WO1985003736A1

WO1985003736A1 - Palette rotary machine

Info

Publication number: WO1985003736A1
Application number: PCT/BE1985/000002
Authority: WO
Inventors: Jean-Marie Hublet
Original assignee: Hublet Jean Marie
Priority date: 1984-02-15
Filing date: 1985-02-14
Publication date: 1985-08-29
Also published as: EP0152395A1; LU85216A1; EP0204703A1

Abstract

Palette rotary machine comprising a cylinder (3) wherein a piston (5) is housed, said cylinder being stopped by two plates provided with bearings of the piston (5), intake and discharge openings (6, 8) for the fluid, characterized in that it comprises at least longitudinal seals (22) applied against the friction surface thereof under the effect of a force, lateral seals between each side of the palettes and the plates, and tranversal seals (25) arranged into grooves (28) provided in the piston and joining two grooves of the palettes (20).

Description

ROTARY PALLET MACHINE. The present invention relates to a rotary vane machine (capsulism machine) comprising at least one retractable pallet or at least two chambers with variable volume during a rotation cycle, capable of operating as a receiving machine (pump , compressor, depressor, ... etc) or in a generating machine (steam engine, internal combustion engine, ... etc).

Various types of rotary machines with capsulism are known, presenting geometric cylinder shapes and relative positions of the rotary piston with respect to the most diverse cylinder.

The performance of these machines is strongly influenced by their particular design and the widespread use of lubricants to reduce their losses in sealing between chambers.

In particular, the lateral tightness, that is to say between each end of the pallet and the flange facing it, is strongly affected on the one hand, by the wear of the said ends of the pallets, by their friction against the flange and secondly by the necessary tolerance between the end of the piston body and the flanges. This transverse sealing deficiency has the effect of allowing all the chambers to inadvertently interfere with one another, which has the effect of drastically reducing the efficiency of the machine.

In addition, in the case of dry compressors, without lubrication, the wear of the friction surfaces is further increased and it is impossible until now to supply a dry compressor operating with a satisfactory performance and during an extended time.

The object of the present invention is therefore to provide a rotary vane machine having a substantially improved yield compared to existing capsulism machines thanks to a particular conception of the sealing of such a machine and of the means in front of it. '' ensure effectively.

According to another aspect of the present invention, it also aims to provide a capsulis¬ me machine that can operate as a dry compressor with a significantly increased energy efficiency. ^*

The object of the present invention is achieved by a rotary vane machine comprising at least one hollow cylinder in which is housed a piston, a cylinder provided with fluid intake and discharge openings and closed on each side by a flange comprising the bearings of the piston, as well as at least one partial pallet, the retractable ent, either in the piston or in the cylinder, and at least two chambers with variable volume during a cycle, said machine being able to operate in receiving machine or generating machine, characterized in that it comprises: - longitudinal sealing elements housed on the longitudinal end of each pallet, which are in friction with the contact surface, said elements being applied against their friction surface under the effect of a force; - lateral sealing elements arranged at each lateral end of the pallets between said pallets and the flanges; and - transverse sealing elements ensuring the etan¬ cheity between the piston, two successive pallets and the lasques.

According to a particularly preferred variant of the present invention, the rotary vane machine described above also includes elements for facial sealing which act between the faces of the pallets and the internal faces of the notches in which they slide and which are essentially the same length as said pallets.

This facial sealing element is intended to prevent any leakage of fluid from one chamber to the other through the notch made either in the piston or in the cylinder, between the pallet and the walls of the en¬ check mark in which it slides. This sealing element can be free or controlled by a pressure of spring or fluid pressure from inside or outside the machine.

It can therefore be seen that the seal is particularly well achieved by having sealing elements around the pallets and between the piston and the flanges.

Being in the presence of substantially sealed variable volume chambers notably increases the efficiency of rotary vane machines. According to a particularly advantageous embodiment, the longitudinal sealing element consists of a linear joint of length substantially equal to the internal length of the cylinder, housed in the thickness of the pallet, opposite the friction surface, so that it can oscillate freely around its longitudinal axis. This seal is advantageously ap¬ applied against the friction surface by a force which, in addition to the centrifugal force may consist of an ac¬ tion of a spring or a fluid pressure, either the compressed fluid or a fluid under pressure from an external source.

Advantageously, the seal between the longitudinal sealing element and the flanges of the machine can be ensured by a perfect application of the latter on the flanges thanks to a pressure that can be obtained by elongation of said sealing element. longitudinal. This possibility of extending the length of said longitudinal sealing element can advantageously be achieved by its particular mechanical design or by a force resulting from a spring or fluid pressure.

The lateral sealing element advantageously consists of a suitable U-shaped seal which fits onto the ends of the pallets. The fitting is such that the lateral sealing element adapts to the longitudinal sealing element and that any leakage of fluid between the two is made impossible. Likewise, its shape is studied so as to ensure a substantial seal. partially complete between the pallet and the longitudinal sealing element despite the mobility of the latter.

Advantageously, the transverse sealing element consists of a seal of suitable shape housed in a recess made in the transverse f f of the piston and which prevents leakage of fluid between the piston, the flanges and the vanes.

To perfect the sealing of the variable volume chambers, facial sealing elements are housed in grooves located in the faces of the pallets or in the walls of the notches thereof.

In this way, the content of each variable volume chamber is perfectly confined due to the absolute tightness compared to the neighboring chambers and to any other part of the machine. Other advantages and variants of the present invention will be given in the following description of a particularly advantageous embodiment. It should be noted that this is given by way of nonlimiting example. The description is based on the appended figures in which:

- Figure 1 is a schematic sectional view of the cylin¬ dre and the piston of a rotary vane machine;

- Figure 2 is a sectional view along line II-II of Figure 1;

- Figures 3 and 4 are detailed views of the longitudinal sealing element;

- Figure 5 is a detailed view on an enlarged scale of a lateral sealing element; - Figure 6 is a detailed view of the end of a pallet;

- Figure 7 shows a transverse sealing element;

- Figure 8 shows another embodiment of said transverse sealing element; - Figure 9 shows an advantageous embodiment of a pallet with its longitudinal, lateral and facial sealing elements; and

- Figure 10 shows a section of the piston and a palette showing a form of positioning of the longitudinal and facial sealing elements. The rotary machine 1 with paddles comprises a hollow cylinder 3 and a piston 5 which are not coaxial. According to FIG. 2, the cylinder is a cylinder of revolution of axis 2 (fig. 1); one can however also provide a trocho'ide, hypotrocho'ide form, ... etc. Still according to the example shown, the piston is a cylinder of axis 4 revolution and has a diameter substantially smaller than that of the cylinder. However, any other suitable form can be provided. In the case treated, the cylinder is fixed and plays the role of stator while the piston plays the role of rotor provided with a PTO 7. In another embodiment, the piston can be fixed and the cylinder movable , the PTO then being mounted on the cylinder 3.

The intake and exhaust operate through openings 6 and 8 (Fig. 2).

The cylinder is closed by two flanges 9, 11 provided, respectively, with bearings 13 and 15. At least one of the flanges 11 has, at the location of the bearing 15, an opening allowing the passage of the pin 7 of the piston serving as a grip. strength.

For reasons of clarity, the cooling means such as water or oil circuits or fins, neither the lubrication circuits, nor the circuits of air or pressurized fluid have not been represented.

Each chamber is delimited (FIG. 2) by the cylinder, the flanges, the piston and two successive flat pallets 20 of an adequate thickness sliding in longitudinal grooves 21 formed in the piston according to planes preferably passing but not necessarily, by the axis of rotation of the piston 5.

The pallets are provided at the end in contact with the friction surface which, in this case, is the interior surface of the hollow cylinder of a longitudinal seal 22 the longitudinal sealing element housed in a groove 23 practiced in the thickness of the pallet. The longitudinal joint 22 has a length substantially equal to the internal length of the cylinder and is free to pivot about its own longitudinal axis in said groove 23. Preferably, said seal is provided, along its length, with a flat 24 intended to be applied advantageously on the internal face of the cylinder.

It is understood that the longitudinal joint 22 described above may be cylindrical or have any other conformation such as for example of rectangular main section or oblong section or of a section having a convexity adapted to the radius of curvature of the internal surface of the cylinder 3.

Preferably, the longitudinal joint 22 shown in detail, seen from above and in front view, respectively, in FIGS. 3 and 4, includes sizes 25 arranged in staggered rows.

Advantageously, the dimension of the notch is greater than half the width of the longitudi¬ nal joint. These notches in the joint make it possible to obtain a certain elasticity thereof, the effect of which increases with the pressure in the corresponding chamber.

In other embodiments, the linear joint 22 may be produced by assembling multiple parts whose elasticity results from the effects of springs or fluid pressures, these parts being used in particularly selected materials to resist the temperatures and pressures encountered in use cases. In this way, very good sealing of the chambers with variable volume is obtained at the place of contact of the pallets, by the interposition of the linear joint, and the friction surface, that is to say the internal surface. - of the cylinder. In addition, with a view to ensuring the effectiveness of the seal *, independently of the intensity of action of the centrifugal force on the pallets, that is to say independently of the speed of rotation of the piston, what is a major advantage especially at low speed or when starting the machine, the longitudinal seal is applied against the friction surface by a force such as that resulting from a spring pressing between the piston and the pallet, or fluid pressure. Another means may advantageously consist of hydraulic or pneumatic pous¬ evenings supplied by a pressure under pressure from an external or internal source, that is to say the compressed fluid itself, for example. The main part of the pallet, that is to say the body of the pallet, can be of a one-piece design, but variants can be of a lamellar or multi-block design which can make it extendable or telescopic. In another variant of the present invention, the opposite grooves 21 in the piston can communicate with each other for the passage of springs, hydraulic lifters or other means intended to apply an ideal pressure between two opposite pallets and real - thereby ser an ideal pressure of these against the internal surface of the cylinder by 1 ^• intermediate longitudinal joint 22.

Another characteristic of the present invention is the presence, at each of the lateral ends of the pallet, of a lateral sealing element (FIG. 5), called lateral seal, preventing leaks between the pallets and the flanges of the rotary machine. Preferably, the side seal is formed by a U-shaped profile 30 placed on the end edge of the pallet and also forms the extension of the groove 23 receiving the longitudinal seal 22 while being kept in permanent contact with the internal face of the flange by a means known per se such as a spring or by hydraulic or pneumatic pressure coming from inside the cylinder and acting through lights located behind said transverse joint.

Advantageously, the joint-shaped side seal has, at each lower part of the branches of the U, a rectangular recess 31 which adapts to a nose 32 (Figures 5 and 6) of the pallet 20 so as to prevent any leakage of the fluid through the joint between the side seal 30 and the pallet 20.

The rotary piston 5 is in itself characterized by the presence on each of the sectors sharing each of its transverse faces, of one or more transverse sealing elements (transverse joints) 27 housed in recesses 28 dug in said transverse faces and joining two successive longitudinal grooves 21 so that the transverse joints 27 are in permanent contact with two successive pallets. These transverse joints 27 seal the part of the chambers corresponding to the interstices separating the transverse faces of the piston from the internal faces of the flanges and the lateral faces of the two successive plates by the pressure which they undergo on the part of a means known per se such as springs or a hydraulic or pneumatic pressure of fluid coming from inside the piston by suitable pipes and which is applied to them through openings made in the recesses 28. As a 'nonlimiting example, let us quote as types of transverse joints preferred rectilinear segments, arcuate segments and joints of substantially triangular shape. FIG. 8 represents an advantageous embodiment of a transverse joint which ensures an ideal balance of pressures on the joint and which causes a self-tightening of the latter between two successive pallets. According to another embodiment of the transverse joint, the self-tightening thereof can be effected thanks to one or more partial cuts which allow a certain elastic deformation of the joint under the influence of the pressure prevailing in, the variable volume chamber, pressure which causes the notches of the joint to widen.

These transverse joints can be made of materials particularly suited to pressures and temperatures that they will have to bear in the different embodiments of the rotary machine.

According to a particularly preferred embodiment of the present invention, the interfaces between the faces of the pallet and the faces of the grooves 21 in which they slide, comprise facial sealing elements (facial seal) which prevent any communication of a chamber to the other by bypassing the pallets via the interior of the piston and which also appreciably improve the guidance and the sliding of the pallets in their notches.

Advantageously, each face of the pallet and each internal face of the notches in which the coulis feel the pallets are provided with at least one longitudinal groove 36 in which is housed a face seal 35 (FIG. 10).

It is specified that the longitudinal 22 and lateral 30 seals of the pallets as well as the transverse seals 27 and the face seals 35 can be made of any material of metallic or synthetic, mineral or organic nature, satisfying the requirements of hermeticity of the contact surfaces without reciprocal wear and resistance to mechanical, thermal and chemical stresses to which they will be subjected during the work of the machine.

By way of example, for such materials, mention may be made of graphite, ceramics, special steels, carbon fibers, plastics and other materials which are very suitable for this type of application and suitable for the type of machine.

This machine is characterized by the elements used to achieve complete sealing of each chamber, that is to say to strictly locate the fluids there which undergo variations in volume, pressure and temperature, as well as by the proper arrangement of each element and their relative position with respect to each other.

These characteristics of the invention make it possible to achieve the object of the invention which is to significantly improve the energy efficiency of the rotary capsulism machines used to modify the state of a gas supplied to it or to supply energy, that is to say operating in compressor, depressor, pump or motor.

Finally, note that it is not out of the invention to use the rotary vane machine thus perfected with liquids to which it communicates energy (pump) or from which it receives an energy which it transforms into mechanical energy (hydraulic motor).

Claims

CLAIMS. 1. Rotary vane machine (1) comprising at least one hollow cylinder (3) in which is housed a piston, cylinder provided with inlet (6) and outlet (8) openings and closed on each side by a flange (9, 11) comprising the bearings (13, 15) of the piston (5), and at least one pallet (20) at least partially retractable, either in the piston (5) or in the cylinder (3), and at least two variable volume chambers during a cycle, said machine being able to operate as a receiving machine or as a generating machine, characterized in that it comprises:

- Longitudinal sealing elements (22) housed on the longitudinal end of each pallet (20), which are in friction with the contact surface, said elements (22) being applied against their friction surface under the effect of 'a strength;

- Lateral sealing elements (30) arranged at each lateral end of the pallets (20) between said pallets and the flanges (9, 11); and

- transverse sealing elements (27) ensuring the sealing of each chamber with variable volume between the piston (5), two successive vanes (20) and the flas¬ cs (9, 11).

2. Rotary machine according to claim 1, characterized in that it also comprises facial sealing elements (35) which act between the faces of the pallets and the internal faces of the notches in which these slide and which are essentially the same length as said pallets.

3. rotary vane machine according to any one of the preceding claims, characterized in that the longitudinal sealing element consists of a linear seal ⁽ 22 ⁾ of length substantially equal to the internal length of the cylinder, of circular or oblong section, housed in the thickness of the pallet, opposite the friction surface so that it can oscillate freely around its longitudinal axis.

4. Rotary vane machine according to Reven¬ dication 3 characterized in that the longitudinal sealing element is provided, over its length, with a flat (24) intended to be applied advantageously on the inner face of the cylinder.

5. Rotary vane machine according to any one of claims 3 or 4 characterized in that the sealing element comprises partial notches (25) arranged in staggered rows and passing through the entire thickness of the joint.

6. rotary vane machine according to any one of the preceding claims, characterized in that the lateral sealing element is formed by a ϋ profile (30) fitted on the end edge of the pallet and also forms the extension of the groove (23) of the longitudinal sealing element.

7. Rotary vane machine according to reven¬ dication 6 characterized in that the U-shaped lateral sealing element (30) comprises on each branch of the ϋ a rectangular recess (31) which adapts to a nose

(32) of the pallet (20) so as to prevent any leakage of fluid through the joint between the lateral sealing element (30) and the pallet (20).

8. Rotary vane machine according to any one of the preceding claims, characterized in that the transverse sealing element consists of a seal (27) housed in a recess (28) hollowed out in said transverse face and joining two longitudinal grooves the (21) successive so that the transverse joints (27) are in permanent contact with two successive pallets.

9. Rotary vane machine according to Reven¬ dication 8 characterized in that the transverse étan¬ shéités elements consist of sectors subjected to a pressure of a spring or a fluid.

10. Rotary vane machine according to Reven¬ dication 8 characterized in that the transverse étan¬ shéités elements consist rectili- genes or arched provided with notches which allow a certain elastic deformation of the joint under the effect of pressure.

11. Rotary vane machine according to any one of the preceding claims, characterized in that the facial sealing elements consist of facial seals (35) housed in grooves ^' res (36) practi¬ cated in each face of the pallet (20) and / or in each interior face of the notch in which the latter slides.