Abstract:
A gearing unit of a power transferring system includes an input shaft, a hydraulic pump, a hydraulic motor, a worm rod and a worm wheel which is cooperated with a pair of planet gears. An output shaft is connected with the worm wheel to transfer torque so as to improve the initial speed, upward slope driving, gear shifting and braking of vehicles.

Description:
FIELD OF THE INVENTION 
       [0001]    The present invention relates to a gearing mechanism, and more particularly, to an improved clutch and gearing mechanism of a power transferring system for vehicles and mechanical machine. 
       BACKGROUND OF THE INVENTION 
       [0002]    A conventional power transferring system for vehicle is shown in  FIG. 1  and generally includes an engine  10   a,  a clutch  12   a,  a gearing and manual brake device  13   a,  a turbo compressor  16   a  and an air releasing valve for braking  17   a  which reduces the air supply to the engine and causes the un-complete combustion such that the compression force in the engine is used to brake the vehicle. The exhaust air is released via a catalyzer converter  18   a  and a muffler  19   a.    
         [0003]    In the conventional power transferring system, the engine receives extra air from the turbo and this is affected only when the revolution of the engine is at mediate level and is useless when the vehicle starts from stationary status or when the high gear is shifted to low gear. There are two types of operation of the gearing device and the first one is manual operation and the second one is automatic operation. When shifting by manual, the torque drops immediately and the torque cannot be increased immediately. The automatic operation uses a torque converter to cooperate with the acceleration valve to maintain the toque. However, the temperature of the engine oil is high in the engine and this cause low efficiency of transmission. The heavier the load is, the higher the heat lost is. The conventional braking system causes high temperature when the braking device is operated frequently such as when the vehicle goes on a downward slope road. The air releasing valve for braking  17   a  does not work at high gear position with low revolution. Besides, the in-complete combustion generates problems related to air pollution. 
         [0004]    The present invention intends to provide a gearing unit of a power transferring system wherein the revolution of each gear of the gearing unit can be increased to its maximum revolution. When the acceleration pedal is pushed, the output shaft is affected. When the acceleration pedal is released, the engine brake feature is performed. 
       SUMMARY OF THE INVENTION 
       [0005]    The present invention relates to a gearing unit of a power transferring system includes an input shaft, a hydraulic pump, a hydraulic motor, a worm rod and a worm wheel which is cooperated with a pair of planet gears. An output shaft is connected with the worm wheel to transfer torque. 
         [0006]    The present invention will become more obvious from the following description when taken in connection with the accompanying drawings which show, for purposes of illustration only, a preferred embodiment in accordance with the present invention. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0007]      FIG. 1  shows a conventional power transferring system for vehicles; 
           [0008]      FIG. 2  is a cross sectional view of the gearing unit of the present invention; 
           [0009]      FIG. 3  is a perspective view of the gearing unit of the present invention; 
           [0010]      FIG. 4  shows a cross sectional view of the second gearing unit of the present invention; 
           [0011]      FIG. 4A  shows a cross sectional view along line  4 A- 4 A in  FIG. 4 ; 
           [0012]      FIG. 5   a  is a diagram to disclose the optimized revolution line of the power transferring system of the present invention, the revolution line of the conventional power transferring system, the optimized section of the clutch, the interruption line of the static wind speed, and the optimized combustion zone; 
           [0013]      FIG. 5   b  shows the maximum torque line, gear ratio of the present invention and the maximum torque line after gear shifting of the conventional power transferring system, and 
           [0014]      FIG. 5   c  shows that the power transferring system is operated at gear three and operation of the conventional power transferring system at gear three. 
       
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
       [0015]    Referring to  FIGS. 2 to 5   c,  the first gearing unit  20  of the power transferring system of the present invention comprises a casing  31  in which an input shaft  21  is received and the input shaft  21  has a first end and a second end. The first end of the input shaft  21  extends out from the casing  31  so as to receive power, and the second end of the input shaft  21  is connected to an output shaft  42  which extends out from the casing  31 . 
         [0016]    A hydraulic pump  22  is located around the input shaft  21  and a hydraulic control valve  221  is connected to the hydraulic pump  22 . The hydraulic control valve  221  communicates with a hydraulic hose  41  which is connected to an automatic control valve  40 . The automatic control valve  40  is controlled by a control pedal  38  and a clutch pedal  39 . 
         [0017]    An oil tank  24  is connected to the hydraulic motor  26  and includes multiple passages  23 . A hydraulic motor  26  is connected to the hydraulic pump  22  and located opposite the input shaft  21 . At least one hydraulic pipe  25  is connected between the hydraulic motor  26  and the hydraulic pump  22 . A worm rod  27  is connected to the hydraulic pump  26 . 
         [0018]    A rotatable ring gear  28  is located a side of the hydraulic pump  26  and opposite the hydraulic pump  22 . The rotatable ring gear  28  is located around the input shaft  21 . A fixed ring gear  29  is located on a side of the rotatable ring gear  28  and opposite the hydraulic motor  22 . The fixed ring gear  29  is located around the input shaft  21 . 
         [0019]    A circular frame  30  is located between the rotatable ring gear  28  and the fixed ring gear  29 , and the circular frame  30  is located around the input shaft  21 . An output main gear  33  is located in the fixed ring gear  29  and located around the input shaft  21 . A plurality of output planet gears  32  is located in the fixed ring gear  29  and located outside of the output main gear  33 . An input main gear  35  is located in the rotatable ring gear  28  and located outside of the input shaft  21 . An input planet gear  34  is located in the rotatable ring gear  28  and located around the input main gear  35 . A worm wheel  36  is located between the rotatable ring gear  28  and the hydraulic pump  22 . The worm wheel  36  is engaged with the worm rod  27 . 
         [0020]    The present invention allows the vehicle to immediately increase the maximum horse power after each shifting so as to avoid lack of torque after each shifting. By this way, the driver needs not to shift to a lower gear due to lack of torque. As shown in  FIGS. 2 and 3 , when the gearing device needs not to be changed, the output shaft  21  is assumed to be (+) and the hydraulic pump  22  is rotated in positive direction which does not affect the hydraulic oil thereof so that the hydraulic motor  26 , the worm rod  27 , the worm wheel  36  and the rotatable ring gear  28  are stationary. The input main gear  35  (+) drives the input planet gear  34  (−). Because the rotatable ring gear  28  is stationary, the circular frame  30  is forced to rotate in (+) direction and the output planet gear  32  is driven which is rotated in (−) direction due to the fixed ring gear  29 . The output main gear  33  rotates in (+) direction and outputs from the output shaft  42  in (+) direction. Because the rotatable ring gear  28  and the stationary ring gear  29  are the same size, so that the input and the output of the system is the same. 
         [0021]    When the gearing device needs to be changed, the pedal  38  is pushed and the valve  37  is activated so that the hydraulic pump  22  outputs hydraulic oil. The driver controls the pedal  38  to control the volume of the hydraulic oil sent to the hydraulic motor  26  to control the revolution of the worm rod  27 . This makes the rotatable ring gear  28 (−) to generated controllable rotation in reverse direction. In the meanwhile, both the output shaft  42  and the output main gear  33  (+) rotate in (+) direction, and drive the output planet gear (−), the circular frame  30 , the input planet gear  34  (−), the input main gear  35  (+) and the output shaft  21 (+) to drive the engine. It is noted that the rotatable ring gear  28  (−) drives the input planet gear  34  (−) in the reverse direction to accelerate the speed of the input planet gear  34  more quickly in (−) direction, the input main gear  35  (+) accelerates in (+) direction. Therefore, the resistance in the engine is small so that the engine can be operated at high speed. Because the input planet gear  34  is a free gear which does not affect the revolution of the circular frame  30  (+). When the engine is accelerated to its maximum revolution, the driver releases the pedal  38  gradually to slow down the rotatable ring gear  28  which makes the input planet gear  34  exert a force in (+) direction to the input main gear  35  and the circular frame  30  (+) rotates faster to quickly accelerate the vehicle. The rotatable ring gear  28  is forced to rotate in (−) direction so that the worm wheel ( 36 ) and the worm rod  27  can be activated simply by releasing the friction force therebetween. Therefore, the engine is able to randomly increase its output to maximum horse power in any gearing. The fuction can also be used in automatic gear shifting engine without using a torque converter. 
         [0022]    Referring to  FIG. 5   a  which shows the optimized revolution line  70  of the power transferring system of the present invention, the revolution line of the conventional power transferring system, the optimized section  72  of the clutch, the interruption line  73  of the static wind speed, and the optimized combustion zone  74 .  FIG. 5   b  shows the maximum torque line  75 , the gear ratio  76  of the present invention and the maximum torque line  77  after gear shifting of the conventional power transferring system.  FIG. 5   c  shows that the operation line  78  of the power transferring system operated at gear three and operation line  79  of the conventional power transferring system at gear three. 
         [0023]    The related speed of the input main gear  35 , the circular frame  30  and the rotatable and fixed ring gears are disclosed as follows: 
         [0024]    If the rotatable ring gear  28  is not rotated, the revolution (+) of the input main gear  35 =(the number of the ring gear  28 /(the number of teeth of the input main gear  35 +1)×the number of revolutions (+) of the circular frame  30 . 
         [0025]    If the circular frame  30  is not rotated, the revolution (+) of the input main gear  35 =(the number of the ring gear  28 /the number of teeth of the input main gear  35 )×the number of revolutions (−) of the ring gear  28 . 
         [0026]    If the circular frame  30  is not rotated, the revolution (+) of the ring gear  28 =(the number of teeth of the input main gear  35 /the number of the ring gear  28 +1)×the number of revolutions (+) of the circular frame  30 . 
         [0027]    As shown in  FIGS. 4 and 4A , which show a second gearing unit “A” which includes a second input shaft  43  which is assumed to rotated in (+) direction, a active wheel  45  which is connected to the second input shaft  43  so as to drive a cam disk  48  which is rotated with the second input shaft  43 . At least one roller  47  is located between the cam disk  48  and the passive shaft  49 . When the hydraulic tank  46  is activated by hydraulic oil from the braking action by the driver, the hydraulic tank  46  drives a slide  44  to push the cam disk  48  upward so as to move the at least one roller  47  to be engaged with a recess in the passive shaft  49 , such that the passive shaft  49  is rotated in (+) direction. A detection device is used to monitor the speed, the temperature and vibration of the second gearing unit “A”. 
         [0028]    While we have shown and described the embodiment in accordance with the present invention, it should be clear to those skilled in the art that further embodiments may be made without departing from the scope of the present invention.