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
  • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
  • F01C1/063—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them
  • F01C1/073—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them having pawl-and-ratchet type drive

Definitions

• the present invention relates to a rotary piston machine usable in particular as a heat engine, for example of the so-called explosion or diesel type.
• Engines comprising several pairs of pistons driven in rotation about the axis of a power take-off shaft, each of the pairs of pistons determining a variable volume chamber into which during the intake phase is introduced the mixture gaseous.
• the rotation of the power take-off shaft results from the expansion of the gases during the corresponding phase of the thermodynamic cycle.
• One of the two pistons is fixed to the power take-off shaft, the other piston being fixed to a return shaft kinematically linked to the power take-off shaft by a motion transmission.
• the power take-off shaft and the return shaft are mounted coaxially one inside the other and the movement transmission induces an alternating rotational movement of the return shaft relative to the power take-off shaft , so that the volume of the chamber determined by each pair of pistons, alternates between a minimum and a maximum and this in accordance with the phases of the thermodynamic cycle used.
• This type of motor comprises a disengageable means for actuating the second rotor, said means being constituted by a transmission of movement between the first rotor and the second.
• the object of the present invention is to solve the above-mentioned problems and relates to an engine of the aforementioned type comprising an engine block 1 in which is
• a cylindrical chamber 2 in which are mounted coaxially, in interpenetration, two rotors 5, 8 which form with said chamber at least one capsulism subject to rotate around the geometric axis of the cylindrical chamber 2 and in which a gas mixture according to the phases of a thermodynamic cycle, one of the two rotors, the rotor 5 being driven by a continuous rotational movement while the other, the rotor 8 being driven by an intermittent rotational movement likewise meaning that the first, the said machine further comprising:
• a disengageable means for actuating the second rotating rotor constituted by a movement transmission means between the rotor 5 and the rotor 8, coupled on the one hand to the first rotor 5 and on the other hand to the rotor 8, the said means transmission, on the kinematic chain of transmission of movement between the rotor 5 and the rotor 8, comprising a clutch member.
• This machine is essentially characterized in that it is provided with a non-return mechanism comprising a first element 12 fixed to the engine block 1 and a second element 13 in engagement with the rotor 8 in operation intermittent, the said elements 12, 13, during the expansion and admission phases cooperate in angular locking with each other to prevent the retrograde movement of the rotor 8 with intermittent movement, and that the means of
• a hydraulic pump 24 coupled by its rotor to the rotor 5 and by its stator to the engine block
• a hydraulic motor 25 coupled to the rotor 8 and connected via a closed loop hydraulic circuit or hydrostatic transmission to the hydraulic pump,
• FIG. 1 is a cross-sectional view of an engine according to a first embodiment
• FIG. 2 is a cross-sectional view of an engine according to a second embodiment
• FIG. 3 is a partial view, in longitudinal section of the engine according to the invention.
• FIG. 4 is a cross-sectional view of a
• FIG. 5 is a view in longitudinal section along the line A / A of FIG. 4,
• FIG. 6 is a cross-sectional view of a
• FIG. 7 is a view in longitudinal section along the line B / B in FIG. 6,
• FIG. 8 shows in cross section a hydraulic actuator which can be associated with the non-return mechanism
• - Figure 9 is a half-sectional view of the means of
• FIG. 10 is a partial sectional view, along the line C / C of FIG. 9,
• FIG. 11 is a section along line D / D of FIG. 9,
• FIG. 12 is a detail sectional view along the line E / E of FIG. 3,
• FIG. 13 is a cross-sectional view of a hydraulic motor
• FIG. 14 is a view in partial longitudinal section of the hydraulic motor
• FIG. 15 is a schematic view of an engine
• FIG. 16 is a view in partial longitudinal section of the engine according to FIG. 15,
• FIG. 17 is a section along line F / F of FIG. 16,
• FIG. 18 is a sectional view along the line G / G of FIG. 16,
• FIG. 19 is a partial sectional view along the line H / H of FIG. 18,
• FIGS. 20 to 25 show the intake phase of the engine according to FIG. 1,
• FIGS. 26 to 31 show the compression and ignition phase of the engine according to FIG. 1,
• FIGS. 32 to 36 show the expansion phase, and the start of the engine exhaust according to FIG. 1,
• FIGS. 37 to 42 show the exhaust phase of the engine according to FIG. 1,
• FIG. 55 is a longitudinal sectional view of a non-return mechanism according to a third form of production
• FIG. 56 is, on a reduced scale, a sectional view along the line JJ of FIG. 54,
• FIG. 57 is a view in longitudinal section of a fourth embodiment of a non-return mechanism
• FIG. 58 is, on a reduced scale, a sectional view along the line KK of FIG. 57,
• FIG. 59 is, on a reduced scale, a sectional view along line LL in FIG. 57,
• FIG. 60 is a sectional view of a pump and hydraulic motor assembly according to another embodiment
• FIG. 61 is a sectional view along the line MM in FIG. 60.
• FIG. 62 is a view in longitudinal section of a variant of the engine according to the second embodiment.
• FIG. 63 is a sectional view along line NN in FIG. 62.
• FIG. 64 is a sectional view of a pump according to another embodiment
• Figure 65 is a section along the line OO of Figure 64
• FIG. 66 is a section along the line QQ in FIG. 65.
• FIG. 67 is a schematic view of a piloted valve, calibrated for the discharge of the hydraulic circuits.
• FIG. 68 is a view of a crown according to the arrow F in FIG. 60.
• internal combustion thermal combustion type for example, or diesel type includes at least one engine block 1 in which is bored a cylindrical chamber 2 in which are mounted at a distance from each other two bearings 3 intended for support a hollow rotor 5 constituting the engine power output shaft.
• a sealing barrier constituted for example by a lip seal (fig 3).
• the hollow rotor 5 of generally cylindrical shape is traversed right through along its longitudinal axis by a bore cylindrical 6.
• the rotor 5 has at least one recess 7. This obviously, in a section perpendicular to the axis of the rotor 5 follows the contour of a circular crown sector. According to a section
• the faces 7A and 7B are angularly separated from one another by an arc of circumference of value greater than 110 °.
• the engine comprises at least two
• the solid parts 5A each constitute a piston.
• the rotor 5 has projecting on its external cylindrical surface one or more sealing 4 which may be continuous, arranged around the orifice of each recess
• a second rotor 8 consisting of a shaft 9 engaged in rotation in the bore 6 of the first rotor and by at least one piston 10 fixed radially to said shaft 9 and engaged in the recess 7.
• the rotor 8 is supported by two bearings 11 mounted at a distance from each other in a housing coaxial with the bore 6 of the rotor 5. Between the bore 6 of the rotor 5 and the shaft 9 of the rotor 8 will be arranged, in particular around the orifices of the recesses 7, sealing beads which may be of the type of those described above with the aim of forming a continuous waterproof barrier at this level.
• the rotor 8 preferably comprises at least two diametrically opposite pistons 10 housed respectively in the two recesses 7.
• Each piston 10 has a sealing segment at the periphery subject to coming against the cylindrical surface of the chamber 2 on the one hand and against the surfaces 7C of the recess 7 on the other hand, this sealing segment preferably conforming to the outline of a U.
• the two pistons 10 are rooted in the same body extending diametrically through the shaft 9 of the second rotor 8 and form with the body only one and the same part, as can be seen more particularly in the figures 1 and 2.
• Figure 63 we can see that the pistons 10 are rooted directly to the shaft 9
• Each piston 10 produces two capsulisms with the cylindrical chamber 2 and with the corresponding recess 7, that is to say, with the lateral faces 7C, the face 7A of one of the pistons 5A and the face 7B of the other. piston 5A.
• only one of these two capsulisms is used for the evolution of a gas mixture according to the thermodynamic cycle, but as a variant, provision may be made for the use of these two.
• capsulism In the attached figures, it can be noted that the capsulism used is that delimited in particular by the piston 10 and by the face 7A of the corresponding piston 5A.
• thermodynamic cycle namely, admission, compression
• ignition-trigger or combustion-trigger, exhaust, rotor 5 constituting power output shaft accomplished about a quarter of a turn.
• the rotor 8 during the phases of admission of the gas mixture into each capsulism and of expansion of the gases in the latter (FIGS. 20 to 25, 32 to 36, 43 to 48) is subjected by a non-return mechanism to remain angularly fixed by relation to the engine block at least in the downward direction, while during each of the phases of compression of the gas mixture and exhaust of the burnt gases ( Figures 26 to 31, 37 to 42, 49 to 54), it is secured by a means of movement transmission to be completed approximately half a turn with respect to the engine block. During these two phases, the rotor 8 accomplished with respect to the rotor 5 about a quarter of a turn.
• the rotor 8 can occupy two diametrically opposite stop positions, one of which coincides with that which it occupies during the expansion phase and the other coincides with that which it occupies during phase d 'admission.
• the purpose of the non-return mechanism is to oppose the retrograde movement which the rotor 8 could accomplish, in particular under the effect of the torque induced by the thrust forces which are exerted on at least one of the pistons 10 during the gas expansion phase.
• This non-return mechanism comprises a first element 12 mounted in a housing coaxial with the chamber 2, in attachment to the engine block 1 and a second element 13 in engagement with the rotor 8 and mounted in the first, one of the two elements being a wheel.
• the other element has two radial pawns 15
• the pins 15 form pistons in their bore and are mobilized towards their exit and engagement position in their tooth 14 by a spring and / or by the hydraulic pressure delivered by a source of hydraulic pressure.
• FIGS. 4 and 5 a non-return mechanism comprising an external ratchet wheel, the pins 15 being slidably engaged in a common bore formed in a cylindrical body integral with the rotor 8, said bore being able to be supplied with hydraulic pressure by a axial drilling connected to a supply line with pressurized hydraulic fluid via a rotating joint.
• the ratchet wheel is integral with the rotor 8, the two pins 15 being mounted in two opposite bores, aligned with each other according to the same diameter.
• the two bores can be connected to the same pressure source.
• Each pin 15 of one or the other embodiment may be associated with an elastic member such as a compression spring with turns, mounted in the corresponding bore. This elastic member applies a pushing action to the corresponding pin 15 towards its exit position.
• an elastic member such as a compression spring with turns
• the first element 12 of the non-return mechanism is fixed to the engine block by means of a system 30 for absorbing and dissipating mechanical shocks.
• This system is constituted for example by several damping elements, regularly distributed in the annular interval between the first element 12 and the engine block, in deformable cells each delimited by two radial walls extending in the annular interval, one of which is fixed to the first element and the other is fixed to the engine block.
• the source of hydraulic pressure for actuating the pistons 15 towards their position of engagement in the teeth 14 may be constituted by an actuator
• the paddles 17 separate the internal volume of the stator from the hydraulic actuator into a front chamber 18 and into a rear chamber 19 connected to each other via a non-return valve 20.
• annular groove 21 on the edges of which each pallet 17, by one of its ends is subject to sliding.
• the cylindrical housing has in the groove 21 two diametrically opposite sealing segments 22, the angular position of the sealing segments 22 coinciding with the two rotor stop positions 8.
• the pallets 17 are slidably mounted in a diametric housing of the hydraulic actuator rotor.
• the two chambers 18 and 19, when the pallets 17 are angularly offset relative to the sealing elements 22, are in communication with one another by the groove 21.
• the front 18 and rear 19 chambers are in communication with each other only by means of the valve
• non-return 20 which prevents any backflow of oil from the rear chamber 19 to the front chamber 18.
• a slight retrograde movement of the rotor 8 drives the rotor of the actuator in the same direction, which creates a
• the rear chamber 19 of the actuator 16 is in communication with the bore or bores of the radial pins 15.
• each pallet 17 from its end closest to the center of the rotor is hollowed out with a groove 23 extending radially relative to the eccentric rotor of the actuator 16, this radial groove making a passage towards the diametrical housing of the eccentric rotor when only the pallet occupies an exit position relative to this housing.
• This pallet 17 occupies this position when its groove 23 is in communication with the rear chamber 19.
• the groove 23 is not formed over the entire length of the pallet and its end furthest from the center of the rotor remains away from the corresponding end of the pallet so that when the latter is fully retracted into the housing
• the diametrical housing of the eccentric rotor is in communication by means of a bore and / or a rotary joint with the guide bore or holes of the pins 15.
• a non-return mechanism has previously been described, the elements 12 and 13 of which cooperate in angular locking with one another by penetration of pins 15 in teeth 14.
• the first element 12 secured to the engine block and the second element 13 secured to the intermittent operating rotor 8 form at least one cell 55 in which, during the expansion and intake phases, a volume d oil to prevent at least the retrograde rotation of the second element 13.
• the first element 12 comprises a chamber 56 in which the second element 13 is mounted.
• This chamber accepts as an axis of symmetry the geometric axis of rotation of the rotors 5 and 8.
• This chamber is delimited by two walls, front 57 and rear 58, arranged in separation from one another and each extending perpendicular to the axis of symmetry and by an envelope wall 59 arranged between the front and rear walls.
• non-return is constituted by a central core 13A coupled to the rotor 8 and by two vanes 60 extending radially from the core and in a diametrically opposite manner.
• the core 13A of the second element is extended axially by a shaft with grooves intended to be coupled
• the shaft is smooth so as to cooperate with a sealed guide bearing mounted in the bore.
• the central core 13A of the second element is extended axially by a second shaft engaged in a second guide bearing mounted in a bore formed in the rear wall 58.
• the face 59A internal to the chamber 56 of the envelope wall 59 comprises two surface sectors 61 diametrically opposite with respect to the axis of rotation of the second element 13 against which the end of the radial vanes 60 are applied when the two elements of the non-return mechanism are in angular locking relation to one another.
• One of the two elements of the non-return mechanism carries in the chamber two sealing members 62 preferentially constituted each by a flap and the other element of the non-return mechanism is provided in the chamber with two diametrically opposed surface sectors 63 relative to the axis of rotation of the second element against which the sealing members 62 apply when the two elements 12 and 13 are in angular locking relation to each other.
• the surface sectors 63 are less spaced from the axis of rotation of the second element than are the surface sectors 61.
• the paddles 60, the sealing members 62 and the internal faces of the chamber of the front walls 57, rear 58 and of the casing 59 form two cells 55 diametrically opposite, sealed, filled with oil, angularly separated from one another by two dead volumes 55A also filled with oil.
• the sealing member 62 of each cell is located in front of the pallet of this cell.
• the volume of oil trapped in each cell opposes the variation of the volume of the latter in the direction of a decrease which corresponds to the retrograde direction of movement of the second element.
• the second element and therefore the rotor 8 are locked in rotation in the retrograde direction.
• the expansion phase begins before the intermittent movement rotor comes to a complete stop, so that at the very start of this phase, the rotor, due to its inertia, performs a fraction of a turn while decelerating to at zero speed, then under the effect of the pressure prevailing in the motor capsulin (s) is driven in the retrograde direction.
• the cells 55 are formed at the end of the compression phase so that during the movement in the direction of rotation of the motor, of the second element 13, at the end of the compression phase and at the very beginning of the expansion phase, is created in each cell a depression relative to the pressure prevailing in the dead volumes 55A, due to the increase in the volume of the latter.
• a non-return valve 55D which authorizes the introduction of oil into said cell, this oil being in the dead volume 55A.
• this indexing means allowing retrograde movement. from the second element 13 to its blocking position by controlling this movement.
• the two surface sectors 61 each have a leakage section 64 which allows
• This trailing section 64 as long as the corresponding pallet 60 is at its level, allows a slight retrograde movement of the second element 13 which will be blocked angularly as soon as the pallet has crossed the trailing section 64.
• the angular stop position is slightly variable and depends on many parameters among which we can cite, the internal oil leaks at the level of the cells, which themselves depend on the engine speed and the load.
• This stop position fluctuates according to the above-mentioned parameters around an origin position.
• the two grooves 13B of the core 13A are diametrically opposite, and the core 13A of the bottom from one of the two grooves at the bottom of the other is traversed right through by a cylindrical bore 13C in which engages in sliding fit a cylindrical finger 6OA that comprises the pallet 60.
• the elastic member 6OB is arranged in compression in the radial bore 13C between the finger 6OA of one of the pallets and the finger 6OA of the other, this elastic member being constituted by a coil spring.
• these two fingers 60A are each provided with a blind axial bore in which the elastic return member 60B engages.
• each pallet 60 is equipped with several fingers 60A.
• the core 13A of the second element carries the two sealing members 62 which occupy a fixed position relative to the latter, and are angularly separated from the pallets 60.
• the surface sectors 63 are formed in the face 59A of the envelope wall 59 with an angular spacing of the surface sectors 61 and the said chamber follows a substantially oval outline.
• Each sealing member 62 according to this form of
• an embodiment protrudes from the core and is held in a fixed angular position relative to the latter against an abutment surface of the core, by an elastic member such as a leaf spring.
• the surface sectors 61 and 63 may belong to cylindrical surfaces.
• Each of these channels also opens into the bottom of a blind bore made in this wall.
• a cylindrical pad 55C bearing against the engine block.
• the front wall 57 is mounted with the possibility of limited axial displacement.
• the pallets of the second element 13 are fixed relative to the core 13A of the latter and the surface sectors 61 and 63 belong respectively to cylindrical surfaces.
• the sectors 63 are formed on the core 13A with an angular spacing of the pallets 60.
• cylindrical carrying the cylindrical sectors 61 is of larger diameter than the cylindrical surface carrying the sectors 63.
• the sealing members 62 are hingedly attached to the first element 12 and are controlled in their pivoting movement towards the core 13A of the first element 13 or away from it by at least one cam 65 coupled to the rotor with continuous movement 5, or alternatively to the rotor with intermittent movement.
• the sectors of cylindrical surfaces 61 are both formed respectively in two thicknesses of the cylindrical envelope, these two thicknesses being diametrically opposite.
• Each flap 62 comprises a foot 66 provided with two retaining pins 67 engaged in two holes made opposite one another in the front wall 57 and in the rear wall 58 and this along the pivot axis of the shutter.
• an arm 68 in the form of a torsion spring, at the end of which is mounted at least one finger 69 slidingly bearing on the cam surface 65 which is preferably provided in a sleeve coupled to the rotor 5 and disposed in front of the front wall 57.
• cams 65 are provided arranged side by side and at the end of the tension spring of each flap are mounted two fingers 69 cooperating respectively in sliding support with the two cam surfaces. These two cams 65 alternately command and control the tilting movement of the associated flap 62.
• this cam surface can be formed on the second element 13 of the non-return mechanism and the flap 62 will cooperate in sliding support with this cam surface. It can be kept in abutment against this surface by an organ
• elastic return which may be constituted by a torsion spring fixed on the one hand to its foot and on the other hand to one of the front 57 and rear 58 walls of the chamber 56.
• the foot of the flap 62 has a convex guide surface in the form of a sector of cylindrical surface whose axis is that of pivoting of the flap. This sector of cylindrical surface is subject to sliding during the
• the head 62A of the flap 52 has a head surface in the form of a sector of cylindrical surface whose axis of revolution coincides with the pivot axis of the flap 62.
• the flap 62 in its pivoting movement is guided on the one hand by the convex surface of its foot caused to slide against the concave surface of the envelope wall, lateral to one of the extra thickness, and on the other hand by the head surface caused to slide on a sealing segment mounted in a groove made in the other additional thickness.
• each flap 62 from the head surface to the foot is traversed right through by a channel.
• this channel when the head forms with the pallet the alveolus 55, is in relation to the said alveolus, so that pressurized oil reaches between the base of the flap and the face 59A of the envelope wall 59. This arrangement ensures the hydrostatic balance of the flap 62.
• the second element 13 is rotated and each flap 62 by cooperation of the cams 65, the fingers 69, and the arm 68 is separated from the core 13A of the second element 13 and from the path pallets 60.
• the flaps 62 will be brought back against the core of the second element 13.
• the latter can be connected to each other by a balancing channel formed in the core 13A.
• the non-return mechanism has an oil inlet opening into at least one of the two dead volumes 55A. and an oil flow to ensure the renewal and cooling of the oil.
• the means for actuating the rotor 8 actuates the latter in rotation during the compression and exhaust phases. It is preferably coupled to the rotor 5 and to the rotor 8 and ensures the transmission of the rotational movement. On the kinematic chain of motion transmission between the first rotor 5 and the second 8 is preferably arranged a clutch member which occupies a disengaged position during the intake and expansion phases so that the rotational movement of the rotor 5 n 'is no longer transmitted to the rotor 8 during these phases.
• the organs On the kinematic chain of motion transmission between the first rotor 5 and the second 8 is preferably arranged a clutch member which occupies a disengaged position during the intake and expansion phases so that the rotational movement of the rotor 5 n 'is no longer transmitted to the rotor 8 during these phases.
• This actuation means consists of a pump hydraulic 24 coupled by its rotor to the rotor 5 and by its stator to the engine block, as well as by a hydraulic motor 25 coupled to the rotor 8 and connected via a hydraulic circuit to the hydraulic pump.
• the hydraulic motor is coupled by its stator to the rotor 5 while by its rotor it is coupled to the rotor 8.
• the stator of the hydraulic motor is rotated by the rotor 5.
• hydraulic 25 causes a relative rotation of the second rotor 5 with respect to the first rotor 8.
• the actuating means preferably comprises a clutch member constituted for example by a valve, which during the intake and expansion phases partially or completely opens the hydraulic circuit between the engine and the pump and closes it during the phases of
• the hydraulic motor 25 comprises at least one rear chamber and at least one front chamber, both connected via the hydraulic circuit to the hydraulic pump 24.
• the clutch member constituted for example by a rotary valve.
• This rotary valve during the intake and expansion phases performs a shunt hydraulics by connecting the front and rear chambers of the hydraulic motor and the inlet and outlet of the hydraulic pump to each other, which then flow on themselves, this hydraulic shunt being comparable to the opening of the hydraulic circuit between pump and motor.
• the hydraulic pump 24 comprises radial pistons 26 each slidably mounted in a cylindrical chamber 27 formed radially in its rotor.
• the pistons each comprise at least one roller 28 subjected to rolling successively during the rotation of the rotor on internal cam surfaces 31 formed in the stator of the pump.
• the pump 24 is equipped with four piston 26 and chamber systems
• each system through its chamber 27 is hydraulically connected to the chamber 27 of its opposite by at least one diametric bore in order to balance the pressures.
• the stator of the pump 24 is equipped with four cam surfaces 31 arranged one after the other around the rotor. At each instant, each cam surface 31 cooperates with a piston 26 and only one. These cam surfaces are shaped so as to allow, when the pump rotor rotates, the movement towards the center of the rotor of the two pistons of one of the groups of systems and the movement of the two other pistons of the other group towards the periphery of the rotor. This results in an instantaneous variation in volume of the chambers 27 of the systems, the absolute values of the instantaneous volume variations being substantially equal.
• the hydraulic motor is built according to the same architecture as that of the heat engine previously described.
• the hydraulic motor 25 ( Figures 13 and 14 and 60) is constituted by at least two consecutive capsulisms produced by rotors 5 'and 8', one of these capsulisms constitutes the front chamber and the other the rear chamber.
• the rotors 5 'and 8' respectively constituting the stator and the rotor of the hydraulic motor, can be independent elements coupled to the rotors 5 and 8
• the rotors 5 'and 8' are mounted in interpenetration and the rotor 5 'is hollow and comprises two recesses 7' of the same shape as the recesses 7 of the rotor 8 and two pistons 5'A of the same shape as the pistons 5A of the rotor 5 said pistons 5'A having a face 7'A and a face 7'B.
• the rotors 5 'and 8' are mounted in a cylindrical chamber 2 'formed in a tubular element 54, the rotors 5', 8 'and the cylindrical chamber are coaxial.
• the tubular element 54 is fixed to the rotor 5 ′, the latter by the cylindrical surface of each of its pistons 5 ′ A is mounted in close fit in the cylindrical chamber 2 ′.
• the pistons 5'A, 10 'and the cylindrical chamber form four capsulisms
• each piston 5'A open two pipes, one of which is a supply pipe 29A and the other a delivery pipe 29B.
• the tubular element 54 can be mounted in rotational guide bearings and can be fixed to the rotor of the pump 24. It can also be integral with the pump rotor 24.
• the hydraulic motor will be separated axially from the heat engine and formed in the cold part of the engine block.
• the hydraulic motor and the heat engine operate in phase.
• the front chamber of the hydraulic motor is supplied with hydraulic fluid by the hydraulic pump 24 while the fluid contained in the rear chamber of this motor is called upon to flow back to the pump which allows the driving the rotor 8 about a quarter of a turn relative to the rotor 5, the latter during these phases performing about a quarter of a turn, the association of these two relative movements leading the rotor 8 to make a half turn relative to the block engine.
• the rotor 5 can rotate 100 degrees relative to the engine block while the rotor 8 rotates 80 degrees relative to the rotor 5.
• the movement of the rotor 8 is first accelerated to a maximum speed and then slowed down.
• the supply to the front chamber of the hydraulic motor ensures the mobilization of this rotor 8 during the acceleration phase of the rotational movement. This mobilization is controlled during the deceleration phase of the rotor 8 by the rear chamber of the hydraulic motor.
• the oil flow supplied by the pump to the front chamber of the hydraulic motor during the compression phase is therefore variable, that is to say that it is first increasing then decreasing.
• the increasing phase of the flow corresponds to the acceleration of the movement of the rotor 8 while the decreasing phase corresponds to the slowing down of the movement of the piston 8, this movement always being controlled by the rear chamber of the hydraulic motor.
• the oil contained in the rear chamber of the hydraulic motor is caused to flow back to the pump always at a variable flow rate.
• connection between the hydraulic motor 24 and the hydraulic pump 25 when the actuating means is engaged. and therefore that the motor and the pump operate in closed loop, is a hydrostatic transmission.
• the rotational speed of the intermittent movement rotor is constantly controlled by the hydraulic pump, whether during an acceleration or deceleration period.
• the front and rear chambers of the hydraulic motor are isolated from one another by the rotary valve, which allows the mobilization of the rotor 8.
• the rotary valve ensures communication between the front and rear chambers of the hydraulic motor 25 and the inlet and outlet of the pump 24.
• the rotary valve establishes a hydraulic communication between the lines 29A and 29B, which produces a hydraulic shunt, this communication is broken during the compression and exhaust phases.
• Each cylindrical chamber 27 is associated with a pipe 29A or 29B depending on whether this chamber 27 is connected to the internal volume of one of the capsulisms forming the front chamber of the motor 25 or to the internal volume of one of the
• Each pipe 29A or 29B is established on the one hand between the associated chamber 27 and the corresponding capsulism and on the other hand between said chamber 27 and the rotary valve. These lines 29A, 29B are formed in the rotor of the pump.
• the two pipes 29A are arranged diametrically opposite, the same is true for the pipes
• This rotary valve is, for example, constituted by a disc
• the tips 33 of the pipes 29A are diametrically opposite, the same is true for the tips of the pipes 29B.
• lines 29A can be angularly offset by 90 ° with respect to those of lines 29B.
• the two end pieces 33 associated with the pipes 29A evolve in a common circular orbit different from the common orbit according to which the end pieces 33 of the pipes 29B evolve.
• the disc is hollowed out by two diametrically opposite grooves 34, developing along an arc of circumference substantially equal to 90 °.
• the disc of the rotary valve is set angularly with respect to the motor so that the start of the phases
• each end piece 33 is greater than the width of each groove so that the end piece 33 when it is opposite the groove, slides on the edges of the latter.
• Each nozzle 33 is opposite one of the grooves of its orbit during the expansion and admission phases, therefore the conduits 29A and 29B are in communication with each other through the volume of the chamber cylindrical 32A and grooves 34.
• the end pieces 33 are angularly separated from their respective groove 34 and are closed by the flat face of the disc 32, which interrupts the communication between the pipes 29A and 29B.
• the pump stator forms a sealed housing in which the rotor of the pump rotates.
• the sealed housing is also filled with oil.
• the pistons no longer have a roller 28 but each a sliding shoe 70 subject to sliding on the concave surfaces of cam 31 preferably formed in an internal ring 24A of the stator of the pump 24.
• crown as can be seen in FIG. 61, has two lateral surfaces 24B perpendicular to the axis of rotation of the rotor.
• Each sliding shoe 70 has a convex surface 71 in a spherical cap, which comes to bear in a
• flaring 72 substantially conical in the piston 26. This arrangement allows the pivoting of the shoe relative to the piston.
• the sliding shoe 70 is provided with two sides
• the sliding pad 70 furthermore comprises two parallel support lips 74, spaced from one another,
• the pump rotor is equipped with two flanks 77 in the form of a disc coming to be disposed on either side of the internal ring 24A.
• the sides 77 of the pump rotor are each fitted with a radial opening 78 between the edges of which the sliding shoe 70 is mounted by one of its sides 73.
• rear edge of each opening 78 comes into contact with the corresponding flank 73 of the pad.
• sliding shoe 70 follows the contour of an arc of circumference of a circle.
• the rotary valve of the pump according to this embodiment is constituted by the circular ring 24A on the one hand and by the sliding pads on the other hand. From each of the side faces 24B are hollowed out in the circular ring 24A two diametrically opposite grooves each arranged adjacent to a cam surface 31 and developing in parallel with the corresponding cam surface.
• the two grooves hollowed out 24C in the crown, from one of its lateral surfaces 24B, are offset by 90 degrees relative to the grooves 24C hollowed out in the crown 24A from the other lateral surface.
• the grooves are arranged on the orbits of the sides 73 of the sliding pads 70.
• the two grooves of one of the lateral surfaces 24B are intended to cooperate with the chamber systems 27 and pistons 26 assigned to the mobilization of the rotor 8 'of the hydraulic motor.
• the other two grooves are intended to cooperate with the other two systems, the latter being in relation to the rear chambers of the hydraulic motor and being assigned to control the mobilization of the rotor 8 'during the phase of
• the grooves intended to cooperate with the systems assigned to the mobilization of the rotor 8 ′ are respectively adjacent to the two cam surfaces cooperating during compression and exhaust, with the two systems assigned to the
• the cam surfaces 31 of the rotary piston pump according to the two embodiments preferably provide a sinusoidal variation in the volume of the capsulism formed by each piston 26 and chamber 27 assembly.
• the volume variation instant of the front and rear chambers of the hydraulic motor is constant while the instantaneous volume variation of the abovementioned capsulisms are sinusoidal.
• each of them To facilitate the admission of oil into the different assemblies and avoid excessive depression in each of them, provision will be made for each of them to have a channel formed in the pump rotor from one of the external faces of the latter towards for example 'the corresponding cylinder 27. To this channel will be associated a non-return valve preventing any backflow of oil, through the channel from the cylinder 27 to the sealed housing.
• This back pressure can be created for example by a pressure limiter disposed on the oil delivery circuit to the sealed housing.
• the start of the compression phase for the thermal engine and therefore the start of pressurization of the front chambers of the hydraulic motor correspond to the equality of the absolute value of the oil flow at the outlet of the systems assigned to the mobilization of the rotor 8 'with the absolute value of the oil flow that can be introduced into the front chambers of the hydraulic motor. In this way the setting in motion of the rotor 8 'is started smoothly.
• the four phases of the thermodynamic cycle are completed on a complete turn, each phase corresponding approximately to a quarter turn of the rotor 5, the rotor performing a stop during the intake phase a rotation of a half turn during the compression phase, a stop during the ignition-expansion phase or
• exhaust valves 37 for example four grouped in pairs diametrically opposite. The position
• the two capsulisms are in communication with one another by an orifice 51 formed in the rotor 8 and more precisely in the piston body 10.
• a single pair of capsulism may be provided or, according to a variant, several pairs of capsulism. According to this embodiment, a single pair of capsulism may be provided or, according to a variant, several pairs of capsulism. According to this embodiment, a single pair of capsulism may be provided or, according to a variant, several pairs of capsulism. According to this embodiment, a single pair of capsulism may be provided or, according to a variant, several pairs of capsulism. According to this
• the capsulism pairs will be shifted
• the phase of expansion of the gases in the capsulisms of one of the pairs of capsulisms may correspond to the phase of admission of the gases into the two capsulisms of the other.
• the partition walls are radial partitions of the rotor 5, the latter comprising several pairs of recesses 7 axially spaced from one another with or without offset
• the rotor 8 according to this form of embodiment will be equipped with several pairs of pistons 10 cooperating respectively with the recess pairs 7.
• thermodynamic cycle taking place in one of the two capsulisms is offset in phase with respect to the cycle taking place in the other, the four phases of the cycle carried out by the two capsulisms being accomplished over a half-turn.
• valves 36, 37 are controlled in the direction of opening and closing by hydraulic members such as rotary actuators.
• Each valve may be constituted by an axis rotatably mounted in a cylindrical housing made in
• the valve will have a diametral bore 39 in the form of a light which can be aligned with the radial passage 38 or else offset
• the valve axis comprises, at a distance from the diametric bore, a piston 40 disposed in a housing 41 of the body 1.
• This piston 40 divides this housing into two chambers, a front chamber and a rear chamber. In each chamber there is a hole connected to a hydraulic circuit for controlling the position of the valve in relation to the phases of the thermodynamic cycle.
• Each valve may also be constituted by a rotary plug 79 as can be seen more
• This rotary valve will be housed in a cylindrical chamber of the engine block arranged adjacent to the cylindrical chamber 2 and in relation to the latter by communication orifices 80 alternately closed and released by the rotary valve 79 and this in accordance with the phases of the thermodynamic cycle taking place in the motor capsulins.
• Figures 62 and 63 is shown a motor according to the second embodiment and the rotary valve is associated with intake ports.
• the rotary valve is diametrically opposed to the spark plug and we notice that the intake and compression of gases are carried out in the cold part of the engine which favors the
• the volume of gases admitted into the chamber is approximately 10% greater than the volume of the finally expansion chamber, which can be assimilated to a
• the gas mixture is first introduced into the chamber of the rotary valve 79 and is then introduced into the engine capsulisms by passing through the intake orifices 80.
• the rotary valve 79 consists of a cylindrical element hollow comprising perpendicularly to its axis of revolution an end wall 81 by which it is fixed to a drive shaft 83 rotatably mounted in a bearing and coupled to a toothed pinion 84 cooperating in mesh with a toothed crown 85 in engagement with the rotor 5.
• the cylindrical wall of the rotary plug has a longitudinal opening 82 delimited by two longitudinal edges.
• the angular speed of the plug 79 is twice that of the rotor 5 and the arc of circumference of the circle separating the two longitudinal edges of
• the opening 82 has the value 180 °.
• the introduction of gas into the valve chamber is carried out axially and the gases by passage through the hollow valve first then by passage through the intake orifices on the other hand is introduced into the chamber. admission.
• the rotary plug is associated with a lubrication element 86 housed in a cylindrical chamber adjoining that of the plug 79 and in communication with the latter.
• This lubricating element made of porous and spongy material, for example of felt, is supplied with lubricating oil and is subjected to come against the surface.
• cylindrical outer plug 79
• the bushel transports oil delivered to the gas mixture. This provision provides lubrication of the motor capsulism.
• the engine as described comprises a cooling circuit from which is drawn a fluid
• cooling such as air.
• the rotor 8 is hollow and the axial bore that it presents constitutes a part of the air cooling circuit.
• the engine also includes a water cooling circuit 95 comprising a water inlet 96 and an outlet 97.
• each pair of piston 10 is hollowed out at least one channel 42 opening on the one hand into the axial bore of the rotor and on the other hand into one of the two capsulisms not used for the evolution of the gas mixture , this drilling and this capsulism constitute the other part of the cooling circuit.
• the cooling fluid is evacuated from this capsulism by passage through the exhaust.
• the channel 42 can be replaced by at least one radial hole made in the wall of the rotor 8. Furthermore, in the core 13A of the non-return mechanism will be provided
• the wheels and the pinion are dimensioned so that the motor shaft 43 rotates twice as fast as each rotor 5.
• each motor assembly comprises a hydraulic pump 24 with radial pistons actuated by a rotor, formed on the motor shaft 43, the rotor being common to all the pumps 24.
• Each pump comprises two pistons 87, 88, each mounted in a cylinder 27 and arranged in the same plane radial to the shaft 43 , each piston being actuated in its cylinder by the pump rotor.
• Each pump feeds via a rotary joint 52 to the rear chamber of the hydraulic motor 25 of the corresponding motor assembly and via a rotary joint 53 supplies the front chamber of this same hydraulic motor 25.
• the cylinder 27 'of one of the pistons is connected via the rotary joint 52 with the rear chamber of the engine 25, the other cylinder 27' being connected via the rotary joint 53 with the hydraulic motor front chamber 25.
• the rotor is formed by two eccentrics 47 and 48 of the same diameter, axially spaced from one another and angularly offset from each other by an angle of 180 degrees. With these two eccentrics cooperate respectively the two pistons 87, 88 of each pump and by rotation of the eccentrics, one of the pistons is actuated in its cylinder 27 'in the direction of insertion while the other is actuated in its cylinder in the direction of exit. As said previously, the volume variations of the cylinders remain substantially equal in absolute value.
• each piston is hollow.
• the piston receives a compression spring bearing against the bottom of the cylinder.
• the displacement of the piston in the driving direction is therefore effected against the action exerted by the compression spring.
• This compression spring moreover, maintains contact between the piston and the eccentric.
• the piston by its foot bears against the cylindrical surface of the eccentric by
• the contact surfaces between the sliding shoe 49 and the foot of the associated piston being in the form of a spherical cap to allow misalignment.
• a rotary valve common to all the pumps are operated on the rotor, this valve being formed by the two eccentrics 47, 48 which for this purpose are each equipped with a groove 50 hollowed out in their cylindrical surface according to a fraction of their perimeter.
• the foot of each piston and the sliding shoe 49, in line with the trajectory of the corresponding groove, are drilled right through.
• the sealed chamber 44 is filled with oil.
• the upstream ends of the grooves 50 have no angular offset from one eccentric to the other.
• each eccentric 47, 48 closes the orifice of the sliding pad 49.
• the orifice of the pad 49 is closed during the compression and exhaust phases, during the intake and expansion phases, this orifice being opposite the groove 50.
• each engine 25, or driving chamber is pressurized and supplied before the rear chamber is closed at the pad 49.
• Figures 64, 65 and 66 is shown a thermal machine with only two engine blocks.
• the radial pistons 87, 88 of the pumps are held against the eccentrics 47, 48 by elastic rings 89 surrounding the common rotor of the radial piston pumps and each cooperating with the piston of one pumps and the piston on the other.
• the hollow formed in each piston is of frustoconical shape.
• each piston penetrates a fixed keel 90 secured to the pump body.
• each pump is connected to the corresponding motor by two rotary joints 91, 92 coaxial, tubular, mounted one inside the other.
• One of the tubular seals, the seal 91 is in communication with the rear chambers of the engine, the other with the front chambers.
• the two rotating joints of different length
• compartments 93A, 93B separates the two rotary joints 91, 92 from one another.
• One of the compartments of the housing is in communication with one of the seals 91 on the one hand and with one of the cylinders 27 'of the pump on the other hand while the other compartment is in relation on the one hand with the 'other joint and with the other cylinder on the other hand.
• the hydraulic pump in its various embodiments comprises at least one motor system constituted by a piston 26 and a cylinder 27 associated with the front driving chamber of the hydraulic motor and forming with the front chamber a hydraulic motor circuit, and a control system constituted by another piston 26 and another cylinder 27, associated with the rear chamber of the engine
• At least one tared means is provided for automatically discharging one of the circuits when the pressure in the other reaches a determined taring value.
• a calibrated means is provided by hydraulic circuit.
• Each calibrated means essentially consists of a piloted valve 99 with calibration spring 100, this valve by its pilot being associated with the pressure circuit. and comprises a piston 101 displaceable axially in a cylinder 102 under the effect of a hydraulic thrust at
• the piston has a diametral bore 103 which when the piston is pushed back into the cylinder by an action equal to or greater than the setting value comes opposite the radial bore 104 made in the wall of the cylinder, one of which is related to the hydraulic circuit to be placed at the landfill and the other is related to this landfill.
• Each hydraulic pump 24 may comprise a device for admitting oil into the associated hydraulic circuit or for booster, when the latter is subjected to vacuum.
• this device consists of an intake check valve 98.
• This valve is in relation on the one hand with the internal volume of the pump and on the other hand with an oil supply orifice, the oil can be under pressure.
• valve 98 is mounted in a housing of the keel 90. We can also see that this keel from the valve housing is pierced
• command and control circuits will be equipped with all the necessary safety devices, and pressure relief valves associated with each circuit may be provided to

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Hydraulic Motors (AREA)
• Pistons, Piston Rings, And Cylinders (AREA)
• Reciprocating Pumps (AREA)
• Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Applications Claiming Priority (5)

Publications (2)

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ID=26230970

Family Applications (1)

Country Status (8)

Cited By (1)

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• 1994
  • 1994-12-23 FR FR9415686A patent/FR2716494B1/fr not_active Expired - Fee Related
• 1995
  • 1995-02-16 WO PCT/FR1995/000185 patent/WO1995022684A1/fr not_active Ceased
  • 1995-02-16 DE DE69507128T patent/DE69507128T2/de not_active Expired - Lifetime
  • 1995-02-16 EP EP95909837A patent/EP0748415B1/de not_active Expired - Lifetime
  • 1995-02-16 AT AT95909837T patent/ATE175471T1/de active
  • 1995-02-16 US US08/693,046 patent/US5992371A/en not_active Expired - Fee Related
  • 1995-02-16 JP JP52163295A patent/JP3612334B2/ja not_active Expired - Fee Related
  • 1995-02-16 CA CA002182742A patent/CA2182742C/fr not_active Expired - Fee Related

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