CA2145766A1 - Volumetric fluid machine equipped with pistons without connecting rods - Google Patents
Volumetric fluid machine equipped with pistons without connecting rodsInfo
- Publication number
- CA2145766A1 CA2145766A1 CA002145766A CA2145766A CA2145766A1 CA 2145766 A1 CA2145766 A1 CA 2145766A1 CA 002145766 A CA002145766 A CA 002145766A CA 2145766 A CA2145766 A CA 2145766A CA 2145766 A1 CA2145766 A1 CA 2145766A1
- Authority
- CA
- Canada
- Prior art keywords
- pistons
- axis
- liners
- fluid machine
- volumetric fluid
- 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.)
- Abandoned
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/22—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2035—Cylinder barrels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/22—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
- F04B1/24—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons inclined to the main shaft axis
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
Abstract
The volumetric machine for fluids, endothermic or not, have liners with non-linear or curved development, which are ma-chined, or not, in a rotating liner block (7, 45, 63, 75) on an axis that can be coinciding or passing with the axis of the shaft (1, 37), from the side of its center curvature; the pistons (5, 42, 59, 62) rotate with the liners, but on an inclined axis coinciding with the axis of rotation of the liners or passing through the same center, without the interposition of elements having alternate motion.
Description
~ WO94/10~2 2 ~ 4 5 716 6 PCT/1~2/0013~
DESCRIPTION OF THE INVENTION
VOLUMETIC FLUID MACHINE EQUIPPED WITH PISTONS WITHOUT CONNECTING RODS
The invention relates to a pump, compressor and/or an engine, which can also be endothermic, that while func-tioning, achieves a displacement by means of pistons con-nected to the driving shaft without oscillating connecting 10 rods. The displacement can, furthermore, be changed as wished if necessary.
The state of the art comprises in the field of endo-thermic engines: engines with alternative pistons which 15 are connected to the crankshaft with connecting rods; the volumetric lobe engine (Wankel), with rotor eccentric to the driving shaft, or engines which have axial pistons, i.e. parallel to the driving shaft and driven in the al-ternating motion with a circular sloped course in order to 20 achieve the axial displacement of the piston and which does not have high performance. In the field of pumps/en-gines or fluid compressors, both compressible and not, there are various known arrangements of the pistons in line, mounted axially, or with oscillating barrel or with 25 oscillating plate, or mounted be radially.
However, all above mentioned pistons are connected to the driving shaft with connecting rods, which are oscillating on a surface perpendicular to said shaft, or with connect-ing rods, in the case of axial pistons, which oscillate 30 when running on a conoid surface, because the inclination of course of the big end of the connecting rod has a vari-ation of range, while the small end is driven into the ~ liner by the piston.
The above mentioned mechanisms, exept the endothermic lo-35 be engine (Wankel), have large dimensions, and none have SUB~ I I ~ ~JTE S~E T
w094~0442 ~ 7~6 -2- PCT/IT92/001.~
high efficiency which depends on the conditions of utili-zation.
In particular:
- for the rotary lobe engine (Wankel), the sealing parts 5 have short life due to the heavy wear to which these are subject, with loss of compression and, therefore, loss of efficiency. The use of special materlals is required which are very expensive and difficult to obtain.
- The endothermic piston engines, in all their various 10 configurations, have limited speed of rotation, due to the presence of parts with alternating or oscillating motion, pistons, connecting rods, valves and also the crankshaft, which is always of difficult construction; the axial thrust from the piston is transmitted to the connecting 15 rod by the presence of the reaction of the cylinder wall:
this reaction causes heavy wearing and therefore high per-formance lubricating oils are needed for; in four-stroke engines, efficiency is reduced because of the impossibili-ty to design the combustion chamber in the ideal way due 20 to the dimensions and the restricted passage of the valves.
- As regards pumps/engines for compressible fluids, the disadvantages are the same as those caused by the con-necting rods in endothermic engines, with low efficiency 25 due to mechanical friction produced by these connecting rods, and high weight, dimensions and costs.
- As regards pumps/engines for incompressible fluids, typ-ically for hydrostatic trensmissions, but also for the pumping of other liquids, the various disigns, offer dis-30 tinguishing inconveniences, such as: pumps/engines withradial cylinder or cylinder in line, whilst providing fairly good performance, present high dimensions and con-struction costs; pumps/engines with axial cylinder, subdi-vided in the two following categories: cylinders with in-35 clined barrel, as regards the axis of the shaft, or with 214~766 inclined plate for the guidance of the big end and cylin-ders which are parallel to the axis of the shaft. Both first present inacceptable limitations of speed of rota-tion, caused by possible centrifugation of the big ends;
5 the second presents very low efficiency at the starting point and also impossibility of working in an open cir-cuit. The diffusion of both has beeen limited by the high construction costs.
From WO-A-86/00662 is known a piston machine of the kind in which an assembly of cylinders is arranged equi-distantly around a first axis of rotation and an assembly of corresponding pistons is arranged equi-distantly around a second axis of rotation; each piston comprising a ring 15 member that is displaceble laterally of the piston itself, to enable that ring member to move substantilly rectiline-arly of the corresponding cylinder whilst the piston it-self moves through a curved path relative thereto; the second axis passing to the center of the intersection with 20 the circular plane comprising that spherical ring members and said first axis. This machine, however eliminate a lot of parts with alternate motion, but have a lot of problems by way of the periodic shocks of that ring mem-bers during operation: no high performances are possible 25 if vibrations are generated and if friction is made by centrifugation and thrust of that ring members towards the cylinder surfaces.
From US-A-3910239 is known a piston power unit primari-30 ly for use as an internal combustion engine and having a single cylinder curved about a center, intake and exhaust ports at opposite ends of the cylinder, a pair of opposed pistons movable in the cylinder towards and away from each other in compression and power strokes, said pistons cov-35 ering these ports during most of their strokes, and suc-ENDED SltEET .
21~5~66 - 3a cessively opening the ports as the pistons approach the ends of their respective power strokes, a pair of crank shafts including intermeshing gears, and a~pair of connecting rods connecting the crankshafts to the pistons.
This piston engine presents problems for the thrust of the pistons towards the cylinder surface and its centrifugation increase the friction of that pistons towards the cylinder outwardly surface. Thus, no high performances are possible and this embodiment is usefull only for engines with assimetrical port timing, as clearly stated in the specification therein;
the improvements made from US-A-3338137 of the same inventor are for structural complications of construction only.
Such state of the art may be subject to large improvements as regards:
improving the characteristics of the mechanisms of reciprocating volumetric machines by increasing efficiency in all conditions, reducing weight, dimension and construction costs.
From what has been said so far the technical problem would be solved, in reciprocating volumetric machines, by eliminating all parts with oscillating motion, improving performances and in the same time reducing the dimensions and the weights.
The present invention solves the above-mentioned techical problem by adopting:
a volumetric fluid machine, endothermic or not, equipped with pistons, having reciprocating movement in the liner block without connecting rods, rigidly connected to the driving shaft or not, including mobile pistons AMEN~ED SHEE~
3b-?l~576~
inside linears, which are machined, or not, in a rotating liner block on an axis that can be coinciding or intersecting with the axis of the shaft;
the pistons rotate with the liners, but on an inclined axis coinciding with the axis of rotation of the liners or passing through the same center, without the interposition of elements having alternate motion, characterised in that the liners are of arched form, with its concavity turned towards said center, with center of curvature of their axis of rotation, that can be coinciding or passing, in the same center of curvature, as the axis of driving shaft; the pistons rotate in syncronism with the liners, but on an inclined axis coinciding with the axis of rotation of the liners or passing through the same center curvature;
adopting: the variation of the inclination between the axis of rotation of the liner block and of the.pistons, in order to obtain the variation of displacement;
adopting: pistons connected in a rigid or oscillating way to their shaft or rotation plate, without the interposition of connecting rods;
adopting: pistons with spherical head, equipped with seal rings which also have spherical faying surface, located in the piston head in such a way as to come into contact with respective liner wall radially with respect to the axis of that same liner;
adopting: the pistons are arched in the same way as the liners and are equipped with seal rings with spherical faying surface.
Adopting in the case of the internal combustion engine: a distribution plate, adjacent to the liner block with at least one communication port to - the liners for induction, at least one outlet port and at least one combustion chamber, that rotates or not with respect to the casing;
AMENDE0 S~E~T c:
21457~6 adopting: on the distribution plate, closed zones in intermediate positions, that coincide with the end position of scavenging fase and thus achieve null -volume in four-stroke cycles;
adopting: one single auxiliary cooling and lubricating circuit;
- 5 adopting: the liner block as the mobile part of the pump for the cooling and lubricating circuit.
Adopting, in the case of a volumetric machine for fluids:
AMENDED ~fEEr ` - `- -~
21~57~6 WO94/1~2 5 PCT/IT92/0013 either the piston-holder plate or the liner block keyed or rigidly connected to the shaft;
adopting: pistons with head connected rigidly to the shank, which is in turn rigidly connected to the rotating 5 plate that can be inclinable, inclined, or not adopting: oscillating piston heads with contact surface with the shank and contact surface with head of the con-necting bolt, also spherical and concentric;
adopting: the variation of the displacement obtained by 10 varying the inclination between pistons and liners, bear-ing on the plate whose rear surface is cylindrical surface with axis of rotation that passes through in the same crossing point between the axis of rotation of the liner block and pistons.
The advantages achieved by the present invention, for all types of volumetric machines for fluids, can be sumar-ized by the absence of parts in alternating and oscillat-ing motion, such as connecting rods, the traditional pis-20 tons and valves: all this leads to a considerable reduc-tion in noise, due to the absence of thrust elements that when oscillating create noise because of the unavoidable presence of clearances between components. The elimina-tion of the radial loading of the pistons on the walls of 25 the cylinder, because the.thrust of the fluid is always tangential to the curvature of the liner, which always co-incides with the center of the spherical piston, whether fixed or oscillating; consequently there is a considerable reduction in wearing and an increase in efficiency, spe-30 cially at starting-up in the case of volumetric devices;
there are fewer parts to be constructed and there is con-siderable reduction in swarf machining required; consider-- able reduction of the axial and radial dimensions of the machines, for the higher powers and efficiencies obtaina-35 ble. Particulary, for the internal combustion engines, WO94/10~2 6 PCT/1~2/0013 -5~6 problemg regarding centrifugation or elasticity that can increase rotation speed are eliminated; moreover, cooling is facilited both of the pistons from the internal part of the housing and of the rotating liner block, which can easily operate as a cooling liquid pump; the restintances and the choking of the valves are eliminated; the lubrica-tion and cooling circuits are not separate, as it is pos-sible to utilize the cooling liquid that has lubrication function too.
10 Furthermore, particulary for volumetric machines pumps/engines or compressors, compensation of the axial thrusts on the pistons being facilitates, further reduces friction and so increases efficiency; connecting members between the piston-holder plate and the liner block are 15 not required, which on the other hand are obligatory in barrel pumps or engines; the pistons with fixed spheric head connected to the piston-hoder are suitable for low or medium angles between the shaft and the inclined element (pistons or liner block) and enable high speeds to be ob-20 tained as there are no components subject to centrigfuga-tion. The pistons with oscillating head enable very large angles to be used and enablbling dimensions to be reduced even with large displacements. The heads, that self-cen-ter on the tangent at the line of curvature at any point 25 along the liner ned, therefore, on the thrust of the fluid, do not radially load the liner wall, limiting wear-ing and increasing efficiency.
Finally, the pumps of the hydraulic circuits can work in-differently in both open circuit and closed circuit at the 30 same speed of rotation, as there are no components of ar-ticulated elements (typically connecting rods) that could disconnect and centrifugate; the feeding of the closed circuit is obtainable also directly without the tradition-al use of the so called charge pumps; in the combination 35 of more pumps for different hydraulic circuits the pairing W094tlO~2 ; PCT/1192/00134 of more pumps on one same shaft, is easily achieved and with reduced dimensions; each of these pumps is sized and/or adjusted for the particular requirements of the circuit, avoiding the use of expensive mechanical couples.
A few embodiments of the invention are shown in the five drawing tables attached, in which: Figure 1 shows a sec-tion of an internal combustion engine, with four pistons and four-stroke cycle, in accordance with the invention;
10 Figure 2 is the side view of distribution plate faced on to the block of rotating liners; Figure 3 is a partial section of an ignition device of a two-stroke engine; Fig-ure 4 and figure 5 are views according to two lateral di-rections at 90 of the curved piston; Figure 6 is the lon-15 gitudinal section of a pump/engine or compressor forfluids, with variable displacement in both directions, with rotating and inclinable block of liners. Figure 7 is partial view from the supply side of the plate of inclina-tion and of the distribution of fluid to the block of ro-20 tating liners; Figure 8 is the section of a piston withoscillating head; Figure 9 is a longitudinal section of a pump/engine for fluids, the same as Figure 6, but with an inclinable piston holder plate instead of the liner block;
Figure 10 and 11 are the same views of Figure 4 and 5 but 25 for a piston not for internal combustion engine; Figure 12 is a sied view of a spherical piston; Figure 13 is the longitudinal section of a pump/engine for fluids, the same as Figures 6 and 9, without inversion of motion of fluid;
Figure 14 is a longitudinal section of a pump/engine for 30 fluids, the same as the previous Figure with both mecha-nism having a variable displacement.
- The indication are as follows: 1 (Figure 1) is the dri-ve shaft that rotates, on bearings in the housing 2 of the - 35 endothermic engine and positioned on each end 3 of the WO94/1~W2 2 1 4~ ~ 6 6 -8- PCT/1~2/0013 ~
shaft, each of which is coupled with piston pin 4 to the corrispondent curved piston 5; this last piston is driven from the mentioned ends to move inside the liners, which are machined in the rotating liner block 7; with 8 the 5 distribution plate, rotating on the ring 9; with 10 and 11 the exhaust pipe and induction pipe; with 12 the head, equipped with ignition plug 13, which is facing the piston in a position of maximum compression, through an anti-wear ring 14 and the combustion chamber 15, which is machined 10 in the thickness of the distribution plate; with 17 the spring for the recovery of clearances for the sealing be-tween distribution plate 8 and the liner block 7, which bears on the spherical articulation 18 of centering block of the shaft; with 19 guide bearings of the tube 20 the 15 distribution plate, comanded through internal coaxial shaft 21 rotating with the liner block 7 and through re-duction gearing of speed 22,23 and 24; with 26 refriger-ating duct of the distribution plate and of the manifold 10 and ll,and with analogous 27 duct in liner block; with 20 28 a radial hole in each liner for the assembly of the piston pin 4; with 29 the seal rings of the pistons 5, connected to the respective pin boss 30 through the piston pins at each end 3; with 31 and 32 (Figure 2) the holes and the suction ports on the distribution plate and with 25 33 and 34 the holes and the corrispondent exhaust ports;
with 35 (Figure 3) the chamber of combustion in the fixed distribution plate 36 of a two-stroke engine.
In the second embodiment of the invention, the indica-30 tions are as follow: with 37 (Figure 6) a drive shaft of the pumps/engine or volumetric compressor on which the piston holder plate 39 is splined, by means of a splined profile 38; the pistons are screwed on to the plate by means of a thread; with 40 the piston shank has a central 35 hole 41 of compensation of the axial hydraulic thrusts, 2~ S766 W094/10~2 PCT/~2/00134 it presents a head with a spherical swelling 42 and a seal ring 43 with external spherical swelling; the above men-tioned pistons are driven into the liners 44 of the rotat-ing liner block 45, which is driven to the mentioned shaft - 5 37 through a ball joint 46; with 47 the end clearances of the compensation springs acting on the mentioned joint and against the plate 39, which slides against the anti-wear lining 48 to which the compensation cavities 49 of the ax-ial hydraulic thrust are facing; with 50 the hole for the 10 passage of the fluid from the liner to the distribution cap 51, equipped with slots 52 and ports 53, on the side of the liner block 45, which is fed through ducts 54 and 55 for the passage of fluid; with 56 a slot on the axis distribution cap 51 for oscillation, which is driven from 15 the parallel surface, which couples with the envelope 58;
with 59 the head of the spherical piston, can oscillate on the shank 40 through a spherical headed screw 60 and a corrispondent spherical surface 61 between the shank and the piston head 59.
In the third embodiment of the invention, without repeat-ing the numbers of the common parts found in following Figures, are as follows; with 62 the curved piston, are mobile in the liners of the block 63, which presents fed-25 ing holes, facing the cover 65 with feeding lines of thefluid; with 66 a piston holder plate driven from the ball joint 46 and facing a corrispondent inclinable cap 67, with a parallel surface 68, against a block inserted 69 inside the envelope 58; with 70 the central axis of a cur-30 vature of the liners; with 71 (Figure lO) the seating ofthe seal ring 43 and with 72 the axis of the piston shank 40.
-Lastly, the indications shown are the following: with -- 35 73 (Figure 13) a plate which is splined on the shaft 37 by WO94/10~2 6 -10- PCT/1~2/0013.~
G
means of splined profile, and supports two series of pis-tons, which are connected to the plate and which are op-posed to one another, there are equipped with axial holes 74 for connection of the corrispondent chambers of the 5 liners; with 75 a liner block without feeding lines, ro-tating like block 45, but diesel ~ycle, starts the combus-tion through the special chamber 15 or 35, in the case of two-stroke engines that have the distribution plate fixed to the cylinder head 12; the drive of the coaxial driving 10 shaft 21, together with the wheel work 22,23 and 24, halves the rotation, because of the distribution plate control 8, through sleeve 20.
During the stroke of the pistons 5 inside the liners 6, the slight differences of path, which are also due to the 15 high angles between the the spin axis are compensated by slight oscillations on the gudgeon pins 4 in the hubs 30 besides slight radial slidings of the pistons in the in-termediate positions of 45, 135, 225 and 315 of rota-tion. The coolant is sucked from the radiator through the 20 pipe 25 and is conducted right into the liner block 7 through the hollow shaft 21; the holes 27 riceive the coolant by means of radial ducts, which are not shown in the drawing, and that are situated between the liners: the coolant is therefore centrifugated by the rotation of the 25 liner block and fills the internal volume of box 2 then hot it flows out of it, into tubes that are not shown in the drawing towards the radiator; the coolant, by means of the cavity wall between the sleeve 20 and the coaxial shaft 21, cools the central part of the distribution plate 30 8 and with the ducts it also cools the manifolds.
The functioning of the pump/engine or compressor for fluid refered to the second embodiment carried out occurs in the following way: the fluid under pressure, flowing in 35 the ducts 54 and 55 and crossing the slots 52, the parts ~
21457~6 W094/10442 -11- PCT/I~2/00134 53 and the holes 50, enters the liners 44; the action on the surface of the piston head 42 is distributed with re-lation to the position of the seal ring 43, i.e. exactly axial to the shank 40, without radial components driven 5 from the piston to the liners; the rotation that is im-pressed to the piston-holder plate 39 is driven to the driving a shaft 37 by splined fitting 38: the cavities 49, which are held at the same pressure of the liners 44 by the hole 41, balance the axial hydraulic thrusts on the 10 mentioned plate and on the pistons; the Belleville washers 47 stop the end clearances beteewen the liner block 45, the cap 51, and the envelope 58: the preloading is consid-erably superior to the force generated during the suction of the fluid at atmospheric pressure. The variation of 15 displacement and, therefore, a major versatility during use is possible by changing the inclination of the cap 51 by sliding on the cylindrical surface 57. The head of the oscillating piston 59, for the employment of the pistons and of the liners with ample angles between the axis of 20 rotation, results to be always balanced, because the cen-ter of oscillation is out of the piston and inside the fluid. On the contrary usual pistons, have the piston pin situaded considerably far from the surface in contact with the fluid.
The functioning of the pump/engine or compressor for fluids referred to the third type carried out, occurs in the following way: the keying position to the shaft 37 is inverted: i.e., it is the liner block 63 that drives the 30 couple: this disposition generates a radial component for the piston heads 62, rapidly wearing out the liners. The curved piston with head 62, results to be more adapted for - disposition with a high angle of inclination between the axis even if it is more difficult to construct. Also for 35 this realization, the variation of the displacement ob-wo 94~l0~2 ~ ~5~ 12- PCT/1~2/0013 ~
tained with the inclination of the cap, in this case number 67.
Figures 13 and 14 show two realizations for pumps/engines 5 or compressor for fluids, for use in different fields: the first is a pump/engine with a series of pistons of vari-able displacement and the other series of fixed displace-ment, in all without inversion of direction of the fluid;
the second is equipped with both the series of pistons 10 with variable displacement and the inversion of the flow, as indicated by the arrows next to the feeding lines 54,55 is possible; the caps 51 and/or 76 are to be inclined through external control with well known mechanisms. In both two realizations the piston-holder plate 73 keyed on 15 the driving-shaft 37, balances the axial thrust between the opposing liners 44 and being the axial holes 74 in the pistons, the less work is done by the fluid in passing through.
20 The functioning as a pump/compressor can comfortably oc-cur for all the angles of the cap (51 and/or 76), while when functioning as an engine, due to the known impossi-bility of zero setting the displacement, the angle must not be too reduced. Moreover, being the elimination of 25 the fluid motion between the two series of pistons of the double device in figures 13 and 14, which reduce the efficiency, the displacement in the mechanism of figure 13 must not be completely zero setted: the cap 76 must not be placed with opposed inclination to that figure; the dis-30 placement in the mechanism of figure 14 must not be variedby controlling the caps 76 and 51 inverted sincronism, therefore the caps 76 and 51 will result parallel when the displacement state is null, while they will result to be inclined as in the drawing or in opposing way due to the 35 flow of fluid in both directions respectively.
21~5766 If in practice materials, dimensions and operative de-tails should be different from those indicated, but tech-. nically equivalent, the patent will still apply.
- 5 In this way the pumptengine or compressor in Figures 6 or 9 can be obtained at a fixed displacement, or even a pump and an engine can be paired through the cavities 49 or the feeding ports 64, by interposing a fixed distributor to the housing, in order to carry out compact hydrostatic 10 drives: the advantages due to the reduction of dimensions, weight and to run high speed of rotation make this type of embodiment extremely interesting.
Finally, fixing the pistons rigidly to the housing and placing the liner block in oscillation by means of axial 15 or radial cam connected to the driving shaft, a pump/engine or compressor, without moving parts will be obtained with exception for the cam: this is very conven-ient in the case of pumps or engines for liquids. On the analogy of the displacement variation pumps engines or 20 compressor, it is possible to carry out, with the configu-ration of pistons 5, 42, 59 or 62, and of the rotating liner block 7 of the present invention, endothermic en-gines, that can reduce displacement, facilitating the mix-ing of the gasoline with air, without the complex artific-25 es that are employed at pFesent for the adjustment of itscomposition, achieving advantageous efficiencies at low charge.
DESCRIPTION OF THE INVENTION
VOLUMETIC FLUID MACHINE EQUIPPED WITH PISTONS WITHOUT CONNECTING RODS
The invention relates to a pump, compressor and/or an engine, which can also be endothermic, that while func-tioning, achieves a displacement by means of pistons con-nected to the driving shaft without oscillating connecting 10 rods. The displacement can, furthermore, be changed as wished if necessary.
The state of the art comprises in the field of endo-thermic engines: engines with alternative pistons which 15 are connected to the crankshaft with connecting rods; the volumetric lobe engine (Wankel), with rotor eccentric to the driving shaft, or engines which have axial pistons, i.e. parallel to the driving shaft and driven in the al-ternating motion with a circular sloped course in order to 20 achieve the axial displacement of the piston and which does not have high performance. In the field of pumps/en-gines or fluid compressors, both compressible and not, there are various known arrangements of the pistons in line, mounted axially, or with oscillating barrel or with 25 oscillating plate, or mounted be radially.
However, all above mentioned pistons are connected to the driving shaft with connecting rods, which are oscillating on a surface perpendicular to said shaft, or with connect-ing rods, in the case of axial pistons, which oscillate 30 when running on a conoid surface, because the inclination of course of the big end of the connecting rod has a vari-ation of range, while the small end is driven into the ~ liner by the piston.
The above mentioned mechanisms, exept the endothermic lo-35 be engine (Wankel), have large dimensions, and none have SUB~ I I ~ ~JTE S~E T
w094~0442 ~ 7~6 -2- PCT/IT92/001.~
high efficiency which depends on the conditions of utili-zation.
In particular:
- for the rotary lobe engine (Wankel), the sealing parts 5 have short life due to the heavy wear to which these are subject, with loss of compression and, therefore, loss of efficiency. The use of special materlals is required which are very expensive and difficult to obtain.
- The endothermic piston engines, in all their various 10 configurations, have limited speed of rotation, due to the presence of parts with alternating or oscillating motion, pistons, connecting rods, valves and also the crankshaft, which is always of difficult construction; the axial thrust from the piston is transmitted to the connecting 15 rod by the presence of the reaction of the cylinder wall:
this reaction causes heavy wearing and therefore high per-formance lubricating oils are needed for; in four-stroke engines, efficiency is reduced because of the impossibili-ty to design the combustion chamber in the ideal way due 20 to the dimensions and the restricted passage of the valves.
- As regards pumps/engines for compressible fluids, the disadvantages are the same as those caused by the con-necting rods in endothermic engines, with low efficiency 25 due to mechanical friction produced by these connecting rods, and high weight, dimensions and costs.
- As regards pumps/engines for incompressible fluids, typ-ically for hydrostatic trensmissions, but also for the pumping of other liquids, the various disigns, offer dis-30 tinguishing inconveniences, such as: pumps/engines withradial cylinder or cylinder in line, whilst providing fairly good performance, present high dimensions and con-struction costs; pumps/engines with axial cylinder, subdi-vided in the two following categories: cylinders with in-35 clined barrel, as regards the axis of the shaft, or with 214~766 inclined plate for the guidance of the big end and cylin-ders which are parallel to the axis of the shaft. Both first present inacceptable limitations of speed of rota-tion, caused by possible centrifugation of the big ends;
5 the second presents very low efficiency at the starting point and also impossibility of working in an open cir-cuit. The diffusion of both has beeen limited by the high construction costs.
From WO-A-86/00662 is known a piston machine of the kind in which an assembly of cylinders is arranged equi-distantly around a first axis of rotation and an assembly of corresponding pistons is arranged equi-distantly around a second axis of rotation; each piston comprising a ring 15 member that is displaceble laterally of the piston itself, to enable that ring member to move substantilly rectiline-arly of the corresponding cylinder whilst the piston it-self moves through a curved path relative thereto; the second axis passing to the center of the intersection with 20 the circular plane comprising that spherical ring members and said first axis. This machine, however eliminate a lot of parts with alternate motion, but have a lot of problems by way of the periodic shocks of that ring mem-bers during operation: no high performances are possible 25 if vibrations are generated and if friction is made by centrifugation and thrust of that ring members towards the cylinder surfaces.
From US-A-3910239 is known a piston power unit primari-30 ly for use as an internal combustion engine and having a single cylinder curved about a center, intake and exhaust ports at opposite ends of the cylinder, a pair of opposed pistons movable in the cylinder towards and away from each other in compression and power strokes, said pistons cov-35 ering these ports during most of their strokes, and suc-ENDED SltEET .
21~5~66 - 3a cessively opening the ports as the pistons approach the ends of their respective power strokes, a pair of crank shafts including intermeshing gears, and a~pair of connecting rods connecting the crankshafts to the pistons.
This piston engine presents problems for the thrust of the pistons towards the cylinder surface and its centrifugation increase the friction of that pistons towards the cylinder outwardly surface. Thus, no high performances are possible and this embodiment is usefull only for engines with assimetrical port timing, as clearly stated in the specification therein;
the improvements made from US-A-3338137 of the same inventor are for structural complications of construction only.
Such state of the art may be subject to large improvements as regards:
improving the characteristics of the mechanisms of reciprocating volumetric machines by increasing efficiency in all conditions, reducing weight, dimension and construction costs.
From what has been said so far the technical problem would be solved, in reciprocating volumetric machines, by eliminating all parts with oscillating motion, improving performances and in the same time reducing the dimensions and the weights.
The present invention solves the above-mentioned techical problem by adopting:
a volumetric fluid machine, endothermic or not, equipped with pistons, having reciprocating movement in the liner block without connecting rods, rigidly connected to the driving shaft or not, including mobile pistons AMEN~ED SHEE~
3b-?l~576~
inside linears, which are machined, or not, in a rotating liner block on an axis that can be coinciding or intersecting with the axis of the shaft;
the pistons rotate with the liners, but on an inclined axis coinciding with the axis of rotation of the liners or passing through the same center, without the interposition of elements having alternate motion, characterised in that the liners are of arched form, with its concavity turned towards said center, with center of curvature of their axis of rotation, that can be coinciding or passing, in the same center of curvature, as the axis of driving shaft; the pistons rotate in syncronism with the liners, but on an inclined axis coinciding with the axis of rotation of the liners or passing through the same center curvature;
adopting: the variation of the inclination between the axis of rotation of the liner block and of the.pistons, in order to obtain the variation of displacement;
adopting: pistons connected in a rigid or oscillating way to their shaft or rotation plate, without the interposition of connecting rods;
adopting: pistons with spherical head, equipped with seal rings which also have spherical faying surface, located in the piston head in such a way as to come into contact with respective liner wall radially with respect to the axis of that same liner;
adopting: the pistons are arched in the same way as the liners and are equipped with seal rings with spherical faying surface.
Adopting in the case of the internal combustion engine: a distribution plate, adjacent to the liner block with at least one communication port to - the liners for induction, at least one outlet port and at least one combustion chamber, that rotates or not with respect to the casing;
AMENDE0 S~E~T c:
21457~6 adopting: on the distribution plate, closed zones in intermediate positions, that coincide with the end position of scavenging fase and thus achieve null -volume in four-stroke cycles;
adopting: one single auxiliary cooling and lubricating circuit;
- 5 adopting: the liner block as the mobile part of the pump for the cooling and lubricating circuit.
Adopting, in the case of a volumetric machine for fluids:
AMENDED ~fEEr ` - `- -~
21~57~6 WO94/1~2 5 PCT/IT92/0013 either the piston-holder plate or the liner block keyed or rigidly connected to the shaft;
adopting: pistons with head connected rigidly to the shank, which is in turn rigidly connected to the rotating 5 plate that can be inclinable, inclined, or not adopting: oscillating piston heads with contact surface with the shank and contact surface with head of the con-necting bolt, also spherical and concentric;
adopting: the variation of the displacement obtained by 10 varying the inclination between pistons and liners, bear-ing on the plate whose rear surface is cylindrical surface with axis of rotation that passes through in the same crossing point between the axis of rotation of the liner block and pistons.
The advantages achieved by the present invention, for all types of volumetric machines for fluids, can be sumar-ized by the absence of parts in alternating and oscillat-ing motion, such as connecting rods, the traditional pis-20 tons and valves: all this leads to a considerable reduc-tion in noise, due to the absence of thrust elements that when oscillating create noise because of the unavoidable presence of clearances between components. The elimina-tion of the radial loading of the pistons on the walls of 25 the cylinder, because the.thrust of the fluid is always tangential to the curvature of the liner, which always co-incides with the center of the spherical piston, whether fixed or oscillating; consequently there is a considerable reduction in wearing and an increase in efficiency, spe-30 cially at starting-up in the case of volumetric devices;
there are fewer parts to be constructed and there is con-siderable reduction in swarf machining required; consider-- able reduction of the axial and radial dimensions of the machines, for the higher powers and efficiencies obtaina-35 ble. Particulary, for the internal combustion engines, WO94/10~2 6 PCT/1~2/0013 -5~6 problemg regarding centrifugation or elasticity that can increase rotation speed are eliminated; moreover, cooling is facilited both of the pistons from the internal part of the housing and of the rotating liner block, which can easily operate as a cooling liquid pump; the restintances and the choking of the valves are eliminated; the lubrica-tion and cooling circuits are not separate, as it is pos-sible to utilize the cooling liquid that has lubrication function too.
10 Furthermore, particulary for volumetric machines pumps/engines or compressors, compensation of the axial thrusts on the pistons being facilitates, further reduces friction and so increases efficiency; connecting members between the piston-holder plate and the liner block are 15 not required, which on the other hand are obligatory in barrel pumps or engines; the pistons with fixed spheric head connected to the piston-hoder are suitable for low or medium angles between the shaft and the inclined element (pistons or liner block) and enable high speeds to be ob-20 tained as there are no components subject to centrigfuga-tion. The pistons with oscillating head enable very large angles to be used and enablbling dimensions to be reduced even with large displacements. The heads, that self-cen-ter on the tangent at the line of curvature at any point 25 along the liner ned, therefore, on the thrust of the fluid, do not radially load the liner wall, limiting wear-ing and increasing efficiency.
Finally, the pumps of the hydraulic circuits can work in-differently in both open circuit and closed circuit at the 30 same speed of rotation, as there are no components of ar-ticulated elements (typically connecting rods) that could disconnect and centrifugate; the feeding of the closed circuit is obtainable also directly without the tradition-al use of the so called charge pumps; in the combination 35 of more pumps for different hydraulic circuits the pairing W094tlO~2 ; PCT/1192/00134 of more pumps on one same shaft, is easily achieved and with reduced dimensions; each of these pumps is sized and/or adjusted for the particular requirements of the circuit, avoiding the use of expensive mechanical couples.
A few embodiments of the invention are shown in the five drawing tables attached, in which: Figure 1 shows a sec-tion of an internal combustion engine, with four pistons and four-stroke cycle, in accordance with the invention;
10 Figure 2 is the side view of distribution plate faced on to the block of rotating liners; Figure 3 is a partial section of an ignition device of a two-stroke engine; Fig-ure 4 and figure 5 are views according to two lateral di-rections at 90 of the curved piston; Figure 6 is the lon-15 gitudinal section of a pump/engine or compressor forfluids, with variable displacement in both directions, with rotating and inclinable block of liners. Figure 7 is partial view from the supply side of the plate of inclina-tion and of the distribution of fluid to the block of ro-20 tating liners; Figure 8 is the section of a piston withoscillating head; Figure 9 is a longitudinal section of a pump/engine for fluids, the same as Figure 6, but with an inclinable piston holder plate instead of the liner block;
Figure 10 and 11 are the same views of Figure 4 and 5 but 25 for a piston not for internal combustion engine; Figure 12 is a sied view of a spherical piston; Figure 13 is the longitudinal section of a pump/engine for fluids, the same as Figures 6 and 9, without inversion of motion of fluid;
Figure 14 is a longitudinal section of a pump/engine for 30 fluids, the same as the previous Figure with both mecha-nism having a variable displacement.
- The indication are as follows: 1 (Figure 1) is the dri-ve shaft that rotates, on bearings in the housing 2 of the - 35 endothermic engine and positioned on each end 3 of the WO94/1~W2 2 1 4~ ~ 6 6 -8- PCT/1~2/0013 ~
shaft, each of which is coupled with piston pin 4 to the corrispondent curved piston 5; this last piston is driven from the mentioned ends to move inside the liners, which are machined in the rotating liner block 7; with 8 the 5 distribution plate, rotating on the ring 9; with 10 and 11 the exhaust pipe and induction pipe; with 12 the head, equipped with ignition plug 13, which is facing the piston in a position of maximum compression, through an anti-wear ring 14 and the combustion chamber 15, which is machined 10 in the thickness of the distribution plate; with 17 the spring for the recovery of clearances for the sealing be-tween distribution plate 8 and the liner block 7, which bears on the spherical articulation 18 of centering block of the shaft; with 19 guide bearings of the tube 20 the 15 distribution plate, comanded through internal coaxial shaft 21 rotating with the liner block 7 and through re-duction gearing of speed 22,23 and 24; with 26 refriger-ating duct of the distribution plate and of the manifold 10 and ll,and with analogous 27 duct in liner block; with 20 28 a radial hole in each liner for the assembly of the piston pin 4; with 29 the seal rings of the pistons 5, connected to the respective pin boss 30 through the piston pins at each end 3; with 31 and 32 (Figure 2) the holes and the suction ports on the distribution plate and with 25 33 and 34 the holes and the corrispondent exhaust ports;
with 35 (Figure 3) the chamber of combustion in the fixed distribution plate 36 of a two-stroke engine.
In the second embodiment of the invention, the indica-30 tions are as follow: with 37 (Figure 6) a drive shaft of the pumps/engine or volumetric compressor on which the piston holder plate 39 is splined, by means of a splined profile 38; the pistons are screwed on to the plate by means of a thread; with 40 the piston shank has a central 35 hole 41 of compensation of the axial hydraulic thrusts, 2~ S766 W094/10~2 PCT/~2/00134 it presents a head with a spherical swelling 42 and a seal ring 43 with external spherical swelling; the above men-tioned pistons are driven into the liners 44 of the rotat-ing liner block 45, which is driven to the mentioned shaft - 5 37 through a ball joint 46; with 47 the end clearances of the compensation springs acting on the mentioned joint and against the plate 39, which slides against the anti-wear lining 48 to which the compensation cavities 49 of the ax-ial hydraulic thrust are facing; with 50 the hole for the 10 passage of the fluid from the liner to the distribution cap 51, equipped with slots 52 and ports 53, on the side of the liner block 45, which is fed through ducts 54 and 55 for the passage of fluid; with 56 a slot on the axis distribution cap 51 for oscillation, which is driven from 15 the parallel surface, which couples with the envelope 58;
with 59 the head of the spherical piston, can oscillate on the shank 40 through a spherical headed screw 60 and a corrispondent spherical surface 61 between the shank and the piston head 59.
In the third embodiment of the invention, without repeat-ing the numbers of the common parts found in following Figures, are as follows; with 62 the curved piston, are mobile in the liners of the block 63, which presents fed-25 ing holes, facing the cover 65 with feeding lines of thefluid; with 66 a piston holder plate driven from the ball joint 46 and facing a corrispondent inclinable cap 67, with a parallel surface 68, against a block inserted 69 inside the envelope 58; with 70 the central axis of a cur-30 vature of the liners; with 71 (Figure lO) the seating ofthe seal ring 43 and with 72 the axis of the piston shank 40.
-Lastly, the indications shown are the following: with -- 35 73 (Figure 13) a plate which is splined on the shaft 37 by WO94/10~2 6 -10- PCT/1~2/0013.~
G
means of splined profile, and supports two series of pis-tons, which are connected to the plate and which are op-posed to one another, there are equipped with axial holes 74 for connection of the corrispondent chambers of the 5 liners; with 75 a liner block without feeding lines, ro-tating like block 45, but diesel ~ycle, starts the combus-tion through the special chamber 15 or 35, in the case of two-stroke engines that have the distribution plate fixed to the cylinder head 12; the drive of the coaxial driving 10 shaft 21, together with the wheel work 22,23 and 24, halves the rotation, because of the distribution plate control 8, through sleeve 20.
During the stroke of the pistons 5 inside the liners 6, the slight differences of path, which are also due to the 15 high angles between the the spin axis are compensated by slight oscillations on the gudgeon pins 4 in the hubs 30 besides slight radial slidings of the pistons in the in-termediate positions of 45, 135, 225 and 315 of rota-tion. The coolant is sucked from the radiator through the 20 pipe 25 and is conducted right into the liner block 7 through the hollow shaft 21; the holes 27 riceive the coolant by means of radial ducts, which are not shown in the drawing, and that are situated between the liners: the coolant is therefore centrifugated by the rotation of the 25 liner block and fills the internal volume of box 2 then hot it flows out of it, into tubes that are not shown in the drawing towards the radiator; the coolant, by means of the cavity wall between the sleeve 20 and the coaxial shaft 21, cools the central part of the distribution plate 30 8 and with the ducts it also cools the manifolds.
The functioning of the pump/engine or compressor for fluid refered to the second embodiment carried out occurs in the following way: the fluid under pressure, flowing in 35 the ducts 54 and 55 and crossing the slots 52, the parts ~
21457~6 W094/10442 -11- PCT/I~2/00134 53 and the holes 50, enters the liners 44; the action on the surface of the piston head 42 is distributed with re-lation to the position of the seal ring 43, i.e. exactly axial to the shank 40, without radial components driven 5 from the piston to the liners; the rotation that is im-pressed to the piston-holder plate 39 is driven to the driving a shaft 37 by splined fitting 38: the cavities 49, which are held at the same pressure of the liners 44 by the hole 41, balance the axial hydraulic thrusts on the 10 mentioned plate and on the pistons; the Belleville washers 47 stop the end clearances beteewen the liner block 45, the cap 51, and the envelope 58: the preloading is consid-erably superior to the force generated during the suction of the fluid at atmospheric pressure. The variation of 15 displacement and, therefore, a major versatility during use is possible by changing the inclination of the cap 51 by sliding on the cylindrical surface 57. The head of the oscillating piston 59, for the employment of the pistons and of the liners with ample angles between the axis of 20 rotation, results to be always balanced, because the cen-ter of oscillation is out of the piston and inside the fluid. On the contrary usual pistons, have the piston pin situaded considerably far from the surface in contact with the fluid.
The functioning of the pump/engine or compressor for fluids referred to the third type carried out, occurs in the following way: the keying position to the shaft 37 is inverted: i.e., it is the liner block 63 that drives the 30 couple: this disposition generates a radial component for the piston heads 62, rapidly wearing out the liners. The curved piston with head 62, results to be more adapted for - disposition with a high angle of inclination between the axis even if it is more difficult to construct. Also for 35 this realization, the variation of the displacement ob-wo 94~l0~2 ~ ~5~ 12- PCT/1~2/0013 ~
tained with the inclination of the cap, in this case number 67.
Figures 13 and 14 show two realizations for pumps/engines 5 or compressor for fluids, for use in different fields: the first is a pump/engine with a series of pistons of vari-able displacement and the other series of fixed displace-ment, in all without inversion of direction of the fluid;
the second is equipped with both the series of pistons 10 with variable displacement and the inversion of the flow, as indicated by the arrows next to the feeding lines 54,55 is possible; the caps 51 and/or 76 are to be inclined through external control with well known mechanisms. In both two realizations the piston-holder plate 73 keyed on 15 the driving-shaft 37, balances the axial thrust between the opposing liners 44 and being the axial holes 74 in the pistons, the less work is done by the fluid in passing through.
20 The functioning as a pump/compressor can comfortably oc-cur for all the angles of the cap (51 and/or 76), while when functioning as an engine, due to the known impossi-bility of zero setting the displacement, the angle must not be too reduced. Moreover, being the elimination of 25 the fluid motion between the two series of pistons of the double device in figures 13 and 14, which reduce the efficiency, the displacement in the mechanism of figure 13 must not be completely zero setted: the cap 76 must not be placed with opposed inclination to that figure; the dis-30 placement in the mechanism of figure 14 must not be variedby controlling the caps 76 and 51 inverted sincronism, therefore the caps 76 and 51 will result parallel when the displacement state is null, while they will result to be inclined as in the drawing or in opposing way due to the 35 flow of fluid in both directions respectively.
21~5766 If in practice materials, dimensions and operative de-tails should be different from those indicated, but tech-. nically equivalent, the patent will still apply.
- 5 In this way the pumptengine or compressor in Figures 6 or 9 can be obtained at a fixed displacement, or even a pump and an engine can be paired through the cavities 49 or the feeding ports 64, by interposing a fixed distributor to the housing, in order to carry out compact hydrostatic 10 drives: the advantages due to the reduction of dimensions, weight and to run high speed of rotation make this type of embodiment extremely interesting.
Finally, fixing the pistons rigidly to the housing and placing the liner block in oscillation by means of axial 15 or radial cam connected to the driving shaft, a pump/engine or compressor, without moving parts will be obtained with exception for the cam: this is very conven-ient in the case of pumps or engines for liquids. On the analogy of the displacement variation pumps engines or 20 compressor, it is possible to carry out, with the configu-ration of pistons 5, 42, 59 or 62, and of the rotating liner block 7 of the present invention, endothermic en-gines, that can reduce displacement, facilitating the mix-ing of the gasoline with air, without the complex artific-25 es that are employed at pFesent for the adjustment of itscomposition, achieving advantageous efficiencies at low charge.
Claims (13)
1. Volumetric fluid machine, endothermic or not, equipped with pistons, having reciprocating movement in the liner block without connecting rods, rigidly connected to the driving shaft or not, including mobile pistons inside liners, which are machined, or not, in a rotating liner block (7, 45, 63, 75) on an axis that can be coinciding or intersecting with the axis of the shaft (1, 37); the pistons (5, 42, 59, 62) rotate with the liners, but on an inclined axis coinciding with the axis of rotation of the liners or passing through the same center, without the interposition of elements having alternate motion, cha-racterised in that the liners (6, 44) are of arched form, with its concavity turned towards said center, with center of curvature on their axis of rotation, that can be coinciding or passing, in the same center of curva-ture, as the axis of driving shaft (1, 37); the pistons rotate in syncronism with the liners, but on an inclined axis coinciding with the axis of rotation of the liners or passing through the same center curvature.
2. Volumetric fluid machine, according to the previous claims, characterised in that the variation of the incli-nation between the axis of rotation of the liner block (7, 45, 63, 75) and of the pistons (5, 42, 59, 62), al-lows the variation of displacement.
3. Volumetric fluid machine, according to one or more of the previous claims, characterised in that the pistons are connected in a rigid or oscillating way to their shaft (1, 37) or rotation plate (39, 66, 73), without the interposition of connecting rods.
4. Volumetric fluid machine, according to one or more of the previous claims, characterised in that the pistons have a spherical head (42, 59), equipped with seal rings (29, 43) which also have a spherical faying surface, lo-cated in the piston head in such a way as to come into contact with respective liner (6, 44) wall radially with respect to the axis of that same liner.
5. Volumetric fluid machine, according to one or more of the previous claims 1 to 3, characterised in that the pistons (5, 62) are arched in the same way as the liners (6, 44) and are equipped with seal rings (29, 43) with spherical faying surface.
6. Volumetric fluid machine with internal combustion, ac-cording to one or more of the previous claims, characte-rised in that it has a distribution plate (8), adjacent to the liner block (7) with at least one communication port (31, 32) to the liners for induction, at least one outlet port (33, 34) and at least one combustion chamber (15), that rotates or not with respect to the casing (2).
7. Volumetric fluid machine, according to the previous claim, characterised in that distribution plate (8) has closed zones in intermediate positions, that coincide with the end position of scavenging fase and thus achieve null volume in four-stroke cycles.
8. Volumetric fluid machine, according to one or more of the previous claims 6 and 7, characterised in that it has one single auxiliary cooling and lubricating circuit.
9. Volumetric fluid machine, according to one or more of the previous claims 6 to 8, characterised in that the liner block (7) act as the mobile part of the pump for the cooling and lubricating circuit.
10. Volumetric fluid machine, according to one or more of the previous claims 1 to 5, characterised in that either the piston-holder plate (39, 66, 73) or the liner block (45, 63, 75) is keyed or rigidly connected to the shaft (37).
11. Volumetric fluid machine, according to one or more of claims 1 to 5 or 10, characterised in that it has pistons with head connected rigidly to the shank (40), which is in turn rigidly connected to the rotating plate (39, 66, 73) that can be inclinable, inclined, or not.
12. Volumetric fluid machine, according to one or more of the previous claims, characterised in that the oscillat-ing piston heads (59) with contact surface (61) with the shank (40) and contact surface with head (60) of the con-necting bolt, also being spherical and concentric.
13. Volumetric fluid machine, according to one or more of the previous claims, characterised in that it has varia-ble displacement obtained by varying the inclination between pistons and liners, bearing on the plate (51, 67, 76) whose rear surface is a cylindrical surface with axis of rotation that passes through in the same point of in-tersection between the axis of rotation of the liner block (45, 63) and pistons.
Priority Applications (28)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5505092A JPH06510486A (en) | 1991-09-12 | 1992-09-14 | Method and apparatus for producing billets and blooms from continuous cast steel exhibiting high or very high quality |
| DE69209656T DE69209656T2 (en) | 1991-09-12 | 1992-09-14 | METHOD AND DEVICE FOR THE PRODUCTION OF STEEL STRINGS OR BLOCKS BY CONTINUOUSLY CASTING WITH A HIGH OR EXCELLENT QUALITY |
| EP92920674A EP0603330B1 (en) | 1991-09-12 | 1992-09-14 | A process and apparatus for the manufacture of billets and blooms from a continuously last steel showing high or excellent quality |
| PL92302730A PL170722B1 (en) | 1991-09-12 | 1992-09-14 | Method of and apparatus for continuously casting steels |
| AU26504/92A AU658451B2 (en) | 1991-09-12 | 1992-09-14 | A process and an apparatus for the manufacture of billets and blooms from a continuously cast steel showing high or excellent quality |
| RU9294017661A RU2094139C1 (en) | 1991-09-12 | 1992-09-14 | Method and apparatus for manufacture of continuously cast steel billets |
| BR9206488A BR9206488A (en) | 1991-09-12 | 1992-09-14 | Process and equipment for the production of billet billets or rebar from a cast iron continuously presenting high or excellent quality |
| US08/199,137 US5497821A (en) | 1991-09-12 | 1992-09-14 | Manufacture of billets and blooms from a continuously cast steel |
| RU95109872A RU2112889C1 (en) | 1992-10-30 | 1992-10-30 | Positive-displacement machine for displacement of fluid media equipped with pistons without connecting rods |
| EP92923969A EP0676009B1 (en) | 1992-10-30 | 1992-10-30 | Volumetric fluid machine equipped with pistons without connecting rods |
| BR9207174A BR9207174A (en) | 1992-10-30 | 1992-10-30 | Volumetric machine for fluids |
| JP51086894A JP3429764B2 (en) | 1992-10-30 | 1992-10-30 | Fluid operated machine with a piston without connecting rod |
| US08/424,304 US5636561A (en) | 1992-10-30 | 1992-10-30 | Volumetric fluid machine equipped with pistons without connecting rods |
| PL92308761A PL169513B1 (en) | 1992-10-30 | 1992-10-30 | Volumetric fluid machine provided with pistons without connection rods |
| AU29553/92A AU2955392A (en) | 1992-10-30 | 1992-10-30 | Volumetric fluid machine equipped with pistons without connecting rods |
| CZ951102A CZ110295A3 (en) | 1992-09-14 | 1992-10-30 | Volumetric liquid apparatus |
| SK411-95A SK41195A3 (en) | 1992-10-30 | 1992-10-30 | Volumetric fluid machine |
| PCT/IT1992/000134 WO1994010442A1 (en) | 1992-10-30 | 1992-10-30 | Volumetric fluid machine equipped with pistons without connecting rods |
| CA002145766A CA2145766A1 (en) | 1992-09-14 | 1992-10-30 | Volumetric fluid machine equipped with pistons without connecting rods |
| CN93117871A CN1043437C (en) | 1992-10-30 | 1993-09-20 | Volumetric fluid machine |
| EP93924794A EP0682748A1 (en) | 1992-10-30 | 1993-10-29 | Volumetric fluid machine equipped with pistons without connecting rods |
| PCT/IT1993/000113 WO1994010443A1 (en) | 1992-10-30 | 1993-10-29 | Volumetric fluid machine equipped with pistons without connecting rods |
| NO940748A NO301809B1 (en) | 1991-09-12 | 1994-03-04 | Method and apparatus for producing blanks, especially roll blanks and larger blocks of continuous cast steel which exhibit high or excellent quality |
| FI941115A FI97956C (en) | 1991-09-12 | 1994-03-09 | Process and apparatus for producing non-uniform materials of continuous cast steel |
| BG98646A BG61684B1 (en) | 1991-09-12 | 1994-03-10 | Method and device for the manufacture of billets and intermediate products by continuous steel casting of high or excellent quality |
| NO951238A NO951238L (en) | 1992-10-30 | 1995-03-30 | Volumetric fluid machine equipped with pistons without coupling rods |
| FI952068A FI952068A0 (en) | 1992-10-30 | 1995-04-28 | Volumetric machine, endothermic or non-endothermic, intended for liquids and equipped with reciprocating pistons in the linear block without connecting rods, which pistons are or are not rigidly connected to the drive shaft |
| GR960400154T GR3019548T3 (en) | 1991-09-12 | 1996-04-04 | A process and apparatus for the manufacture of billets and blooms from a continuously last steel showing high or excellent quality. |
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/IT1992/000113 WO1993004802A1 (en) | 1991-09-12 | 1992-09-14 | A process and apparatus for the manufacture of billets and blooms from a continuously last steel showing high or excellent quality |
| CA002145766A CA2145766A1 (en) | 1992-09-14 | 1992-10-30 | Volumetric fluid machine equipped with pistons without connecting rods |
| CZ951102A CZ110295A3 (en) | 1992-09-14 | 1992-10-30 | Volumetric liquid apparatus |
| PCT/IT1992/000134 WO1994010442A1 (en) | 1992-10-30 | 1992-10-30 | Volumetric fluid machine equipped with pistons without connecting rods |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2145766A1 true CA2145766A1 (en) | 1994-05-11 |
Family
ID=27169982
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002145766A Abandoned CA2145766A1 (en) | 1991-09-12 | 1992-10-30 | Volumetric fluid machine equipped with pistons without connecting rods |
Country Status (6)
| Country | Link |
|---|---|
| CN (1) | CN1043437C (en) |
| BR (1) | BR9207174A (en) |
| CA (1) | CA2145766A1 (en) |
| CZ (1) | CZ110295A3 (en) |
| PL (1) | PL169513B1 (en) |
| WO (2) | WO1994010442A1 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2098702A1 (en) * | 2006-12-29 | 2009-09-09 | Yau Cheung Kwok | Top rotating engine |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5794514A (en) * | 1995-01-19 | 1998-08-18 | S.A.I. Societa' Apparecchiature Idrauliche S.P.A. | Volumetric machine with curved liners |
| DE50306608D1 (en) | 2002-12-18 | 2007-04-05 | Bosch Rexroth Ag | axial piston |
| WO2008136386A1 (en) | 2007-04-27 | 2008-11-13 | Ntn Corporation | Grease composition and grease-sealed bearing |
| CN106593800A (en) * | 2015-10-16 | 2017-04-26 | 熵零控股股份有限公司 | Positive feedback plunger fluid mechanism |
| DE102015224132A1 (en) * | 2015-12-03 | 2017-06-08 | Robert Bosch Gmbh | Hydrostatic axial piston machine with control disc |
| CN110359962B (en) * | 2019-07-17 | 2021-01-05 | 顾新钿 | Pneumatic motor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1408719A (en) * | 1964-02-07 | 1965-08-20 | Pump or volumetric motor with adjustable flow | |
| US3485218A (en) * | 1967-10-04 | 1969-12-23 | Nat Res Dev | Rotary piston machines |
| FR2083995A5 (en) * | 1970-03-02 | 1971-12-17 | Lotesto Umberto | |
| US3648567A (en) * | 1970-07-06 | 1972-03-14 | Gen Motors Corp | Variable displacement axial pump or motor |
| US3809025A (en) * | 1973-02-02 | 1974-05-07 | Harper Dev Corp | Rotary engine having inclined piston and cylinder rotation axes |
| US3910239A (en) * | 1974-06-10 | 1975-10-07 | Richard James | Opposed piston power unit |
| GB2027122B (en) * | 1978-05-25 | 1982-08-25 | Searle R J | Reciprocating piston machines |
| GB8417816D0 (en) * | 1984-07-12 | 1984-08-15 | Searle R J | Piston machines |
| US5138993A (en) * | 1991-02-11 | 1992-08-18 | Kim Jong D | Rotary wavy motion type engine |
-
1992
- 1992-10-30 WO PCT/IT1992/000134 patent/WO1994010442A1/en active IP Right Grant
- 1992-10-30 CZ CZ951102A patent/CZ110295A3/en unknown
- 1992-10-30 PL PL92308761A patent/PL169513B1/en unknown
- 1992-10-30 CA CA002145766A patent/CA2145766A1/en not_active Abandoned
- 1992-10-30 BR BR9207174A patent/BR9207174A/en not_active Application Discontinuation
-
1993
- 1993-09-20 CN CN93117871A patent/CN1043437C/en not_active Expired - Fee Related
- 1993-10-29 WO PCT/IT1993/000113 patent/WO1994010443A1/en not_active Application Discontinuation
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2098702A1 (en) * | 2006-12-29 | 2009-09-09 | Yau Cheung Kwok | Top rotating engine |
| EP2098702A4 (en) * | 2006-12-29 | 2011-10-19 | Yau Cheung Kwok | Top rotating engine |
Also Published As
| Publication number | Publication date |
|---|---|
| WO1994010442A1 (en) | 1994-05-11 |
| CN1088657A (en) | 1994-06-29 |
| CZ110295A3 (en) | 1995-12-13 |
| BR9207174A (en) | 1995-12-12 |
| PL169513B1 (en) | 1996-07-31 |
| CN1043437C (en) | 1999-05-19 |
| WO1994010443A1 (en) | 1994-05-11 |
| PL308761A1 (en) | 1995-08-21 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FZDE | Discontinued |