JPH0436242B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a machine having a piston with a non-linear movement, especially used as a combustion engine, compressor, pump, etc., avoiding linear movements of moving parts.

The object of the invention is to provide a machine of simple and robust construction in which the sealing problems as well as the friction and maintenance problems can be easily solved.

Such a machine can be found, for example, in the proposal of US Pat. No. 4,021,158. These existing machines require that the pistons perform their own rotational motion, their kinematic linkage to the machine shaft is complex, creates sealing problems between the pistons along their hinge line, and the spherical pistons and require a chamber. Since they do not have a continuous longitudinal axis, these machines are not suitable for transmitting torque.

Pistons that move within a chamber and have a rotational motion relative to the chamber can only be of spherical shape. These relative movements that are not performed along only one direction make it difficult to maintain a tight seal between the pistons and their chambers.

Other problems with all internal combustion engines are caused by the extremely high pressures that exist between the pistons and their chambers, resulting in significant deformations of the chambers, such as ovalization of the cylinders and wear of the pistons in ordinary motors. give rise to

The invention further provides that during the working cycle the pistons do not rotate on their own and have only one angular movement relative to their chambers, and the pressures between the pistons and the chambers due to compression and explosion cancel each other out. The purpose is to provide machinery.

This machine with a rocking chamber and a piston has the characteristics of claim 1.

An embodiment of a machine according to the invention and some variations thereof are shown in the figures.

The machine shown in FIGS. 1-6 includes only one actuating unit for the sake of clarity of drawing and description. In practice, the machine can include a plurality of actuating units, for example four, six or more, which are connected together.

The machine includes a through shaft 1 journalled on a frame 2 in two bearings 3 . A central cylindrical bearing 4 is carried on the shaft 1, the axis of which is perpendicular to the shaft 1. This bearing 4
is fixed against angular movement with the shaft 1 by a pin 5 and axially fixed with the shaft 1 by a screw 6.

The cylindrical central bearing 4 is used as a hinge for the pivot 7, the longitudinal axis of which cuts the axis of the through shaft 1 at o. This central pivot 7 is thus fixed in angular and axial movement with respect to the through shaft 1, but relative to said axis 1 in a plane formed by the axis of said central pivot 7 and one of the through shafts 1. It can be swung. The axis of the central pivot 7 is therefore inclined on its own with respect to the axis of the through shaft 1.

In this embodiment, the through shaft 1 has a central axis 7
At the same time, the control member of this central axis is mechanically connected to the central axis.

The illustrated single machine further includes two chambers 8, 9, each of which is formed by a first outer shell 10 and a second inner shell 11, the upper and lower ends of which fit one over the other. Ai, Katsukuriyu 1
3 to the central pivot 7 by a fastener 12 which is likewise secured together to the distal end of the central pivot 7.

Each shell 10 includes a cylindrical boss 14 whose axis passes through the intersection o of the axis of the central pivot 7 and the through shaft 1 and is perpendicular to said two axes.

A circular distribution ring 15 surrounds the two shells 10 and includes two housings that receive the bosses 14 of these shells 10. Therefore this distribution ring 15
The movement is fixed to the outer shell 10, and then to the central pivot 7 and the through shaft 1.

A seal is provided between the shell 10 and the distribution ring.

A passageway 16 is provided in the cylindrical boss 14 of the shell 10 which connects the chambers 8, 9, respectively, to a housing 17, 18, respectively, provided in the distribution ring 15.
These housings 17, 18 are connected to the frame 2 via passages 19, 20, as will be seen in the description below.
These slots are themselves connected to the inlet and outlet or discharge ducts of the machine, respectively, as well as to the ignition system of the machine.

A hermetic seal is provided between the distribution ring 15 and the frame 2.

The single machine shown also has two working surfaces 24, 24a and 2 each moving freely within the chambers 8, 9.
Two compound pistons 2 with 5 and 25a respectively
Including 2,23. These working surfaces of the piston 2
4 and 25 are made from parts assembled to the pistons 22 and 23. These mounting parts 26 are slidable in their plane relative to the piston, ensuring a self-centripetal action of these parts in the chambers 8, 9. These fittings 26 contain sealing elements, such as segment-shaped, thereby ensuring a complete seal between their edges and the inner walls of the chambers 8, 9 formed by the shells 10, 11. guaranteed.

The pistons 22, 23 each have an opening 27 providing passage to the through shaft 1 and include an arm 28 at their respective lower end. These arms 28
carries a guide slide 29 which slides in a cup 30 provided at each end of the central pivot 7. In this way, the piston is maintained in a fixed axial position relative to the central pivot 7 and pivoted concentrically on said pivot.

These arms extend beyond the upper and lower ends of the working surface of the piston.

In this way, complete guidance of the piston within the chamber is achieved and the piston moves freely within the chamber without any contact except by the sealing segment.

The illustrated unitary machine further includes eccentric members 31, 32 journalled concentrically with the through shaft 1 and whose working parts 33, 34 have axes, the axes of which extend to the central pivot 7 from the through shaft. It intersects at the point o where it also intersects. These working surfaces of the eccentrics rotate within housings 35, 36 provided on the pistons 22, 23. Eccentric member 33, 3
Each working part of 4 is traversed entirely by a through-shaft 1, and these eccentrics, by virtue of their construction with large dimensions, ensure that the pistons are moved while ensuring a significant angle between the axes of said eccentrics and the axes of the through-shaft 1. It turns out that they allow large angular movements with respect to each other.

This single machine has at least one eccentric member 31,
It further includes a kinematic device for providing relative rotation between 32 and the through shaft 1. In the illustrated example, the two eccentric members 31 and 32 are rotationally driven with respect to the through shaft 1. A first kinematic coupling mechanism couples the eccentric member 31 to the through shaft 1, and a second kinematic coupling mechanism couples the eccentric member 32 to said through shaft 1.

The kinematic coupling mechanism between the eccentric member 31 and the through shaft 1 includes a toothed pinion fixed to the eccentric member 31 and concentric with the through shaft 1, with a pin 48 and a screw 4
9 meshes with a pinion 38 freely rotating on a shaft 39 which is fixed to the through shaft 1 and a crank 40 which itself is fixed. This satellite-moving idling pinion 3
8 meshes with a toothed crown 41 which is also rigidly connected to the frame 2. The separation ratio of this kinematic coupling is determined such that the eccentric member 31 rotates about the through shaft 1 in the same direction as the through shaft 1 at a speed V ₂ that is always greater than the rotational speed V ₁ of the through shaft.

The kinematic coupling mechanism connecting the eccentric member 32 to the through shaft 1 includes a pinio 42 fixed to the eccentric member and concentric with the through shaft 1, and a crank 45 which is itself fixed to the through shaft 1 by a pin and screw. It meshes with a first satellite pinion 43 that freely rotates on a fixed axis 44. This crank 45 is connected to the second axis 4
6 and on its axis the first satellite pinion 43 on the one hand and the frame 2 on the other hand.
A second planetary pinion 43a that meshes with a toothed crown 47 fixed thereon is provided with an idling journal bearing. The separation ratio of this kinematic linkage is such that the rotational speed V ₃ of the eccentric member 32 about the through-axis 1 is equal to the absolute value of the rotational speed of the eccentric member 31 about this same axis 1 but opposite in direction. determined. Through these kinematic coupling mechanisms, |V ₂ |= |V ₃ |＞|V ₁
｜You can know the relationship. In this example machine, each piston 22, 23 has a corresponding chamber 8,
9, two alternating movements are performed for one revolution of the through shaft 1. To obtain these four movements of each piston, the separation ratio of the kinematic linkage is 1:2. By varying these ratios, various numbers of reciprocating pistons can be obtained per revolution of the through shaft.

In FIG. 3, the fixing member 12 and the screw 13 are
The details of the method of fixing the shells 10, 11 on the central axis 7 can be found here.

It can be seen that the upper edge 10 of the outer shell rests on a shoulder provided on the upper edge of the inner shell 11. Fixed member 12
are arranged on the tops of these two shells 10, 11 to maintain these shells in an axial position relative to the central axis 7, while at the same time keeping the shells 10, 11 relative to the central axis 7 by means of the outer shoulder of the fixing member. maintain the radial position of This fixation ensures a tight seal between the edges of the shell that are in contact.

In FIG. 3, a variant embodiment is shown in which the chambers 8, 9 have a rectangular cross section. This is due to the fact that the piston performs a simple angular movement relative to these chambers 8, 9, which is carried out only by rotation about the central axis 7, with these chambers fixed and in concentric relation. It is absolutely possible.

The extremely primitive structure and design of the machine described above makes it necessary to mention a certain number of features achieved with it.

1 During the rotation of the through shaft 1, the rotation of the distribution ring 15 takes place with the same speed V ₁ and without any translational movement or tilting of this ring 15. This greatly facilitates the inflow and outflow operations of the chambers 8,9.

Due to the relative rotational movement between the eccentric members 31, 32 and with the through shaft 1, the working surfaces of the pistons 22, 23 move closer to each other and move away from each other, changing the volumes of the chambers 8, 9.

During this movement, the axis of the piston traces a conical shape,
Its apex is located at the intersection o of the axis of the central pivot 7 and the through shaft 1, while the pistons do not rotate on their own due to the slippage between them and their eccentric members. This is possible due to the fact that the piston has a large opening that allows passage into the through shaft 1. This opening is at least equal in surface to the intersection of the piston and the conical surface, its top is located at point o and its bottom is constituted by the edge of the active part of the corresponding eccentric.

Note that during this movement, the central pivot 7 performs an angular swing, and the chambers 8, 9 and the shells 10, 11 rigidly attached thereto rotate around the central cylindrical bearing 4, and the through shaft 1
The inclination of the axis of the center pivot 7 is changed with respect to the axis of the central pivot 7.

Working parts of eccentric members 33 and 34 and each piston 2
2, 23, these pistons do not rotate by themselves, while the eccentric member 3
1 and 32 rotate around the axis of the through shaft 1.

This therefore corresponds to the piston 22 for the chambers 8, 9,
The movement of 23 is a simple turning movement around the central axis 7. Therefore, these chambers do not necessarily have to be spherical, but can be of any shape, provided that the outer and inner surfaces of these chambers are rotating surfaces with a central pivot axis relative to the axis of rotation.
It is therefore possible to design a curved chamber whose outer or inner line has an arc, a zigzag line or a right angle. As can be seen in FIG. 4, when the eccentric members are facing each other, the central pivot axis 7 is perpendicular to the through axis 1. In this position, the pistons 22, 23
are at their extreme positions. However, if the eccentric members are located in parallel planes, their axes are aligned and the central pivot 7 has a maximum inclination with respect to the through axis 1. In this position the pistons are in their central position (FIG. 5).

The active part of the eccentrics 33, 34 is due to the fact that these eccentrics are located very close to the center of the unit and that they move within the chambers 8, 9. It can have extremely large dimensions without limiting the opening angle between the faces. This arrangement is possible because the large opening of the piston allows it to move about the through axis 1.

The distribution ring 15 rotates at the same speed and in the same direction as the through shaft 1, and these elements are rigidly connected to each other by the casing. This case replaces cranks 40, 45, and satellite gears 38, 43,
43a. This provides a strong structure, and not only transmits torque through the through shaft 1, but also partially takes charge of the torque through the distribution ring 15 and the case. Thus, it is possible to realize a motor with an extremely coherent configuration having an outer distribution ring but nevertheless having a small diameter, which is important for high speed rotation.

The forces are evenly distributed on the two eccentric members of large diameter.

The piston exerts no force on the chamber wall except by the sealing segment. This significantly reduces piston and chamber wear. The working surface of the piston is centripetal.

Multiple units can be arranged on the same through axis. In this case, the central pivot is mounted to swing against the balance of the assembly.

During the explosion or combustion of the mixture, the gases tend to project outwards strongly. This is advantageous in this construction since the piston has a larger working surface towards the outside than in the centre. The explosive force is divided into two working surfaces, and thus two bearings of the eccentric, and this working force is distributed even better in the case of diesel motors, for example.

This machine has two chambers fixed to the central axis,
and is well balanced due to the fact that the unbalanced mass constituted by the piston and the eccentric member is easily compensated by the balanced mass.

To operate this machine as a four-stroke cycle combustion engine (Figures 7 and 8), a)
The separation ratio between the through shaft 1 and the eccentric members 31 and 32 is set to 1:2 and 1:-2, respectively. Thereby, for one complete revolution of the through shaft 1, the pistons make two reciprocating movements in each of their chambers, which corresponds to one complete cycle. b) Providing housings 17, 18, respectively, of distribution ring 15 for chambers 8, 9, respectively, opening on opposite sides of distribution ring 15; c) Provide a window or slot on the right side of the frame 2 (Figure 8). The inlet slot 50, which extends over approximately 90°, is followed by a closed area over approximately 90°. At this point, an ignition point 51 is formed, for example, by a spark plug, which is followed by a further closed area extending over approximately 90 DEG and in addition a drain hole 52 extending over approximately 90 DEG is formed. d) On the left side of the frame 2, identical slots 50, 52 and an ignition part 51 are provided, offset by 90° to the right side of the stator (FIG. 7).

This staggered arrangement of the slots and the ignition point is necessitated by the fact that when one chamber has its minimum volume, ie at the beginning of its introduction, the other chamber is at its maximum volume. Since the ignition point is separated by 180° from the initial position of the introduction, it is possible to shift the inlet, outlet and ignition device by 90° between the two chambers 8,
It is necessary between 9 and 9.

To make this machine work as a compressor,
For example, a) the ratio between each eccentric member 31, 32 and its through shaft 1 is 1:3 and 1:-3, respectively;

In this way, for each complete revolution of the through shaft 1, the piston of one chamber makes three reciprocating movements.
b) Since this cycle has only two phases, namely compression and introduction, the housings 17, 18
are opened on the same side of the distribution ring and the introduction 53
The stator is provided with a series of slots extending over approximately 60 DEG for alternating the discharges 54 and 54.

A wide variety of variations of this machine are possible. Instead of multiple pistons, it can also be constructed with only one chamber and two single pistons. Similarly 2
It is also possible to provide only one dual piston or single piston cooperating with two respective chambers.
In this case, the chambers are closed at one of their front ends by a fixing member.

It is also possible to provide a kinematic coupling mechanism that drives the fixed through shaft and the eccentric members 31, 32 that rotate in opposite directions and at the same speed around the through shaft.

In such a state, the piston has only a pivoting movement about the axis of the central pivot 7 and a rocking motion corresponding to the rocking of said central pivot. The chambers 8, 9 only pivot around the boss 14 by themselves. For the distribution of such machines with fixed through shafts, valves or any other slot system can be provided between the rocking part and the frame.

Furthermore, it is also possible to have chambers of different dimensions, in which case the pistons each have a large and small working surface. Such a design can realize a two-stage compressor.

A second embodiment of this machine is shown in FIG. This machine is also unique in order to simplify explanation and display.
Contains two actuating units. The machine includes a fixed frame 70 that houses all the moving parts of the machine. This machine also has two working surfaces 7
Piston 71 with 3, 74, 73a, 74a,
72, said working surfaces being formed by assembled parts as described in the first embodiment, which parts are connected to the working surfaces 73, 74 so as to have their centripetal nature within the chambers 75, 76. It can move parallel to the piston.

These pistons 71, 72 are guided axially and radially on a central pivot 77, as in the first embodiment. The outer surface of this central pivot 77 constitutes the inner wall of the chambers 75 and 76. The outer walls of these chambers 75, 76 are formed by a shell 78 fixed to the central axis and having a coaxial rotating part 79 perpendicular to the axis of the machine and to the axis of the central axis 77 and passing through the intersection o of these two axes. built.

These rotating parts 79 have and communicate on the one hand with passages 80 and on the other hand with inlet and outlet slots as well as ignition elements in the case of the combustion engine which are provided or fixed in the frame 70. It is disposed within a housing provided within a dispensing case 81 having a passageway 82 therein.

This machine further includes two eccentric members 83, 84.
, the active parts of which are constituted by trunnions 85, 86 and are accommodated in corresponding bearings provided in the pistons 71, 72. The eccentric member 84 is journalled on a shaft 87 that is rigidly connected to the frame 70 and extends coaxially with the longitudinal axis of the machine. This eccentric member 84 is connected to two satellite gears 9 that freely rotate on an axis fixed to the distribution case 81.
It includes a pinion 88 coaxial with a fixed shaft 87 kinematically connected to the toothed crown 89 by 0,91.

The other eccentric member 83 is in this case journalled on a control member formed by a drive shaft 92 pivotally mounted in the frame coaxially with the longitudinal axis of the machine.

This drive shaft 92 is in rigid contact with the distribution case 81. The eccentric member 82 carries a pinion 93 kinematically connected to a toothed crown 94 fixed to the frame 70 by means of a satellite gear 95 idling on an axis fixed to the distribution case 81 .

In this embodiment, the working part 8 of the eccentric member
The axes 5 and 86 also pass through the intersection o of the longitudinal axis of the machine and the axis of the center pivot 77.

Kinematic coupling mechanisms 93, 94, 95 coupling eccentric member 83 to dispensing case 81 and kinematic coupling mechanisms 88, 89, 90, 91 coupling eccentric member 84 to dispensing case 81 are connected to this dispensing case 8.
1 so that the eccentric members rotate in opposite directions and at the same speed.

In this embodiment, the machine has no through shaft;
The center axis is held only by the distribution case 81 via the shell 78, and the shell 78 and the distribution case 81 are fixed.

Also, the omission of the through shaft means that, as mentioned above, in one working unit with two pistons, the chambers 75, 76 are fixed to the central pivot 77, so that the longitudinal axis of the machine is This is possible due to the fact that it does not create an axial thrust. All the energy generated in the chambers 75, 76 is transferred to the control member or drive shaft 92 by the eccentric member, kinematic linkage and distribution case.

Obviously, this second embodiment of the machine can have only one chamber cooperating with only one double piston or with one or two single pistons.

The third embodiment of the machine shown in FIG. 11 is a machine that includes a plurality of actuating units, represented by four in the figure.

The machine includes two groups of two units mounted parallel on a drive shaft 100. Each group of units includes two units mounted in series on a through shaft 101.

In this embodiment, each actuating unit includes an oscillating central pivot 102 rotatably mounted on a through shaft 101. This central pivot 102 is rigidly connected, as in the previously described embodiment, to two chambers formed by a shell 103 fixed to rotate together with the dispensing case 104 about a through shaft 101. As in the previously described embodiment, this distribution case 10
4 cooperate with the fixed frame 105 and connect the chambers of the unit alternately to inlet slots 106 and outlet slots 106a formed in the frame 105. Channels 107 in the distribution cases 104 and 107a of the shell 103 are necessarily provided.

In this embodiment, each actuating unit includes two pistons 108,109, the working surfaces of which move within chambers 110,111. These pistons are guided on the ends of the central pivot 102, as in the previously described embodiments.

Further, these pistons 108 and 109 rotate on the active portions of eccentric members 112 and 113, and their axes intersect at the intersection o of the central axis 102 and the axis of the through shaft 101.

The eccentric member 112 of each working unit is in this case fixed to the through shaft 101, while the other eccentric member 113 of each working unit is journalled concentrically to the through shaft and is implemented by means of a kinematic coupling mechanism. Distribution case 10 constituting the control member in the example
Combined with 4.

The kinematic linkage includes an eccentric member 113 coaxial with the through shaft 101 and a fixed pinion 114 meshing with a satellite gear 115 carried on the distribution case 104 and freely rotating on an axis;
At the same time, it meshes with the toothed crown 116 fixed to the fixed frame 105. This kinematic coupling mechanism allows the eccentric member 113 to move in the same direction as the distribution case 104, but at a higher speed than the through shaft 104.
It is configured to rotate around.

In this embodiment, the distribution case 104 constitutes the control members for two coaxially actuated units.

One of the eccentric members 113 carries a pinion 117 coaxial with the through shaft 101 meshing with a gear 118 fixed to the drive shaft 100.

Finally, this drive shaft 100 further includes a pinion 119 meshing with a satellite pinion 120 idling on a shaft fixed to the fixed frame 105. This satellite gear 120 meshes with a gear 121 fixed to the through shaft 101.

The ratios of the various kinematic linkages are such that the relative rotational speeds of the eccentric members 112, 113 with respect to the control member, in this case the distribution case 104, are always equal but opposite in direction.

In the illustrated example, gear 118 and pinion 11
The ratio between pinion 119 and gear 1 is 1.5:1.
The ratio between 21 is 1:2, and the eccentric member 113 and the distribution case 104, that is, the coupling mechanisms 114, 115, 116
The ratio between them is 1:2.

Therefore, when the distribution case 104 rotates in one direction, the eccentric member rotates twice in the same direction relative to the case 104, and the eccentric member 112 fixed to the through shaft 101 rotates twice in the opposite direction. Thus, with respect to frame 105, one revolution of distribution case 104 corresponds to three revolutions of eccentric member 113 in the same direction and one revolution of eccentric member 112 in the opposite direction.

In this way, one revolution of the drive shaft 100 corresponds to one half revolution of the dispensing case 104, or one opening movement and one closing movement of the pistons 108, 109.

The arrangement of this third embodiment of the machine is extremely compact;
It allows the combination of several groups of actuating units in a closed cavity formed around a single drive shaft.

In general, all possible embodiments of the machine according to the invention have the following features:

1. One or several chambers fixed to the pivot axis.

2. A control member fixed in rotation with the chamber about an axis coaxial with the axis of rotation of one or several eccentric members.

3. A kinematic linkage providing relative rotation of an eccentric member with the same speed in opposite direction to the control member. This means whatever the control member is, i.e. a piston rotating on the working member of the eccentric member and guided axially and angularly with respect to the pivot axis, by means of a through-shaft or 4. The working surfaces move within the chambers to change the volumes of those chambers. The only movement of the piston within the chamber is pivoting around the central axis to which the chamber is fixed.

5 Preferably, the piston, other than the sealing member,
Pivoted about a central pivot to avoid friction between the piston and the chamber.

Next, the effects of the present invention are listed below.

1 Since the machine of the present invention has no valves, camshafts, or crankshafts, the engine is more compact and easier to manufacture and maintain than existing engines.

2. Since the machine of the invention has a hemispherical combustion chamber, it has higher combustion efficiency than engines with non-spherical combustion chambers.

3. The engine of the invention greatly reduces wear on the piston and the chamber, as the piston does not directly exert force on the walls of the chamber, and wear on the clamping segments is greatly reduced.

4. The machine of the present invention can be operated as a combustion engine or a compressor, and a wide range of functions and effects can be expected.

5. By adjusting the reduction ratio between the shaft and the eccentric of the machine of the invention, it is possible to select the number of operating strokes of the engine per revolution of the motor shaft. For this reason, it is possible to select the optimum relationship between smooth operation of the engine and movement of the piston.

[Brief explanation of drawings]

1 is a longitudinal section through a machine with one actuating unit corresponding to a two-cylinder machine, the piston being in one of its extreme positions; FIG. 2 shows the machine in that position shown in FIG. 3 is a partial top view with some parts broken or removed; FIG.
4 is a cross-sectional view along a plane perpendicular to the through axis and through the central pivot axis of a variant embodiment of the invention, the chamber being rectangular in shape, and FIG. FIG. 5 is a partial explanatory diagram corresponding to the member shown in FIG. 4, in which the piston is in an intermediate position between them, and this diagram is a view from above, not a side view. , FIG. 6 is a partially cutaway side view of the machine shown in FIG.
The figure shows the distribution surface of the distribution stator of a machine acting as a pump or compressor with three shifts of two strokes in one cycle; FIG. 10 is a sectional view of a second embodiment of the machine according to the invention; FIG. 11 is an illustration of a third embodiment of the machine according to the invention, which has several actuating units connected to one central drive shaft. Symbols in the diagram: 1... Penetration shaft, 2... Frame, 3...
Bearing, 4... Center bearing, 5... Pin, 6... Screw,
7... Central axis, 8, 9... Chamber, 10... Outer shell, 11...
Inner shell, 12...fixing device, 13...screw, 14...
Boss, 15... Distribution ring, 16... Passage, 17,1
8... Housing, 19, 20... Passage, 21... Slot, 22, 23... Piston, 24, 25... Working surface, 26... Assembly parts, 27, 28... Opening, 29...
Slide, 30... Cup, 31, 32... Eccentric member, 33, 34... Working part, 35, 36... Housing, 37... Pinion, 38... Pinion, 39...
Shaft, 40... Crank, 41... Crown, 42... Pinion, 43... Pinion, 44... Axis line, 45... Crank, 46... Second axis line, 47... Crown, 48
...Pin, 49...Screw, 50...Slot hole, 51...Ignition part, 52...Slot hole, 53...Introduction slot, 54...Discharge slot, 70...Frame, 71, 72...Piston,
73, 74... Working surface, 75, 76... Chamber, 77... Central pivot, 78... Shell, 79... Rotating member, 80... Passage, 81... Case, 82... Passage, 83, 84... Eccentric member, 85, 86... Trunnion, 87...shaft, 8
8... Pinion, 89... Crown, 90, 91... Satellite gear, 92... Drive shaft, 93, 94, 95... Connection mechanism, 100... Drive shaft, 101... Penetration shaft, 102
...Central axis, 103...Shell, 104...Distribution case,
105...Frame, 106...Introduction slot, 107...
Discharge slot, 108, 109... Piston, 110,
111... Chamber, 112, 113... Eccentric member, 114
...pinion, 115...pinion, 116...crown, 117...pinion, 118...gear, 119...
A pinion, 120...pinion, 121...gear are shown.

Claims (1)

[Scope of Claims] 1. A machine having a plurality of swing chambers and a plurality of pistons, comprising: a control member 1, 92, 104 having an axis; a central pivot 7, 77, 102 which is swingable relative to the control member about an axis perpendicular to and intersecting the axis of the control member; a swing path of the axis of the central pivot that crosses both sides of a plane passing through the intersection of the two, the axis of which forms an acute angle with the axis of the control member 1, 92, 104, and an axis passing through the intersection of the rotary bearing; at least one eccentric member 33, 83, 113, at least one chamber 9 rotating on said rotational bearing, pivoted concentrically with the axis of said central pivot and fixed against rotation with respect to said central pivot; ，
at least one piston 22, 71, 108 having at least one surface 24, 74 moving inside said eccentric member 33, 83, 113 and providing relative rotation between said eccentric member 33, 83, 113 and control member 1, 92, 104; Drive means and other machinery. 2. Machine according to claim 1, in which the control member 92 is a drive shaft fixed to the casing 81 which rotates together with the first chamber 76. 3 The second chamber 8, 75, 110 is the first chamber 9, 7
Central axis 7, 77, 102 opposite to 6, 111
and the second pistons 23, 72, 10
2. Machine according to claim 1, characterized in that 9 moves within the second chamber in the same direction as the direction of movement of the first piston. 4 The second piston 23, 72, 109 rotates on the second eccentric member 34, 84, 112, and the second eccentric member It has an axis passing through the intersection 0, and the driving means is the second eccentric member 34, 84, 1.
12. The machine according to claim 1, wherein a rotational force greater than that of the control members 1, 92, 104 is applied to the control members 12 in the same direction. 5. The chambers 8, 75, 110, 9, 76, 111 are composed of outer shells 10, 78, 103 forming their outer walls, and their inner walls are connected to the central axis 7, 77, 1.
Claim 1 consisting of the outer surface of 02
Machines listed in section. 6 Pistons 21, 22, 23, 72, 108,
10. A machine as claimed in claim 1, in which the peripheral seals 26 permit each self-centering. 7 The eccentric shaft 32, 33, 83, 84, 11
2, 113 and said central pivot 7, 77, 102 rotate in opposite directions at the same rotational speed. 8 Said chamber 8, 9, 75, 76, 110, 111
Machine according to claim 1, characterized in that the axis of rotation coincides with the central axis (7, 77, 102). 9 Said chamber 8, 9, 75, 76, 110, 111
9. A machine according to claim 8, wherein the outer surface of is part of a spherical surface. 10. Machine according to claim 1, comprising an annular distribution member ring (15) fixed for rotation with said at least one chamber about said axis of said control member (1). 11 the annular distribution member ring 15 is connected to the chamber 8;
Machine according to claim 1, comprising a pre-combustion chamber (17, 18) communicating with a pre-combustion chamber (9). 12 Several of the above machines form one casing 104
A machine according to claim 1, wherein the machine is located within a machine. 13. The machine of claim 1, wherein the casing 104 has at least one bearing, and the eccentric member 112 of each machine is rotatably supported thereon. 14 The second piston 23, 72, 108 rotates on the second eccentric member, and the second eccentric member 34, 84, 1
The axis of 12 passes through the intersection point 0 of the center pivot and the axis of the control member, and the driving means moves the second eccentric member 34, 84, 112 with respect to the control member and the first eccentric member 33, 83, 113 with respect to the control member. Machine according to claim 1, adapted to rotate at a speed and in the opposite direction. 15 The driving means is connected to both eccentric members 33, 3.
At the same speed as 4, 83, 84, 112, 113,
15. The machine according to claim 14, wherein the machine rotates in the opposite direction. 16 The driving means is one of the eccentric members 11
3. The machine according to claim 1, wherein the eccentric member 112 is connected to the control casing 104, while the other eccentric member 112 is fixed to the control member 101. 17 The piston 22, 23, 71, 72, 1
2. Machine according to claim 1, comprising means for guiding 08, 109 axially and radially onto said central pivot 7, 77, 102. 18. The machine of claim 17, wherein said guide means is located outside the chamber adjacent to said piston. 19. Machine according to claim 18, comprising two pistons each having said guide means. 20. The machine of claim 1, wherein the control member is a casing 104 that rotates with the chamber 111 and wherein the means cause relative rotation between the eccentric member 117 and the casing 104. 21 Claim 2, wherein the eccentric member 112 includes a through shaft 101 fixed for rotation.
The machine described in item 0. 22. The machine of claim 20, wherein the drive means couples the eccentric member 112 to the casing 104. 23 The control member is at least the drive member 1
A through shaft 101 passing through one of 12 and 113,
A machine according to claim 1. 24. The machine of claim 23, wherein the eccentric member 113 passes inside the chamber 9, 76, 111 during one rotation thereof. 25 The eccentric member 113 is connected to the piston 109
25. Machine according to claim 24, passing through the area of the chamber 111 swept by. 26 The driving means is the eccentric member 112, 11
24. Machine according to claim 23, drivingly coupling the through-shaft 101 with the through-shaft 101. 27 The drive means moves each eccentric member 112, 113 to the control member 1 by means of an external shaft 100.
27. The machine of claim 26, which is coupled to 04.