WO1998004808A1

WO1998004808A1 - A mechanism for the conversion of reciprocating motion into rotary and vice versa

Info

Publication number: WO1998004808A1
Application number: PCT/BG1996/000014
Authority: WO
Inventors: Dimiter Metodiev Ivanov
Original assignee: Dimiter Metodiev Ivanov
Priority date: 1996-07-25
Filing date: 1996-11-05
Publication date: 1998-02-05
Also published as: BG100746A; BG62456B1

Abstract

The invention refers to a mechanism that converts the reciprocating motion of machinery parts - usually pistons in an internal and external combustion engine's cyclinders, compressors and hydro-pumps, into rotary motion of an outgoing axle - or vice versa. The invention refers especially to a mechanism in which such conversion is realized by two couples of forces. To achieve this, pistons that always travel opposite to each other in boxer-placed cylinders are connected by piston rods with yokes that are put-on-bearing in the straight channels of the thick-walled cylindrical sleeve. The two couples of sliders, put-on-bearing both on the pawls on both sides of the yokes and between the walls of an endless channel of the converting cylindrical sleeve (mounted and put-on-bearing on the thick-walled cylindrical sleeve) rotate the converting cylindrical sleeve always one-way direction, by the means of two couples of forces with a big arm generated by the contact with the walls. On the converting cylindrical sleeve (split to two parts by the converting channel) is mounted an immobile cylindrical sleeve with a gear ring. The sleeve fixes the two halves of the thick-walled cylindrical sleeve. The rotary motion is transmitted out of the engine's body by the means of motion-transmitting axle. All the bearing units in the mechanism are compulsory lubricated with a transmission oil under pressure, coming from an oil system, fed by gear oil pump. Since the sliders attack the converting channel at a variable angle, it is possible to achieve a constant rotation moment that is generated by the progressively decreasing engine's gas power. The constant angle of the channel's walls allows the achievement of constant flowrates of the hydro-pumps. A constant resisting moment of the gas power can be realized too, having a variable angle of the channel's walls in the compressors.

Description

A MECHANISM FOR THE

CONVERSION OF RECIPROCATING

MOTION INTO ROTARY AND VICE VERSA

TECHNICAL SPHERE

The invention refers to a mechanism that converts the reciprocating motion of machinery parts - usually pistons in an internal and external combustion engine's cylinders, compressors and hydro-pumps, into rotary motion of an outgoing axle - or vice versa. The invention refers especially to a mechanism in which such conversion is realized by two couples of forces.

PRIOR TECHNICAL STATE

There have been patented and are known plenty of mechanisms that convert the reciprocating motion of pistons and other parts into rotary and vice versa, but in the engineering and especially in the engine-building most popular remains the crankshaft mechanism. It is used in almost all piston machines - internal and external combustion engines, pumps and compressors.

The pistons suited within the cylinders of the reciprocating machines are connected by a hinge to one of the hubs of the connecting rod, and the second one is put-on-bearing in the crank arm by base bearings in the machine's body. All the bearing units of the piston, piston rod, connecting rod and crankshaft are mutually coaxial.

The crankshaft mechanism implements the following design disadvantages that are proved undoubtedly during the operation of every piston machine: ^•

The design gas forces that constantly press the piston and the inertial forces of the connecting rod load all the elements of the crankshaft mechanism, including the pistons, the cylinders and the bearings in such a way, so the friction among the is increased and they are elliptical worn out.

The crankshaft mechanism's rotating moment is unequal and depends on the gas power, the diameter and the travel of the piston, and the crankshaft arm's turning angle. The maximum rotating moment basically depends on revolution speed and on the inertial forces of the unbalanced mass with circular, reciprocating and complex-fluctuating motion.

The crankshaft mechanism has a low surcharge coefficient and itself stops when operating at low revolution speed. This imposes the usage of a big flywheel or a multi-cylinder option of the piston machine.

The gas power reaches its maximum value at and after top dead point during the expansion stroke in the internal combustion engine. Till the moment of turning the crank arm at 30° it doesn't have any rotating moment because of a lack of turning arm, and only surcharges the bearing units.

The task of the invention is to create such a mechanism for the conversion of reciprocal motion of machinery parts (pistons and others) into rotary motion through an outgoing axle (or vice versa), that has higher and more equable rotating moment, higher surcharge coefficient, coaxial and always opposite, totally and mutually balancing gas and inertial forces of reciprocating moving masses, non- elliptical wearing bearings, including the pistons and the cylinders, higher efficiency coefficient, abrupt acceleration when turning and stopping, more simple, more liable and easy-tomend construction, avoiding difficult joints, adjustments and centring, easy to maintain and operate with, using only transmission oil.

TECHNICAL ESSENCE

According to the invention the task is done as follows: a thick-walled cylindrical sleeve with cut in it four symmetrical, longitudinal channels that have parallel walls, is double-sided covered by conical bearing thrusts, adjacent to flanges that are provided with outside hubs. The thick-walled sleeve is embraced by the converting sleeve which is put-on-bearing in the thrusts of the flanges, and is split to two symmetrical equal parts by an endless converting channel, in which are suited pawls on two yokes with parallel walls. The yokes are suited and put-on-bearing (their open end is directed inside) in the channels of the thick-walled sleeve. They are connected to piston rods which are fitted and slide-put-on-bearing in the central coaxial orifices of the yokes. The two parts of the converting sleeve are embraced and immovably connected by a fixing sleeve which is provided with gear ring. The two flanges are connected to each other by a hollow body which to some extend is filled with oil.

The thick walled cylindrical sleeve is made as one unit together with the conical bearing thrust, the flange and the adjacent hub. The second flange with its adjacent bearing thrust and hub, is mounted stationary on the thick- walled sleeve but could be disassembled by a screw joint.. On the pawls of the two yokes are put-on-bearing sliders which external surface is formed in a way that can secure an unceasing contact with parallel formed walls of the converting endless channel in the converting sleeve.

The forcible and booster synchronic motion are directed through a groove in the mechanism's body by a gear wheel that is constantly meshed to the gear ring on the fixing sleeve. The latter is mounted on a force-transmitting axle that is put-on-bearing in the wall of the mechanism's body.

The lubrication of all bearings and friction parts is considered and is realized compulsory and constantly by transmission oil which is fed by pressure through a system of orifices and channels, connected in a general oil system with an oil pump that sucks the oil through an oil filter from the mechanism's body.

The invention provides the following advantages: The converting the reciprocating but always opposite motion of mobile machinery parts (pistons) from gas or other power into rotary motion to an outgoing axle is realized by the connected by piston rods (or other parts) to them yokes which are put-on-bearing in the straight channels of the thick- walled cylindrical sleeve, directly by sliders walls (put-on-bearing on the pawls of the yokes) in the walls of the converting endless channel of the converting cylindrical sleeve which is fulfilled by two co-directed couple of forces (a result from the forcible contact) that turn the converting cylindrical sleeve in one direction only but with bigger arm.

All the gas and inertial forces are axial, opposite and mutually completely balanced which is the reason for the non-elliptical wearing of the bearings, including the connected by piston rods to the mechanism pistons and engine cylinders or other machinery parts.

The rotating moment of the mechanism is almost a constant, which is a function of the progressively decreasing gas power, the energy accumulated in its elements' inertial forces and the progressively increasing slider's attack angle against the converting channel's wall.

The maximum rotating moment of the mechanism is many times higher than that of the crankshaft mechanism due to the big cotangent of the small angle, by which the gas power after top dead centre attacks the channels walls with two couples of turning forces.

The converting cylindrical sleeve which is in a joint with the fixing one and the gear ring that are statically and dynamically balanced, is charged only radial by the outer force-transmitting gearing.

This is a high-technology mechanism, highly liable, easy to exploit, maintain and revamp, with no difficult joints, complex and unstable centring, and operates with transmission oil.

ILLUSTRATION OF THE APPLIED FIGURES AND EXAMPLES OF THE REALIZATION OF THE INVENTION

An exemplary accomplishment of the invention is illustrated with the help of the applied drawings. The basic Fig.l is a complete longitudinal vertical section along its axle.

Fig.2 is a complete layout of the converting cylindrical sleeve and the thick-walled cylindrical sleeve under it, including the situated in their channels yokes, pawls and sliders.

Fig.3 is a cross section of a pawl in dead centre with a slider that is put- on-bearing on it and in the walls of the endless converting channel. The slider has profile-outer-grinded walls, as well as the adjacent channels.

Fig.4 is a complete cross vertical section of the mechanism in the AA flat.

Fig.5 shows the mechanism mounted on different two-cylinder boxer engines. The left side shows an option of one-stroke piston turbo-engine, and the right side shows one-stroke piston turbo-injection engine.

According to Fig.l the mechanism comprises one thick walled cylindrical sleeve 1, formed by a flange 2 and a hub 3. Between the inner head of the flange 2 and the sleeve 1 is formed a conical bearing thrust 5 which is provided with one concentric surface lubricating channel 6, as well as two crossed surface lubricating channels 7. In the sleeve's wall are cut four symmetric longitudinal channels 4 with parallel walls. On its other side to the front of the sleeve is connected by a screw joint flange 2a with hub 3a and bearing thrust 5a which are similar to the shape and size of flange 2 and the adjacent hub 3 and bearing thrust 5, formed together with sleeve 1. The conical thrust 5 has the same lubricating channels 6a and 7a, as well as thrust 5. They are connected to the central oil system by channels 8, 8a, 9 and 9a. In the flanges 2 and 2a and their outer hubs there are central orifices 10 and 10a and in each of them are suited two, separated by oil-seals 11 and i la, leading inner 12 and 12a and outer 13 and 13a bearing slider yokes. The inner bearing sleeves 12 and 12a have longitudinal channels 14 and 14a in their walls. They are constantly directed to the central oil system via channels 9 and 9a in the flanges 2 and 2a.

Upon the sleeve 1 is fitted and put-on-bearing in the thrusts 5 and 5a the converting cylindrical sleeve 16 with reverse conical bearing thrust 17 in its both ends. This converting cylindrical sleeve 16 is split to two symmetrical halves by a converting channel provided in its wall.

In each couple, at 180° longitudinal leading channels 4 in the cylindrical sleeve 1, with their open end pointed inside are put-on-bearing two blind yokes 18 with parallel walls. In the both ends of each yoke 18 there are cylindrical pawls 19 which emerge out of the channels 4 of the cylindrical sleeve 1, and their axles are normal to its axle and conclude an angle of 90°. In the centre of the outer wall of each yoke 18 there is a central orifice 20 connected constantly to its own axial longitudinal oil channel 21 which is connected constantly to the blind axial longitudinal oil channels 22 in the pawls 19. On the parallel grinded walls of the yokes 18 there are surface channels 23 connected via orifices 24 through their walls to their longitudinal axial channel 21. On the grinded necks of the pawls there is an outer channel 25 connected via orifices through their walls to their longitudinal blind axial channels 22. On the outer grinded cylindrical pawls 19 are put-on-bearing at one and the same time as in the converting channel 15 the sliders 27 with grinded profile outer surfaces. Inside the orifices 28 of the sliders 27 there are blind inner longitudinal channels 29 that are constantly connected to the concentric outer channels 25 of the pawls 19. These longitudinal channels 29 are connected via their orifices 30 through their walls to the inner profile surfaces of the sliders 27. On the cylindrical sleeve 1, with the mounted on it left half of the converting cylindrical sleeve 16 and the mounted in the channels 4 and yokes 18 with pawls 19 and sliders 27, is added the right half of the converting sleeve 16. On its two halves is mounted the fixing sleeve 31 which presses them to each other and has a gear ring 32 on its outer surface. On the two coaxial flanges 2 and 2a by a screw joint is mounted the body (shell) 33 of the mechanism. In the body 33 there is a cut 34 through which gear wheel 35 (mounted stationary on an outgoing force-transmitting axle 36) is meshed constantly with the gear ring 32. The gear wheel 35 and the outgoing axle 36 are put-on-bearing in a bearing body 37 which is adjacent to the body of the mechanism. In the outer bearing sleeves 13 and 13a, the oil-seal units 11 and 11a, and the inner bearing sleeves in the hubs 3 and 3a are suited piston rods 38 with central blind holes 39 (on the side of the yokes 18), connected by their orifices 40 in their walls to an outer channel 41. The outer channels 41 are constantly connected to the longitudinal channels 14 in the inner leading flanges 12.

The piston rods 38 are connected stationary (can be disassembled) to yokes 18 by their central holes 20. The central oil system fed by gear oil pump which is connected to the mechanism by a gearing, feeds transmission oil under pressure to all bearing units and friction parts through a system of holes and channels that are connected to the radial channels 9/

USAGE OF THE INVENTION

In order to start operating as a mechanism which is converting the reciprocating motion of the piston rods 38 into rotary motion of the outgoing axle 36, is necessary that the connected to them pistons be driven at once inside or outside in their cylinders. Then the connected to the piston rods 38 yokes 18 will be driven reciprocally in the channels 4 of the cylindrical sleeve 1, and the pawls 19 and the sliders 27 travelling reciprocally in the endless converting channel 15 of the converting cylindrical sleeve 16 impose a stress on its walls. In the zone of the contact between the sliders 27 and the walls of the converting channel 15 are generated two couples of forces that turn the converting sleeve 16 always in one direction at 90°. The converting sleeve executes one revolution after four double mutually opposite reciprocating motions of the piston rods 38. The generated inertial forces of the reciprocating driven pistons, piston rods 38, yokes 18, pawls 19 and sliders 27 are always coaxial and mutually opposite, due to which they completely balance each other at any moment. The accumulated in them energy is used for the accomplishment of the compression stroke and for the amelioration the rotation moment characteristics of the mechanism.

In the mechanism, the conversion of the reciprocating motion of the pistons via the connected to them piston rods 38, yokes 18 with the pawls 19 and the mounted on the pawls 19 sliders 27 into rotary motion of the outgoing axle 36 (or vice versa) is realized directly by the sliders 27 which travel reciprocally (and turn around the pawls 19) by duress upon the walls of the endless converting channel 15. Two couples of forces are formed. These forces turn the cylindrical sleeve in one direction together with the placed on it fixing sleeve 31 with a gear ring 32.

Claims

PATENT CLAIMS

1. A mechanism for the conversion of the reciprocating motion of machinery parts (pistons and others) into rotary motion of an outgoing axle (and vice versa) connected by piston rods or otherwise, distinguishing with the fact that includes cylindrical thick-walled sleeve (1) with cut in it four symmetrical longitudinal channels (4) and double-covered by conical bearing thrusts (5, 5a) adjacent to flanges (2, 2a) which are provided with outer hubs (3, 3a) in which situation the thick-walled sleeve (1) is coaxial embraced by the converting sleeve ( 16) put-on-bearing in the thrusts (5 and 5a) and is split to two symmetrical halves by an endless converting channel (15) in which are placed the pawls (19) of two yokes (18) with grinded walls put-on-bearing in the channels (4). The yokes (18) are provided with piston rods (38) slide-put- on-bearing in the central coaxial orifices of the hubs (3, 3a). The two halves of the converting sleeve (16) are stationary connected by a fixing sleeve (31) provided with a gearing ring (32), and the two flanges (2, 2a) are connected to each other by a hollow body.

2. A mechanism, according to claim 1, distinguishing with the fact that the cylindrical sleeve (1) is one-sided accomplished as a whole part with the conical bearing thrust (5), the flange (2) and the adjacent hub (3).

3. A mechanism, according to claim 1, distinguishing with the fact that to the pawls (19) of the yokes (18) are put-on-bearing sliders (27) which outer surface is formed in order to provide a constant contact with the grinded walls of the converting channel (15).

4. A mechanism, according to claim 1, distinguishing with the fact that in all friction and bearing parts as sleeve (1), yokes (18), pawls (19), sliders (27), piston rods (38), bearing thrusts (5 and 5a) and sleeves (12) are designed channels and holes of an oil system for compulsory feeding of the oil under pressure from an oil pump.