SE516724C2 - Hydraulically or pneumatically actuated pendulum or ring piston motor - Google Patents

Abstract

A hydraulically or pneumatically operated pendulum piston or ring piston engine, comprising a cylinder housing (1) having a toroid shaped cylinder race (2, 3), in which a pendulum piston means (6-8) is rotatable in two opposed rotary directions, and in which the cylinder race, at a place thereof is divided by a piston chamber wall having pressure supply means (15), and in which the pendulum piston means (6-8) is integral with a fly mass (9) which is connected to a central, output shaft (11), and in which the toroid shaped cylinder race (2, 3) is formed with two opposed, closed cylinder chambers (2, 3) each extending over nearly 120 DEG , and in which the pendulum piston means include two pistons (6, 7) which are integral over a bow formed piston rod (8) extending over an angle of about 240 DEG , and which piston rod (8) at an intermediate position between said pistons (6, 7) is controlled by and connected to (10) the output shaft (11) over the fly mass (9), and in which the fly mass (9) is connected to a reversing mechanism (19) for providing a reversing of functional operation of the output shaft (11) when the pendulum piston means (6-8) changes rotary direction, so that the output shaft (11) constantly rotates in one and the same direction.

Description

once: 10 15 20 25 30 516 724 2 EHRNERS 23540 is a solid, cohesive unit with few components, especially with a single arcuate drive means with two pistons each acting in a toroidal cylinder, a single power transmission means and a single simple turning means for reverse the direction of rotation at one piston movement to effect a rotation in one and the same direction of a central output drive shaft.

A motor of this type has a number of different advantages, namely that it can be designed small and light, the power of the motor can be very easily adapted to the needs, it can be driven with many different types of hydraulic or pneumatic pressure media, it provides very high efficiency in relation to its weight, it provides a practically constant force over the entire working class, it can be operated with a pressure medium that does not produce any exhaust fumes or other adverse environmental effects, it can be manufactured at a much lower cost, calculated in relation to the engine power, than what is possible with conventional OTTO, DIESEL or WANKEL engines or other types of internal combustion engines. A further great advantage of the engine in question is that the engine for each work cycle develops a work which is far greater than that developed by an internal combustion engine, namely 6-10 times greater work than that developed per work cycle of a conventional 4-stroke internal combustion engine. , or at least 4 times as much work developed by an internal combustion engine of the 2-stroke type. In the attached fi gur 4 the known principle of an internal combustion engine with rotating piston and rotating crankshaft with output shaft is shown in a diagram. It is known that the power from such an engine develops according to a kind of GAUSS curve which rises slowly from 0 ° for a 2-stroke engine, or from 360 ° for a 4-stroke engine, gives maximum power to the output shaft at approximately 90 ° and 450 °, respectively, and then slowly drops to zero force at or immediately after 180 ° and 540 °, respectively.

A pendulum piston motor can be designed so that it provides full power during almost the entire pendulum movement in each direction. The limitation of the power take-off consists of the means for supplying and reversing the direction of the hydraulic or pneumatic pressure medium, which means can be limited to an angle of 5-10 °. A rivet 10 15 20 25 30 516 724 3 EHRNERS 23540 pendulum piston engine according to the invention is schematically illustrated in Figures 1, 2 and 3, and in the curve in Figure 4, in parallel with the curve of a 4-stroke engine (dot-marked curve), the curve for power / work with the oblique parts of the curve. It appears that the work developed by a 4-stroke engine is about 10-15% of a work cycle comprising two revolutions on the output shaft, while a pendulum piston engine according to the invention is close to 95-100% during the same work comprising two revolutions on the output shaft. The power output shown for a 4-stroke engine with the dot-marked curve is between 360 ° and 540 °, ie at 2 rpm rotation of the engine, where the power begins to develop at 360 °, rises according to a Gaussian-like curve to a maximum at about 450 ° and gradually drops to zero at 540 °. The force from a pendulum piston engine is practically constant over the entire working motion of 720 °.

It appears that the average work that a 4-stroke engine develops is only about 1/8 of the work that is developed by a pendulum piston engine during the same working time. The average work from a 2-stroke engine is “only about 1/4 of the work that a pendulum piston engine develops over a period of time corresponding to two rotational revolutions on the output shaft.

As mentioned above, an ordinary pendulum piston motor provides a reciprocating or oscillating movement, which cannot be used without special means as a driving force in cases where a driving force with a constant direction of rotation is desired.

According to the invention, therefore, the pendulum piston motor is designed with means for reversing the rotational movement of the output shaft at either the clockwise movement or the counterclockwise movement of the pendulum piston. This can be done by the engine being designed with a 4-gear gear of the differential type with the gear ratio 1: 1, which in cooperation with two freewheels reverses the direction of rotation at one pendulum piston movement. To enable a power take-off during both rotational movements, the engine also comprises two freewheel clutches, which drive in different directions with respect to the shaft rotation, respectively, giving a freewheel function in the opposite direction. The two freewheel clutches are opposed to each other, so that they allow propulsion and disengagement in opposite directions of rotation, respectively, whereby the output shaft is driven with a constant direction of rotation. Suitably the differential gear has a gear ratio of 1: 1, but in order to achieve special effects it is also possible to use any other gear ratio for the planetary gear, whereby a periodic fluctuation of the drive movement on the output shaft can be obtained.

In a particularly preferred embodiment of the invention, the pendulum piston engine is designed so that the propellant (gas or liquid) acts on one piston on the piston side and the other piston on the piston rod side with the same pressure, the rotational movement taking place with about 50-80% greater force than towards the piston side, which has occurred before.

The invention will now be described in more detail with reference to the accompanying drawings. In the drawings, Figure 1 schematically shows in a cross section a first step in the function of a first embodiment of the invention, Figure 2 shows the situation after some movement in a first direction, and Figure 3 shows the situation immediately after reversing the direction of rotation. Figure 4 shows a comparative diagram of the work performed on a 4-stroke engine and a pendulum piston engine, respectively, according to the invention over the rotation of two revolutions on the output shaft. Figure 5 shows, in the same way as in Figure 2, a cross section through a second embodiment of the invention. Figure 6 shows a section along the line V1-V1 in Figure 5. Figure 7 shows schematically and in a section parallel to the output shaft two pendulum piston motors acting in parallel on one and the same axis, and Figure 8 shows in a schematic cross section two pendulum piston motors according to the invention mounted in parallel on one and the same output shaft with rotated at a certain angle in relation to each other.

The pendulum piston engine according to the invention shown in the drawings generally consists of a cylinder housing 1 with two toroidal cylinder bores 2 and 3 extending from a top position at 0 ° in 120 ° clockwise (0-120 °) and counterclockwise (360-240 °), respectively. , ie about one third of the rotational revolution in each direction. The cylinder housing 1 extends with its outer wall 4 around the entire engine and encloses all parts of the engine, while the inner wall 5 delimits the mentioned cylinder races 2 and 3 at 120 ° and 240 °, respectively. In each cylinder race 2 and 3: run 10 15 20 25 30 516 724 5 EHRNERS 23540, a piston 6 and 7, respectively, is movable between about: 0 ° -120 ° and i240 ° -360 °, respectively.

The pistons are connected and held in position by an arcuate piston rod 8, which in turn is connected to a pivot mass 9 via a projecting actuating arm 10. The pivot mass is mounted centrally in the housing, and it is connected to a central output shaft 11. The arm 10 is fi xered to the piston rod midway between the two pistons 6 and 7, and the system of pistons 6, 7, pivot 9 and arm 10 can rotate back and forth about 120 °, i.e. with the arm movable between 120 ° and 240 °. The pivot mass 9 carries a turning mechanism (see urer gures 6), and these parts are kept centered by two or more fixed bearings12.

The cylinder housing 1 consists of two housing halves 13 and 14, which are divided perpendicular to the output shaft 11, and which are sealed in a known manner both outwards and inwards, so that they delimit the two opposite, mutually sealed piston chambers 2 and 3.

For supplying pressure medium (gas or liquid) the device comprises a pressure supply and pressure cover means 15 which forms a relatively narrow end wall 16 at 0/360 ° in the cylinder housing 1. The pressure supply means comprises a reversing valve 16, which can alternatively be connected to an inlet channel 17 to the clock chamber 2 and the counter-chamber 3. The valve 16 can be mechanically, electrically or otherwise controlled so that it automatically reverses the supply of pressure medium to the opposite working chamber when the piston 6 or 7 approaches the end position in its working chamber.

As a result, the pressure medium will be supplied alternately and in practice without interruption to the two piston chambers 2 and 3. Figure 1 shows the housing the pressure medium has just begun to be supplied to the clock chamber 2, and Figure 2 shows that the pistons 6 and 7 with the piston rod 8 perform a rotational work under about 80 °. When the piston 7 approaches its end position next to the cover member 15, the valve 16 turns and the pressure is then applied to the counterclockwise chamber 3.

The turning mechanism 19, which is coupled to the pivot mass 9, forms a differential gear with 2 pairs of opposite angular teeth 20 and 21 cooperating with each other, which mutually have the same number of teeth, so that the gear ratio becomes 1: 1. The gear unit 19 is supported on the output shaft 11, which in its uranium: 10 15 15 25 25 EHRNERS 23540 516 724 e is stored in a bearing 22, 23 in each housing half 13, 14. Between each tooth 20 and the output shaft 11 is a freewheel 24, 25 mounted. One freewheel, such as the freewheel 24, provides drive in one direction (e.g., clockwise direction, see arrows in Figures 6 and 7) and a freewheel function in the opposite direction, and the other freewheel has the opposite function and provides a counterclockwise drive and a freewheel function in the opposite direction.

The flywheel 9 is connected to one of the gears 27 in the gear pair 20, for example by means of screws 26, and this means that this gear 27 always follows the rotation of the flywheel 9, the pistons 6, 7 and the piston rod 8.

Therefore, when the pistons 6 and 7 are driven clockwise by supplying pressure medium through the channel 17 to the clock chamber 2, the freewheel 24 will transmit this drive of the flywheel 9 and the gear 27 to a clockwise rotation of the output shaft 11. At the same time the rotating movement, due of the design of the turning mechanism as a kind of differential to the opposite gear 28 in the gear pair 20 by the action of the gears 29 and 30 in the lateral gear pair 21. The gear 25 of the gear 28 has a freewheel function in this clockwise rotation of the piston system 6-8 in Figures 6 and 7. The movement of the gear 27 is thus also transmitted to the gears 29 and 30 in the lateral pair of gears 21. These latter gears 29 and 30 are supported against the shaft 11 by means of bearings 31. During the clockwise rotation the motor piston chamber 3 is evacuated, as indicated by arrow 32a in fi gurerna.

When the piston mechanism 6-8 reverses direction at the end of the clockwise rotation, the pressure breaks the clockwise chamber 2, and this chamber is put under evacuation, see arrow 32b, and at the same time the counterclockwise chamber 3 is pressurized, the piston system 6-8 being rotated counterclockwise. The freewheel 24 obtains a freewheel function, while the freewheel 25 transmits the rotation to a rotation of the output shaft 11, which rotation takes place in the same direction as before. The turning mechanism 19 in combination with the freewheels 24 and 25 thus causes the output shaft to rotate constantly in one and the same direction. It is obvious that it is possible to effect a rotation of the output shaft 11 by shifting the operating direction on the freewheels 24 and 25.

The essential thing is that the two freewheels 24 and 25 have opposite operating directions with respect to the axle rotation.

Figure 5 shows an alternative embodiment of the invention, where the engine is designed with a double pressure function. For this purpose, a branch line 34 leads from the clockwise channel 17 of the pressure inlet at the reversing valve 16 and to the end 35 of the counterclockwise chamber 3, which in this case is sealed with a seal 36 at this end. A second branch line 37 leads from the counterclockwise channel 18 of the reversing valve 16 to the end 38 of the clockwise chamber 2, which end is sealed by means of a seal 39. Each piston 6 and 7 will thereby be able to be actuated both from the piston chamber side and from the piston rod side. clockwise rotation by the piston 6 in the piston chamber 2 being actuated on the piston chamber side by the pressure from the clockwise channel 17 at the same time as the piston 7 in the piston chamber 3 is actuated on the piston rod side by the same pressure from the clockwise channel 17, and - by counterclockwise rotation from the motor channel 18 at the same time as the piston 6 in the piston chamber 2 is actuated on the piston rod side with the same pressure from the motor channel 18.

The device is thus actuated with pressure from two different directions, namely 100% pressure on the piston chamber side and about 75% pressure from the piston rod side, whereby the transmitted total force becomes about 175% in relation to the pressure when one-sided actuation of the pistons 6 resp. 7. It is obvious that the functions of clockwise rotation and counterclockwise rotation are exactly analogous, and that the output shaft 11 is thus constantly actuated in one and the same with the same greatly increased torsional force.

Thanks to the very simple and compact design of the described device, it is possible to design the motor as a flat motor package, and that two or more such motors can be connected in parallel on a common output shaft 11 as shown in Figure 7. The two motors can have a common pressure supply means (not shown in the figure), and they may be single-acting, 1:11: 1011 516 724 8 EHRNERS 23540 as shown in Figures 1-3, or double-acting as shown in Figures 5 and 8.

By means of such a parallel connection, motors with strongly varying power can be produced by means of a single uniform basic unit which is connected in parallel on a common output shaft.

The flywheel mass 9 forms a flywheel which bridges the very insignificant interruption of operation which inevitably occurs when the piston system 6-8 changes direction of movement at the end of a rotational movement. If it is desired to eliminate such an interruption, it is possible as shown in figure 8. The mutual rotation of the motor units can be varied as desired, but in order to overcome any interruptions of operation of the individual motor units, it is sufficient to give the motors a mutual rotation of only 5-10 °. In the case of parallel connection, the motors can thus be arranged in an angular system of 355 ° -0 ° -5 °.

The pressure supply can be varied as desired and with regard to the torque and rotational speed desired on the output shaft 11.

The device may be formed with a throttle valve connected to the pressure medium means to provide a smooth start and a controlled speed and controlled torque.

A pendulum piston motor of the type described can be used for a variety of purposes, for example as a drive motor in a vehicle or a machine of any kind, even without the use of a gearbox, since the power and speed can be varied from zero to maximum only by regulation of the pressure on the driving pressure medium. nor is any decoupling required to achieve a smooth start, as this is easily accomplished by means of a throttle valve which regulates pressure and flow to the working chambers from zero to maximum. A free-rolling gear on the vehicle is obtained under the action of the two freewheel clutches 24 and 25. A reversing function can be achieved by using a simple mechanical turning gear.

The means for reversing the pressure medium supply from the clockwise passage 17 to the counterclockwise channel 18 and vice versa may be of known mechanical, electrical, pneumatic or hydraulic type and shall not be described in detail. It should be added, however, that this change can take place under the influence of the pistons 6 and 7 themselves, in that at the end of their work they mechanically actuate a rotatable slide or similar means, which can be designed with projecting and on each side of the piston chamber wall is supported by the piston when it reaches the end of its working stroke, whereby the valve is switched from clockwise to counterclockwise and vice versa.

The described pendulum piston engine operates at 120 ° of the rotational speed, and it appears from the schematic curves in Figure 4 that full force is developed from the moment pressure is applied to the pressure chambers 2 and 3, respectively, and that full work is developed during the entire work movement, and that the pressure is then switched between the pressure chambers, and that full work is performed during the entire rotational revolution except for the small starting torque which can be about 5 °, which is significantly higher than the work developed during 2 rotational revolutions on the crank in an OTTO or DlESEL type internal combustion engine. It appears that a four-stroke engine during a corresponding time performs a work that is on average only about 1/8 of the work of the pendulum piston engine, and that a two-stroke engine performs a work corresponding to a maximum of 1/4 of the work of the pendulum piston engine. avsuø 10 15 20 EH RNERS 23540 516 HÄNwsNmGsswFRoR 1 cy fi nderhus 2 cy | inder | opp, -kammare 3 cy | inder | opp, -kammare 4 outer wall (1) 5 inner wall (1) 6 kow 7 kow 8 piston rod 9 svängrnassa 10 arn1 ( 9) 11 output shaft 12 bearings 13 hushawa 14 hushawa 15 pressure supply means 16 reversing valve 17 kanaLrneduæ 18 channel, counterclockwise 19 turning mechanism 20 tooth pairs 724 10 21 22 23 24 25 26 27 28 29 30 31 32a 32b 34 35 36 37 38 39 tooth pairs bearings bearing fnmul fnmul screws gears (20) cog flfl (20) cog fl H (21) cog fl n (21) stock pH pH branch line end seal branch line end seal

Claims (9)

10 15 20 25 E&D, SE 990313-9, Ref. 23540 516 724 11 PATENT REQUIREMENTS A hydraulically or pneumatically actuated pendulum piston engine or ring piston engine, consisting of a cylinder housing (1) with a toroidal cylinder bore (2, 3), in which a pendulum piston member (6-8) is pivotable in two opposite directions of rotation, and wherein the cylinder bore at a place is divided by a piston chamber wall (15), and where the pendulum piston means (6-8) is connected to a pivot mass (9) which is connected to a central, output shaft (11), and where the pendulum piston means (6-8) divides the toroidal cylinder bore in two opposite, closed cylinder chambers (2, 3), each extending over about 120 ° from a central point in the dividing piston chamber wall (15), and where the pendulum piston means consists of two pistons (6, 7) which are connected with each other over an arcuate piston rod (8) substantially midway between the pistons (6, 7), which extends over an angle of about 240 ° and carries at its ends the pistons (6, 7), and which at a central position between the pistons ( 6, 7) is controlled by, and forb with (10) the output shaft (11) via the pivot mass (9), characterized in that - the pivot mass (9) is coupled (26) to a turning mechanism (19) to effect a reversal of the functional influence of the output shaft (11) when the pendulum piston means (6-8) changes direction of rotation, so that the output shaft (11) is constantly rotated in one and the same direction, - which turning mechanism contains two pieces of freewheel clutches (24, 25) connected in opposite directions which are connected between the turning mechanism ( 19) and the output shaft (11) - and are mounted with mutually opposite engagement / freewheel functions, - and means (27-30) for transmitting a rotational movement between the said freewheel couplings (24, 25). A pendulum piston engine according to claim 1, characterized in that the turning mechanism consists of a differential-shaped gear with 4 cooperating 10 15 20 25 516 724 12 E & D, SE 990313-9, Ref. 23540 bevel gears (27-30), in which two opposing drive gears (27, 28) are connected to the output shaft (11) via their respective freewheel hubs (24, 25), and in which one drive gear (27) is connected (26) with the pivot mass (9), which in turn is connected (10) to the pendulum piston member (6-8). A pendulum piston engine according to claim 2, characterized in that the gears (27-30) in the turning mechanism (19) have a gear ratio of 1: 1. A pendulum piston engine according to any one of the preceding claims, characterized in that the dividing piston chamber wall (15) houses an inlet for a pneumatic or hydraulic pressure medium, an inlet-evacuation channel (17) to a clockwise cylinder chamber (2) an inlet channel (18) to a counterclockwise cylinder chamber (3) and a reversing valve (16) arranged to reverse the pressure direction and the evacuation direction between the two inlet / evacuation channels (17, 18) at the end of a working stroke, so that the pendulum piston means (6-8) reverses the working direction. A pendulum piston motor according to claim 4, characterized in that each piston chamber (2, 3) is closed with a seal (36, 39) at each end (35, 38), which seals against the intermediate piston rod (8). A pendulum piston motor according to claim 5, characterized in that each piston chamber (2, 3) has a pressure connection at each piston chamber end (35, 38), which pressure connection is connected via a branch line (34, 37) to the inlet duct (17, 18). ) for the opposite piston chamber (2, 3), whereby pressure is given simultaneously to the piston chamber (2 and 3, respectively) and to the opposite piston rod chamber. A pendulum piston motor according to any one of the preceding claims, characterized in that it comprises a control valve for regulating the flow and pressure of the hydraulic or pneumatic pressure medium to the piston chambers (2, 3) and thereby regulating the speed and torque of the output shaft (11) . s a. o, see 990313-9, Ref. 23540 5 1 6 7 2 4 1 3 A pendulum piston engine according to any one of the preceding claims, characterized in that it is composed of two or two parallel interconnected pendulum piston motor units acting on one and the same output shaft (11). (Figure 7) A pendulum piston motor according to claim 8, characterized in that the parallel-coupled motor units are rotated at least at an angle of 5 ° relative to each other in the direction of the output shaft (11), so that the different motor units reverse the direction of rotation in different angular positions with respect to the output shaft (13).