CA1108009A - Rotary axial vane mechanism - Google Patents
Rotary axial vane mechanismInfo
- Publication number
- CA1108009A CA1108009A CA301,168A CA301168A CA1108009A CA 1108009 A CA1108009 A CA 1108009A CA 301168 A CA301168 A CA 301168A CA 1108009 A CA1108009 A CA 1108009A
- Authority
- CA
- Canada
- Prior art keywords
- vane
- cam
- rotary axial
- fluid
- vane mechanism
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
- F01C1/344—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F01C1/3448—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member with axially movable vanes
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
The disclosure herein describes a mechanism which includes: a housing having a generally cylindrically shaped interior profile and a median wall; means located centrally of the interior profile, having a generally cylindrical outer surface defining with the interior profile and the median wall, on opposite sides thereof, two separate annular chambers; a pair of cam means respectively mounted in each chamber opposite to the median wall, the cam means having coactingly shaped plane surfaces parallel to one another and inclined with respect to the longitudinal axis of the interior profile; and cylindrical vane means slidably and rotatably mounted in the channel means, the vane means having opposite inclined end walls in coacting engagement with the cam surfaces whereby relative rotation between the housing and the cam means results in the rotation and in the longitudinal translation of the vane means in the channel means.
The disclosure herein describes a mechanism which includes: a housing having a generally cylindrically shaped interior profile and a median wall; means located centrally of the interior profile, having a generally cylindrical outer surface defining with the interior profile and the median wall, on opposite sides thereof, two separate annular chambers; a pair of cam means respectively mounted in each chamber opposite to the median wall, the cam means having coactingly shaped plane surfaces parallel to one another and inclined with respect to the longitudinal axis of the interior profile; and cylindrical vane means slidably and rotatably mounted in the channel means, the vane means having opposite inclined end walls in coacting engagement with the cam surfaces whereby relative rotation between the housing and the cam means results in the rotation and in the longitudinal translation of the vane means in the channel means.
Description
FIELD OF THE INVENTION
This invent;on relates to rotary axial vane mechanisms which may be used in pumps, compressors, fluid motors, internal combustion engines, and the like; hence, these mechanisms may be used for driving a fluid or for being driven by a fluid.
BACKGROUND OF THE INVENTION
The invention is particularly directed to that type of rotary mechanism which contains ~wo annular working chambers flanking a median casing wall. These chambers are closed by coactingly shaped end walls disposed opposite to the median wall and defining vane-guiding cam surfaces; these surfaces are generated by revolving a radial line perpendicular to the axis of rotation of the rotary mechanism. The chambers are sepa-rated into several compartments by one or more vanes slidably mounted in the median wall for longitudinally reciprocating motion as they are engaged with both of the guiding cam surfaces.
Hence, the motion of the vanes is in a direction transverse to the plane of rotat;on of the rotary mechanism.
The ;nvention is applicable in general to such structure as described in U.S. patent Nos. 2,154,458 issued April 18, 1939 to R.T. Knapp, 2,672,099 issued March 16, 1944 to J. Deubel, 2,593,457 issued April 22, 1952 to W. Jastrzebski,
This invent;on relates to rotary axial vane mechanisms which may be used in pumps, compressors, fluid motors, internal combustion engines, and the like; hence, these mechanisms may be used for driving a fluid or for being driven by a fluid.
BACKGROUND OF THE INVENTION
The invention is particularly directed to that type of rotary mechanism which contains ~wo annular working chambers flanking a median casing wall. These chambers are closed by coactingly shaped end walls disposed opposite to the median wall and defining vane-guiding cam surfaces; these surfaces are generated by revolving a radial line perpendicular to the axis of rotation of the rotary mechanism. The chambers are sepa-rated into several compartments by one or more vanes slidably mounted in the median wall for longitudinally reciprocating motion as they are engaged with both of the guiding cam surfaces.
Hence, the motion of the vanes is in a direction transverse to the plane of rotat;on of the rotary mechanism.
The ;nvention is applicable in general to such structure as described in U.S. patent Nos. 2,154,458 issued April 18, 1939 to R.T. Knapp, 2,672,099 issued March 16, 1944 to J. Deubel, 2,593,457 issued April 22, 1952 to W. Jastrzebski,
2,462,622 issued April 5, 1949 to W.R. Tucker et al., 2,902,942 issued September 8, 1959 to M. Pelladeau and 3,489,126 issued January 13, 1970 to K.N. Regar.
Irrespective of the particular arrangements used in the above-listed patents, these mechanisms share several common disadvantages:
(a~ cams and slots are expensive to make;
~b) vanes are too weak For long strokes and/or large pressures;
(c) sliding friction between vanes in cases where several vanes work in the same slot is high and causes sticking and wear;
(d) cam-vane contact is limited to almost a linei hence~
poor sealing and excessive wear;
(e) vane-channel contact surface is quite limited; hence, leakage and wear;
(f) in cases where the vanes rotate, the centrifugal forces cause wear along the narrow longitudinal edge of the vanes; and (g) the contact line between the cam and the median wall allows large leaks.
OBJECTS ARD STATEMENTS OF THE INVENTIQN
One object of the present invention is to overcome most-of the d;sadvantages listed above w;th respect to prior rotary mechanisms and to provide an axial rotary vane mechanism adaptable to various functional applications.
The operation of the mechanism of the present invention is based on the relative rotation imparted between two inclined cam surfaces and a housing which contains at least one transverse channel in its central wall and a cylindrical ~ane located in this channel; the vane has two end surfaces remaining in continuous sliding contact with their corre sponding cam surface. This relative rotation results in the longitudinal reciprocating movement of the vane and in its rotation about its own axis.
The present invention therefore relates, in its broadest aspect, to a rotary axial vane mechanism which includes:
a hous;ng having a generally cylindrically shaped interior profile and a median wall; means, located centrally of the interior profité, having a generally cylindrical outer surface defining with ~he interior profile and the median wall, on OppQSite sides thereof, two separate annular chambers; a pair of cam means respect;vely mounted in each chamber opposite to the median wall, the cam means having coactingly shaped plane surfaces`parallel to one another and in.clined with respect to the longitudinal axis of the interior profile; at least one cylindrical channel means extending through the median wall and having an axis parallel to the longitudinal axis;
cylindrical vane means slidably and rotatably mounted in the 1~ channel means, the vane means having opposite inclined end 1¦
walls ;n coacting engagement with the cam surfàces whereby relative rotation between the housing and the cam means results in the rotation and in the longitudinal translation of the vane means in the channel means.
The such defined mechanism may be uti-lized-in a pump, an hydraulic motor, a compressor, a vacuum pump, a pneumatic mo~or, a steam motor, an internal combustion engine and the ¦
like.
Other objects and further scope of applicability of the present invention will become apparent from the detailed description given hereinafteri it should be understood however that this description, while indicating preferred embodiments of the invention, is given by way of illustration only since various changes and modifications within the spirit and scope o~ the invention will become apparent to those skîlled in the art from reading this description. One such mod;Fication would involve separate chambers of different sizes, hence of cylindrical channels and cylindrical vanes having two portions of two differen~ diameters.
BRIEF DESCRIPTION OF THE DRAWINGS
Figuré 1 is a perspective exploded view of a rotary mechani sm wi th rotati ng cam members and s~ationary housing in accordance with one embodiment of the present invention, part of one end cover and of the central cas.ing having been omitted for clarity;
Figure 2 is an elevational cross-sec~ional view of the rotary mechanism shown in Fig. l;
Figure 3 is a sectional perspective view of the dis-charge ports, manifold and valving which may be used in a mechanism such as t~e one illustrated in Fig. l;
Figure 4 is a transverse cross-section through the median wall of a variant of the mechanism shown in Fig. 1 `
' illustrating transfer passages in a vane;
Figure 5 is a perspective exploded view of a rotary mechanism with fixed cams and rotary housing in accordance with anothe.r embodiment sf-the present invention, one half of the casing, parts of the rotary housing and of the second half of the casing having been omitted for-clarity;
Figure 6 is a longitudinal cross-sè~tion through a hollow vane with closed ends;
Figures 7 and 8 are, respectively, an elevational end view and a longitudinal cross-sectional view of the rotary portion of a mechanism made in accordance with the present invention with plane annular surface on the median walli Figure 9 is a perspective view of a fixed cam member cooperating with the rotor portion illustrated in Figures 7 and 8;
Figure lOa is a perspective view of a fixed cam member in the first half stage of a second-stage compressor constructed in accordance with the present inventioni Figure lOb is a perspective view of a fixed cam member in the sécond half stage of the said second~stage compressor;
Figure 11 is an elevational side view of a rotor cooperating with the cam members oF Figs. lOa and lOb;
F;gure 12 ;s an elevat;onal end v;ew of a rotor ;n an internal combustion engine in accordance with the present invention;
Figure 13 is a perspective view of a cam member cooperating with the rotor of Fig. 12;
Figures 14a, 14b, 14c are end views of the cam member 1 .
of F;g. 13 with the successive positions of the three vanes.
DESCRIPTION OF PREFERRED EMBODIMENTS
In the following description, the same reference numerals will be used to designate identicai parts and .
configurations. As the rotary axial vane mechanism of the present invent;.on ;nclude.s.two separate s;des divided by a central wall and having therein generally iden~ical parts and 1.
configurations in the.drawings, the refe.rence numerals shown on the left-hand side of the central wall will bear the subscript "a" while those on the right-hand side will bear the 20 subscript "b". :
The mechanism shown in Figs. 1 and 2 ill.ustrates a stationary housing 10 having a generally cylindrically shaped interior profile 12 separated by a centrally disposed partition median wall 14 having outer opposite identical conical surfaces 16 and cylindrical extensions 20. Each ;nterior profile 12, conical surface 16 and cylindrical extension 20 define an annular chamber 18 These chambers 18 are closed by a pair of cam members 24, each haYing an inclined plane surface 22; these cam members are identically shaped and their surfaces 22 are parallel to one another and inclined with respect to a central shaft 26 which longitudinally traverses the housing 10. The .
~ 8~
angle which the cam surfaces 22 make with the longitudinal axis of the shaft is the same as the vertex angle o~ the conical sur~aces 16. The cam members 24 are fixedly mounted on shaft 26 by appropr;ate keys 27 received in grooves 28 so that the inclined surface planes remain constantly parallel to one another. By being keyed to the shaft 26 in the position shown in Figures 1 and 2, the long;tud;nal d;stance separating the inclined surfaces 22 is constant. The outer and inner ellipt;cal per;pheries 30 and 32 of each cam surface maintain small running clearances with respect to the outer and inner cylindr;cal walls 12 and 20 of chambers 18. Each ;nclined face ' of the cam members has a recessed radial segment 34 which engages with the respective conical surface 16 across a small running clearance. The housing 10 is closed at its opposite ends by two cover plates 36 by means of bolts 38. These plates contain the outer races 40 of tapered roller bearings 42, the inner races of which are mounted on shoulders 44 of the respective cam members; this arrangement offloads the shaft of bending stresses.
A cylindrically shaped channel 46 in the median wall 14 extends parallel to the axis o~ shaft 26 and has a diameter sligh~ly exceeding the annular width o~ chambers 18. The inner walls 20 and the outer walls 12 include oppositely facing concave recesses 48 and 50 which def;ne arc surfaces in ~rolongation with the inner wall surface of channel 46 so that a cylindrical vane 52 may extend through channel ~6 and be contained between the opposite recesses 48 and 50. The cylindrical vane 52 has opposite end walls 5~ and 56 which are inclined and parallel to one another and which make the same angle as the inclined plan~ surfaces 22 with respect to the shaft 26. The iength of vane 52 is substantially equal to the constant distance separating the cam surfaces 22 so that the inclined faces 54,5~ of the vanes are constantly in contact with the cam surfaces.
Vane 52 and each recessed segment 34 divides each corresponding chamber into two working chambers; as the sha~t rotates, so do the inclined cam surfaces and the vane is forced tO reciprocate longitudinally and to turn once around its own axis for every turn of shaft 26. Simultaneously, the recessed se9ment 34 revolves with the inclined cam surface and together with the vane causes a cycl;c volume change for each of the corresponding two working chambers. The volume changes in the two working chambers of ~he other half occur with a phase angle of 180. The increasing volume of a working chamber draws in fluid from an intake manifold 58 through a port 60 extending longitudinally in each interior pro~ile of the housing lO along the recess 50;-the:manifold~58 is connected to appropriate fluid drawing means.through port.62.in the cover plate 36. Simultaneously, the decreasing volume of the second working chamber expells the fluid, already admitted during the previous cycle, through a port (not shown but extending longitudinally and adjacent to the recess 50) into an exhaust manifold 66. The exhaust manifold is also connected to external fluid receiving means through a port 68 provided in cover plate 36.
Although the inertia forces associated with a hollow vane such as 52 are quite small, it is preferable in larger units to use a balancing member 70 which is ident;cally shaped to the vane 52 but has a smaller diameter and weighs just as much. The balancing member is located at 180 with respect to the vane 52 and reciprocates parallel to the shaft within a channel 72 provided in median wall l4 and parallel to vane .
channel 46; its role is to reduce the level of vibration.
Leaks across various running clearances between , parts in relative motions are m,inimized by relatively wide mating surfaces, such as recesses 34, 48 and 50 and also by grooves ;n these mat;ng surfaces. Each such groove acts as a cavity interposed between the regions of higher and lower pressures; the c'avity fills up with fluid and the resulting inflow and outflow are substantially smaller than the leakage flow which would have ex;sted otherw;se in the absence of the cavity. Indeed, each radial segment 34 has a radial groove 74 in its central port;on; each cam 24 has a circular groove ' 76 and long;tudinal serrat;ons 78 aruund its outer periphery and another circular groove 80 around its inner periphery.
The longitudinal concave recesses 50 and 48 have longitudinal grooves 82 and 83, respectively, located in their middle.
The hollow interior of vane 52 acts as a leak reducing cavity.
The cover at the shaft's drive end is equipped with an axial seal assembly which consists of: a stationary sealing disc 86 having an appropriate bearing surface and secured to the cover plate 36, a rotating sealing disc 87 slidably mounted on shaft 26 and spring loaded against disc 87 by a spring 88.
An "O"ring 84 in the sealing disc 87 prevents leakage along the shaft.
The pressure builds up behind the cams 24 because of the axial seal assembly and the closed cover plate at the other end of the mechanism; this in turn causes a further reduction in leaks and a d;minished axial load on the roller bearings.
The inlet ports 60 and the outlet ports 64 located ;n the cylindrical interior profile of the chambers are progressively uncovered by the outer peripheries of the cam members as the rate of volume change increases, the maximum occurring when the vane is fully extended. This feature provides constant speed of flow through the ports if the fluid is a liquid; moreover, the combined inflow rate to both halves of the mechanism remains also constant, the same occurring wi th the outflow; the result is r;pple-free flow. Furthermore, the theoret;cal torque absorbed or developed by the mechanism remains substantially constant and provides a smooth operation. The intermediate pressure established on the vanes end surfaces and on the balancing member 70 end surfaces has a balancing effect and allows a smooth travel of these members over the inclined surfaces. In addition to their sealing roles, the longitudinal ' recesses 48 and 50 act as effective guides and bearing surfaces for vane 52 and allow the use of long strokes and high pressure differences in the mechanism.
For rotary axial vane mechanisms of relatively small size, the inner cylindrical wall portio.ns 20 are preferably bolted to the median wall.14 rather. than being an integral part thereof as shown in the drawings; this provides an easier machining of the conical surfaces 16; the vane 52 may also be made of solid l;ghtweight material and the roller bearings may be replaced with plain bushings, self-lubricated or not.
The rotary mechanism of.the present invention operates as a motor if the fluid at the intake is at higher pressure than at thé exhaust and it operates as a pump in the opposite case. The pressure difference between a set of two working chambers is exerted on the respective inclined faces and produces a resisting or a.driving torque on the shaft as the case may be.
With equal sized ports, the mechanism shown in Fig.
1 is both reversible in direction and function. It could ~ 8~
operate as a gas motor in which case the gas is discharged without any expansion within the working chamber; the resulting higher gas consumption is, however, tolerable in small sized motors where compactness is essential.
By providing automatic discharge valves at the exhaust ports 64, the mechanism of Fig. 1 could be operated as a gas compressor. Fig. 3 shows a reed valve 90 secured midway to the median wall 14; the ports are equipped with valve seats 92a, 92b and the access to the valve assembly is provided by an opening 94 in the outlet manifold 66; this opening is closed with a cover (not shown).
Fig. 4 shows a cross-section through the median wall 14' of a variant of the present invent;on where the solid vane 52' carries, around its outside, four fluid transfer passages ~6 which consist of- longitudinal grooves communicating cycli-cally with ports 60' and 64' located in the median wall. Such an arrangement-eliminates-the ports and the-ma-nifolds in th-e outer cylindrical walls; i~ is, however, applicable only to small units because of the inherent limitations of the transfer passages.
Fig. 5 shows an energy converting mechanism 100 in ~ccordance with the present invention which retains the basic principles of the unit shown in Fig. 1, but is designed par-ticularly for gases; it provides a built-in compression or expansion ratio, as the case may be. The unit, as shown, has three equally spaced vanes 102 (I, II, III) within channels 104 (I, II, III) made in housing 106; these vanes are hollow and closed at both ends as shown in Fig. 6, they may also be solid. The housing 106 is the rotor and is keyed to the shaft 108 by appropriate means (not shown). The pair of cams 110 with inclined surfaces 112 are fixed at their respective bottoms of the two outer casing halves 114i these halves are bolted toge~her and contain appropriate inlet and outlet manifolds (not shown) as well as attachment lugs 116. In a sl;ghtly different arrangement ~not illustrated), the outer casing may consist of a pipe-like portion closed at both ends with covers containing the cams and the means for external support. The covers are bolted to the pipe or held together with tie bolts. The inlet ports 118 and outlet ports 120 are located in the inclined surfaces 112 and communicate with their respective manifolds in the outer casings 114. The inclined surfaces engage the respect;ve con;cal surfaces 122 of the rotor over recessed segments 124; this feature means that in a compressor of this design, the clearance space is almost nil. The number of vanes dictates the compression or expansion ratio attainable in the device; a minimum of two vanes is required for effecting compression or expansion and for balancing centrifugal forces as well as reduci-ng the vibrations.
The ratio is defined as that between the maximum volume confined between two consecutive vanes and the volume reached as the leading vane is just uncovering the outlet port. The com-pression ratio for three vanes is about 4.3. In the position shown in Fig. 5 and considering the direction of ro~ation when operating as compressor, the vane 102-I is expelling the gas through port 120b; the gas confined between the vanes 102-III ànd 102-I is being compressed; the space between 102-II
and 102-III is being f;lled with fresh gas arriving through port 118b.
In a device operating as a gas motor, the high pressure gas is admitted through port 120b and the force exerted on vane 102-I drives the rotor 106 ln the opposite direction to that of the arrow 126. When the next vane 102-II
., . .. , . , :. :
p~sses by port l20b, the working chamber between 102-I and 102-II stops being.charged with h;gh pressure gas; as the rotor continues to turn, this charge expands until the volume of the working chambers reaches a maximum (this happens when the vane 102- I i s at 240 and 20- I I at 120 with respect to the radial segment 124b, the angles being measured in the direction of rotation); further rotation brings ~he expanded gas in communication with port 118b through which it is dis-charged. Some compression occurs as the vanes approach the radial segment after.having discharged the gas and helps ;n reducing leaks across the segment.
The a~orementioned compression or expansion oper-ations occur for any numbers of vanes exceeding one, the only difference being the compression or expansion ratios attained in the operation.
As compared with the rotating cam design, the fixed cam approach.ne-cessitates more complicated inlet and outlet manifolds s;nce the ports in the two halves are on the opposlte sides. On the other hand, the fixed cam design provides a larger displacement within the same frame.
The features used in the rotating cam design for reducing the various leaks are also incorporated in the .fixed cam designs. The end faces of the outer and inner cylindrical walls 128 are prov;ded with circular grooves 130 and 132 and the closed ends of the vanes include small recessed cavities 174. Sealing can be substantially improved by injecting oil in the working chambers, which provides, at the same time, lubrication and internal cooling. The oil must be subsequently separated from the discharged mixture, cooled, and sent to a tank from which it is drawn again into an active cycle.
~, ' Figures 7, 8 and 9 show a variation of a multi-vane design: the aforementioned radial segmen~s do not ex;st because the conical surfaces of the median wall are now replaced with plane annular surfaces 134. The unit contains two close-end vanes sliding in bores 136-I and 136-II located at 180 from one another. The ports 138 and 140 of the cams 142 are located in the inclined surfaces 144, on the minor axis 145 of the ellipses defined by the inner and outer peripheries of the cam surfaces 144 and are fully covered and uncovered by the vanes as they rotate with the rotor. If the rotor turns as shown by arrow 146 in Fig. 7, port 140 stays in communication with an expanding working chamber while port 138 does the opposite; the fluid is drawn in through 140 and expelled through 138. Because the m;nimum volumes of the working chambers are quite substantia-l, this arrangement is best suited for pumps and motors using liquids.
The side-by-side location of the two halves in any energy converter in accordance with the present invention lends itself very well to the use of two different functions in the two halves provided the two fluids are compatible with each other from a chemical standpoint. The choice of a particular design (fixed or rotary cams) depends upon the nature of fluids involved.
In one such variation, one side acts as a fluid motor driven from a source of high pressure fluid whereas the other side acts as a l;quid pump, vacuum pump or compressor for a second fluid. In another variation, one side acts as a first stage pump for a liquid while the other acts as the second stage.
In still another variation, one side acts as a first stage compressor while the other acts as the second stage, the fluid being intercooled between stages. Such a compressor contains four vanes and fixed inclined cam surfaces as shown in Figs. lOa and lOb. The "a" side acts as the first stage while the "b" side acts as the second stage. The port ar-rangement shown on the inclined surfaces 146a, 146b corresponds to the direction of rotation of the rotor as indicated by arrow 148 in Fig. 11. ~he ports 149 are for admission, while ports 150 are for evacuation. Their wide variations in size result from the fact that the physically equal displacements of both sides have to be drastically modified to accommodate the variations in densities in the second stages.
If the gas admitted in the first stage is air from an enclosure and is discharged into the atmosphere at the second stage outlet, the resulting mechanism is a two stage vacuum pump.
Another embodiment consists of one side acting as an internal combustion engine with fuel injection and plug ignition, and the second side acting as a compressor. The embodiment uses the fixed cam approach with a rotor which possesses three vanes. The compressor section is built and operates in the manner already described above. The internal combustion engine presents several features which appear in the Figs. 12 and 13; the inclined cam surface 151 maintains a certain clearance with respect to the conical surface of the median wall in the housing and contains an exhaust port 152, an admission port 154? a fuel injection nozzle 156, and an ignition plug 158.
In Fig. 14a, the vane 160-II has just passed the ignition plug and is expelling the combustion gases previously generated between vanes 160-I and 160-II. Vane 160-III has just passed the fuel injection nozzle and the compressed air-fuel mixture trapped between 160-II and 160-III is ignited at the plug end. Vane 160-I is starting to compress the air previously admitted between 160-I and 160--III and the fuel in3ection nozzlè is just starting to inject fuel into the a;r being compressed.
In Fig. 14b, vane 160-II is pushed by the burning mixture and the expanding gases confined between 160-II and 160-III; vane 160-II continues to expell the exhaust gases through port 152 while simultaneously air from a supercharger driven by the engine itself is being admitted through port 154.
Tlle supercharged air is oriented towards vane 160-I by the 'inclinat;on of port 154 and tends to f;ll the space to the right thereof before escaping partly through port 152, thereby providing a scavenging action. The charge in the working chamber between 160-I and 160-III is being compressed and, at the same time, enriched by the incoming fuel through the injection nozzle 15-6-. In the working chamber between 160 and 160-III, the flame front ~ravels towards the approaching vane 160-III thereby providing a good, progressive combustion;
simultaneously the already burnt gases expand towards vane 160-II.
In Fig. 14c, the three vanes have temporarily closed the ports, the plug and the nozzle; the working chamber between 160-I and 160-II contains supercharged air with very little residual exhaust gases left after the previous scavenging action; the working chamber between 160-I and 160-III contains a charge of fuel-air mixture of correct concentration and at high pressure, this charge being ready to ignite as soon as vane 160-III uncovers the ignition plug 158; the working chamber between 160-III and 160-II contains combustion gases which exert a pressure cn vanes 160-III and 160-II with the latter carrying a far greater forcei these gases are ready to be ex~elled as soon as vane 160-II uncovers port 152.
There are three explosions per revolution and there is always a net driving torque for driving the next room compressor and the other auxiliaries such as: fuel injection pump, the supercharger, etc. These aux;l;a-r;es are not shown nor discussed because they are like any other standard equipment used on existing engines. The fuel injection occu-rs continuously as the successive air charges between consecutive vanes are being compressed to the final pressure dictated by the compression ratio; the injection is interrupted only for a brief moment when a vane covers the nozzle.
The ignition plug could produce sparks at the right moments (hence, three sparks per revolut;on) or it could be o~
the type which remains continuously incandescent (glow plug) and ignites any fresh charge which contàcts it.
Since the combustion occurs always at the same location, the unit requires cooling which could be done by circulating oil through the rotor and the inclined cam surface 151.
Since oil flooding of the working chambers is imposs;ble, the sealing must rely on additional sealing elements such as the longitudinal strips 164 and 165 loca~ed as shown in Fig. 12, respectively, in grooves 166 in the outer cylindrical wall 168 and in grooves 170 in the inner cylindrical wall 172. The strips 164 are forced by the pressure differences against the longitudinal walls of the grooves and against the outer periphery of the respective vane. As already mentioned, and as shown in Fig. 6, the small cavities 174 at the inclined closed ends of the vanes reduce the leaks across the cam surface-vane end clearance.
. . . .
Sufficient lubrication is provided by the next room flooding with oil. The rotor crown has an external gear 176 which is engaged by the pinion of a starting motor.
If the compressor section is replaced with another identical internal combustion engine section, the resulting combination would be an internal combustion engine capable of dr;ving loads outside its own frame. Such an arrangement requires a lubricating oil pump in addition to all the other auxiliaries already mentioned.
Irrespective of the particular arrangements used in the above-listed patents, these mechanisms share several common disadvantages:
(a~ cams and slots are expensive to make;
~b) vanes are too weak For long strokes and/or large pressures;
(c) sliding friction between vanes in cases where several vanes work in the same slot is high and causes sticking and wear;
(d) cam-vane contact is limited to almost a linei hence~
poor sealing and excessive wear;
(e) vane-channel contact surface is quite limited; hence, leakage and wear;
(f) in cases where the vanes rotate, the centrifugal forces cause wear along the narrow longitudinal edge of the vanes; and (g) the contact line between the cam and the median wall allows large leaks.
OBJECTS ARD STATEMENTS OF THE INVENTIQN
One object of the present invention is to overcome most-of the d;sadvantages listed above w;th respect to prior rotary mechanisms and to provide an axial rotary vane mechanism adaptable to various functional applications.
The operation of the mechanism of the present invention is based on the relative rotation imparted between two inclined cam surfaces and a housing which contains at least one transverse channel in its central wall and a cylindrical ~ane located in this channel; the vane has two end surfaces remaining in continuous sliding contact with their corre sponding cam surface. This relative rotation results in the longitudinal reciprocating movement of the vane and in its rotation about its own axis.
The present invention therefore relates, in its broadest aspect, to a rotary axial vane mechanism which includes:
a hous;ng having a generally cylindrically shaped interior profile and a median wall; means, located centrally of the interior profité, having a generally cylindrical outer surface defining with ~he interior profile and the median wall, on OppQSite sides thereof, two separate annular chambers; a pair of cam means respect;vely mounted in each chamber opposite to the median wall, the cam means having coactingly shaped plane surfaces`parallel to one another and in.clined with respect to the longitudinal axis of the interior profile; at least one cylindrical channel means extending through the median wall and having an axis parallel to the longitudinal axis;
cylindrical vane means slidably and rotatably mounted in the 1~ channel means, the vane means having opposite inclined end 1¦
walls ;n coacting engagement with the cam surfàces whereby relative rotation between the housing and the cam means results in the rotation and in the longitudinal translation of the vane means in the channel means.
The such defined mechanism may be uti-lized-in a pump, an hydraulic motor, a compressor, a vacuum pump, a pneumatic mo~or, a steam motor, an internal combustion engine and the ¦
like.
Other objects and further scope of applicability of the present invention will become apparent from the detailed description given hereinafteri it should be understood however that this description, while indicating preferred embodiments of the invention, is given by way of illustration only since various changes and modifications within the spirit and scope o~ the invention will become apparent to those skîlled in the art from reading this description. One such mod;Fication would involve separate chambers of different sizes, hence of cylindrical channels and cylindrical vanes having two portions of two differen~ diameters.
BRIEF DESCRIPTION OF THE DRAWINGS
Figuré 1 is a perspective exploded view of a rotary mechani sm wi th rotati ng cam members and s~ationary housing in accordance with one embodiment of the present invention, part of one end cover and of the central cas.ing having been omitted for clarity;
Figure 2 is an elevational cross-sec~ional view of the rotary mechanism shown in Fig. l;
Figure 3 is a sectional perspective view of the dis-charge ports, manifold and valving which may be used in a mechanism such as t~e one illustrated in Fig. l;
Figure 4 is a transverse cross-section through the median wall of a variant of the mechanism shown in Fig. 1 `
' illustrating transfer passages in a vane;
Figure 5 is a perspective exploded view of a rotary mechanism with fixed cams and rotary housing in accordance with anothe.r embodiment sf-the present invention, one half of the casing, parts of the rotary housing and of the second half of the casing having been omitted for-clarity;
Figure 6 is a longitudinal cross-sè~tion through a hollow vane with closed ends;
Figures 7 and 8 are, respectively, an elevational end view and a longitudinal cross-sectional view of the rotary portion of a mechanism made in accordance with the present invention with plane annular surface on the median walli Figure 9 is a perspective view of a fixed cam member cooperating with the rotor portion illustrated in Figures 7 and 8;
Figure lOa is a perspective view of a fixed cam member in the first half stage of a second-stage compressor constructed in accordance with the present inventioni Figure lOb is a perspective view of a fixed cam member in the sécond half stage of the said second~stage compressor;
Figure 11 is an elevational side view of a rotor cooperating with the cam members oF Figs. lOa and lOb;
F;gure 12 ;s an elevat;onal end v;ew of a rotor ;n an internal combustion engine in accordance with the present invention;
Figure 13 is a perspective view of a cam member cooperating with the rotor of Fig. 12;
Figures 14a, 14b, 14c are end views of the cam member 1 .
of F;g. 13 with the successive positions of the three vanes.
DESCRIPTION OF PREFERRED EMBODIMENTS
In the following description, the same reference numerals will be used to designate identicai parts and .
configurations. As the rotary axial vane mechanism of the present invent;.on ;nclude.s.two separate s;des divided by a central wall and having therein generally iden~ical parts and 1.
configurations in the.drawings, the refe.rence numerals shown on the left-hand side of the central wall will bear the subscript "a" while those on the right-hand side will bear the 20 subscript "b". :
The mechanism shown in Figs. 1 and 2 ill.ustrates a stationary housing 10 having a generally cylindrically shaped interior profile 12 separated by a centrally disposed partition median wall 14 having outer opposite identical conical surfaces 16 and cylindrical extensions 20. Each ;nterior profile 12, conical surface 16 and cylindrical extension 20 define an annular chamber 18 These chambers 18 are closed by a pair of cam members 24, each haYing an inclined plane surface 22; these cam members are identically shaped and their surfaces 22 are parallel to one another and inclined with respect to a central shaft 26 which longitudinally traverses the housing 10. The .
~ 8~
angle which the cam surfaces 22 make with the longitudinal axis of the shaft is the same as the vertex angle o~ the conical sur~aces 16. The cam members 24 are fixedly mounted on shaft 26 by appropr;ate keys 27 received in grooves 28 so that the inclined surface planes remain constantly parallel to one another. By being keyed to the shaft 26 in the position shown in Figures 1 and 2, the long;tud;nal d;stance separating the inclined surfaces 22 is constant. The outer and inner ellipt;cal per;pheries 30 and 32 of each cam surface maintain small running clearances with respect to the outer and inner cylindr;cal walls 12 and 20 of chambers 18. Each ;nclined face ' of the cam members has a recessed radial segment 34 which engages with the respective conical surface 16 across a small running clearance. The housing 10 is closed at its opposite ends by two cover plates 36 by means of bolts 38. These plates contain the outer races 40 of tapered roller bearings 42, the inner races of which are mounted on shoulders 44 of the respective cam members; this arrangement offloads the shaft of bending stresses.
A cylindrically shaped channel 46 in the median wall 14 extends parallel to the axis o~ shaft 26 and has a diameter sligh~ly exceeding the annular width o~ chambers 18. The inner walls 20 and the outer walls 12 include oppositely facing concave recesses 48 and 50 which def;ne arc surfaces in ~rolongation with the inner wall surface of channel 46 so that a cylindrical vane 52 may extend through channel ~6 and be contained between the opposite recesses 48 and 50. The cylindrical vane 52 has opposite end walls 5~ and 56 which are inclined and parallel to one another and which make the same angle as the inclined plan~ surfaces 22 with respect to the shaft 26. The iength of vane 52 is substantially equal to the constant distance separating the cam surfaces 22 so that the inclined faces 54,5~ of the vanes are constantly in contact with the cam surfaces.
Vane 52 and each recessed segment 34 divides each corresponding chamber into two working chambers; as the sha~t rotates, so do the inclined cam surfaces and the vane is forced tO reciprocate longitudinally and to turn once around its own axis for every turn of shaft 26. Simultaneously, the recessed se9ment 34 revolves with the inclined cam surface and together with the vane causes a cycl;c volume change for each of the corresponding two working chambers. The volume changes in the two working chambers of ~he other half occur with a phase angle of 180. The increasing volume of a working chamber draws in fluid from an intake manifold 58 through a port 60 extending longitudinally in each interior pro~ile of the housing lO along the recess 50;-the:manifold~58 is connected to appropriate fluid drawing means.through port.62.in the cover plate 36. Simultaneously, the decreasing volume of the second working chamber expells the fluid, already admitted during the previous cycle, through a port (not shown but extending longitudinally and adjacent to the recess 50) into an exhaust manifold 66. The exhaust manifold is also connected to external fluid receiving means through a port 68 provided in cover plate 36.
Although the inertia forces associated with a hollow vane such as 52 are quite small, it is preferable in larger units to use a balancing member 70 which is ident;cally shaped to the vane 52 but has a smaller diameter and weighs just as much. The balancing member is located at 180 with respect to the vane 52 and reciprocates parallel to the shaft within a channel 72 provided in median wall l4 and parallel to vane .
channel 46; its role is to reduce the level of vibration.
Leaks across various running clearances between , parts in relative motions are m,inimized by relatively wide mating surfaces, such as recesses 34, 48 and 50 and also by grooves ;n these mat;ng surfaces. Each such groove acts as a cavity interposed between the regions of higher and lower pressures; the c'avity fills up with fluid and the resulting inflow and outflow are substantially smaller than the leakage flow which would have ex;sted otherw;se in the absence of the cavity. Indeed, each radial segment 34 has a radial groove 74 in its central port;on; each cam 24 has a circular groove ' 76 and long;tudinal serrat;ons 78 aruund its outer periphery and another circular groove 80 around its inner periphery.
The longitudinal concave recesses 50 and 48 have longitudinal grooves 82 and 83, respectively, located in their middle.
The hollow interior of vane 52 acts as a leak reducing cavity.
The cover at the shaft's drive end is equipped with an axial seal assembly which consists of: a stationary sealing disc 86 having an appropriate bearing surface and secured to the cover plate 36, a rotating sealing disc 87 slidably mounted on shaft 26 and spring loaded against disc 87 by a spring 88.
An "O"ring 84 in the sealing disc 87 prevents leakage along the shaft.
The pressure builds up behind the cams 24 because of the axial seal assembly and the closed cover plate at the other end of the mechanism; this in turn causes a further reduction in leaks and a d;minished axial load on the roller bearings.
The inlet ports 60 and the outlet ports 64 located ;n the cylindrical interior profile of the chambers are progressively uncovered by the outer peripheries of the cam members as the rate of volume change increases, the maximum occurring when the vane is fully extended. This feature provides constant speed of flow through the ports if the fluid is a liquid; moreover, the combined inflow rate to both halves of the mechanism remains also constant, the same occurring wi th the outflow; the result is r;pple-free flow. Furthermore, the theoret;cal torque absorbed or developed by the mechanism remains substantially constant and provides a smooth operation. The intermediate pressure established on the vanes end surfaces and on the balancing member 70 end surfaces has a balancing effect and allows a smooth travel of these members over the inclined surfaces. In addition to their sealing roles, the longitudinal ' recesses 48 and 50 act as effective guides and bearing surfaces for vane 52 and allow the use of long strokes and high pressure differences in the mechanism.
For rotary axial vane mechanisms of relatively small size, the inner cylindrical wall portio.ns 20 are preferably bolted to the median wall.14 rather. than being an integral part thereof as shown in the drawings; this provides an easier machining of the conical surfaces 16; the vane 52 may also be made of solid l;ghtweight material and the roller bearings may be replaced with plain bushings, self-lubricated or not.
The rotary mechanism of.the present invention operates as a motor if the fluid at the intake is at higher pressure than at thé exhaust and it operates as a pump in the opposite case. The pressure difference between a set of two working chambers is exerted on the respective inclined faces and produces a resisting or a.driving torque on the shaft as the case may be.
With equal sized ports, the mechanism shown in Fig.
1 is both reversible in direction and function. It could ~ 8~
operate as a gas motor in which case the gas is discharged without any expansion within the working chamber; the resulting higher gas consumption is, however, tolerable in small sized motors where compactness is essential.
By providing automatic discharge valves at the exhaust ports 64, the mechanism of Fig. 1 could be operated as a gas compressor. Fig. 3 shows a reed valve 90 secured midway to the median wall 14; the ports are equipped with valve seats 92a, 92b and the access to the valve assembly is provided by an opening 94 in the outlet manifold 66; this opening is closed with a cover (not shown).
Fig. 4 shows a cross-section through the median wall 14' of a variant of the present invent;on where the solid vane 52' carries, around its outside, four fluid transfer passages ~6 which consist of- longitudinal grooves communicating cycli-cally with ports 60' and 64' located in the median wall. Such an arrangement-eliminates-the ports and the-ma-nifolds in th-e outer cylindrical walls; i~ is, however, applicable only to small units because of the inherent limitations of the transfer passages.
Fig. 5 shows an energy converting mechanism 100 in ~ccordance with the present invention which retains the basic principles of the unit shown in Fig. 1, but is designed par-ticularly for gases; it provides a built-in compression or expansion ratio, as the case may be. The unit, as shown, has three equally spaced vanes 102 (I, II, III) within channels 104 (I, II, III) made in housing 106; these vanes are hollow and closed at both ends as shown in Fig. 6, they may also be solid. The housing 106 is the rotor and is keyed to the shaft 108 by appropriate means (not shown). The pair of cams 110 with inclined surfaces 112 are fixed at their respective bottoms of the two outer casing halves 114i these halves are bolted toge~her and contain appropriate inlet and outlet manifolds (not shown) as well as attachment lugs 116. In a sl;ghtly different arrangement ~not illustrated), the outer casing may consist of a pipe-like portion closed at both ends with covers containing the cams and the means for external support. The covers are bolted to the pipe or held together with tie bolts. The inlet ports 118 and outlet ports 120 are located in the inclined surfaces 112 and communicate with their respective manifolds in the outer casings 114. The inclined surfaces engage the respect;ve con;cal surfaces 122 of the rotor over recessed segments 124; this feature means that in a compressor of this design, the clearance space is almost nil. The number of vanes dictates the compression or expansion ratio attainable in the device; a minimum of two vanes is required for effecting compression or expansion and for balancing centrifugal forces as well as reduci-ng the vibrations.
The ratio is defined as that between the maximum volume confined between two consecutive vanes and the volume reached as the leading vane is just uncovering the outlet port. The com-pression ratio for three vanes is about 4.3. In the position shown in Fig. 5 and considering the direction of ro~ation when operating as compressor, the vane 102-I is expelling the gas through port 120b; the gas confined between the vanes 102-III ànd 102-I is being compressed; the space between 102-II
and 102-III is being f;lled with fresh gas arriving through port 118b.
In a device operating as a gas motor, the high pressure gas is admitted through port 120b and the force exerted on vane 102-I drives the rotor 106 ln the opposite direction to that of the arrow 126. When the next vane 102-II
., . .. , . , :. :
p~sses by port l20b, the working chamber between 102-I and 102-II stops being.charged with h;gh pressure gas; as the rotor continues to turn, this charge expands until the volume of the working chambers reaches a maximum (this happens when the vane 102- I i s at 240 and 20- I I at 120 with respect to the radial segment 124b, the angles being measured in the direction of rotation); further rotation brings ~he expanded gas in communication with port 118b through which it is dis-charged. Some compression occurs as the vanes approach the radial segment after.having discharged the gas and helps ;n reducing leaks across the segment.
The a~orementioned compression or expansion oper-ations occur for any numbers of vanes exceeding one, the only difference being the compression or expansion ratios attained in the operation.
As compared with the rotating cam design, the fixed cam approach.ne-cessitates more complicated inlet and outlet manifolds s;nce the ports in the two halves are on the opposlte sides. On the other hand, the fixed cam design provides a larger displacement within the same frame.
The features used in the rotating cam design for reducing the various leaks are also incorporated in the .fixed cam designs. The end faces of the outer and inner cylindrical walls 128 are prov;ded with circular grooves 130 and 132 and the closed ends of the vanes include small recessed cavities 174. Sealing can be substantially improved by injecting oil in the working chambers, which provides, at the same time, lubrication and internal cooling. The oil must be subsequently separated from the discharged mixture, cooled, and sent to a tank from which it is drawn again into an active cycle.
~, ' Figures 7, 8 and 9 show a variation of a multi-vane design: the aforementioned radial segmen~s do not ex;st because the conical surfaces of the median wall are now replaced with plane annular surfaces 134. The unit contains two close-end vanes sliding in bores 136-I and 136-II located at 180 from one another. The ports 138 and 140 of the cams 142 are located in the inclined surfaces 144, on the minor axis 145 of the ellipses defined by the inner and outer peripheries of the cam surfaces 144 and are fully covered and uncovered by the vanes as they rotate with the rotor. If the rotor turns as shown by arrow 146 in Fig. 7, port 140 stays in communication with an expanding working chamber while port 138 does the opposite; the fluid is drawn in through 140 and expelled through 138. Because the m;nimum volumes of the working chambers are quite substantia-l, this arrangement is best suited for pumps and motors using liquids.
The side-by-side location of the two halves in any energy converter in accordance with the present invention lends itself very well to the use of two different functions in the two halves provided the two fluids are compatible with each other from a chemical standpoint. The choice of a particular design (fixed or rotary cams) depends upon the nature of fluids involved.
In one such variation, one side acts as a fluid motor driven from a source of high pressure fluid whereas the other side acts as a l;quid pump, vacuum pump or compressor for a second fluid. In another variation, one side acts as a first stage pump for a liquid while the other acts as the second stage.
In still another variation, one side acts as a first stage compressor while the other acts as the second stage, the fluid being intercooled between stages. Such a compressor contains four vanes and fixed inclined cam surfaces as shown in Figs. lOa and lOb. The "a" side acts as the first stage while the "b" side acts as the second stage. The port ar-rangement shown on the inclined surfaces 146a, 146b corresponds to the direction of rotation of the rotor as indicated by arrow 148 in Fig. 11. ~he ports 149 are for admission, while ports 150 are for evacuation. Their wide variations in size result from the fact that the physically equal displacements of both sides have to be drastically modified to accommodate the variations in densities in the second stages.
If the gas admitted in the first stage is air from an enclosure and is discharged into the atmosphere at the second stage outlet, the resulting mechanism is a two stage vacuum pump.
Another embodiment consists of one side acting as an internal combustion engine with fuel injection and plug ignition, and the second side acting as a compressor. The embodiment uses the fixed cam approach with a rotor which possesses three vanes. The compressor section is built and operates in the manner already described above. The internal combustion engine presents several features which appear in the Figs. 12 and 13; the inclined cam surface 151 maintains a certain clearance with respect to the conical surface of the median wall in the housing and contains an exhaust port 152, an admission port 154? a fuel injection nozzle 156, and an ignition plug 158.
In Fig. 14a, the vane 160-II has just passed the ignition plug and is expelling the combustion gases previously generated between vanes 160-I and 160-II. Vane 160-III has just passed the fuel injection nozzle and the compressed air-fuel mixture trapped between 160-II and 160-III is ignited at the plug end. Vane 160-I is starting to compress the air previously admitted between 160-I and 160--III and the fuel in3ection nozzlè is just starting to inject fuel into the a;r being compressed.
In Fig. 14b, vane 160-II is pushed by the burning mixture and the expanding gases confined between 160-II and 160-III; vane 160-II continues to expell the exhaust gases through port 152 while simultaneously air from a supercharger driven by the engine itself is being admitted through port 154.
Tlle supercharged air is oriented towards vane 160-I by the 'inclinat;on of port 154 and tends to f;ll the space to the right thereof before escaping partly through port 152, thereby providing a scavenging action. The charge in the working chamber between 160-I and 160-III is being compressed and, at the same time, enriched by the incoming fuel through the injection nozzle 15-6-. In the working chamber between 160 and 160-III, the flame front ~ravels towards the approaching vane 160-III thereby providing a good, progressive combustion;
simultaneously the already burnt gases expand towards vane 160-II.
In Fig. 14c, the three vanes have temporarily closed the ports, the plug and the nozzle; the working chamber between 160-I and 160-II contains supercharged air with very little residual exhaust gases left after the previous scavenging action; the working chamber between 160-I and 160-III contains a charge of fuel-air mixture of correct concentration and at high pressure, this charge being ready to ignite as soon as vane 160-III uncovers the ignition plug 158; the working chamber between 160-III and 160-II contains combustion gases which exert a pressure cn vanes 160-III and 160-II with the latter carrying a far greater forcei these gases are ready to be ex~elled as soon as vane 160-II uncovers port 152.
There are three explosions per revolution and there is always a net driving torque for driving the next room compressor and the other auxiliaries such as: fuel injection pump, the supercharger, etc. These aux;l;a-r;es are not shown nor discussed because they are like any other standard equipment used on existing engines. The fuel injection occu-rs continuously as the successive air charges between consecutive vanes are being compressed to the final pressure dictated by the compression ratio; the injection is interrupted only for a brief moment when a vane covers the nozzle.
The ignition plug could produce sparks at the right moments (hence, three sparks per revolut;on) or it could be o~
the type which remains continuously incandescent (glow plug) and ignites any fresh charge which contàcts it.
Since the combustion occurs always at the same location, the unit requires cooling which could be done by circulating oil through the rotor and the inclined cam surface 151.
Since oil flooding of the working chambers is imposs;ble, the sealing must rely on additional sealing elements such as the longitudinal strips 164 and 165 loca~ed as shown in Fig. 12, respectively, in grooves 166 in the outer cylindrical wall 168 and in grooves 170 in the inner cylindrical wall 172. The strips 164 are forced by the pressure differences against the longitudinal walls of the grooves and against the outer periphery of the respective vane. As already mentioned, and as shown in Fig. 6, the small cavities 174 at the inclined closed ends of the vanes reduce the leaks across the cam surface-vane end clearance.
. . . .
Sufficient lubrication is provided by the next room flooding with oil. The rotor crown has an external gear 176 which is engaged by the pinion of a starting motor.
If the compressor section is replaced with another identical internal combustion engine section, the resulting combination would be an internal combustion engine capable of dr;ving loads outside its own frame. Such an arrangement requires a lubricating oil pump in addition to all the other auxiliaries already mentioned.
Claims (25)
1. In a rotary axial vane mechanism, (a) a housing having a generally cylindrically-shaped interior profile and a median wall;
(b) means, located centrally of said interior profile and on opposite sides of said median wall, having a generally cylindri-cal outer surface defining with said interior profile and said median wall two separate annular cavities;
(c) cam means, mounted in each cavity opposite said median wall, closing said cavities to define annular chambers, said cam means having coactingly shaped plane surfaces parallel to one another and inclined with respect to the longitudinal axis of said interior profile; said median wall including opposite conical surfaces having vertex angles equal to the angles made by said surfaces of said cam means with respect to said longitudinal axis; said surfaces of said cam means each including radial recessed segments extending from the outer periphery of said surface to the inner periphery thereof, each said recessed segment being in substantially sliding contact with the respective said conical surface;
(d) at least one cylindrical channel means extending through said median wall and having an axis parallel to said longitu-dinal axis;
(e) cylindrical vane means slidably and rotatably mounted in said channel means, said vane means being in coacting engagement with said interior profile of said housing and the outer surface of said centrally located means, said vane means having opposite inclined end walls in coacting engagement with said cam means surfaces whereby relative rotation between said housing and said cam means results in the rotation and in the longitudinal translation of said vane means in said channel means.
(b) means, located centrally of said interior profile and on opposite sides of said median wall, having a generally cylindri-cal outer surface defining with said interior profile and said median wall two separate annular cavities;
(c) cam means, mounted in each cavity opposite said median wall, closing said cavities to define annular chambers, said cam means having coactingly shaped plane surfaces parallel to one another and inclined with respect to the longitudinal axis of said interior profile; said median wall including opposite conical surfaces having vertex angles equal to the angles made by said surfaces of said cam means with respect to said longitudinal axis; said surfaces of said cam means each including radial recessed segments extending from the outer periphery of said surface to the inner periphery thereof, each said recessed segment being in substantially sliding contact with the respective said conical surface;
(d) at least one cylindrical channel means extending through said median wall and having an axis parallel to said longitu-dinal axis;
(e) cylindrical vane means slidably and rotatably mounted in said channel means, said vane means being in coacting engagement with said interior profile of said housing and the outer surface of said centrally located means, said vane means having opposite inclined end walls in coacting engagement with said cam means surfaces whereby relative rotation between said housing and said cam means results in the rotation and in the longitudinal translation of said vane means in said channel means.
2. In a rotary axial vane mechanism as defined in Claim 1, said centrally located means being extensions of said median wall; concave recesses in said extensions and in said interior profile, said recesses being oppositely disposed to receive therebetween said vane means.
3. In a rotary axial vane mechanism as defined in Claim 1, each said annular chamber communicating with fluid inlet and outlet means.
4. In a rotary axial vane mechanism as defined in Claim 1, shaft means longitudinally extending through said centrally located means, said shaft and said cam means being rotatable in said housing.
5. In a rotary axial vane mechanism as defined in Claim 1, said housing being rotatable while said cam means are stationary.
6. In a rotary axial vane mechanism as defined in Claims 3 and 4, said fluid inlet and outlet means containing inlet and outlet ports located in the interior profile of each annular chamber, on either side of said vane means; inlet and outlet manifolds in said housing in respective fluid communi-cation with said inlet and outlet ports; end covers confining lengthwise said housing; inlet and outlet openings in at least one of said end covers, said openings being in communication with the respective said inlet and outlet manifolds.
7. In a rotary axial vane mechanism as defined in Claims 3 and 4, said fluid outlet means comprising outlet ports made in said interior profile of each annular chamber; valve means located at said outlet ports to provide automatic fluid discharge.
8. In a rotary axial vane mechanism as defined in Claims 3 and 4, said fluid inlet and outlet means including fluid inlet and outlet ports consisting of longitudinal grooves in the outer periphery of said vane means and fluid inlet and outlet manifolds located within said median wall on either side of said each vane means.
9. In a rotary axial vane mechanism as defined in Claim 4, said median wall including a further channel means diametrically disposed relative to said channel means; a further vane means in said further channel means to provide in operation a reduction in the level of vibration.
10. In a rotary axial vane mechanism as claimed in Claim 4, said vane means being tubular.
11. In a rotary axial vane mechanism as claimed in Claim 5, two diametrically opposed channel means in said median wall; two identical vane means in said channel means;
said vane means having closed ends; said cam surfaces being defined by elliptically shaped inner and outer peripheries;
fluid inlet and outlet ports located in each said cam surface along the minor axis thereof.
said vane means having closed ends; said cam surfaces being defined by elliptically shaped inner and outer peripheries;
fluid inlet and outlet ports located in each said cam surface along the minor axis thereof.
12. In a rotary axial vane mechanism as defined in Claim 2, said concave recesses including leak reducing grooves extending therein.
13. In a rotary axial vane mechanism as defined in Claim 1, said radial recessed segments including leak reducing grooves extending therein.
14. In a rotary axial vane mechanism as defined in Claim 3, said fluid entering in both chambers at high pressure and being expelled from both chambers at lower pressure, the mechanism thereby producing mechanical work.
15. In a rotary axial vane mechanism, as defined in Claim 3, which is driven by a prime mover, fluid being admitted in both chambers at low pressure and being expelled from both chambers at higher pressure.
16. In a rotary axial vane mechanism as defined in Claim 3, one chamber receiving a fluid at high pressure and expelling said fluid at lower pressure while the other chamber receives another fluid at low pressure and expells said another fluid at higher pressure.
17. In a rotary axial vane mechanism as defined in Claim 14, the fluid expelled from a first chamber of the housing being readmitted into a second chamber of the housing.
18. In a rotary axial vane mechanism as defined in Claim 15, the fluid expelled from a first chamber of the housing being readmitted into a second chamber of the housing.
19. In a rotary axial vane mechanism as defined in Claim 5, three equidistantly spaced channel means extending through said median wall, three identical vane means in said channel means, said vane means having closed ends; fluid inlet and outlet means located in each cam surface; radial recessed segments extending from the outer periphery of said cam surface to the inner periphery thereof, each said recessed segment being in substantially slidable contact with the respective said conical surface.
20. In a rotary axial vane mechanism as defined in Claim 19, said closed ends of said vanes being slightly recessed with respect to said inclined end walls.
21. In a rotary axial vane mechanism as defined in Claim 19, said outlet ports being each located adjacent to said radial segment.
22. In a rotary axial vane mechanism as claimed in Claim 5, three equidistantly spaced channel means extending through said median wall, three identical vane means in said channel means, said vane means having closed ends; fluid inlet and outlet ports located on either side of a radial line on said cam surface said radial line being the farthest from the associated conical surface; fuel injection means and ignition means in said cam surfaces, the distance between said inlet and outlet ports, said fuel injection means and said ignition means being such that once per revolution they are simultane-ously covered by the end walls of said three vane means.
23. In a rotary axial vane mechanism as claimed in Claim 22, a predetermined clearance being maintained between each said conical surface and a radial line on said associated cam surface, said radial line being the closest thereto.
24. In a rotary axial vane mechanism as claimed in Claim 5, one of said cam surfaces being in substantially sliding contact with the associated conical surface, said one cam surface having an outlet port adjacent to a radial segment on said one cam surface which is the closest to said associated conical surface, the other of said cam surfaces maintaining a predetermined clearance between its associated conical surface and a radial line on said other cam surface which is the closest thereto; inlet and outlet ports in said other cam surface on either side of a radial line thereon, said radial line being the farthest from the associated conical surface;
fuel injection means and ignition means in said other cam surface, the distance between said inlet and outlet ports, said fuel injection means and said ignition means being such that, once per revolution, they are simultaneously covered by said vane means; three equidistantly spaced channel means extending through said median wall, three identical vane means in said channel means, said vane means having closed ends.
fuel injection means and ignition means in said other cam surface, the distance between said inlet and outlet ports, said fuel injection means and said ignition means being such that, once per revolution, they are simultaneously covered by said vane means; three equidistantly spaced channel means extending through said median wall, three identical vane means in said channel means, said vane means having closed ends.
25. In a rotary axial vane mechanism as defined in Claim 5, four equidistantly spaced channel means extending through said median wall; four identical vane means in said channel means, said vane means having closed ends; fluid inlet and outlet means located in each cam surface; radial recessed segments in each said cam surface r said recesses extending from the outer periphery of said surface to the inner periphery thereof, and being in substantially slidable contact with the respective said conical surface.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA301,168A CA1108009A (en) | 1978-04-14 | 1978-04-14 | Rotary axial vane mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA301,168A CA1108009A (en) | 1978-04-14 | 1978-04-14 | Rotary axial vane mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1108009A true CA1108009A (en) | 1981-09-01 |
Family
ID=4111242
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA301,168A Expired CA1108009A (en) | 1978-04-14 | 1978-04-14 | Rotary axial vane mechanism |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1108009A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4460319A (en) * | 1982-02-08 | 1984-07-17 | Baruir Ashikian | Two-stage rotary compressor |
| US4553903A (en) * | 1982-02-08 | 1985-11-19 | Baruir Ashikian | Two-stage rotary compressor |
| WO2014110659A1 (en) * | 2013-01-16 | 2014-07-24 | Albert's Generator Services Inc. | Compressor with rotating cam and sliding end vanes |
| US9695821B2 (en) | 2013-01-16 | 2017-07-04 | Albert's Generator Services Inc. | Compressor with rotating cam and sliding end vanes |
| US9964109B2 (en) | 2015-12-10 | 2018-05-08 | Albert's Generator Services Inc. | Apparatus for driving fluid having a rotating cam and rocker arm |
-
1978
- 1978-04-14 CA CA301,168A patent/CA1108009A/en not_active Expired
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4460319A (en) * | 1982-02-08 | 1984-07-17 | Baruir Ashikian | Two-stage rotary compressor |
| US4553903A (en) * | 1982-02-08 | 1985-11-19 | Baruir Ashikian | Two-stage rotary compressor |
| WO2014110659A1 (en) * | 2013-01-16 | 2014-07-24 | Albert's Generator Services Inc. | Compressor with rotating cam and sliding end vanes |
| US8985980B2 (en) | 2013-01-16 | 2015-03-24 | Alberts Generator services inc. | Compressor with rotating cam and sliding end vanes |
| US9695821B2 (en) | 2013-01-16 | 2017-07-04 | Albert's Generator Services Inc. | Compressor with rotating cam and sliding end vanes |
| US9964109B2 (en) | 2015-12-10 | 2018-05-08 | Albert's Generator Services Inc. | Apparatus for driving fluid having a rotating cam and rocker arm |
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