through the gap in the interface between the blade wall and the wall of the rotor groove.

The effective sealing of the working chambers, provided by the system of three types of seals, leads to an increase in the specific power and weight and size characteristics of the engine.

Claims (1)

The sealing system of a rotary internal combustion engine containing radial, mechanical and tangential seals, with radial seals located in the grooves of the blades, tangential seals made in the form of plates installed in the walls of the groove of the rotor on both sides of the blades, characterized in that the radial seals are made in the form of -shaped plates, spring-loaded to the working surface of the housing, each of which is connected to the counterweight by means of two-arm levers, installed in pairs relative to the legs П-о for each plate, the ends of two shoulders of the levers have common axes installed in crackers located in the windows of the counterweights and legs of the U-shaped plates, and the axis of rotation of the two shoulders of the levers are coaxial and installed in the walls of the blades, mechanical seals are made in the form of plates mounted on both sides of the rotor in parallel its rotation planes with adjustable stops, tangential seals - in the form of rectangular plates.

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