Patent Abstract:
Improvements in a transmission are provided for transferring power from a power source to a work unit. The pump transfers energy received from the power source into a fluid or gas. The first turbine is fixed to output shaft, and a plurality of additional turbines are fixed on either one-way overrunning clutches or multi-disc clutches and these clutches are fixed to the output shaft and after each turbine is a multi-valves that discharges the fluid or gas. After all of the multi-stage turbines a first planetary gear set connects the transmission to the vehicle or work unit. The second planetary gear set is located between the last turbine and the first planetary gear set. During braking the planetary gear set reverses turning direction of the turbines and convert the turbines into pumps where they will pump low pressure fluid to a high pressure accumulator.

Full Description:
CROSS REFERENCE TO RELATED APPLICATION 
     This application is a continuation-in-part of applicant&#39;s co-pending application Ser. No. 12/421,286 filed on Apr. 9, 2009 continuation-in-part of applicant&#39;s co-pending application Ser. No. 12/145,469 filed Jun. 24, 2008 and PCT/US09/40060 filed Apr. 9, 2009 which is a continuation-in-part of applicant&#39;s co-pending application Ser. No. PCT/US08/08139 filed Jun. 30, 2008 the entire contents of which is hereby expressly incorporated by reference herein. 
    
    
     STATEMENT REGARDING FEDERALLY SPONSORED RESEARCH OR DEVELOPMENT 
     Not Applicable 
     THE NAMES OF THE PARTIES TO A JOINT RESEARCH AGREEMENT 
     Not Applicable 
     INCORPORATION-BY-REFERENCE OF MATERIAL SUBMITTED ON A COMPACT DISC 
     Not Applicable 
     FIELD OF THE INVENTION 
     This invention relates to improvements power transmission between a motor to a vehicle and energy recovery from the breaking system. More particularly, the present hydraulic hybrid turbo transmission includes an input shaft coupled to a power source and to a pump that is configured to rotate with the input shaft. The hydraulic pump transfers energy received from the power source into a fluid. The transmission includes an output shaft and a multi-stage turbine in line with each other. The first turbine is fixed to output shaft, the rest of the turbines are fixed on either one-way overrunning clutches or multi-disc clutches and these clutches are fixed to an output shaft and after each turbine that has multi-valves to discharge the fluid or gas. After the multi-stage turbines a planetary gear set to redirect the operation of the vehicle from forward drive (D) or to neutral (N) or to reverse drive (R). Energy recovery is stored in a high pressure accumulator. 
     BACKGROUND OF THE INVENTION 
     Most automatic transmissions being used today normally have high fuel consumption because of the weight of the transmission, complicated system and does not meet economical driving conditions. Most manual transmission and automatic transmission are mechanical in nature and a portion of the time the speed and torque of the transmission does not match the speed and torque that is required by a vehicle or by other means. The transmission matches the speed of the vehicle but produces more or less torque that is required by the vehicle therefore there are some energy losses. 
     Hydraulic hybrid turbo-transmission is hydraulic transmission and is continuously variable transmissions therefore the speed and torque will match the speed and torque is required by the vehicle therefore less energy loss. 
     Modern automatic transmissions use four or more multiple-disc clutches where the clutch plate has rough frictional material on their faces. When the multiple-disc clutches are not applied the disc will run with engine or with transmission output therefore each disc acts as disc pump and will consume energy and produce heat in the transmission. Modern automatic transmission and manual transmissions use more than eight gears when the gears run with and without engagement with the output shaft or input shaft will act as a pump because of the teeth of the gear therefore they consume energy and produce heat in the transmission. Exemplary examples or hydraulic hybrid turbo transmission units are provided herein. 
     A hydraulic hybrid turbo transmission is a transmission and has the ability for energy recovery using low pressure storage and a high pressure accumulator to store recovered energy from braking. 
     The inventor&#39;s prior pending application Ser. No. 12/481,159, 12/269,261, PCT/US09/46745 and PCT/US09/4509 provides some initial features and functions that are further refined and elaborated in this application. 
     U.S. Pat. No. 2,890,600 issued Jun. 16, 1959 to R. L. Smirl et al., and U.S. Pat. No. 2,812,670 issued Nov. 12, 1957 to M. P. Winther both disclose a single stage hydraulic transmission where a viscous fluid transfers power between two vanes. These two patents disclose the early stages of a torque converter where rotational speed of the motor created connected the engine to the drive wheels. While these transmissions disclose power transmission they are limited to only a single speed with a multi-speed gearbox. 
     U.S. Pat. No. 2,671,543 issued Mar. 9, 1964 to J. Bosch discloses a fluid transmission system. The fluid transmission system uses two opposing turbines separated by a gap. Both the engine speed and the gap distance are variable to provide some additional speed variation between the motor and the driven wheels. While this patent discloses a more variable speed system the transmission has only one gear and is therefore limited in the range of speed control. 
     U.S. Pat. No. 4,100,823 issued Jul. 18, 1978 discloses an automatic transmission having a hydrodynamic torque converter between the input shaft and the gear system. The torque converter can be disengaged from the gear system to allow for changing of the gear ratio before re-engaging the torque converter. While this patent uses a hydrodynamic torque converter, gears are still used to change the ratio turning ration of the input to output shaft. 
     U.S. Pat. No. 4,624,110 issued Nov. 25, 1986 to Harry H. Levites discloses a fluid powered turbine using multiple turbines. The multiple turbines are configured in a tapers housing where the velocity of the fluid within the housing is increased as the fluid passes though a smaller cross sectional area thereby increasing the rotating speed of each turbine placed further down the tapered housing. While this patent describes the use of multiple turbine blades it operates as a steam turbine to generate power from steam entering the system. The generation of the pressure to turn the turbines is created external to the system as opposed to between turbines. 
     U.S. Published application 2005/0016167 that was published on Jan. 27, 2005 to Rodney Singh discloses a Hydraulic drive system and improved filter sub-system therefore. This hydraulic drive system uses an accumulator to store pressurized fluid in a tank and the pressurized fluid is later used to drive the vehicle. While this application shows a storage tank the fluid is not pressurized from the braking system and further does not use a second pump to increase the stored pressure. There system requires a transmission, pump and pump/motor as a separate system. 
     U.S. Pat. No. 7,337,869 issued Mar. 4, 2008 to Charles Gray Jr., discloses a Hydraulic hybrid vehicle with integrated hydraulic drive module and four-wheel-drive, and method of operation thereof. The drive system uses a motor to drive a hydraulic pump that provides hydraulic power to drive the vehicle as a two wheel or four wheel drive vehicle. Accumulator of hydraulic pressure does not pass through a two stage pump to increase the pressure for storage. There system requires a transmission, pump and pump/motor as a separate system 
     U.S. Pat. No. 7,082,757 issued Aug. 1, 2006 to Chris Terlak discloses a Pump/motor operating mode switching control for hydraulic hybrid vehicle. This patent discloses allowing the hydraulic pump/motor to change between the two modes of operation based upon the vehicle being accelerated or stopping. When the brake pedal is depressed the motor turns into a pump and pressurizes hydraulic fluid into a reservoir and the pressurized fluid is later used to accelerate the vehicle. While this application pressurizes fluid from regenerative braking the system does not provide for a two stage pump and further does not use the motor as a transmission for the drive wheels. There system requires a transmission, pump and pump/motor as a separate system 
     What is needed is a transmission with multiple turbines that are individually controlled and connected with one-way clutches to the output shaft. The proposed application provides this solution in a simple single unit and there is not a need for the pump and motor for energy recovery from the braking system. The proposed solution is a simple single unit that works either as a pump/motor or a pump plus pumps. Therefore there is not a need for an outside unit such as a pump/motor or a pump. 
     BRIEF SUMMARY OF THE INVENTION 
     It is an object of the hydraulic hybrid turbo-transmission to operate without frictional disc clutched or gears that create heat that results in a loss of energy. 
     It is an object of the hydraulic hybrid turbo-transmission to create a hydraulic hybrid turbo-transmission that is simpler and has fewer components than a modern automatic transmission. Only one controller is used with a few solenoid valves where the solenoids control by the transmission module (TCM) and that the transmission acts as an automatic transmission. Manual shifting can be done by operating the solenoid valves manually to act as a manual transmission or by (TCM). It is simpler in operation and less expensive than modern automatic or manual transmissions. 
     It is another object of the hydraulic hybrid turbo-transmission to eliminate a torque converter. The torque converter is not required in the hydraulic hybrid turbo-transmission and therefore more energy is saved from efficiency loss and weight reductions. 
     It is another object of the hydraulic hybrid turbo-transmission to be used in all vehicles from small vehicles to large vehicles by changing the surface are of the turbine blades and or the angle of the turbine blades and or by using two or more pumps inline for heavy equipment such as trucks, tractors or bulldozers 
     It is still another object of the hydraulic hybrid turbo-transmission to be used in other application such as pump drivers by using the motor as a power source where the hydraulic hybrid turbo-transmission acts as a variable torque drive or variable speed drive for the pump and other applications. 
     It is still another object of the hydraulic hybrid turbo-transmission to operate for energy recovery from the vehicle&#39;s braking system without the need for an outside pump/motor. 
     Various objects, features, aspects, and advantages of the present invention will become more apparent from the following detailed description of preferred embodiments of the invention, along with the accompanying drawings in which like numerals represent like components. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  shows a block diagram of the hydraulic hybrid turbo-transmission connected between an engine and a vehicle under normal operation. 
         FIG. 2  shows a block diagram of the hydraulic hybrid turbo-transmission during braking condition. 
         FIG. 3 . Shows a system curve for a three speed hydraulic hybrid turbo-transmission. 
         FIG. 4A-4E  shows a three speed hydraulic hybrid turbo-transmission and the fluid flow through each of the three speeds. 
         FIG. 5  shows a side cross sectional view of a three speed hydraulic hybrid turbo-transmission without a clutch. 
         FIG. 6  shows a side cross sectional view of a five speed hydraulic hybrid turbo-transmission. 
         FIG. 7  shows a system curve for a five speed hydraulic hybrid turbo-transmission. 
         FIG. 8  shows the five speed hydraulic hybrid turbo transmission with two planetary gears with a reservoir and an accumulator. 
         FIG. 9  shows the five speed hydraulic hybrid turbo transmission with one planetary gear set and one pump. 
         FIG. 10  shows the five speed hydraulic hybrid turbo transmission with one planetary gear with a reservoir, an accumulator and a pump/motor. 
         FIG. 11  shows a side cross sectional view of two planetary gear sets. 
         FIG. 12  shows a side cross sectional view of one planetary gear set. 
         FIG. 13  shows a front cross sectional view of one turbine of a hydraulic hybrid turbo-transmission with the valves closed. 
         FIG. 14  shows a front cross sectional view of one turbine of a hydraulic hybrid turbo-transmission with the valves open. 
         FIG. 15  shows a partial isometric view of one-way overrunning clutches or roller clutches that connect the speed turbines to the driven shaft. 
         FIG. 16  shows a partial isometric view of a multiple disc clutch that connects the speed turbines to the driven shaft. 
         FIG. 17  shows a side cross-sectionals view of a multiple-disk clutch used in the hydraulic hybrid turbo-transmission. 
         FIG. 18  shows a side cross sectional view of a three speed hydraulic hybrid turbo-transmission with a direct drive clutch. 
     
    
    
     DETAILED DESCRIPTION 
       FIG. 1  shows a block diagram of the hydraulic hybrid turbo-transmission connected between an engine and a vehicle. From this block diagram a power source  20  such as an engine or motor is connected to the hydraulic hybrid turbo-transmission  30 . Within the transmission is a pump  40 , fluid coupled to turbines  50  and then coupled to a gear set  120 . The hydraulic hybrid turbo-transmission  30  is then connected to a work unit  21  such as a vehicle. A low pressure fluid storage  16  and a high pressure fluid accumulator. 
       FIG. 2  shows a block diagram of the hydraulic hybrid turbo-transmission during braking. From this block diagram a power source  20  such as an engine or motor is connected to the Hydraulic hybrid turbo-transmission  30 . Within the transmission is a pump  40  and turbine  50  that acts as a fluid coupled to turbines  50  that act as pumps by reverse rotation of the turbines  50  on the shaft by a second gear set. A low pressure fluid storage  16  and a high pressure fluid accumulator  17 . The Hydraulic hybrid turbo-transmission  30  is then connected to a work unit  21  such as a pump or other uses. 
       FIG. 3 . Shows a system power curve for the Hydraulic hybrid turbo-transmission. The left vertical axis  71  is head in ft for a pump. The right vertical axis  73  is Torque in lb-ft for turbines on an output shaft. The upper horizontal axis  70  is N for the speed for a turbine in Revolutions per Minute (RPM). The bottom horizontal axis  72  is Q for Gallons per Minute (GPM) for a pump or turbine. Solid curved lines  74  represent system curves for a pump at different N, RPM(s). Dashed curved lines  75  represent system curves for turbines. From these curves the 1 st  Gear curve  76  shows the first gear, Turbine  1  (T 1 )+Turbine  2  (T 2 )+Turbine  3  (T 3 ) in operation. The curve of 2 nd  Gear  77  shows the second gear, Turbine  1 +Turbine  2  in operation. The curve of 3 rd  Gear  78  shows the third gear, Turbine  1  in operation. The turbines and gears are described in more detail with  FIGS. 4   a - 4   d.    
       FIG. 4A-4E  shows a three speed Hydraulic hybrid turbo-transmission and the fluid flow through turbines. The chart shown in  FIG. 4E  identifies the activation of the three solenoids to allow flow through the three turbines. The solenoids are designated as ON or OFF and their activation or de-activation allows or prevents flow from the pump  40  through the turbines  51 - 53 . When any solenoid valve is on (closed) no flow will exist to the solenoid valve and the valve is OFF (open) flow will be allowed to pass though the valve.  FIG. 4A  represents a third gear where solenoid  1  is OFF and  2  and  3  are ON. Input shaft  26  turns pump  40  that supplies output flow  25  through turbine (T 1 )  51 . Because solenoids  2  and  3  are ON no flow is made through turbines (T 2 )  52  or (T 3 )  53 . Roller clutches in these turbines allow the turbine to free spin on the output shaft  90 .  FIG. 4B  represents second gear where solenoid  2  is OFF and solenoids  1  and  3  are ON. Input shaft  26  turns pump  40  that supplies output flow  25  through turbine (T 1 )  51  and turbine (T) 2   52 . Because solenoid  2  is OFF no flow is made through turbine or (T 3 )  53 . Roller clutch in this turbine allow the turbine to free spin on the output shaft  90 .  FIG. 4C  represents first gear where solenoid  3  is OFF and solenoids  1  and  2  are ON. Input shaft  26  turns pump  40  that supplies output flow  25  through turbines (T 1 )  51 , (T 2 )  52  and (T 3 )  53  that turn the output shaft  90 . Return flow  24  goes from the turbines back to the pump  40 .  FIG. 4D  shows the turbines acting as pumps in braking. During braking the turbines act as pumps. During braking the turbine shaft will turn in the reverse direction by the second planetary gear set  120  (shown in  FIG. 11 ) and then the turbines will act as a pumping system. The engine will turn the pump  40  and the braking system will turn pumps  1 ,  2  and  3  that will pump the low pressure fluid  40  to a higher pressure fluid  25  into the accumulator  17 . 
       FIG. 5  shows a side cross sectional view of a three speed hydraulic hybrid turbo-transmission without a clutch.  FIG. 18  shows a side cross sectional view of a three speed hydraulic hybrid turbo-transmission with a clutch for direct drive as another contemplated option. The hydraulic hybrid turbo-transmission is essentially round and where the piston components are shown on the top of this figure are also shown on the bottom of this figure. A brief look at  FIGS. 15 and 16  show a cross section view of a set of three valves around the hydraulic hybrid turbo-transmission and each of the three sets has eight valves it is contemplated that more or less than eight valves can be used. Rotational bearings  27 ,  28  and  29  support the various input  26  and output  90  shafts as the power is transmitted to the input shaft  26  through the pump hydraulic hybrid turbo-transmission to the output shafts  90  and  91 . In operation input shaft  26  is turned by a motor or the like. When input shaft  26  is turned it will turn pump  40 . A portion of the flow  37  will be used to operate solenoids  81 - 83  that control valves  61 - 63  that allow one or more of the turbines  51 - 53  to turn. Valves  61 - 63  are maintained in the open position with spring(s)  69 . A multi-check valve  59  prevents high pressure from flowing back through stream  24  when the engine is not turning. 
     The output flow  25  from pump  40  will push against first turbine  51  and will turn the turbine on. Output flow from turbine  51  will push through the nozzle  112  to redirect flow to turbine  52  and will turn the turbine on. The flow then goes through nozzle  113  to redirect the flow to another turbine  53  and turn the turbine on and then the flow  24  will return back to the pump through nozzle  111 . The pressure after the pump  40  will be larger than the pressure at the nozzle  112 . The pressure through each successive turbine will drop gradually as the fluid flows though each turbine. Specifically the pressure at nozzle  112  will be greater than the pressure at nozzle  113  and the pressure at nozzle  113  will be larger than the pressure after turbine  53 . 
     In this figure flow  37  is shown passing through only valves  82  and  83  because valve  81  is closed. Flow through the solenoids  82  and  83  then flows into valves  61  and  62  that block flow from returning  24  back to the pump. The output flow will push through nozzles  112  and  113  to turn their respective turbines. Turbines  52  and  53  are connected to the shaft with one-way clutches  101  and  102  the turn the shaft and also allow the turbines  52  and  53  to free spin on the shaft when flow, or insufficient flow, is not running though the turbines. Two planetary gear sets  120  are located after the hydraulic hybrid turbo-transmission. The energy recovery system is shown and described in more detail in  FIG. 8 . 
       FIG. 6  shows a side cross sectional view of a five speed Hydraulic hybrid turbo-transmission. The transmission shown in this figure is similar to the transmission shown in  FIG. 5 . The major differences are that this transmission has five turbines to simulate a three speed transmission and a permanent planetary gear set overdrive  36  exists between the input shaft  26  and the pump  40  turbines. Output flow  25  from the pump  40  is fed to the solenoids  81 - 85  and the turbines. In this figure solenoid  83  is off therefore the valve  63  is open. When this valve  63  is open return flow  24  will flow back to the pump  40 . The remaining valves  61 ,  62 ,  64  and  65  will be closed and no flow will go through the opening to pump  40 . In this figure the turbines are connected to the shaft  90  with one-way clutches  101 - 104 . Flow to and through a turbine will turn on the turbine and engage the clutch(s). When there in minimal or insufficient flow the turbine will free spin on the shaft. 
       FIG. 7 . Shows a system curve for a five speed hydraulic hybrid turbo-transmission. The transmission shown in this figure is similar to the three speed transmission in shown and described in  FIG. 3  except the speed of the pump  74  will be higher than the speed of the engine because of a permanent planetary overdrive that is located between the engine and the pump. 
       FIG. 8  shows the five speed hydraulic hybrid turbo transmission with two planetary gears  120  that are shown and described in  FIG. 11 . The first gear set is used in the vehicle for forward, neutral and reverse modes. The second gear set is also used for turbine operation. Under normal operation the gear set sits in a forward mode and the turbines work as motors. When the brakes are applied the gear set sits in the reverse modes and the turbines operate as pumps. During the braking mode the pump  40  is uses the energy from the engine as power recovery and the pumps (turbine/pumps) use the energy from the braking system. All of the pumps use the low pressure flow  24  and send the outlet flow  25  to the high pressure accumulator  17  through conduit, line or pipes  137  and  139 . Conduit  139  has a check valve  93  and a valve  79  that opens during braking. When the gas pedal of the vehicle is depressed, valve  97  will open to allow high pressure fluid through a throttling valve  97 , check valve  93  and into the transmission where it will turn the turbines  101 - 104  to move the vehicle. 
       FIG. 9  shows the five speed hydraulic hybrid turbo transmission with a drive motor with a reservoir and a high pressure storage tank. This is another preferred embodiment of the hydraulic hybrid turbo transmission where a low pressure fluid storage tank  16  holds and supplies hydraulic fluid to the system. This embodiment also has a high pressure fluid accumulator  17 . When the brakes are applied valve  79  will open and hydraulic fluid will be pumped from the pump  40  through pipe  137  and into a second pump  87  that is driven by drive  86  that will further increase the pressure of the hydraulic fluid and pump the higher pressure fluid into the high pressure accumulator  17 . When the user presses the accelerator of the vehicle, valve  79  will be closed and, throttling valve  97  will open and high pressure hydraulic fluid will be passed back through pipe or tube  137  back into the hydraulic hybrid turbo transmission where it will turn the transmission and propel the vehicle. 
       FIG. 10  shows the five speed hydraulic hybrid turbo transmission with one planetary gear with a pump/motor  88 . In this embodiment of the hydraulic hybrid turbo transmission where a low pressure fluid storage tank  16  holds and supplies hydraulic fluid to the system. Pipe  11  supplies the hydraulic fluid from the storage tank into the body of the hydraulic hybrid turbo transmission. This embodiment also has a high pressure storage tank accumulator  17 . When the brakes are applied valve  94  will open and hydraulic fluid will be pumped from the pump  40  through pipe  139  and into a second pump/motor  88  that is driven by drive  86  that will further increase the pressure of the hydraulic fluid and pump the higher pressure fluid through valve  92  and into the high pressure reservoir accumulator  17 . The valve  89  and valve  97  will be closed when the user presses the accelerator, throttling valve  97  will open and high pressure hydraulic fluid will be passed back through pipe or tube  138  back into the pump/motor  88  where it will turn the drive  86  that will turn output shaft  90  to propel the vehicle. The valves  89  and  97  will be open and the valves  92  and  94  will be closed/ 
       FIG. 11  shows a cross-sectional view of two planetary gear sets  120 . The first gear set is used in driving mode where it locks the multi-disc clutch  32 . In reverse mode, braking band  127  is locked. For neutral, the multi-disc clutch  32  and the brake band  127  is free and the system has a piston  109  that pushes against the multi-disc clutch  32 , planetary gear carrier  35 , planetary gear  107 , sun gear  108  and common ring gear  126 . The ring gear  126  has a one-way clutch to let the ring gear  105  turn on only one direction. The second planetary gear is used either for forward mode where the turbines act as motors by locking the multi-disc clutch  32 . For reverse mode, the turbines act as pumps when the brakes are applied. The reverse mode is performed by locking the brake band  128  and releasing the disc clutch  32 . 
       FIG. 12  shows a cross sectional view of one planetary gear set  119  and is similar to the first gear shown and disclosed in  FIG. 11 . 
       FIG. 13  shows a front cross sectional view of one turbine of a Hydraulic hybrid turbo-transmission with the valves closed.  FIG. 9  shows a front cross sectional view of one turbine of a Hydraulic hybrid turbo-transmission with the valves open. While it is shown with eight valves  62   a - 62   h  existing around the hydraulic hybrid turbo-transmission it is contemplated that more or less than eight valves can be used. In  FIG. 8 , the solenoid,  82  is open and flow enters all the valves  62   a - 62   h , whereby pushing the valves closed. In this orientation flow will be blocked from exiting the opening after turbine  52  (not shown). In  FIG. 9 , the solenoid,  82  is closed and flow is blocked from all the valves  62   a - 62   h , whereby allowing flow  39  through the opening after turbine  52  (not shown). Note that the spring(s)  69  maintains the valve(s) open in  FIG. 14 . 
       FIG. 14  shows a partial isometric view of one-way overrunning clutches or roller clutches that connect the speed turbines to the driven shaft. This figure shows one contemplated embodiment of a one way clutch using a plurality or dogs or sprags  130  connected around a shaft  90 . When the turbine  132  turns in one direction the dogs or sprags  130  grip onto the shaft  90  to turn the shaft. When the turbine  132  stops or turns  133  in the opposite direction, the dogs or sprags release the shaft and allows the turbine to free spin on the shaft  90 . While dogs or sprags are shown and described a number of other one-way clutches or bearing are contemplated that perform equivalently. 
       FIG. 15  shows a partial isometric view of a multiple disc clutch that connects the speed turbines to the driven shaft.  FIG. 16  shows a side cross-sectionals view of a multiple-disk clutch used in the Hydraulic hybrid turbo-transmission.  FIG. 16  shows a shaft  90  connected to a multi-disc clutch plate  32  through bearing  131 . The multi-disc clutch pack  32  is shown with more detail in  FIG. 17 . This configuration uses the pressure of the output flow  25 , which comes from the pump, to go through opening  138  to push piston  139  and lock the disk clutch  141 . The moving clutch plate has the turbine blades  132  to provide rotational motion  133  on the output shaft  90 . In addition to the output flow  25  entering the opening  138  flow will also move through the nozzle(s)  140 . 
       FIG. 17  shows a partial cross-sectional view of the turbine with a multiple-disc clutch connected to output shaft  90  with bearing  131 . When the differential pressure before or after the turbine is sufficient to turn the turbine and lock the multi-disc clutch then the power will transfer to output shaft  90 . The pressure  25  will turn the turbine  132  and push through opening  138  where it will push piston  139  against the disk clutch  141  and lock the turbine to output shaft  90 . 
       FIG. 18  shows a side cross sectional view of a three speed hydraulic hybrid turbo-transmission with a direct drive clutch with all of the details of  FIG. 18  that were explained in  FIG. 5  except for the clutch. The clutch is a multi-disc clutch that locks-up shaft  26  with shaft  90  as a mechanical lock for direct drive. The transmission shown in  FIG. 5  uses a hydraulic lock for direct drive while in  FIG. 18  the transmission uses a mechanical lock or hydraulic lock for direct drive where the other gears use all hydraulic locks. The mechanical lock includes a multi-disc clutch  32 , a piston plate  109 , a spring return for the piston  45 , a secondary pump  46  and a solenoid valve  56  for operation of the piston plate  109 . To operate the direct drive, the fluid flows through pipe  37  and then through pipe  41  into pump  46 . This pump increases the pressure of the hydraulic fluid. The higher pressure fluid exits the pump  46  and through pipe  42  where it is controlled by solenoid valve S 6 . When valve S 6  is opened, fluid will flow through pipe  43  and through flow conduit  44  that flows through the input shaft  26 . When high pressure hydraulic fluid enters behind pressure plate piston  109  the pressure will overcome return springs  45  and the multi-disc clutch plates  32  will be forced together thereby positively locking the input  26  and output  91  shafts together. When the solenoid valve  56  is closed, the multi-disc clutch  32  disengaged and the pump  132  and the turbines will run at different speeds for different gear ratios. All of the solenoid valves are controlled by a transmission controller. 
     Thus, specific embodiments of a hydrodynamic hydraulic hybrid turbo-transmission have been disclosed. It should be apparent, however, to those skilled in the art that many more modifications besides those described are possible without departing from the inventive concepts herein. The inventive subject matter, therefore, is not to be restricted except in the spirit of the appended claims.

Technology Classification (CPC): 5