MXPA97003473A - Oscilac machine - Google Patents

Abstract

An oscillation machine is described that includes a cyclic kinematic chain in which the power is transferred between the translational and rotational movement. The kinematic chain includes a piston (2) that moves reciprocally in a cylinder (1), connected through two connecting rods (9, 10) to crank arrows of opposite rotation on (7, 8) are arranged symmetrically from the axis of movement of the piston (2), and the crank pins (15, 16) of the crank arrows (7, 8) to which connecting rods (9, 10) are connected, which are symmetrically aligned around the axis of movement of the piston (2). The small ends of the connecting rod (13, 14) meet in their connection to the piston (2). The distance between the axis of the double crank handles, the length of the connecting rods, the position of the connecting rods to the piston and the diameter of rotation of the crank pin around the crank arrow shafts are such that in movement, the ratio of the length of each stroke of the piston the diameter of rotation of the crank pins around the crank arrow shafts is at least 1.1 to

Description

OSCILLATION MACHINE TECHNICAL FIELD This invention relates to an oscillating machine having a cyclic kinematic chain and which has been developed particularly, but not only as a cylinder, oscillating piston and rotating crank shaft assembly for use in an internal combustion engine (I. EC). It should be appreciated that this same technology can be applied to similar assemblies in hydraulic devices such as pumps and motors and other similar means, in addition to the conventional use in combustion engines.

BACKGROUND OF THE INVENTION Oscillation machines that have kinematic and cyclic chains described in the previous patent specifications describe piston, cylinder and arrow crank assemblies for IE, specifically USA 4809646, Japan 57-171001, Japan 01-73102 and Germany 4013754 have included arrow of double crank with double connecting rods (connecting rods) one for each piston to a crank arrow of opposite rotation, the crank arrows being substantially equidistant from the center line of the piston trajectory. An advantage of such assemblies has been identified as a reduction in the friction of the cylinder walls. It is an object of the present invention to provide an oscillating machine having a cyclic kinematic chain, which at least provides the public with a useful choice.

DESCRIPTION OF THE INVENTION Accordingly, the invention consists of an oscillating machine that includes a cyclic kinematic chain in which the power is transferred between the translational and rotational movement of such a kinematic chain that includes means of cyclically moving reciprocal movement along a line of movement through a first race between a first position and a second position, and through a second race from the second position back to the first position, the kinematic chain having rotational means in the form of a pair of crank arrows that they have substantially symmetrical axes disposed on opposite sides of and normal to the line of movement of the translation means, the translation means having a pair of pivotal connection means, the axes of which are parallel and such moving axes follow trajectories parallel to the line of movement, the crank arrows taking each u a crank pin, the axis of which follows an orbital trajectory of a predetermined diameter in motion, a pair of connecting bars, each having a first end and a second end, the first end of each connecting rod being connected to through pivotal connection means through means of attachment to the translation means, the axes of the pivotal connection means being arranged between the translation means and a line between the axes of the crank arrows and the second end of each one of the connecting rods being rotationally connected to the respective crank pins, the distance between the crank shaft axes, the length of the connecting rods, the placement of the pivotal connection means in relation to the translation means and the predetermined diameter of the orbital trajectories and the construction and disposition being such that during the movement, the relation of the The length of each stroke at the predetermined diameter is at least 1.1 to 1.

BRIEF DESCRIPTION OF THE DRAWINGS A preferred form of the invention and its modifications will now be described with reference to the accompanying drawings in which: Figure 1 is a cross-sectional view through an oscillating machine having a cylinder, a piston and a kinematic chain of According to a preferred embodiment of this invention, Figure 2 is a cross-sectional view through a part of the machine of Figure 1. Figure 3 is a cross-sectional view of an alternative arrangement of the machine part of Figure 2. Figures 45, 6 are cross-sectional views of other embodiments of the invention, showing the effect of different dimensions and arrangements of their elements. Figure 7 is an alternative transverse elevation of that part shown in Figure 2, Figure 8 is a cross-sectional view of another embodiment of the invention showing alternative translation means, and Figure 9 is a cross-sectional view on the line xx of the Figure 8 MODES FOR CARRYING OUT THE INVENTION As shown in Figure 1, a preferred form of the invention comprises a cylinder 1 in which translating means in the form of a piston head forming part of a piston 2, cyclically move inside the cylinder wall 3 in a known form. The piston head is preferably only of a thickness in order to adapt to other accessories, for example, piston rings. The piston 2 is arranged to travel on a first stroke of a predetermined length of a cyclic oscillation movement forward between a first position 4 and a second position 5 and backward between a position 5 and the position 4 during a second stroke. As desired, additional conventional apparatus such as seal rings can be provided to seal the piston 2 adjacent to the cylinder wall 3, but it should be noted that only the short piston head must be guided by the cylinder wall 3. , thus reducing the friction area compared to a conventional piston. As shown in the drawing of Figure 1, the first position of the piston 4 for the piston 2 corresponds to a position known as the upper dead center (TDC) being the closest point of travel of the piston 2 towards the top of the cylinder 1. The second position 5 corresponds to a lower dead center (BDC) with the degree of travel of the piston 2 at the other end of its oscillation movement, the first and second strokes of the piston movement being cyclically repeated in a known manner . The piston 2 is connected to a kinematic chain comprising two crank arrows, the axes of which are referenced 7 and 8, a pair of connecting rods (connecting rods) 9 and 10 and a piston pin 11 and 12. In the preferred form of the invention, two crank arrows 7 and 8 are symmetrically placed on opposite sides and each one being equidistant from and normal to the center line of cylinder 1 which is also the centerline of the movement of piston 2. As shown in Figure 1, the axes of the crank shaft 7 and 8 are provided on a plane substantially transverse to the line of movement of the piston 2. Each connecting rod 9 and 10 has a small first end pivotally connected to connecting means configured which comprise an elongated piston extension 24 which forms an additional part of the piston 2 and through pivotal connections being the stump pins 11 and 12 and the small ends 13 and 14 of the connecting rods 9 and 10 respectively. In this embodiment of the invention, the extension of the piston 24 is not guided by the cylinder wall 3. The kinematic chain, as described in this preferred form of the invention, causes the substantial forces to act in a lateral direction to the direction of trajectory of the piston 2. Therefore, in order to reduce the transmission of such forces, stop means are provided between the pivotal connections. Preferably, as shown in Figures 2 and 3, the stop means comprise external cylindrical portions 51 and 52 at the small ends 13 and 14 of the connecting rods 9 and 10. These cylindrical portions 51 and 52 at the ends of the rods 9 and 10 are arranged to bump, so that at least much of the lateral force of each of the connecting rods 9 and 10 is found by an equal or opposite force transmitted through these stop means from the other connecting rod and this way reducing the wear of the stump pins 11 and 12 and / or between the piston 2 and the cylinder wall 3. It should be noted that as shown in Figure 3, the cylindrical portions 51 and 52 preferably extend over the available width and arc portions of the rods 9 and 10, which during use bump through the trajectory of the piston 2 and the consequential rotation of the rods 9 and 10 with respect to one another around their pin shafts stump respect you.

In this way in Figure 3, the piston extension 24 has a space within which the connecting rods 9 and 10 are adjusted so that the stump pins 55 and 56 pass through a small first end of each of the rods. 9 and 10, respectively, and are connected to those portions of the piston extension 24 on both sides of the space where the connecting rods 9 and 10 are adjusted. The stop of the portions 51 and 52 is shown by the line 57. of Figure 3, it will be evident that the connecting rods are centrally arranged in the diameter of the piston 2 and opposite each other. The connecting rods 9 and 10 have second ends, which are rotatably connected to crank pins 15 and 16 on the crank arrows 7 and 8 through large ends 17 and 18 of the rods 9 and 10, respectively. The axes of the crank pins each follow an orbital circular path 22 and 23 of a predetermined diameter. The construction details different from those of the crank arrows, the cranks connecting the crank pins to the crank arrow and the connecting rods and their large ends, are in a well known way. From the foregoing, it will be evident that when applying the present invention to a machine, the parameters of the elements in the kinematic chain of the invention can be varied to give the required length of piston stroke 2 relative to a predetermined diameter of the orbit of the axes of the crank pins 15 and 16 and for the first stroke over a required angle of rotation of the crank arrows 7 and 8. These variations can be made in: 1. The distance between the crank arrows 7 and 8 2. The distance between the stump pins 11 and 12 3. The radial distance between the crank shaft axes and their respective crank pins, ie the diameter of the orbital trajectories of the crank pin shafts. 4. The effective lengths of the connecting rods. The distance between the piston head 6 and the stump pins 11 and 12 does not affect the ratio of the stroke to the diameter of the orbit of the crank pins 15 and 16, but a designer must take this parameter into consideration when making the design . The operation of the kinematic chain incorping the invention will be evident from the following. The oscillating movement of the piston 2 causes the rotation of the crank arrows 7 and 8, which are interlocked to rotate inwardly in an opposite manner. According to the dimension and placement of the elements of the kinematic chain, the relationship between the stroke of the piston 2 and the diameter of the orbital trajectories of the crank pin shafts are fixed as the ratios of the first translational movement stroke to the first arc of the rotational movement and the relation of the second translational motion race to the second arc of rotational movement. In the preferred form of the invention shown in Figure 1, the parameters are: separation of crank shaft shafts 70 units separation of axes of stump pin 10 units length of connecting rod 55 units stroke 73 units diameter of the orbit of crank pin shafts 50 units giving a stroke ratio to the orbital diameter of the crank pin axis of 1.46 to 1 and a rotational ratio of first arc to second arc of about 2.16 to 1, the first arc of rotation being 246 ° and the second arc of rotation being 114 °.

In Figures 4, 5 and 6, different parameters have been used to show the variation of the kinematic chain of Figure 1. Referring now to Figure 4 (since in all the Figures the same reference numbers are used to refer to to the same elements since only the positions and dimensions vary) the parameters shown here are: crank arrow separation 70 units trunnion shaft axle spacing 10 units connecting rod length 75 units stroke 55 units crank pin shaft orbit diameter 50 units giving a running ratio to the orbital diameter of the crank pin axis from 1.1 to 1 and a rotation ratio of first arc to second arc of about 1.25 to 1, the first arc of rotation being 200 ° and the second arc of rotation being 160 °. Referring now to Figure 5, the parameters shown are: crank shaft clearance 121 units trunnion shaft axle spacing 4 units connecting rod length 68 units stroke 49.5 units crank pin shaft orbit diameter 20 units giving a stroke ratio to the orbit diameter of the crank pin axis from 2.48 to 1 and a rotation ratio of first arc to second arc of about 1.45 to 1, the first arc of rotation being 213 ° and the second arc of rotation being 147 °. A comparison between the modalities of Figure 1 and Figure 5 gives relationships as follows: Figure 1 Figure 5 stroke diameter / orbit 1.46 2.48 first to second arc 2.16 1.45 These relationship differences occur mainly due to the crank arrow separations and one result is the variation in piston speeds and accelerations during both the first and second runs. It should be noted that in Figures 1 and 5, when the piston 2 is in B.D.C. , position 5 of the stump pins becomes very close, but does not pass through the plane where the crank arrow shafts meet. To cyclically repeat the first and second runs, it is not possible for the pin journals to pass the plane where the crank arrow shafts are located. In Figure 6, a configuration is shown wherein a wide separation of the crank arrow is provided, but due to the piston B.D.C. from position 5 is disposed at a far distance, only a moderate orbital stroke / diameter is obtained. In this way, the dimensions are: crank arrow clearance 105 units connecting rod length 127 units stroke 19.25 units crank pin shaft orbit diameter 17.5 units giving a stroke ratio to the orbital diameter of the crank pin axis from 1.1 to 1 and a rotation ratio of first arc to second arc of about 1.04 to 1, the first arc of rotation being 184 ° and the second arc of rotation being 176 °.

It is believed that at least some advantages of the invention will be obtained if the stroke / diameter ratio is between l.l to l and 2.4 to l. As stated in the foregoing, in each of the embodiments, the distance between the stump pins 11 and 12 and the work surface 19 of the piston 2 does not affect the above relations, but allows the piston head to run smoothly in the orbital trajectories of the crank pins 15 and 16 without the interference of any balance weight (not shown) or other crank arrow fittings, and similarly the piston extension 24 is configured to prevent clogging between the movement elements. It is not anticipated that the lateral forces of the material will occur in a direction normal to the axes of the stump pins 11 and 12, but in the event that resistance to such forces is necessary, translation guide means are provided in a further of the invention, as shown in Figures 8 and 9, wherein the piston extension 24 carries sliding shoes 41, which slide against slides 42, which are preferably extensions of the cylinder wall 3 as shown and which are arranged parallel to the line of movement of the piston 2 and allow the clarification of, for example, cranks and crank pins 15 and 16.

The slides 42 are not a complete extension of the cylinder wall 3, but are spaced to allow such clarification. As shown, the arc slides 41 are sliding surfaces provided in areas normal to the trunnion pins 11 and 12. In Figures 1, and 4 to 6, positions 26 and 27 are related to the positions of the crank pins 15 and 16 around the orbital trajectories 22 and 23 respectively when the piston 2 is in the 4 T.D.C. in the case of point 26 and in position 5 B.D.C. with respect to the point 27. Preferably, the pivotal connections 11 and 12 between the rods 9 and 10 to the piston 2 are at a smaller distance or separated from each other than the closest position obtained by the crank pins 15 and 16 as It is shown in the figures. With such a configuration, the connecting rods 9 and 10 during the entire cycle diverge from their first ends 13 and 14 to their second ends 17 and 18. In this way, the distance between the pivotal connections 11 and 12 is smaller than the distance between the pins of crank 15 and 16 as shown, so that connecting rods 9 and 10 never achieve a parallel state. Furthermore, as can be seen in Figures 1, and 4 to 6, the axes of the pivotal connections 11 and 12 follow parallel paths, but separated from the line of movement of the central axis of the piston 2. In the preferred form of the invention and its modifications, the crank pins are arranged to rotate between them during a first part of the first stroke, the first stroke is in a direction towards the plane of the crank axes 7 and 8, and the crank arrows they are interconnected, for example, through gears, to have an opposite rotation. The rotation in the present is referred to as having crank arrows that turn inward. However, for some applications, the crank arrows that rotate outwards 7 and 8 may be beneficial. This may particularly, but not only apply to pumps or hydraulics using this form of apparatus. In an alternative arrangement of the connections between the rods 9 and 10 and the piston 2, as shown in Figure 7, the cylindrical portions 51 and 52 are used to help transfer forces between the piston 2 and the rods 9 and 10 to through the provision of rollers 53 and 54 rotating on the pins fixed to the piston 2, the rollers 53 and 54 abutting the portions 51 and 52 of the connecting rods and helping through their own connection to the piston 2 to transfer forces between the piston and connecting rods 9 and 10.

In Figures 1, 4 to 6, the crank pin positions corresponding to the position 4 T.D.C. they are shown completely and the positions in position 5 B.D.C. They are shown in lines with spikes. An oscillating machine having a kinematic chain and a cylinder and a piston as described may be and preferably is incorporated within a motor such as an internal combustion engine having a plurality of cylinders with a piston in each cylinder connected both the crank arrow 7 and the 8 through connecting bars as described. In addition, each cylinder 1 may contain inlet and outlet valves and / or ports, as required, to correspond to a four-stroke or two-stroke engine. From the described embodiments of the invention it can be seen that a wide variety of crank pin shaft orbit diameter stroke / diameter ratios can be adapted through the use of the invention. It is believed that a minimum novelty of such a ratio is 1.1 to 1 and a maximum novelty of such a relationship is approximately 2.48 to 1. From the foregoing, it can be seen that the invention at least in the preferred form and / or the modifications described herein or the additions thereto have many advantages, some of which are set forth below: 1. The use of this invention in an engine allows the travel of the piston and the working length of the cylinder and the cubic capacity resulting from the motor sweep volume for selected modes to be increased without increasing the orbital radius of each crank pin, thus reducing the motor height for a specific cubic capacity. 2. Compared with a conventional motor, an addition of 66 ° of the rotation of the crank arrow can be achieved for use during each power or first combustion stroke. The overlap of the combustion strokes in, for example, a four-stroke four-cylinder engine, incorporating the invention by proper configuration of the crank pins on the crank shaft and a timing control of the engine can provide an output of power that comes close to being continuous. In this way, it is believed that with some configurations it is necessary to provide at least a reduced flywheel effect. 3. Another benefit that arises from the balanced forces between the piston and the connecting rods is that the side wall 59 of the same piston can be of a reduced depth compared to a conventional piston. This is due to the smaller length of the side wall that is required to keep the piston 2 straight inside the cylinder 1 without the oscillation of the material. In this way, the length of the cylinder 1 can be reduced compared to the stroke length of a piston in a conventional engine. The piston extension 24 does not necessarily have to be guided by the cylinder wall 3. If a plurality of cylinders are provided with the pistons thereof being in contact with the crank arrows, the availability of up to 246 ° of the Crank arrow rotation under power or combustion allows two pistons connected 180 ° apart from the crank arrow to move in the same direction for a portion of the cycle. 5. Other benefits include a lower piston speed during combustion to increase the burn time and energy extraction of a fuel and an increased piston drive by the combustion forces over a wider angle of rotation of the arrow of the piston. crank. 6. In a four-stroke four-cylinder engine, the lower piston speed and overlap inlet strokes increase the suction of the engine and allow quieter suction demands from such an engine. 7. An additional benefit is believed to be provided by such configuration and is the increased action provided to the crank arrows through the angles assumed by the cranks between them and the crank of the crank arrow. 8. Further in the preferred forms of this invention including such an additional apparatus as the stop ends of the connecting rods 9 and 10, the lateral pressure of the connecting rods on the pivotal connections 11 and 12 is reduced to extend the life of any of the bearings. 9. It is believed that there is a reduction in friction between the piston and the cylinder compared to conventional engines with only a single crank shaft. 10. The invention may allow high compression ratios to be used due to the balance of many forces that reduce the probability of leakage, excessive wear and other problems associated with high compression. 11. The invention also provides an engine designer with greater flexibility in the timing of an engine due to the elimination of the phenomenon such as the piston stroke caused by the variations of time in current motors. 12. In a hydraulic apparatus, it may be desirable to run an additional piston and cylinder on the opposite side of the crank arrows, i.e., to provide a hydraulic pump, driven by the primary piston 2 and cylinder 1 as described in FIG. this invention. A direct connection between the pistons is possible to provide the drive of the primary piston as shown towards the second piston (not shown) for pumping the hydraulics.

Claims (15)

1. An oscillating machine that includes a cyclic kinematic chain, characterized in that the power is transferred between the translational and rotational movement of such a kinematic chain that includes means of cyclically moving reciprocal movement along a line of movement through a first stroke between a first position and a second position, and through a second stroke from the second position back to the first position, the kinematic chain having rotational means in the form of a pair of crank arrows having substantially symmetrical axes arranged on the opposite and normal sides to the line of movement of the translating means, the translating means having a pair of pivotal connection means, the axes of which are parallel and the axes in motion follow parallel paths to the line of movement , the crank arrows each having a crank pin, the an axis of which follows an orbital trajectory of predetermined diameter in motion, a pair of connecting rods, each having a first end and a second end, the first end of each connecting rod being connected through the pivotal connection means by means of the means of attachment to the translating means, the axes of the pivotal connecting means being arranged between the translating means and a line between the axes of the crank arrows and the second end of each of the connecting rods being rotationally connected to the respective crank pins, the distance between the axes of crank arrows, the length of the connecting bars, the placement of the pivotal connection means in relation to the translation means and the predetermined diameter of the orbital trajectories and the construction and layout being such that during movement, the ratio of the length of each of the The diameter of the predetermined diameter is at least 1.1 to 1.

2. An oscillating machine according to claim 1, characterized in that the translation means comprise a piston head that moves reciprocally in a cylinder.

3. An oscillating machine according to claim 1 or claim 2, characterized in that stop means are provided between the pivotal connections arranged to transmit forces between the pivotal connections of one another during the movement of the translation means.

4. An oscillating machine according to claim 3, characterized in that the stop means comprise parts of each of the pivotal connections of the connecting rods having cylindrical external surfaces, which abut between them during the movement.

5. An oscillating machine according to any of the preceding claims, characterized in that the crank passages rotate therebetween during a first part of the first stroke and the first stroke is in a direction towards the crank arrows.

6. An oscillating machine according to any of the preceding claims, characterized in that the stop means comprise an extension of the translating means on which the pivotal connections are mounted far away from the translating means.

7. An oscillating machine according to any of the preceding claims, characterized in that the distance between the axes of the pivotal connections is less than the closest distance obtained between the respective axes of the crank pins during the orbit of the crank pins.

8. An oscillating machine according to claim 7, characterized in that the closest distance between the axes of the crank pins is between twice and twenty times the distance between the axes of the pivotal connections.

9. An oscillating machine according to any of the preceding claims, characterized in that during a cycle of movement of the first and second strokes, the orbit of the crank pins through an angular rotation for angles between 183 ° and 246 ° during the first stroke of the piston and a correspondingly smaller rotation during the second race, so that the transfer of power occurs over a corresponding proportion of the time taken for each race.

10. An oscillating machine according to any of the preceding claims, characterized in that translation guide means are provided between the sliding shoes on the joining means and the sliding bars arranged parallel, but separated from the line of movement.

11. An oscillating machine according to any of the preceding claims, characterized in that the ratio of the length of the stroke to the predetermined diameter is selected to be between 1.1 to 1 and 2.48 to 1.

12. An oscillating machine according to any of the preceding claims, characterized in that the length of the stroke to the predetermined diameter is selected to be between 1.2 to 1 and 2.4 to 1.

13. An oscillating machine according to any of the preceding claims, characterized in that it comprises a motor having one or more cylinders.

14. A machine according to claim 13, characterized in that the motor is an internal combustion engine.

15. A machine constructed, arranged and operable substantially as described herein by reference and illustrated in the accompanying drawings.