RU2255227C2 - Positive displacement machine (versions) - Google Patents

Abstract

FIELD: mechanical engineering.

SUBSTANCE: novelty in proposed device is design of drive, main member of diametrically installed rollers, each getting into concentric bore of one of semicylinders-displacers. Axles of one pair of rollers move towards axles of other pair of rollers, thus making system of semicylinders-displacers execute rocking motions forcing out medium from four spaces outside semicylinders-displacers and one space inside semicylinder-displacers. According to one design version, both pairs of rollers move to each other on their shafts relative to fixed cylinder, and according to other design version, axle of one of pairs of rollers are fixed, and other pair of rollers and cylinder rotate.

EFFECT: provision of compact design, reliability and long service life.

5 cl, 5 dwg

Description

The invention relates to mechanical engineering and for the improvement of volumetric machines.

A large number of volumetric machines are known for transferring energy between a continuous medium and a shaft, used as compressors, internal combustion engines (ICE), and pumps.

The most common of them are reciprocating compressors (M.I. Frenkel “Piston compressors.” - L .: Mashinostroenie, 1969, p. 106) and ICE. Piston ICEs, unlike compressors, are not self-acting, but controlled valves with their drive system (camshaft).

The disadvantages of piston machines include: the lack of compactness and inertial imbalance due to both the crank mechanism and the peak nature of the piston forces, as with a sharp change in pressure, the piston area remains constant. Hence the need for a flywheel. High sliding friction and wear in the sealing elements (piston rings). All this reduces the reliability and durability of structures. Valves and their actuators are also an element of unreliability.

More compact and balanced designs are rotary (rotational) volumetric machines of various types, for example screw (I.A. Sakun “Screw Compressors”. L .: Mashinostroenie, 1970, p. 8), or “trochoid” - Wankel engines (V.S. Beniovich and others. “Rotary piston engines. - M.: Mechanical Engineering, 1968, p. 8), compressors (R.M. Sukhomlinov“ Trochoidal rotary compressors ”, Kharkov:“ Visha school ”, 1975, p. 20, 34, 36, 37). But even in these machines there is either significant sliding friction of the sealing elements (trochoid machines), or if the seal is non-contact (small gaps), the gaps are difficult to keep small due to the complex shape of the surfaces (screw compressors). This limits the working pressure relationship, reduces efficiency, complicates the technology. The compactness of these machines, characterized by the ratio of the volume displaced per cycle to the volume of the working chamber without a displacer (piston, rotor), is always much less than unity, which reduces compactness.

Known volumetric machines with oscillating displacers (US 1558106 A2, 11/30/1991 and RU 2052159 C1, 01/10/1996), in the cylindrical working chamber of which four identical half-displacer displaced are connected pivotally. Displacement half-cylinders have an outer diameter equal to half the diameter of the cylinder bore, along which they roll (swing) without sliding. The design is geometrically based on the Copernican theorem (a special case of a hypocycloid) (G. N. Berman “Cycloid.” M .: Nauka, 1980, p. 61, Fig. 65).

Patent RU 2052159 C1 is the closest analogue of the proposed device. The advantages of this design over the well-known are dynamic balance, both inertial and due to the reduction in the area of pressure under compression, high technology, because the main working bodies - cylinders, very high compactness - more than one volume of the working chamber can be forced out per cycle.

In the case of internal combustion engines, for example, it is possible to carry out a four-cycle cycle in one cylinder, using the central volume for pumping a cooling medium or lubricant, or as a gas spring that receives inertial forces.

The disadvantages of such designs are: the need for a crank mechanism, which reduces compactness and dynamic balance, as well as the need for a mechanism that prevents the rotation of the displacer system relative to the housing (slide or gear). The displacers and the joints connecting them are loaded with forces commensurate with the piston, which reduces reliability and durability. The main force is transmitted through the slider with a lot of friction and wear, a lot of fluid lubrication is required, which reduces reliability and durability. The drive mechanism through the slider introduces a non-uniformity in time of compression periods in two pairs of compressible volumes located at an angle of 90 ^° , which worsens the dynamic balance.

The problems solved by the invention are the achievement of compactness, dynamic balance, reliability, durability compared with the closest analogue (RU 2052159 C1).

The volumetric machine is claimed in two versions, united by purpose and general design concept.

In the first embodiment, the problem is solved in a volumetric machine containing a stationary body with end caps and a cylindrical bore, in which four identical half-cylinders-displacers are mounted, pivotally connected to each other and diametrically located carrier links mounted for rotation relative to the central axis of the body bore, as well as valves, according to the invention, in each half-displacer a concentric bore is made in which the roller is placed, the axes of each of the two pairs being opposite GOVERNMENTAL clips secured to ends of the link-carrier mounted on a shaft coaxial with the cylindrical bore of the housing, and these shafts are interconnected kinematically, e.g., gear transmission with a transmission ratio equal to one.

The technical result achieved by this solution is to increase dynamic balance, reduce the load on the hinges, reduce friction and wear of the drive mechanism and the need for plentiful fluid lubrication.

In addition, in a volumetric machine, at least one of the two shafts can be installed distribution disk in contact with the valves. This achieves the simplicity of the design of the distribution mechanism.

In the second embodiment, the problem is solved in a volumetric machine containing a stationary body, a cylinder and end caps, and in the internal bore of the cylinder there are four identical half-cylinders-displacers interconnected pivotally and diametrically located carrier links, one of which is mounted with the possibility of rotation relative to according to the invention, a concentric bore is made in each half-cylinder of the displacer, in which the roller is placed, the axes of one pair being diametrically the located rollers are mounted on the ends of the carrier link mounted on a drive shaft coaxial with the cylinder bore, the axes of the other pair of rollers are mounted on the ends of the carrier link mounted on a fixed end cap, and the cylinder with the other end cap is mounted on another shaft, also coaxial with cylinder bore.

In addition, in a volumetric machine, openings for the entry and exit of the medium can be made on the fixed end cover.

In addition, in a volumetric machine, the drive shaft and the cylinder shaft can be interconnected kinematically by a reduction gear, for example a gear, with a gear ratio of two.

The technical result achieved by such a solution, in addition to the specified technical result of the first embodiment of the device, also consists in the fact that it allows to exclude the valve mechanism, limiting the reliability and durability of volumetric machines.

The invention is illustrated by drawings:

Figure 1 shows a longitudinal section of the first variant of the device.

Figure 2 shows a cross section of a first embodiment of the device.

Figure 3 shows a longitudinal section of a second variant of the device.

Figure 4 shows a cross section of a second variant of the device.

Figure 5 shows the end view at the time of transition of the rollers in the adjacent half-cylinders-displacers ("top dead center").

The volumetric machine according to the first embodiment of the proposed device (Figs. 1, 2) consists of a housing 1 with a cylindrical bore, two covers 2 and 3, two diametrically located carrier links 4 and 5. Inside the housing bore four four displacer 6 cylinders with an outer diameter are placed equal to half the diameter of the bore of the housing 1. The half-displacers 6 are in contact with the cylindrical surface with the bore of the housing 1 and are connected to each other by hinges 7. These lines are the axis of the hinge irov 7.

A concentric bore is made in each of the half-cylinders-displacers 6, in which the roller is placed 8. The axes of each pair of diametrically located rollers 8 are fixed at the ends of one of the carrier links 4 or 5. Each of the carrier links 4 and 5 is mounted on a shaft 9 or 10 coaxial with the bore of the housing 1. Both shafts are connected to each other by gear 11 with a gear ratio equal to one, with the rotation of the shafts 9 and 10 in opposite directions.

On the shafts 9 or 10, a distribution disk 12 can be installed that contacts its protrusions with the valve stems 13 if the valves are not self-acting.

The volumetric machine according to the second embodiment of the proposed device (Figs. 3 and 4) has a cylinder 14 placed in the housing 1 with the possibility of rotation around the axis of its bore. The cover 2 is fixedly connected to the housing 1, and the cover 3 is connected to the cylinder 14. The carrier 4, as in the first embodiment, is located diametrically inside the cylinder 14 on the shaft 9 coaxial with it. The carrier 5 is fixedly mounted on the cover 2 (housing 1 ) and is also located diametrically inside the bore of the cylinder 14.

The half-cylinders-displacers 6 are located inside the cylinder 14, in contact with its bore, and are also interconnected by hinges 7. Just like in the first version of the device, the rollers are located 8. The axes of one pair of rollers 8 are fixed at the ends of the carrier 4, and the axes of the second pair of rollers 8 are fixed at the ends of the fixed carrier link 5. The carrier link 4 is mounted on the drive shaft 9, coaxial with the axis of the bore of the cylinder 14, and the cylinder 14 with the cover 3 are mounted on its shaft 10, also coaxial with the axis of the cylinder 14 . Half-displacer 6 have a side s two flat half-disk cover 15 and the cover 2 are located 16 and discharge holes 17 for suction.

The shaft 9 can be connected with the shaft 10 by a gear gear 18 lowering with respect to the shaft 9, with a gear ratio of two.

In the bores of the housing 1 or cylinder 14, recesses 19 can be made (FIGS. 2 and 4), where the hinges 7 are placed in the extreme positions. This increases the angle of rotation of the half-displacer 6 and productivity.

When the drive shaft 9 is rotated (FIGS. 1, 2), the shaft 10 is rotated in the opposite direction with the same rotation speed using the gear 11. In this case, the carrier links 4 and 5, each with its own pair of rollers 8, rotate counter-along with its shafts. Each roller 8 causes the half-displacer 6, with which it is currently in contact, to rotate around their common axis, rolling without sliding along the bore of the housing 1.

If a pair of neighboring displacers, connected by a common hinge 7, rotates counterclockwise, then the axis of the hinge 7 moves along the diameter of the bore of the housing 1 to its surface.

In the extreme position of the hinge 7 (Figure 5), when it is as close as possible to the bore of the housing 1 (“top dead center”), the rollers 8 “change places”, i.e. half-displacer 6, forcing them to roll in the opposite direction, and their common hinge 7 to move in the opposite direction along the same diameter.

When the hinge 7 moves towards the surface of the bore, the volume closed between adjacent half-cylinders-displacers 6 and the bore decreases (theoretically to 0), and when it moves backwards, it increases (theoretically to a quarter of the volume of the cylinder).

The synchronization transmission 11 transmits half the total power moment.

With controlled valves 13 (ICE), the distribution disk 12 with the necessary protrusions (similar to the camshaft cams) can be mounted directly on the shafts 9 or 10, because the angular position of the shafts is synchronized with the phases of compression-suction in the working cavities.

In the second embodiment of the device, when the drive shaft 9 is rotated (FIGS. 3 and 4), the carrier link 4 with its pair of rollers 8 rotates with respect to the stationary carrier carrier 5 with its pair of rollers 8. The same as in the first embodiment devices, pairs of rollers 8 alternately converge and diverge with respect to each other, forcing half-displacers 6 to roll without sliding along the internal bore of cylinder 14, making oscillating movements.

Unlike the first option, the system of half-displacers 6, connected by hinges 7, rotates in the same direction as the shaft 9, but with half the frequency. In this case, the half-cylinders-displacers 6 carry along the cylinder 14, freely rotating on its supports, because except for an insignificant moment of friction in them, there is no other moment braking the cylinder.

If we imagine the whole picture in relative motion with respect to the system of half-displacers 6 and cylinder 14, we get an analogy with the work of the first option.

Each position of the carrier unit 4 (shaft 9) with respect to the stationary carrier unit 5 (housing 1 and cover 2) corresponds to a certain angular position of the system of half-displacers 6 and their relative position, i.e. a certain phase of compression-absorption of the medium in the working cavities, which makes it possible to realize valveless, spool distribution, i.e. on the surface of the cover 2 to arrange a pair of discharge 16 and suction 17 holes, periodically opened and closed by the surfaces of the half-disks 15 of the half-displacers 6.

For guaranteed coincidence of the rotation of the cylinder 14 with the system of half-cylinders-displacers, you can apply a reduction gear 18, for example a gear, from the shaft 9 to the shaft 10 of the cylinder 14 with a gear ratio of 2.

Unlike transmission 11, this transmission is not power transmission, but performs only the synchronization function and is not a mandatory structural element.

In both versions, the only elements that perform periodic (“swinging”) movement is a system of half-displacers 6, while the shafts and rollers 8 move at constant angular speeds each in one direction and therefore can be mounted on rolling bearings.

The rollers 8 in their oncoming movement set the system of half-displacers 6 a certain relative position and therefore, unlike analogues, there is no need for synchronizing sliders or gear sectors.

The main force effect from the pressure of the medium is transmitted directly from the half displacers 6 to the rollers 8, bypassing the hinges 7, which only synchronize the relative position of the half displacers, i.e. the latter can be lighter, reducing inertial forces, and the hinges 7 are more durable.

Theoretically, each half-displacer can rotate 90 °. In practice, this angle is smaller, because carrier links 4 and 5 and hinges 7 limit full rotation (Figure 5). Therefore, the end sections of the inner bores of the half-displacers 6 can be made along some curves along which the rollers 8 will roll without sliding at the “top dead points”, for example, along the arcs of circles concentric with the bore of the housing 1 or cylinder 14. This is also necessary to reduce inertial forces to change the direction of rolling more smoothly.

To limit the rotation of the half-cylinders-propellants in the “top dead center” can be made limiters, for example, in the form of protrusions on the half-cylinders-propellants or on the bore of the cylinder in the area of the recesses 19.

For one revolution of the shaft 9, half-displacers 6 perform two swing cycles and displace (theoretically) 8 quarters of the cylinder volume, i.e. theoretical coefficient of cylinder volume utilization reaches two, which is not achieved in any of the volumetric machines. This is without taking into account the fifth variable volume inside the half-displacer system. This volume changes at a double frequency compared to four others. It can be used for pumping a cooling medium or lubricant, or as a gas buffer for the accumulation and return of kinetic energy of swinging working bodies.

Claims (5)

1. A volumetric machine comprising a stationary body with end caps and a cylindrical bore, in which four identical half-displacer are mounted, pivotally connected to each other and diametrically located carrier links, mounted for rotation relative to the central axis of the body bore, as well as valves, characterized in that a concentric bore is made in each half-displacer in which the roller is placed, the axes of each of two pairs of opposite rollers being fixed to the end x carrier link mounted on a shaft coaxial with the cylindrical bore of the housing, and these shafts are kinematically connected, for example, by gear transmission with a gear ratio equal to one. 2. Volumetric machine according to claim 1, characterized in that at least one of the two shafts has a distribution disk in contact with the valves. 3. A volumetric machine comprising a stationary body, a cylinder and end caps, wherein four identical half-cylinders-displacers are mounted pivotally connected to each other and diametrically located carrier links, one of which is mounted with the possibility of rotation relative to the central axis of the cylinder bore , characterized in that in each half-cylinder displacer a concentric bore is made in which the roller is placed, and the axes of one pair of diametrically located rollers are installed At the ends of the carrier link mounted on the drive shaft, coaxial with the cylinder bore, the axes of the other pair of rollers are mounted on the ends of the carrier link mounted on the fixed end cap, and the cylinder with the other end cap is mounted on the other shaft, also coaxial with the cylinder bore . 4. The volumetric machine according to claim 3, characterized in that the openings for the entry and exit of the medium are made on the fixed end cover. 5. Volumetric machine according to claim 3, characterized in that the drive shaft and the cylinder shaft are interconnected kinematically by a reduction gear, for example a gear, with a gear ratio of two.

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