HK1127888A - Vane machine with stationary and rotating cylinder parts - Google Patents

Description

Vane machine with stationary and rotating cylinder parts

1. Field of the invention

The present invention relates to vane machines (vane machines) in which one part of the cylinder is stationary while the other part of the cylinder rotates.

The vane-type device may be a working device (engine) to continuously convert fluid energy into mechanical power, or a driving device (pump) to continuously lift, push, compress, or evacuate fluid from a positive displacement rotary-type device by mechanical power or other methods using compressible or incompressible fluid as a working medium.

In the international patent classification, the present application is classified as part F-mechanical engineering; class F01 general-general machines or engines; subclass F01C-rotary piston or oscillating piston machines or engines; large group 13/00-machines or engines suitable for particular applications; a combination of an engine and its driven device; group 13/02-for driving hand tools or the like and 13/04-for driving pumps or compressors.

2. Technical problem

The biggest problems with positive displacement machines, particularly vane positive displacement machines, are volume and mechanical losses. The volume loss is caused by the insufficient opening of the working medium into and out of the working chamber of the device. Volume losses may also occur due to fluid leaking from the high pressure space of the working chamber to the low pressure space of the working chamber. Mechanical losses are due to friction between the rotating and stationary parts of which the equipment is in contact with each other, which constitute the working chamber.

The consequence of higher volumetric and mechanical losses is that the plant is volumetrically and mechanically inefficient, i.e. the overall efficiency is low.

The technical problem solved by the invention is to enhance the filling and emptying of the working chamber with working medium, to reduce also the wear of the vane surfaces in contact with the cylinder axial and radial surfaces, and to enhance the sealing of the vanes with the cylinder axial and radial surfaces.

3. State of the art

In vane machines, the vanes are pressed against the cylinder wall in the working chamber by centrifugal force, in some embodiments additionally by springs or radial surfaces providing working medium pressure to the interior of the vanes.

The wear of stationary cylinder vane equipment is proportional to the total force and coefficient of friction pushing the vane against the cylinder surface in the working chamber. By selecting the materials of construction of the vanes and cylinder, the problem of friction is solved from a number of problems. The vanes can be moved axially so that they rest against the stationary lateral surfaces of the working chamber. Due to the high relative speed between the lateral surfaces of the blade and the working chamber, there is friction on both surfaces in contact, that is to say the mechanical efficiency of the device is impaired. In this embodiment, the working chamber can be radially filled with fluid and emptied of fluid, which is advantageous for volumetric efficiency.

In another vane machine embodiment, the cylinder rotates, and therefore the relative speed at the point of contact between the cylinder surface rotating within the cavity and the vane is reduced, also resulting in reduced wear, which is advantageous for mechanical efficiency. A disadvantage of this embodiment is that the axial inlet and outlet of the working medium is disadvantageous for the filling and emptying of the chambers, so that the volumetric efficiency is worse.

Similar to the first embodiment, the vanes can be moved axially so that they rest against the stationary lateral surface of the cavity. Due to the high relative speed between the vane lateral surface and the working chamber lateral surface, there is wear on both surfaces at the contact point.

4. Summary of the invention

The essence of the invention is an apparatus with a stationary cylinder part and a rotating cylinder part.

In the stationary cylinder part there are radial openings allowing the working medium to flow therethrough into and out of the cylinder working chamber.

The rotating cylinder part is a roller bearing or a slide bearing which is firmly inserted into the stationary cylinder part. The bearing inner race or the additional race body, which is firmly inserted into the bearing inner race, is driven to rotate by the blades.

The side partitions closing the working chambers of the cylinders are solidly connected to the rotor in a telescopic manner and rotate with it.

The vanes, with axial and radial grooves, are inserted into the rotor, enhancing the sealing of the working medium between the contacting vanes and the other parts. The seal is a labyrinth seal.

5. Description of the drawings

Fig.1 shows a front view of an enclosed blade apparatus.

Figure 2 shows a side view of an enclosed vane machine.

Fig. 3 shows a rear view of the enclosed blade apparatus.

Figure 4 shows a cross-sectional view along X-X in figure 1 of the enclosed vane machine.

Figure 5 shows a cross-sectional view along Y-Y in figure 2 of the blade apparatus without the additional ring body.

Figure 6 shows a cross-sectional view along Z-Z in figure 1 of the blade apparatus without the additional ring body.

Fig.7 shows a longitudinal section of the rotating part of the cylinder B without the additional ring body.

Fig. 8 shows a longitudinal cross-sectional view of a blade apparatus with an additional ring body.

Figure 9 shows a lateral cross-sectional view of a vane machine with an additional ring body.

Fig.10 shows a longitudinal section of the rotating part of the cylinder B with the additional ring body.

Fig. 11 shows a front view of the stationary part of cylinder a.

Fig. 12 shows a side view of the stationary part of cylinder a.

Fig. 13 shows a rear view of the stationary part of cylinder a.

Figure 14 shows a longitudinal section of the stationary part of cylinder a taken along R-R in figure 13.

Fig. 15 shows a front view of the cylinder head cover D.

Fig. 16 shows a left side view of the cylinder head cover D.

Fig. 17 shows a right side view of the cylinder head cover D.

Figure 18 shows a cross-sectional view of the cylinder end cover D taken along N-N in figure 17.

Fig. 19 shows a front view of the rotor C.

Fig. 20 shows a side view of the rotor C.

Fig.21 shows a cross-sectional view of the rotor C along P-P in fig. 20.

Figure 22 shows a transverse cross-section of a rotor body with grooves.

Fig.23 shows a perspective view (enlarged) of a blade with a groove E.

Figure 24 shows a p-v graph of the operating cycle of a driven vane machine using a compressible working medium.

6. Detailed description of the preferred embodiments

The present invention relates to the basic version of vane machines, in which the cylinder consists of a stationary part and two rotating parts.

More complex versions of vane machines can be composed of a plurality of stationary and rotating cylinder parts, and all combinations of layout and dimensions depending on the required technical features are possible.

The embodiments of the blade-type apparatus described herein, as shown in fig.1, 2, 3, 4, 5, 6, 8 and 9, include: a stationary cylinder part a, a rotating cylinder part B, a rotor C, an end cover D and vanes F.

Stationary cylinder part A

The cylinder part a is shown in fig. 11, 12, 13 and 14, respectively in a view from the front, the side, the rear and in a section at R-R.

The cylinder part a is made in the shape of a hollow roller, comprising in the centre of its hollow part an inner sleeve 1 with a working surface 2 and a lateral surface 3. The rotor C rotates inside the sleeve.

At the inlet and outlet the stationary cylinder part has openings 4 for the end covers D.

The sleeve 1 has an opening 5 through which the working medium is allowed to flow into the cylinder working chamber and an opening 6 through which the working medium is allowed to flow out of the cylinder working chamber. The openings 5 and 6 are rectangular and radially distributed with respect to the cylinder. The openings 5 and 6 may also be of other shapes.

Rotating cylinder part B

The rotating cylinder part B can be designed as one of the two following variants:

modification 1-no additional collar body;

modification 2-with additional collar.

Fig.7 shows a modification 1 of a rotating cylinder part without an additional ring body, the rotating part of which actually comprises a bearing with an outer ring 7 and an inner ring 8 with a working surface 9. As shown in fig. 5 and 6, the bearing is firmly inserted into the opening 4 of the stationary cylinder part a, against the lateral surface 3 of the sleeve 1. The inner ring 8 is driven to rotate by the vanes F. Fig.10 shows a variant 2 of a rotating cylinder part with an additional ring body, the rotating part of which actually comprises a bearing with an outer ring 7 and an inner ring 8 inside which an additional ring body 10 with a working surface 9 is firmly inserted. As shown in fig. 8 and 9, the bearing is firmly inserted into the opening 4 of the stationary cylinder part a, against the lateral surface 3 of the sleeve 1. The inner ring 10 is driven to rotate by the vanes F.

The rotating cylinder part B, in variants 1 and 2, may be a roller bearing or a plain bearing.

Rotor C

As shown in fig. 19, 20 and 21, the rotor C includes a shaft 11, a body 12 having a longitudinal groove 13, and a side plate 14. The plate 14 is firmly fitted over the shaft and against the rotor body to close the cylinder working chamber 16 from its side. On the rotor body four longitudinal slots 13 at 90 degrees to each other are cut to receive the blades F so that the angle between the blade surface and the radial direction of the rotor is 0. The rotor co-rotates with the plate and vanes within the cylinder working chamber 16. The rotor rotates within a bearing 15 which may be a roller bearing or a sliding bearing. The bearing is firmly inserted into the opening 17 of the end cap D.

The rotor may have one or more blades.

The slots on the rotor body may also be designed such that the blades can move under an angle formed by the blade surface and the radial direction of the rotor.

As shown in fig.22, on the outer surface of the rotor body, longitudinal grooves 15 making labyrinth seals may be cut.

End cap D

As shown in fig. 15, 16, 17 and 18, the end cap D has an opening 17 for receiving the bearing 15 inside which the rotor rotates. The end caps are firmly inserted into the openings 4 of the stationary cylinder part, as shown in fig. 14, so that they rest on the outer ring 7 of the rotating cylinder part B, as shown in fig. 5 and 8. The opening 17 is made eccentric with respect to the axial axis 19 of the end cap.

Blade F

The blade may be manufactured with or without grooves. The present description relates to vane-type apparatus having vanes with grooves (labyrinth seals) on their rotors.

The blade F, as shown in fig.23, has a body 22, which is cut with axial grooves 24 on the central part of the upper surface and between two flat parts 23, and radial grooves 25 on the whole length of the two narrow surfaces. The blades are inserted into slots 13 in the rotor body. The length of the flat part 23 of the vane corresponds to the width of the inner ring 8 or the additional ring body 10, respectively, of the rotating cylinder part. The length of the axial groove 24 corresponds to the width of the sleeve 1 of the stationary cylinder part.

When the rotor rotates, the vane flat portion 23 drives the inner ring 8 or the inner ring 10, respectively, of the rotating cylinder part.

Function of the invention

Views of the enclosed and assembled blade apparatus are shown in fig. 1-front view, fig. 2-side view, fig. 3-rear view, and in fig. 4 in a cross-sectional view along X-X.

The vane machine working chamber 16, as shown in fig. 5, 6, 8 and 9, is defined by the sleeve 1 of the stationary cylinder part a, the inner ring 8 or the additional ring body 10 of the rotating cylinder part B, the plate 14 and the body 12 of the rotor C and the vane flat 23 and the axial grooves 24 of the vanes F. With respect to the number of vanes, the working chamber may be divided into two or more sections. Vane machines work on the principle of creating tangential forces from pressure differences at the rotor blades. The tangential force on the rotor shaft is shown as a moment momentum in addition to the operating revolutions of the plant that generates the engine power. When used as a driving device (engine), the device energy is converted into usable mechanical work, and when used as a working device (pump), the usable energy is used to change the pressure of the working fluid with a specified flow rate.

Vane machines with stationary and rotating cylinder parts are powered by bringing the medium through the opening 5 into the cylinder working chamber 16. During this process of the working medium, the rotor is caused to rotate due to the pressure difference. The medium in the space between the two vanes leaves the cylinder working chamber 6 through the medium outlet on the opposite side of the cylinder, and the cycle is repeated.

The rotation of the rotor creates a centrifugal force that pushes the blades F out of the slots 13, which causes friction between the blade flat portions 23 and the working surface 9 of the bearing inner ring 8 or of the additional ring body 10 and puts them (the inner ring 8 or the additional ring body 10) in motion.

The sliding (slipping) speed of the contact surfaces of the blade and the bearing inner ring or the additional ring body firmly inserted inside the bearing inner ring is such that the instantaneous peripheral speed of the outer edge of the blade and the instantaneous peripheral speed due to the rotation of the inner ring are not the same. In this device, the speed depends on the number of blades. For only one blade in the rotor, the relative speed is 0, whereas for a plurality of blades in the rotor, the maximum sliding speed is equal to the average speed obtained from the difference in blade speed of the maximum and minimum peripheral speeds with respect to the current inner bearing ring rotation speed. The rotating cylinder part with bearing rings has the effect of reducing the sliding speed, to thus reduce the friction, noise and wear rates, which all improve the mechanical efficiency of the vane machine.

The vanes are all axially movable, against the plate 14 of the rotor C. The plates are firmly connected to the rotor and therefore rotate together with it. In this way it achieves a minimum relative speed of sliding between the lateral edges of the blades and the plates, which also results in a reduced rate of friction and wear and an improved mechanical efficiency. The relative speed between the lateral edges of the vanes and the working chamber plate is due to the radial movement of the vanes. There is a gap between the vane and the working surface 2 of the stationary cylinder part, or sleeve 1, so there is no mutual contact, which avoids frictional wear in this area.

This vane-machine embodiment enables the working medium inlet 5 and outlet 6 to be placed radially, which is one of the main disadvantages of the presently known vane-machine embodiments, because of their size, shape and position, achieving better filling and discharge (volumetric efficiency) of the working chamber.

The relative speed between the rotating inner ring or bearing attachment ring and the blades is greatly reduced and therefore the frictional wear of the blades is reduced.

The pressure of the vanes against the rotating inner ring or the bearing attachment ring body creates a seal in this region. This pressure can, if necessary, be additionally increased by means of springs placed in the vane grooves or by supplying a higher pressure working medium to the radial surface on the inside of the vane, which also results in additional radial forces.

The rotation of the rotor allows for periodic charging and discharging of the working chamber, whereby the working chamber pressure from the inlet to the discharge is increased or decreased depending on the purpose of the vane machine.

Vane machines having stationary and rotating cylinder parts reduce wear of the vane contact surfaces that contact the axial and radial walls of the cylinder within the vane machine working chamber, enhance working medium injection and discharge from the working chamber, and address sealing issues between the vanes and the stationary and rotor side plates within the cylinder. This improves the volumetric efficiency of the device and reduces losses due to friction between the contacting surfaces, thus improving the mechanical efficiency of the device.

Figure 24 shows a p-v diagram of the working cycle of a driven vane machine comprising a cylinder with stationary and rotating component parts, using a compressible working medium.

The operation of a vane machine with stationary and rotating cylinder parts is the algebraic sum of the operations of injection, expansion and exhaust for one rotor revolution. The process can be described simply in a closed working cycle with a compressible working medium. The working chamber injection is isobaric, with the state changing from a to b. The expansion process is the change in working chamber volume from b to c. The discharge of the working medium consists of three stages. The first stage is the sudden expansion from c to c' when the discharge slot starts to open. The second phase of the discharge from c' to d is the discharge due to the reduction of the swept volume. The third stage, from d to a', is the compression of the working medium remaining in the working chamber after the discharge slot has been closed. The final phase of the cycle is to inject new working medium into the working chamber so that the isochoric pressure rises abruptly from a' to a.

The following equation shows the process and results in terms of energy balance:

EdQ+dZ_M＝dU+dL+dZ_v

wherein:

EdQ is the energy carried in by the G mass of working medium;

dU is the internal energy change;

dL is the work exchanged with the environment;

dZ_Mis the amount of energy brought into the working chamber due to losses;

dZ_vis energy not used in the working chamber but brought into the environment by the working mediumNumerical values.

The last two energy values above can be determined by the following equation:

dZ_M＝P_M dG_Mand dZ_v＝P_v dG_v，

Wherein:

P_Mis the specific energy (specific energy) of the working medium entering the cycle;

P_vis the specific energy of the working medium leaving the cycle;

dG_Mis the mass of new working medium entering the working chamber from the environment during a cycle;

dG_vis the mass of new working medium that leaves the working chamber into the environment during a cycle.

The main problem of the overall efficiency of the vane machine is the volumetric efficiency due to the injection and discharge of the working medium into and out of the working chamber (processes from a '-a and c-c' -d in the p-v diagram). The volumetric efficiency problem is solved in the present invention by using the stationary parts of the working chamber cylinder wall as radial inlet and discharge channels for the working medium to the greatest extent possible. This structural design enables an additional increase in the cross-section of the working medium inlet and discharge channels, since the vanes do not touch the discharge channels, which can therefore be designed as rectangular openings, while this design achieves their largest possible area, which also improves the filling and discharge conditions of the working chamber of the vane machine.

Another important problem solved by the present invention is the wear of the blades, the inner ring or the additional ring body of the rotary bearing and the rotating rotor plate. Roller bearings or sliding bearings are introduced whose inner ring can be firmly inserted into an additional ring body with sufficient sliding properties for the vanes to rest on, reducing the relative speed of sliding at the sliding contact points and thus also their wear.

The blades can be moved axially because they bear against the rotor lateral plates. In existing vane machine embodiments, the cylinder working chamber lateral plates are stationary, and therefore, the higher speed between the vane lateral edges and the lateral plates results in wear of both surfaces in contact. The introduction of lateral rotating plates on the rotor to close the working chamber reduces the relative speed associated with the vanes, and therefore the lateral wear caused by the friction of the vanes and the plates is reduced. The relative speed between the lateral edges of the vanes and the working chamber plate is due solely to the radial movement of the vanes. The reduction of friction losses improves the mechanical efficiency of the device.

7. Application of the invention

Vane machines with stationary and rotating cylinder parts can be used in industry, for example, as drive or working machines. When used as a working device, mechanical work input with a specified flow rate is converted to a pressure change of the compressible or incompressible working fluid, while when used as a driving device, it converts the main available pressure of the compressible or incompressible working fluid into mechanical work.

As a working or driving device using compressible fluid, it is used as a pneumatic tool, in the mechanization of various technological processes, as a starter for large diesel engines, as a compressor, as a vacuum pump, as an internal combustion engine.

As a working or driving device using incompressible fluid, it is used with force, motion and momentum transfer systems in construction machines, hydraulic cranes, ship hydraulic systems, device fluid drives, and with control, regulation or protection in hydraulic systems aimed at automation of the working process.

As a pump or hydraulic motor, it has two fields of application with respect to working fluids. When the working fluid is mineral oil, the lubrication itself reduces friction and, therefore, wear of the vanes and the casing, which are highly disadvantageous for vane-type machines. This is used with force, motion and momentum transfer systems in construction machines, hydraulic cranes, ship hydraulic systems, equipment fluid transmissions, and with control, regulation or protection in hydraulic systems aimed at automation of working processes. Hydraulic vane machines have a wide range of rotational speeds. The inertia forces of its rotating parts are small, generally making the starting and stopping of the apparatus easier. The problem of vane and casing wear remains a major obstacle for vane-type devices or pumps when used with non-lubricated working media.

The characters and numerals used in the description of the present invention have the following meanings:

stationary part of A-cylinder

1-sleeve

2-working surface of casing

3-lateral surface of the sleeve

4-lateral opening in stationary part of cylinder

5-working fluid inlet

6-working fluid discharge

Rotating part of B-cylinder

7-outer ring of rotating cylinder part

8-inner ring of rotating cylinder part

9-inner ring working surface

10-additional ring body

C-rotor

11-rotor shaft

12-rotor body

13-vane groove

14-rotor side plate

15-rotor bearing

16-cylinder working chamber

D-end cap

17-end cap eccentric opening for rotor bearing

End cap opening for 18-rotor side plate

19-end cap axial axis

20-eccentric opening axial axis

21-opening radial axis

F-blade with groove

22-blade body

23-flat part of blade without groove

24-axial groove

25-radial groove

Claims (9)

1. Vane machine with stationary and rotating cylinder parts, belonging to the positive displacement rotating type, which can be used as a driving or working machine, using compressible or incompressible fluids as working medium, with eccentrically placed rotors with vanes rotating inside the cylinder of the machine, where the machine has one stationary cylinder part (a) with an inner sleeve (1) in its centre and lateral openings (4); a radial rectangular opening (5) allowing the working medium to flow into the cylinder working chamber (16) and a radial rectangular opening (6) allowing the working medium to flow out of the cylinder working chamber (16) are formed on the sleeve (1); the apparatus has two rotating cylinder parts (B); the rotating cylinder part is a roller bearing or a slide bearing which is firmly fitted into the opening (4) of the stationary cylinder part; the device has a rotor (C) with lateral plates (14) rotating together with it; the device has a blade (F) with a groove; the device has an end cap (D) which is firmly fitted into the lateral opening (4) of the stationary cylinder part; an eccentric opening (17) is provided in the end cover (D), in which an eccentric opening a bearing (15) is firmly fitted, within which the rotor (C) rotates.

2. Vane machine according to claim 1, wherein the inner bushing (1) formed in the centre of the stationary cylinder part (A) has a working surface (2) and a lateral surface (3) against which the outer ring (7) of the rotating cylinder part (B) rests.

3. Vane machine according to claim 1, wherein the radial openings (5 and 6) allowing working medium to enter and exit the cylinder working chamber can also be designed in any other form.

4. Vane machine according to claim 1, wherein the rotating cylinder part (B) has an inner ring (8) without an additional ring body (10).

5. Vane machine according to claim 1, wherein the rotating cylinder part (B) can be designed with an additional ring body (10) that fits firmly into the inner ring (8).

6. Vane machine according to claim 1, wherein the rotor lateral plate (14) is firmly sleeved on the shaft (11) to laterally close the cylinder working chamber (16).

7. Vane machine according to claim 1, wherein the vanes (F) with grooves have flat surfaces (23) on the upper side of their body (22), with axial grooves (24) between the flat surfaces (23); when the rotor rotates, the centrifugal force causes the flat portion (23) to come into contact with the working surface (9) of the inner ring (8) or of the additional ring body (10) causing them to rotate; on the lateral part of the body there is a longitudinal radial groove (25) in contact with the rotating lateral plate (14).

8. The vane machine as claimed in claim 1, wherein the vanes can be made without axial and radial grooves.

9. Vane machine according to the preceding claims, wherein more complex machine embodiments can have a plurality of stationary and rotating cylinder parts, all combinations of distribution and size of which are possible.