Abstract:
A grooved double combustion chamber rotary engine includes a rotary compression unit, a rotary gas motor unit, and a combustion chamber, the rotary compression unit being connected to the respective rotary gas motor unit and the combustion chamber to constitute a stroke, and two strokes being alternating to achieve power output.

Description:
BACKGROUND OF THE INVENTION 
     (a) Field of the Invention 
     The present invention relates to an engine, more particularly to a rotary engine that has two combustion chambers, cylinders having curved correction grooves, and rotors provided with blade assemblies. 
     (b) Description of the Prior Art 
     Rotary gas devices of compressors, motors and engines, known in the art, have the function of replacing reciprocating piston engines. However, as the air-tightness and lubricating effects of rotary engines are comparatively poor, they are not as popular as reciprocating piston engines. 
     Reciprocating piston engines have certain drawbacks. One of them is that combustion occurs in constant volume, which causes generation of extremely high temperature and pressure, resulting in discharge of carbon monoxide that seriously pollutes the air. It is therefore worthwhile to make efforts to improve upon existing rotary engines so that they can be widely used. 
     Previously, the inventor had invented a combustion rotary engine and obtained the U.S. Pat. No. 5,596,963. 
     SUMMARY OF THE INVENTION 
     A primary object of the present invention is to provide a grooved double combustion chamber rotary engine that achieves a relative uniform mixing of fuel and air to allow complete combustion and that has enhanced compression effects. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     The foregoing and other features and advantages of the present invention will be more clearly understood from the following detailed description and the accompanying drawings, in which, 
     FIG. 1 is a schematic view of the arrangement of the present invention; 
     FIG. 2 is an exploded perspective view of a single unit of rotary engine of the present invention; 
     FIG. 3 is a perspective exploded view of a blade assembly of the present invention; 
     FIG. 4 is an assembled sectional view of the blade assembly and a rotor of the present invention; 
     FIG. 5 is an assembled sectional view of fixed blades and the rotor of the present invention; 
     FIG. 6 is an assembled sectional view of movable blades and the rotor of the present invention; 
     FIG. 7 is a schematic view illustrating operation of a first unit of the engine; and 
     FIG. 8 is a schematic view illustrating operation of a second unit of the engine. 
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
     With reference to FIGS. 1,  7  and  8 , the present invention essentially comprises a rotary compression unit  1 , a rotary gas motor unit  2  interconnected with the rotary combustion unit  1 , and a compression chamber  3  disposed therebetween. As the present invention is a double chamber construction, there are two units that are not inter-communicated each other. Besides, operation thereof is alternating. 
     As shown in FIG. 2, the rotary compression unit  1  includes a front cylinder ring  11 , a rear cylinder ring  12 , an intermediate ring  13  lockably secured between the front and rear cylinder rings  11 ,  12  by screw rods, a rotor  14  insertably disposed therein, a blade assembly  15  insertably disposed in the center of the rotor  14 . Due to the arrangement of the rotor  14 , the rotary compression unit  1  is divided into a front compression chamber  16  (see FIG. 7) and a rear compression chamber  17  (see FIG.  8 ). The rotor  14  extends along its axis to form opposite output shafts  18 . 
     Referring to FIGS. 3,  4 ,  5  and  6 , the blade assembly  15  includes a plurality of spaced-apart fixed blades  151 with a plurality of gaps  152  defined between adjacent blades  151 . Each of the gaps  152  receives two U-shaped movable blades  153  inserted therein from opposite ends thereof. Therefore, when the rotor  14  rotates, the movable blades  153  will displace outwardly due to centrifugal force to abut tightly against inner walls of the front and rear cylinder rings  11 ,  12 . 
     With reference to FIG. 4, in order that the blade assembly  15  can constantly be positioned with respect to the rotor  14 , indentations  1511  are formed on opposite sides of the fixed blades  151  in the middle, respectively, for insertion of a reed  1512  and an abutting block  1513 . Each two movable blades  153  define a notch  1531  in a position corresponding to that of the indentations  1511  for receiving a spring  1532  to provide a resilient force during retraction of the movable blades  153 . With reference to FIGS. 6 and 7, which illustrate the inter-relationship among the front and rear compression chambers  16 ,  17 , the rotor  14 , and the blade assembly  15 , if the rotor  14  rotates using the output shafts  18  as an axis, due to the centrifugal force of the blade assembly  15 , the true center of the front compression chamber  16  relative to the output shafts  18  is eccentric. Therefore, the shape of the front compression chamber  16  relative to the true circumference (as shown by imaginary lines) is slightly enlarged, and it has curved outward enlargements at the outermost portion of the blade assembly  15 , forming curved grooves  161 ,  171  to avert interference. The same is with the rear compression chamber  17  shown in FIG.  8 . Therefore, when the rotor  14  rotates, the blade assembly  15  can tightly abut against the inner walls of the front and rear compression chambers  16 ,  17  to enhance pressure. 
     In order to achieve intake and exhaust effects, the front and rear cylinder rings  11 ,  12  are respectively formed with a front intake port  111  and a rear intake port  121 , and a front exhaust valve  112  and a rear exhaust valve  122 . The front and rear exhaust valves  112 ,  122  are respectively communicated with the combustion chamber  3 . Therefore, air can enter from the front and rear intake ports  111 ,  121  and, due to the pressing of the blade assembly  15 , pass through the exhaust valves  112 ,  122  into the combustion chamber  3 . 
     The rotary gas motor unit  2  is basically identical with the rotary compression unit  1  in terms of structure, only that it is smaller in size. Like the rotary compression unit  1 , the rotary gas motor unit  2  includes front and rear cylinder rings  21 ,  22 , an intermediate ring  23 , a rotor  24 , a blade assembly  25 , front and rear combustion chambers  26 ,  27 , and output shafts  28 . Besides, the components, such as the fixed and movable blades  251 ,  253 , are the same. Furthermore, inner walls of the combustion chambers  26 ,  27  also have curved outer enlargements  261 ,  271  due to the outward extension of the blade assembly  25  so as to prevent interference and maintain air-tightness. The reference numerals for the components of the rotary gas motor unit  2  correspond to those of the rotary compression unit  1  except that they all start with the number “2”. The only differences are that the rotary gas motor unit  2  has front and rear intake valves  211 ,  221  and front and rear exhaust ports  212 ,  222 , and that the output shafts are connected by a belt or chain to allow synchronous movement. 
     The combustion chamber  3  includes a front chamber and a rear chamber, namely, chamber A and chamber B in FIG.  1 . Operation of the front and rear chambers is alternating. The combustion chamber  3  has cams to control front and rear intake ports  212 ,  222 , and exhaust valves  112 ,  122 . Besides, it is provided with an injector and an ignition device so that a mixture of fuel and air can, after compression, allow injection/explosion. 
     Referring back to FIG. 1, FIGS. 7 and 8 during operation, since there are two chambers, the front chamber, i.e., the chamber A, has the front exhaust valve  112  (designated by V1), the front intake valve  211  (designated by V2), the rear exhaust valve  122  (designated by V3), and the rear intake valve  221  (designated by V2) as control valves. And due to alternating operation, when V1 opens, V2 closes. At this point, compression occurs in chamber A. At the same time, V3 is closed while V4 is open, and explosion occurs in chamber B. Therefore, there is output of power (see FIG.  7 ). Subsequently, V1 closes; V2 opens. Explosion occurs in chamber A and there is power output. At the same time, V3 opens while V4 closes. At this point, compression occurs in chamber B (see FIG.  8 ). Therefore, there are two greater-than-180° strokes within 360°. In other words, the engine having two-chamber construction of the present invention is comparable to a conventional four-cylinder engine in terms of power output. 
     In the present invention, due to the alternating action of the double chamber compression chamber, there can be a relative uniform mixing of fuel and air to achieve complete combustion. Furthermore, because of the arrangement of the grooves, the blade assembly can rotate while abutting tightly against the inner walls of the front and rear compression chambers of the rotary compression unit to enhance compression effects. It can be appreciated that these improvements are not found in conventional rotary engines. 
     Although the present invention has been illustrated and described with reference to the preferred embodiment thereof, it should be understood that it is in no way limited to the details of such embodiment but is capable of numerous modifications within the scope of the appended claims.