Abstract:
An assembly provides an indirect, rather than direct, drive from a power source to a rotating machine powered by the power source. The assembly includes one or more first pulleys that are connected to the drive source by one or more first belts, and one or more second pulleys that are connected to the rotating machine. Power is transmitted by the power source to the one or more first pulleys, to the one or more second pulleys by a shaft, and to the rotating machine by one or more second belts connecting the one or more second pulleys to a pulley of the rotating machine. The assembly provides for greater speed of and/or torque transmission to the rotating machine with fewer associated problems than if the rotating machine were connected directly to the power source.

Description:
BACKGROUND OF THE INVENTION 
       [0001]    The present invention relates to the enhancement in output of rotating machines such as alternators, generators, propellers, and pumps typically driven by a power source such as electric motors, reciprocating engines, micro-hydro turbines, or other power sources that produce rotary output. Typically the rotating machine is linked to the power source through belts or chains via pulleys mounted onto both the motor output shaft and rotating machine input shaft. Improvements in rotating machine output would also be realized in systems where the power source (drive motor) output shaft is coupled directly (direct drive) to the input shaft of the present invention. 
         [0002]    The physical characteristics, geometries, and components of rotating machines are well known. For example, the major components of typical automotive alternators comprise a rotor, stator, slip rings (non brushless) and a rectifier sub-assembly to produce and distribute the electrical power. The alternator also comprises structural components such as front and rear end bells that house the bearings which allow the rotor to spin centered within the stator. Typically, the end bells are held in place with nuts and bolts arrayed around the periphery of the stator which is sandwiched by the end bells. Structural features of the end bells cooperate to maintain and align external and internal components. 
         [0003]    Electric motors designs are similar in design to alternators, with stators, rotors, bearings, and housing components that align and center the rotor within the stator. U.S. Pat. No. 7,122,923 to Lafontaine et al., which is incorporated herein by reference, describes one method of maintaining, aligning, and centering components of a permanent magnet machine through the use of tie rods, outer cylinders, endplates, bearings, and shafts. 
         [0004]    Generally speaking, rotating machines can be divided into two types of components: (1) function components, and (2) structural components that hold and align components to function properly. As will be explained below, the CTC portion of a CTCRM preferably has shafts, bearings, circlips and other hardware that cooperate to transmit power. That hardware along with nuts and bolts that sandwich the stator and help to align and positionally maintain the components of the CTC-RM so it can function properly. That hardware alone may not be enough to align properly the components and that other structures such as locating collars and pins required to maintain rotating machine components in alignment. Although these ancillary components are known, they are extraneous to the functioning of the CTC-RM. Therefore, these features will not be described here. 
         [0005]    In automotive applications the ability to modify (increase or decrease) the RPM of a rotating machine, such as an alternator, pump, or compressor over part or preferably all of the entire operational RPM range of the engine would be of great benefit. For example, alternator output is directly related to the speed of the alternator so that any increase in RPM yields an increase in alternator output. Typically, the vehicle engine is equipped with a crank pulley mounted to the crank shaft, and through the serpentine belt of the Front End Accessory Drive (FEAD), the belt transmits power to the accessories (rotating machines). An accessory such as an alternator (or any other rotating machine driven by the engine) can have increased RPM across the entire RPM range of the engine by either: (1) decreasing the diameter of the rotating machine pulley, or (2) increasing the diameter of the crank pulley. In either case, the crank-to-rotating machine pulley ratio is increased, which increases the speed of the rotating machine. 
         [0006]    Unfortunately, decreasing pulley diameter of the rotating machine introduces the possibility of belt slippage since both belt wrap and belt contact arc length are important factors in power transmission. 
         [0007]    Increasing the diameter of the engine crank pulley is also problematic. Engine crank pulleys not only drive rotating machines through the FEAD, but are also balanced with engine components to assure smooth operation of the engine. Any modification to the crank pulley would likely require redesigning engine components to ensure engine operation is not compromised. It would therefore be desirable to have the ability to increase or decrease the RPM of rotating machines without changing pulley ratios 
         [0008]    Further, in high-speed engine applications such as in racing cars, the elevated engine RPM (as high as 16,000 RPM) would be detrimental to certain components. For example, certain water pumps have an upper RPM limit that if exceeded, could destroy the pump. In those instances it would be beneficial to decrease the RPM of the accessory across part or preferably all of the entire RPM range of the engine. The pump (or any other rotating machine) can yield a net decrease in RPM across the entire RPM range of the engine by either increasing the diameter of the rotating machine pulley or decreasing the diameter of the crank pulley. In either case, the crankto-rotating-machine pulley ratio is decreased, which decreases the speed of the rotating machine. But, increasing pulley diameter of the rotating machine introduces stresses at the shaft and pulley due to the increased rotational inertia of the larger pulley that may prove unacceptable. Another problem is that decreasing the diameter of the crank pulley can produce an imbalance in the pulley/crank system. It would therefore be desirable to have the ability to decrease the RPM of the rotating machine without changing pulley ratios. 
         [0009]    Modifying rotating machine RPM in automotive applications is problematic, but equally difficult is modifying components to increase the amount of power transmitted from the engine to rotating machines (or accessories). For example, high output alternators such as permanent magnet alternators are well known and require greater amounts of input power over conventional alternators to maximize their output capability. This is also true if an accessory such as an air compressor is replaced with a higher CFM compressor: more power is required to optimize output. 
         [0010]    One method of increasing the amount of power that can be transmitted to the rotating machine is to increase the width of the serpentine belt that drives the rotating machine. For example a diesel engine may be equipped with an 8 groove, K profile, polyv belt that cannot deliver adequate power without belt slippage. The solution is to change the crank and accessory pulleys to accept a 10 or 12 groove belt. This may not be possible due to the increased cost, the extra engineering required to assure proper operation, or the space required to accommodate increased belt width may not be available. 
         [0011]    A second method is to increase the diameter of the accessory&#39;s pulley, which increases contact distance (or “contact length”) between the belt and pulley. Contact length is an important factor in the amount of power that can be transmitted to the pulley. As mentioned above, this approach would present structural redesign issues in high speed applications but in low speed applications, such as large diesel engines those issues are not relevant. Unfortunately, this approach results in a decrease in crank-toaccessory pulley ratio, which results in a decrease in the RPM of the accessory. As mentioned previously, alternator output is directly proportional to its speed. This is true of high output alternators as well as conventional alternators, so even though power transmission capability to the rotating machine is improved, the decrease in RPM may result in an unacceptable decrease in alternator output. 
         [0012]    Another method of increasing the amount of power transmitted to an accessory is to increase belt wrap around the accessory pulley. Belt wrap and its ability to transmit power is a complex function of different factors and is not simply a linear relationship; rather, it increases exponentially as belt wrap angle increases so that even small increases in belt wrap can yield significant increases in power transmission capability. This is typically accomplished by mounting idler pulleys in close proximity to the accessory drive pulley in a location that increases belt wrap around the accessory pulley. Unfortunately, finding space or surfaces to mount extra idler pulleys in engine compartments can be problematic. It would therefore be desirable to increase the amount of belt wrap by adding additional idler pulleys without using elaborate brackets or having to locate existing engine features to mount those additional idler pulleys. 
         [0013]    Wind power is of special interest when considering issues of global warming as a result of burning fossil fuels and the rising costs of commercially-produced electrical power. Many wind turbines rotate at speeds that are not favorable for power generation. As mentioned above, the output an alternator or generator can produce is proportional to its speed. This is not particularly important with large wind turbines, which can use elaborate and heavy gear transmissions to multiply the speed of the blades of the generator to increase efficiency and output. This is not true for 50 kW and smaller wind turbines where space and weight are at a premium. Such turbines are used to generate power in homes, farms, ranch settings, or for small boats. Therefore, it would be desirable to have a method of multiplying the speed of a generator powered by a wind turbine without using heavy and elaborate transmissions. 
         [0014]    Hydro power production is similar with respect to wind power in that it can offer a means of producing electricity without the negative impact of burning fossil fuels. Hydro power production is well known with, for example, Kaplan (Bulb) and Francis turbine designs, which have been in use now for many years. Each of these applications couples the generator input shaft directly to the output shaft of the turbine. In the case of Kaplan applications, the turbine shaft rotates at relatively low speeds (typically 80-400 RPM) with Francis turbine rotating at slightly higher speeds (80-1000 RPM). In both applications, the low shaft RPM of Kaplan and Francis generators (&gt;50 kW), is not as significant a limiter of output as would be encountered with small generators because the larger diameter of the rotor can accommodate more poles. The increased number of poles effectively increases output capability, essentially offsetting the deleterious effects of low RPM. The space to accommodate more poles is not available in smaller generators, therefore it would be desirable to increase generator RPM in small Kaplan and Francis generator applications to maximize output with as little modification to the infrastructure as possible. 
         [0000]    Another class of generators are micro turbines that produce significantly smaller amounts of power (1.5 kW or less) where elaborate structures and earth works are not possible resulting in little or no head (low static water pressure). In these instances turbine speed is limited to the speed of the stream as it passes by the turbine. That speed is generally not conducive for power production, so it would be beneficial to have a method of increasing generator speed under those operating conditions. 
         [0015]    Small aircraft applications such as Unmanned Arial Vehicles (UAV) and Remote Control (RC) aircraft (48-inch wingspan and smaller) can benefit from reduced engine RPM while maintaining propeller speed For example, airborne diesel engines are well known (e.g., Junkers Jumo  204 ,  205 ,  206 ,  207 , and  208  engines deployed on civil and military aircraft beginning in 1932). In UAV applications, a small diesel engine can offer many of the advantages of its automotive counterparts: durability, fuel economy, reliability, and high power at low RPM. The relatively low RPM of a UAV diesel engine reduces output capability of an alternator as well therefore; the ability to increase the speed of a UAV alternator relative to the speed of its diesel engine power plant would be of value. 
       SUMMARY OF THE INVENTION 
       [0016]    The present invention, a compact torque converter (CTC), enhances and improves rotating machine functionality with little or no modification to the rotating machine itself or to surrounding structural components. Improvement can be in form of either an increased or decreased RPM of the rotating machine or increased power delivered to the rotating machine. In one category, the CTC is designed as a separate mechanical system linked and mounted to the rotating machine, such as through belts, pulleys and fasteners. In the second category, the CTC is integrated into the rotating machine to form a single assembly while still enhancing rotating machine functionality. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0017]    The present invention will be described in conjunction with the following figures of the appended drawing. 
           [0018]      FIG. 1A  is a front view of a first embodiment in accordance with the present invention, which includes a cut-away view. 
           [0019]      FIG. 1B  is a sectional view (taken along line A-A in  FIG. 1A ) of the first embodiment of the CTC of  FIG. 1 . 
           [0020]      FIG. 1C  is a sectional view (taken along line B-B in  FIG. 1A ) of the first embodiment of the CTC of  FIG. 1 . 
           [0021]      FIG. 1D  is a rear view of the first embodiment of the CTC of  FIG. 1 . 
           [0022]      FIG. 2A  is a simplified front and side view showing a typical, conventional alternator application. 
           [0023]      FIG. 2B  is a schematic of pulley ratios of the typical application shown in  FIG. 2A . 
           [0024]      FIG. 2C  is a schematic showing pulley ratios of an application, wherein the pulley ratios have been modified to increase the RPM of the rotating machine without the benefit of using a CTC. 
           [0025]      FIG. 2D  is a schematic showing pulley ratios of an alternate application, wherein the pulley ratios have been modified to increase the RPM of the rotating machine without the benefit of using a CTC. 
           [0026]      FIG. 2E  is a schematic showing pulley ratios of an application, wherein the pulley ratios have been modified to increase power to a rotating machine without the benefit of using a CTC. 
           [0027]      FIG. 2F  is a front, side and rear view of the first embodiment of the CTC shown in  FIG. 1 . 
           [0028]      FIG. 2G  is a schematic showing pulley ratios of the first embodiment of a CTC shown in  FIG. 1 , wherein increased RPM of the rotating machine is desirable. 
           [0029]      FIG. 2H  is a schematic showing pulley ratios of the first embodiment of a CTC shown in  FIG. 1 , wherein increased power to the rotating machine is desirable 
           [0030]      FIG. 3A  is a front view of a second embodiment in accordance with the present invention, which includes cut-away views. 
           [0031]      FIG. 3B  is a front view of the second embodiment of the CTC of  FIG. 3A  with pulleys removed for clarity. 
           [0032]      FIG. 3C  is a sectional view (taken along line C-C in  FIG. 3A ) of the second embodiment of the CTC. 
           [0033]      FIG. 3D  is a sectional view (taken along line D-D in  FIG. 3A ) of the second embodiment of the CTC. 
           [0034]      FIG. 3E  is a rear view of the second embodiment of the CTC of  FIG. 3A . 
           [0035]      FIG. 4A  is a front view of a third embodiment in accordance with the present invention, including cut-away views. 
           [0036]      FIG. 4B  is a front view of the third embodiment of the CTC of  FIG. 4A  with pulleys removed for clarity. 
           [0037]      FIG. 4C  is a sectional view (taken along line E-E in  FIG. 4A ) of the third embodiment of the CTC. 
           [0038]      FIG. 4D  is a sectional view (taken along line F-F in  FIG. 4A ) of the third embodiment of the CTC. 
           [0039]      FIG. 4E  is a rear view of the third embodiment of the CTC. 
           [0040]      FIG. 5A  is a front view of a fourth embodiment in accordance with the present invention with cut-away views. 
           [0041]      FIG. 5B  is a front view of the fourth embodiment of the CTC of  FIG. 5A  with pulleys removed for clarity. 
           [0042]      FIG. 5C  is a sectional view (taken along line G-G in  FIG. 5A ) of the fourth embodiment of the CTC. 
           [0043]      FIG. 5D  is a view (bounded by detail line H in  FIG. 5C ) of the fourth embodiment of the CTC. 
           [0044]      FIG. 5E  is a rear view of the fourth embodiment of the CTC. 
           [0045]      FIG. 6A  is a front view of a fifth embodiment in accordance with the present invention with cut-away views. 
           [0046]      FIG. 6B  is a front view of the fifth embodiment of the CTC of  FIG. 6A  with pulleys removed for clarity. 
           [0047]      FIG. 6C  is a side view of the fifth embodiment of the CTC. 
           [0048]      FIG. 6D  is a sectional view (taken along line J-J in  FIG. 6A ) of the fifth embodiment of the CTC. 
           [0049]      FIG. 6E  is a view (bounded by detail line K in  FIG. 6C ) of the fifth embodiment of the CTC. 
           [0050]      FIG. 6F  is a rear view of the fifth embodiment of the CTC. 
           [0051]      FIG. 7A  is a front view of a sixth embodiment in accordance with the present invention with cut-away views. 
           [0052]      FIG. 7B  is a front view of the sixth embodiment of the CTC of  FIG. 7A  with pulleys removed for clarity 
           [0053]      FIG. 7C  is a side view of the sixth embodiment of the CTC. 
           [0054]      FIG. 7D  is a sectional view (taken along line L-L in  FIG. 6A ) of the sixth embodiment of the CTC. 
           [0055]      FIG. 7E  is a view (bounded by detail line M in  FIG. 7C ) of the sixth embodiment of the CTC. 
           [0056]      FIG. 7F  is a rear view of the sixth embodiment of the CTC. 
           [0057]      FIG. 8A  is a front view of a seventh embodiment in accordance with the present invention with cut-away views. 
           [0058]      FIG. 8B  is a front view of the seventh embodiment of the CTC of  FIG. 8A  with pulleys removed for clarity 
           [0059]      FIG. 8C  is a sectional view (taken along line N-N in  FIG. 8A ) of the seventh embodiment of the CTC. 
           [0060]      FIG. 8D  is a sectional view (taken along line P-P in  FIG. 8A ) of the seventh embodiment of the CTC. 
           [0061]      FIG. 8E  is a sectional view (taken along line Q-Q in  FIG. 8A ) of the seventh embodiment of the CTC. 
           [0062]      FIG. 8F  is a rear view of the seventh embodiment of the CTC. 
       
    
    
     DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS 
       [0063]    Referring now to  FIGS. 1A-D , which are collectively referred to as  FIGS. 1 , a first embodiment of a CTC assembly  100  comprises: a single shaft CTC body  102 , a shaft  104  and a pulley  106 . Pulley  106  is fixed to shaft  104  by nut  108  to press pulley  106  onto a shaft surface  110 . Pulley  106  is also fixed to shaft  104  by a key  112 . In certain applications the friction developed between pulley  106  and shaft surface  110  by nut  108  is sufficient to resist the torque developed by pulley  106  to eliminate the need for key  112 . Press fitting or gluing pulley  106  onto shaft  104  can also be employed to fix pulley  106  adequately onto shaft  104 . 
         [0064]    CTC  102  body is preferably die-cast or sand-cast aluminum, such as type A356, but other suitable materials such as magnesium, steel, or engineered plastic such as polyamide-imide can be utilized. Alternatively, CTC  102  body can be machined from a solid billet of aluminum such as type 6061-T651 or other suitable material such as magnesium, steel, engineered plastic, or other appropriate material. 
         [0065]    Shaft  104  is preferably stress-proof steel such as type SAE  1144  or similar steel or other material designed to withstand the stresses and loads that are encountered in high stress rotating shaft applications such as those present in alternators and pumps. But, shaft  104  can also be fabricated from other materials as application requirements allow. Pulleys  106  and  114  preferably are machined from cast steel or other appropriate materials. 
         [0066]    CTC body  102  contains through bore  122 . Bearing bore  124  is preferably bored to a high tolerance (e.g., +0.0001 to +0.0004 inches over nominal diameter) to accept a bearing  126  and is concentric with through bore  122 . Bearing  126  is preferably maintained in bearing bore  124  by circlip  128  seated in groove  130 . Bearing  126  is located on shaft  104  between circlip  132  seated in groove  134  and circlip  136  seated in groove  127 . Surface  138  on shaft  104  between groove  134  and groove  127  is preferably machined to a high tolerance (e.g., +0.0000 to −0.0003) to accept bearing  126  in assembly  100 . 
         [0067]    Shaft surface  140  is machined with sufficient clearance to allow bearing  126  to slip past surface  140  during assembly and seat on surface  138 . Bearing bore  144  is preferably bored to a high tolerance (e.g., +0.0001 to +0.0004 inches over nominal diameter) to accept bearing  146  and is concentric with through bore  122 . Bearing  146  is maintained in bearing bore  144  by circlip  148  seated in groove  150 . Bearing  146  is axially located on shaft  104  between circlip  152  seated in groove  154  and circlip  156  seated in groove  129 . Surface  158  on shaft  104  between groove  154  and groove  129  is preferably machined to a high tolerance (e.g., +0.0000 to −0.0003) to accept bearing  146  in assembly. Shaft surface  160  is machined with sufficient clearance to allow bearing  146  to slip past surface  160  during assembly and seat on surface  158 . 
         [0068]    Bearing bores  124  and  144 , and bearings  126  and  146 , cooperate to align shaft  104  with through bore  122 . Bearing  126 , circlips  128  and  132  and  136 , bearing  146 , circlips  148 ,  152  and  156 , cooperate to fix shaft  104  in CTC assembly  100 . Nut  108  and surface  110  fix pulley  106  on shaft  104 . Key  112  also fixes pulley  106  on shaft  104 . Nut  116  and surface  118  fix pulley  114  on shaft  104 . Key  120  also fixes pulley  114  on shaft  104 . 
         [0069]    Power is transmitted to pulley  106  from a pulley mounted to a power source (not shown) through belt  162 . Belt  162  in this embodiment is preferably a poly-v belt but can be a roller chain, v-belt, rope, or any other device suitable for transmitting power to pulley  106 . Pulley  106  transmits power from belt  162  to rotating machine  164  through shaft  104 , pulley  114 , and belt  172  then to pulley  168  of rotating machine  164 . Pulley  168  is fixed to shaft  166  by nut  170  and imparts rotation to shaft  166  which in turn rotates internal components (not shown) of rotating machine  164 , which produces an output. The output of rotating machine  164  can be electrical power, gas compression, fluid flow or any output generated by a rotating machine. Belt  162  is preferably a poly-v belt but can be a roller chain, v-belt, rope, or any other device suitable for transmitting power to pulley  106 . 
         [0070]    For example, in automotive applications the power source is typically an internal combustion engine and the power is transmitted from a crank pulley (not shown), which is fixed to the crankshaft (not shown) of the engine (not shown) to pulley  106 . 
         [0071]    In industrial applications, the power source can be an electric motor, hydraulic motor, pneumatic motor, any suitable power source. The power source is mounted with a pulley on the main shaft to transmit power. Power take offs (PTOs) or other types of engine transmission auxiliary drive shafts can be equipped with pulleys to drive the rotating machine. Belt  172  is preferably a synchronous or ‘cogged timing’ belt but can be equally effective using a roller chain, v-belt, poly-v belt, rope, or any other device suitable for transmitting power from pulley  114  to pulley  168 . Synchronous belts are well known for their capability to transmit large amounts of power relative to their cross sectional areas and ability to resist slippage. 
         [0072]    Mounting ears  174  of rotating machine  164  have holes  176  that are sized to accept threaded slip bushings  178  and align with through holes  180  of mounting ears  182  of CTC body  102 . Mounting ears  184  of rotating machine  164  have clearance holes  186  that accept bolts  188  and align with through holes  180  of mounting ears  182  of CTC body  102 . Bolts  188  are inserted through holes  180  and  186  and thread into slip bushing  178 . When tightened, bolts  188  draw threaded slip bushings  178  against surface  190  of mounting ears  182  of CTC body  102  which in turn draws surface  192  of mounting ear  184  of rotating machine  164  against surface  194  of mounting ears  180  of CTC body  102 . Holes  176 ,  180 , and  186  in cooperation with bolts  188  and threaded slip bushings  178  fix rotating machine  164  to CTC body  102 . 
         [0073]    Mounting ears  196  of CTC body  102  have holes  198  that are sized to accept slip bushings  101  and align with through holes  103  in mounting ears  105  of bracket  107 . Mounting ears  109  of CTC body  102  have holes  111  that are sized to accept bolts  113  and align with through holes  103  in mounting ears  105  of bracket  107 . Bolts  113  are inserted through holes  103  and  111  and thread into slip bushings  101 . When tightened, bolts  113  draw threaded slip bushings  101  against surface  115  of CTC body  102  mounting ears  196  which in turn draws surface  117  of mounting ears  109  of CTC body  102  against surface  119  of mounting ears  105  of bracket  107 . Holes  198 ,  103 , and  111 , in cooperation with bolts  113  and slip bushings  101 , fix CTC body  102  to bracket  107 . Bracket  107  is fixed to mounting surface  121  with bolts  123  that align with tap holes  125  in mounting surface  121 . 
         [0074]    In automotive applications, mounting surface  121  could be the surface of the combustion engine itself. This is typically the case in automotive applications where the rotating machine, in this example an alternator, would use a bracket ( 107 ) to mount the alternator (rotating machine  164 ) to the engine. In applications where bracket  107  is relatively simple, the CTC can be designed to mount directly to surface  121  thereby eliminating the need for bracket  107 . However, many automobile applications have complex bracket assemblies that mount many accessories. In these instances replacing the complex bracket becomes cost prohibitive and the ability to mount the CTC to the existing bracket is advantageous. In industrial applications, the mounting surface can be the floor, a support structure, or other piece of industrial equipment associated with the rotating machine. 
         [0075]    Referring now to  FIGS. 2A-2H  collectively referred to as  FIG. 2 , for rotating machine applications such as alternators, pumps, and compressors, it would be advantageous to have the capability of increasing or decreasing the RPM of the rotating machine with as little alteration to the existing equipment as possible. Equally beneficial would be the ability to increase the amount of power (torque×RPM) delivered to the rotating machine, again with as little alteration to the existing equipment as possible. 
         [0076]    In this embodiment, the rotating machine is an alternator wherein output is directly proportional to the RPM of the alternator, i.e., the higher the RPM the higher the output. Utilizing a large diesel engine for the purpose of this example, a typical alternator output at engine idle (700 RPM) may be expected to be approximately 40 amps and approximately 200 amps at the highest suggested RPM (2400 RPM redline) of the diesel engine. By simply using the original alternator and increasing its RPM across the entire RPM range ( 700  to  2400 ), an increase in output would be realized. There are of course other considerations such as diode and bearing capability to be accounted for but in general, an increase in rotating machine RPM would yield a net increase in output. This is generally true for pumps, compressors, and other rotating machines as well. 
         [0077]    Belt wrap and belt contact (arc length) depicted in  FIGS. 2B ,  2 C and  2 D are not meant to describe an absolute or fixed set of variables, but rather are used as a means to compare relative belt wrap and belt contact and the effect modification has on these variables. Actual application conditions and equipment geometries will vary from application to application. 
         [0078]      FIG. 2A  depicts a typical automotive configuration (front and side view), wherein the rotating machine  201  is mounted to a bracket  203 . Pulley  204  of the rotating machine is driven by serpentine belt  206  wrapped over pulley  204  driven in turn by crank pulley  202  (not shown in  FIG. 2A ). 
         [0079]      FIG. 2B  depicts pulley ratios of the device of  FIG. 2A . Drive (crank) pulley  202  of the diesel engine (not shown) has a diameter of 7.50″ in this embodiment and pulley  204  of the alternator (i.e., the rotating machine, not shown) has a diameter of 3.00″. Belt  206  transmits power from drive pulley  202  to rotating machine pulley  204 . The pulley ratio of drive pulley  202  to rotating machine pulley  204  is 7.50″:3.00″ or 2.5:1. At a ratio of 2.5:1, pulley  204  rotates at 1750 RPM when drive pulley  202  rotates at 700 RPM and 6000 RPM when drive pulley  202  is rotating at 2400 RPM. The belt wrap angle in this configuration is 147° with a belt contact arc length of 3.86″. 
         [0080]    To increase the RPM of the alternator without the benefit of a CTC, one of two options are available. In the first option, crank pulley diameter is increased; in the second, the diameter of rotating machine pulley is decreased. Each of these methods will increase the rotating machine RPM by increasing pulley ratios but also will introduce problems, as discussed previously. 
         [0081]      FIGS. 2C and 2D  depict two options to increase alternator RPM without the benefit of a CTC. 
         [0082]    In  FIG. 2C , the first method of increasing RPM of the rotating machine is shown. The diameter of the drive (crank) pulley  212  is increased to 10.5″ while leaving the rotating machine (alternator) pulley  204  unchanged at 3.00″. Belt  214  would be longer than belt  206  to accommodate the increased diameter of pulley  212 . As can be seen, the resulting ratio increases to 10.50″:3.00″ or 3.5:1 over the 2.5:1 depicted in  FIG. 2B . The belt wrap angle of 147° and belt contact arc length of 3.86″ remain unchanged. 
         [0083]    This approach would increase the RPM of the rotating machine by increasing the pulley ratio to 3.5:1. At a ratio of 3.5:1, the rotating machine pulley  204  rotates at 2450 RPM when drive pulley  212  rotates at 700 RPM and 8400 RPM when drive pulley rotates at 2400 RPM. Although an increase in rotating machine RPM is achieved, in most instances this configuration would prove impractical since modification of the drive pulley could involve a major design changes to the entire system. For example, the crank pulley of a diesel engine is balanced to cooperate with the firing sequence and rotational inertia of the engine; thus, any change to the crank pulley would require considerable engineering changes to assure proper operation of the diesel engine. The increased space required to accommodate the larger crank pulley would also prove problematic. 
         [0084]    In  FIG. 2D  the second method of increasing rotating machine RPM is shown. In this embodiment, the diameter of rotating machine pulley  216  is decreased to 2.14″ while leaving the drive pulley  202  unchanged at 7.50″. Belt  218  will be shorter than belt  206  to accommodate the decrease in diameter of pulley  216 . As can be seen, the resulting ratio increases to 7.50″:2.14″ or 3.5:1 over the 2.5:1 depicted in  FIG. 2B . Rotating machine pulley  216  rotates at 2450 RPM when drive pulley  202  rotates at 700 RPM and 8400 RPM when drive pulley  202  rotates at 2400 RPM. The belt wrap angle decreases from 147° to 136° and belt contact arc length decreases from 3.86″ to 2.55″. This approach would increase the RPM of the rotating machine but could introduce belt slippage since the amount of power that can be transmitted by belt  218  to pulley  216  is a function of belt wrap angle and the length of belt contact with the pulley. Both belt wrap and contact length are decreased using this approach. There are of course other factors that impact the amount of power that can be transmitted by the belt, but the belt wrap angle and the length of belt contact (arc length) with the pulley have the greatest impact on a belt&#39;s ability to transmit power. Belt contact length could be more accurately described as belt contact area, in which both length of contact and belt width (number of groves in a poly-v belt for example) are considered. 
         [0085]    One method of increasing power to the rotating machine is to increase the width of the belt used in transmitting power which effectively increases belt contact area. For example, changing the original 4 groove poly-v belt for 6 or 8 groove poly-v belts would increase power capability by increasing the total belt surface area in contact with the pulley, but can introduce redesign challenges. For any given automotive application, belt type is typically predetermined (e.g., a 4-groove poly-v belt) by the manufacturer. Once a belt width has been selected, the remaining available space is occupied by other engine components. This means that increasing belt width may not be a viable option for many applications. 
         [0086]    A second method of increasing power capability is to increase belt wrap angle through the use of idler pulleys. The amount of power that can be transmitted as it relates to belt wrap is not a simple linear relationship but is more akin to an exponential relationship Therefore, increasing belt wrap can be beneficial for increasing the torque and power through the belt, but is not practical in all applications since the available space to locate idler pulleys is limited. 
         [0087]    A last method that will be discussed to increase power capability without using a CTC is to increase the diameter of the rotating machine pulley, which is depicted in  FIG. 2E . Increasing pulley diameter increases belt contact arc length and to a lesser extent increases belt wrap angle which improves power transmission capability. 
         [0088]    In  FIG. 2E  the diameter of rotating machine (alternator) pulley  228  is increased to 4.00″ while leaving the drive pulley  202  unchanged at 7.50″. Belt  230  will be longer than belt  206  to accommodate the increase in diameter of pulley  228 . The pulley ratio in  FIG. 2E  decreases from 2.5:1 depicted in  FIG. 2A  to 7.50″:4.00″ or 1.88:1 and at that ratio, pulley  228  rotates at 1312 RPM when drive pulley  202  rotates at 700 RPM and 4500 RPM when drive pulley  202  rotates at 2400 RPM. Although power capability is increased, the resulting decrease in RPM may not produce acceptable output (e.g., in the case when the rotating machine is an alternator) due to the decrease in overall RPM of the rotating machine. 
         [0089]    The use of CTCs can provide both increased RPM and ability to manage concomitant increased power management requirements to rotating machines.  FIG. 2F  depicts a typical CTC configuration where CTC  200  is mounted to bracket  203  with rotating machine  201  mounted to CTC  200 . Pulley  204  is fixed to CTC shaft  222  and is driven by serpentine belt  206  wrapped over pulley  204  which in turn is driven by engine crank pulley  202  (not shown). As described in the first preferred embodiment of the present invention, pulley  220  is also fixed to shaft  222  and rotates in unison with pulley  204 . Pulley  224  of rotating machine  201  is linked to pulley  220  with belt  226 . Power is transmitted to pulley  204 , which, being fixed to shaft  222 , transmits power via shaft  222  to pulley  220  which transmits power to pulley  224  of rotating machine  201  through belt  226 .  FIGS. 2F and 2G  illustrate how a CTC can increase rotating machine RPM or increase power capability with little or no alteration to existing equipment. 
         [0090]    Belt wrap and belt contact (arc length) depicted in the schematics of  FIGS. 2G and 2H  are not meant to describe an absolute or fixed set of variables, but rather are used to compare relative belt wrap and belt contact and the effect modification has on the aforementioned variables. Actual application conditions and equipment geometries will have varying effects on belt wrap and belt contact and vary greatly from application to application creating wide variation in those values. When using a CTC, pulley  204  may drop slightly in elevation as compared to that depicted in  FIGS. 2B and 2C . The effect on belt wrap and belt contact is such case is negligible. 
         [0091]    Referring now to  FIG. 2G , the use of CTC  200  can produce increased RPM at the rotating machine (alternator, not shown) while reducing possible belt slippage. In this configuration, pulley  202  has a diameter of 7.50″. CTC  200  comprises pulleys  204  and  220  each with a diameter of 3.00″ and shaft  222 . Both pulley  204  and  220  are fixed to shaft  222  and rotate in unison. Pulley  224  of rotating machine  201  has a diameter 2.14″ and is driven by pulley  220  through synchronous belt  226 . The pulley ratio between pulley  202  and pulley  204  is 7.50″:3.00″ or 2.5:1 and the pulley ratio between pulleys  220  and  224  is 3.00″:2.14″ or 1.40:1, for a combined pulley ratio of 3.5:1 between pulleys  204  and  224 . 
         [0092]    At an overall ratio of 3.5:1, the rotating machine (alternator) pulley  224  rotates at 2450 RPM when drive pulley  202  rotates at 700 RPM and 8400 RPM when drive pulley  202  rotates at 2400 RPM. This increase in RPM matches those depicted in  FIGS. 2C and 2D , but without the adverse effects as a consequence of either increasing drive pulley diameter or decreasing rotating machine pulley diameter. Since the original belt wrap angle of 147° and belt contact arc length of 3.86″ are maintained, power capability at pulley  204  is also maintained. More importantly, belt  226  is a synchronous (cogged) belt further reducing the possibility of belt slippage at rotating machine pulley  224 . 
         [0093]    Referring now to  FIG. 2H , the use of CTC  200  can increase overall power capability without decreasing rotating machine (alternator) RPM as depicted in  FIG. 2E . In this configuration, drive pulley  202  diameter remains at 7.50″. CTC  200  comprises pulley  228  which has a diameter 4.00″ to increase power capability, pulley  232  which has a diameter of 3.0″ and shaft  222 . Pulleys  228  and  232  are fixed to shaft  222  and rotate in unison. Rotating machine pulley  234  has a diameter 2.25″ and is driven by pulley  232  through synchronous belt  236 . Combining pulley ratios of 7.50″:4.00″ or 1.88:1 between pulley  202  and pulley  228  and ratio 3.00″:2.25″ or 1.33:1 between pulleys  232  and  234  produces an overall ratio of 2.5:1 between pulleys  202  and  234 . The overall ratio of 2.5:1 matches that depicted in  FIG. 2A , but more importantly, power capability is significantly enhanced with the increase in belt wrap angle and belt contact arc length at pulley  228 . Equally important, belt  236  is a synchronous belt reducing possible slippage at pulley  236 . 
         [0094]    A CTC according to the invention is not limited to solely altering RPM or increasing power, but can simultaneously do both. The unlimited number of pulley ratios and belt combinations make it possible to deliver any number of RPM and power combinations to rotating machines. 
         [0095]    Referring now to  FIGS. 3A-3E , which are collectively referred to as  FIG. 3 , a second embodiment of a CTC assembly  300  comprises a twin shaft CTC body  302 , a first shaft  304   a , and pulley  306   a , which is fixed to shaft  304   a  by nut  308   a  pressing pulley  306   a  onto shaft surface  310   a . Pulley  306   a  is fixed to shaft  304   a  by key  312   a . In certain applications the friction developed between pulley  306   a  and shaft surface  310   a  by nut  308   a  is sufficient to eliminate the need for key  312   a . Press fitting or gluing pulley  306   a  onto shaft  304   a  can also be employed to fix pulley  306   a  adequately onto shaft  304   a . Pulley  314   a  is maintained on shaft  304   a  by nut  316   a  compressing pulley  314   a  onto shaft surface  318   a . Pulley  314   a  is fixed to shaft  304   a  by key  320   a . In certain applications the friction developed between pulley  314   a  and shaft surface  318   a  by nut  316   a  is sufficient to eliminate the need for key  320   a . Press fitting or gluing pulley  314   a  onto shaft  304   a  can also be employed to fix pulley  306   a  adequately onto shaft  304   a.    
         [0096]    CTC  300  also comprises second shaft  304   b , and pulley  306   b , which is fixed to shaft  304   b  by nut  308   b  pressing pulley  306   b  onto shaft surface  310   b . Pulley  306   b  is fixed to shaft  304   b  by key  312   b . In certain applications the friction developed between pulley  306   b  and shaft surface  310   b  by nut  308   b  is sufficient to eliminate the need for key  312   b . Press fitting or gluing pulley  306   b  onto shaft  304   b  can also be employed to fix pulley  306   b  adequately onto shaft  304   b . Pulley  314   b  is maintained on shaft  304   b  by nut  316   b  pressing pulley  314   b  onto shaft surface  318   b . Pulley  314   b  is fixed to shaft  304   b  by key  320   b . In certain applications the friction developed between pulley  314   b  and shaft surface  318   b  by nut  316   b  is sufficient to eliminate the need for key  320   b . Press fitting or gluing pulley  314   b  onto shaft  304   b  can also be employed to fix pulley  306   b  adequately onto shaft  304   b.    
         [0097]    CTC body  302  is preferably a die-cast or sand-cast aluminum such A356, but other suitable materials, including casting materials such as magnesium, steel, or engineered plastic such as polyamide-imide may be used. Alternatively, CTC body can be machined from a solid billet of aluminum such as type 6061-T651 or other suitable material such as magnesium, steel, engineered plastic, or other appropriate material. Shafts  304   a  and  304   b  are preferably a stress proof steel such as SAE  1144  or similar steel designed to withstand the stresses and loads that are encountered in rotating shaft applications such as alternators and pumps but can be fabricated from other materials as application requirements allow. Pulleys can be cast or machined from appropriate materials such as steel or other appropriate material. 
         [0098]    Twin shaft body  302   a  contains through bore  322   a . Bearing bore  324   a  is preferably bored to a high tolerance (e.g., +0.0001 to +0.0004 inches over nominal diameter) to accept bearing  326   a  and is concentric with through bore  322   a . Bearing  326   a  is maintained in bearing bore  324   a  by circlip  328   a  seated in groove  330   a . Bearing  326   a  is located on shaft  304   a  between circlip  332   a  seated in groove  334   a  and shaft surface  336   a . Surface  338   a  on shaft  304   a  between groove  334   a  and surface  336   a  is preferably machined to a high tolerance (e.g., +0.0000 to −0.0003) to accept bearing  326   a  in assembly. Shaft surface  340   a  is machined with sufficient clearance to allow bearing  326   a  to slip past surface  340   a  during assembly and seat on surface  338   a . Bearing bore  344   a  is preferably bored to a high tolerance (e.g., +0.0001 to +0.0004 inches over nominal diameter) to accept bearing  346   a  and is concentric with through bore  322   a . Bearing  346   a  is maintained in bearing bore  344   a  by circlip  348   a  seated in groove  350   a . Bearing  346   a  is axially located on shaft  304   a  between circlip  352   a  seated in groove  354   a  and shaft surface  356   a . Surface  358   a  on shaft  304   a  between groove  354   a  and surface  356   a  is machined to a high tolerance (e.g., +0.0000 to −0.0003) to accept bearing  346   a  in assembly. Shaft surface  360   a  is machined with sufficient clearance to allow bearing  346   a  to slip past surface  360   a  during assembly and seat on surface  358   a.    
         [0099]    Through bore  322   a , bearing bores  324   a  and  344   a , and bearings  326   a  and  346   a  cooperate to align shaft  304   a  with through bore  322   a . Bearing  326   a , circlips  328   a  and  332   a , surface  336   a , bearing  346   a , circlips  348   a  and  352   a , surface  356   a  cooperate to fix shaft  304   a  in CTC assembly  300   a . Nut  308   a  and surface  310   a  fix pulley  306   a  on shaft  304   a . Key  312   a  radially fixes pulley  306   a  on shaft  304   a . Nut  316   a  and surface  318   a  fix pulley  314   a  on shaft  304   a . Key  320   a  fixes pulley  314   a  on shaft  304   a.    
         [0100]    The pulleys, shafts and methods in which they are fixed within CTC bodies and as will be described, CTC-RM assemblies, are not limited to any particular CTC application and any of the shafts described can be used in any CTC application. 
         [0101]    CTC body  302  also contains through bore  322   b . Bearing bore  324   b  is preferably bored to a high tolerance (e.g., +0.0001 to +0.0004 inches over nominal diameter) to accept bearing  326   b  and is concentric with through bore  322   b . Bearing  326   b  is maintained in bearing bore  324   b  by circlip  328   b  seated in groove  330   b . Bearing  326   b  is located on shaft  304   b  between circlip  332   b  seated in groove  334   b  and shaft surface  336   b . Surface  338   b  on shaft  304   b  between groove  334   b  and surface  336   b  is preferably machined to a high tolerance (e.g., +0.0000 to −0.0003) to accept bearing  326   b  in assembly  300 . Shaft surface  340   b  is preferably machined with sufficient clearance to allow bearing  326   b  to slip past surface  340   b  during assembly and seat on surface  338   b . Bearing bore  344   b  is preferably bored to a high tolerance (e.g., +0.0001 to +0.0004 inches over nominal diameter) to accept bearing  346   b  and is concentric with through bore  322   b . Bearing  346   b  is maintained in bearing bore  344   b  by circlip  348   b  seated in groove  350   b . Bearing  346   b  is located on shaft  304   b  between circlip  352   b  seated in groove  354   b  and shaft surface  356   b . Surface  358   b  on shaft  304   b  between groove  354   b  and surface  356   b  is preferably machined to a high tolerance (e.g., +0.0000 to −0.0003) to accept bearing  346   b  in assembly  300 . Shaft surface  360   b  is machined with sufficient clearance to allow bearing  346   b  to slip past surface  360   b  during assembly and seat on surface  358   b.    
         [0102]    Through bore  322   b , bearing bores  324   b  and  344   b , and bearings  326   b  and  346   b  cooperate to align shaft  304   b  with through bore  322   b . Bearing  326   b , circlips  328   b  and  332   b , surface  336   b , bearing  346   b , circlips  348   b  and  352   b , surface  356   b  cooperate to fix shaft  304   b  in CTC assembly  300   b . Nut  308   b  and surface  310   b  fix pulley  306   b  on shaft  304   b . Key  312   b  fixes pulley  306   b  on shaft  304   b . Nut  316   b  and surface  318   b  fix pulley  314   b  on shaft  304   b . Key  320   b  fixes pulley  314   b  on shaft  304   b.    
         [0103]    Back side (smooth) idler pulley  363  is located on mounting ear  365  of CTC body  302  by bolt  369  inserted through idler pulley  363  threaded into tapped hole  367 . The axis of tapped hole  367  is parallel to both axis of shafts  304   a  and  304   b  and located below the plane formed by the axis of shafts  304  and  305  on a vertical line mid way between shafts  304   a  and  304   b . The location of tapped hole  367  is best seen in  FIG. 3B . Pulleys  363 ,  306   a  and  306   b  are located to form a serpentine path for belt  371  that increases belt wrap angle and belt contact arc length over pulleys  306   a  and  306   b . During operation belt  371  transmits power to both pulley  306   a  and  306   b  simultaneously as belt  371  travels over pulley  306   a , across idler pulley  363 , over pulley  306   b  then returning back to the engine drive pulley (not shown). Although it is advantageous to have idler pulley  363  mounted to CTC body  302 , an idler pulley can be located remotely from CTC body  302  to replicate belt wrap around pulleys  306   a  and  306   b  afforded by mounting idler pulley  363  on CTC body  302 . 
         [0104]    Belt  371  in this embodiment is preferably a poly-v belt but that v belts designed to work with backside idlers may be used as well as roller chains, rope, or any other device suitable for transmitting power to pulley  306   a  and  306   b.    
         [0105]    Pulley  306   a  transmits power from belt  371 , through shaft  304   a , to pulley  314   a  then to belt  381 . Pulley  306   b  transmits power from belt  371 , through shaft  304   b , to pulley  314   b  then to belt  381 . Pulleys  314   a  and  314   b  simultaneously transmit power to pulley  381 . Belt  381  in turn drives pulley  377  of rotating machine  373 . Pulley  377  being fixed to shaft  375  by nut  379  imparts rotation to shaft  375 , which in turn rotates the internal components (not shown) of the rotating machine  373  thereby producing output. Output by rotating machine  373  can be electrical power, gas compression, fluid flow or any output generated by rotating machines. 
         [0106]    In industrial applications, the power source can be an electric motor, hydraulic motor, or pneumatic motor mounted with a pulley on the main shaft to transmit power. The use of power take offs (PTO) or other types of engine transmission auxiliary drive shafts can be equipped with pulleys to drive the rotating machine. Belt  381  in this preferred embodiment is a synchronous or ‘cogged timing’ belt. The use of synchronous belts is well known for their capability to transmit large amounts of power relative to their cross sectional area and ability to resist slippage. Although belt  381  in the preferred embodiment is a synchronous belt it can be effective using a roller chain, v-belt, poly-v belt, rope, or any other device suitable in transferring power from pulley  314   a  and  314   b  to pulley  377 . 
         [0107]    Mounting ears  362  of rotating machine  373  have holes  364  that are sized to accept threaded slip bushings  366  and align with through holes  368  of mounting ear  370  of CTC body  302 . Mounting ears  372  of rotating machine  373  have clearance holes  374  that accept bolts  376  and align with through holes  368  of mounting ear  370  of CTC body  302 . Bolts  376  are inserted through holes  368  and  374  and thread into slip bushing  366 . When tightened, bolts  376  draw threaded slip bushings  366  against surface  378  of mounting ears  370  of CTC body  302  which in turn draws surface  380  of mounting ear  372  of rotating machine  373  against surface  382  of mounting ear  370  of CTC body  302 . Holes  364 ,  368 , and  374  in cooperation with bolts  376  and threaded slip bushings  366 , fix rotating machine  373  to CTC body  302 . 
         [0108]    Mounting ears  384  of CTC body  302  have holes  386  that are sized to accept slip bushings  388  and align with through holes  390  in mounting ears  392  of bracket  394 . Mounting ears  396  of CTC body  302  have holes  398  that are sized to accept bolts  383  and align with through holes  390  in mounting ears  392  of bracket  394 . Bolts  383  are inserted through holes  390  and  398  and threaded into slip bushings  388 . When tightened, bolts  383  draw threaded slip bushings  388  against surface  385  of mounting ears  392  which in turn draws surface  387  of mounting ears  396  against surface  389  of mounting ears  392  of bracket  394 . Holes  386 ,  390 , and  398  in cooperation with bolts  383  and slip bushings  388 , fix CTC body  302  to bracket  394 . Bracket  394  is fixed to mounting surface  391  with bolts  393  that align with tap holes  395  in mounting surface  391 . 
         [0109]    In automotive applications as for all of the CTCs according to the invention, mounting surface  391  would be the surface of the combustion engine itself. This is typically the case in automotive applications wherein the rotating machine, in this example an alternator, would use a bracket ( 394 ) to mount the alternator (rotating machine  373 ) to the engine. In applications where bracket  394  is relatively simple, the CTC can be designed to mount directly to the engine using tapped holes  395  thereby eliminating the need for bracket  394 . However, the many automobile applications have complex bracket assemblies that mount many accessories. In these instances, replacing the complex bracket becomes cost prohibitive, so the ability to mount to the existing mounting features of the bracket is preferred. As with other CTCs according to the invention, in industrial applications, the mounting surface can be the floor, a support structure, or other piece of industrial equipment associated with the rotating machine. 
         [0110]    Referring now to  FIGS. 4A-4E , collectively referred to as  FIG. 4 , a third embodiment of a CTC assembly  400  comprises CTC body  402 , a shaft  404 , and pulley  406  which is fixed to shaft  404  by nut  408  pressing pulley  406  onto shaft surface  410 . Pulley  406  is fixed to shaft  404  by key  412 . In certain applications, the friction developed between pulley  406  and shaft surface  410  by nut  408  is sufficient to resist the torque being developed eliminating the need for key  412 . Press fitting or gluing pulley  406  onto shaft  404  can also be employed to fix pulley  406  adequately onto shaft  404 . Pulley  414  is maintained on shaft  404  by nut  416  pressing pulley  414  onto shaft surface  418 . Pulley  414  is also fixed to shaft  404  by key  420 . In certain applications the friction developed between pulley  414  and shaft surface  418  by nut  416  is sufficient to eliminate the need for key  420 . Press fitting or gluing pulley  414  onto shaft  404  can also be employed to fix pulley  406  adequately onto shaft  404 . 
         [0111]    CTC body  402  shaft  404  and the pulleys used in this embodiment can be made of the same materials as for previously described CTC assembly  300 . 
         [0112]    CTC body  402  contains through bore  422 . Bearing bore  424  is preferably bored to a high tolerance (e.g., +0.0001 to +0.0004 inches over nominal diameter) to accept bearing  426  and is concentric with through bore  422 . Bearing  426  is maintained in bearing bore  424  by circlip  428  seated in groove  430 . Bearing  426  is located on shaft  404  between pulley surface  432  of pulley  406  and shaft surface  436  of shaft  404 . In assembly  400  pulley surface  432  and shaft surface  410  are coplanar. Surface  438  on shaft  404  between shaft surface  410  and shaft surface  436  is preferably machined to a high tolerance (e.g., +0.0000 to −0.0003) to accept bearing  426  in assembly  400 . CTC body  402  also contains bearing bore  444  which is preferably bored to a high tolerance (e.g., +0.0001 to +0.0004 inches over nominal diameter) to accept bearing  446  and is also concentric with through bore  422 . Bearing  446  is maintained in bearing bore  444  by circlip  448  seated in groove  450 . Bearing  446  is located on shaft  404  between pulley surface  452  of pulley  414  and shaft surface  456 . In assembly  400  pulley surface  452  and shaft surface  456  are coplanar. Surface  458  on shaft  404  between pulley surface  452  and shaft surface  456  is preferably machined to a high tolerance (e.g., +0.0000 to −0.0003) to accept bearing  446  in assembly  400 . 
         [0113]    Bearing bores  424  and  444 , bearings  426  and  446  cooperate to align shaft  404  in through bore  422 . Bearing  426 , pulley surface  432 , shaft surface  436 , bearing  446 , pulley surface  452 , and shaft surface  456  cooperate to fix shaft  404  in CTC body assembly  402 . Nut  408  and surface  410  cooperate to fix pulley  406  on shaft  404 . Key  412  also fixes pulley  406  on shaft  404 . Nut  416  and surface  418  cooperate to fix pulley  414  on shaft  404 . Key  420  also fixes pulley  414  on shaft  404 . 
         [0114]    Back side (smooth) idler pulley  462  is located on mounting ear  464  of CTC body  402  by bolt  468  inserted through pulley  462  and threaded into tapped hole  466 . The axis of tapped hole  466  is parallel to the axis formed by shaft  404  and located below and to the right of the shaft  404  axis. Poly-v (grooved) idler pulley  470  is located on mounting ear  464  of CTC body  402  by bolt  476  inserted through idler pulley  470  threaded into tapped hole  474 . The axis of tapped hole  474  is on the same horizontal plane formed by the shaft  404  axis and is located above and to the right of the axis of tapped hole  466 . Idler pulleys  462  and  470  are located to form a serpentine path for belt  478  that increases belt wrap over pulley  406 . Belt  478  is preferably a poly-v belt but vbelts designed to work with backside idler pulleys can be utilized as well as rope, or any other device suitable in transmitting power to pulley  406   
         [0115]    Although mounting ear  464  is designed to accept idler pulleys  462  and  470 , idler pulleys can alternatively be located remotely from CTC body  402  to replicate similar belt wrap around pulley  406 . 
         [0116]    During operation belt  478  transmits power to pulley  406  as belt  478  travels over pulley  406 , across idler pulley  462 , over idler pulley  470  then returning back to the engine crank pulley (not shown). Belt  478  is preferably a poly-v belt but other belts designed to work with backside idlers may be used as well as roller chains, rope, or any other device suitable in transmitting power to pulley  406 . 
         [0117]    Pulley  406  transmits power from belt  478  to rotating machine  480  through shaft  404 , pulley  414 , belt  488  then to pulley  484  of rotating machine  480 . Pulley  484  being fixed to shaft  482  by nut  486  imparts rotation to shaft  482  of rotating machine  480 , which in turn rotates internal components (not shown) of rotating machine  480  producing output. Output by rotating machine  480  can be electrical power, gas compression, fluid flow or any output generated by rotating machines. Belt  488  is preferably a synchronous or ‘cogged timing’ belt. The use of synchronous belts is well known for applications where their capability to transmit large amounts of power relative to their cross sectional areas are advantageous. Although belt  488  in the preferred embodiment is a synchronous belt it can use a roller chain, v-belt, poly-v belt, rope, or any other device suitable in transferring power from pulley  414  to pulley  484 . 
         [0118]    The power source can be any of those described previously for CTC assembly  300 . 
         [0119]    Mounting ears  490  of rotating machine  480  have holes  492  that are sized to accept threaded slip bushings  494  and align with through holes  496  of mounting ear  498  of CTC body  402 . Mounting ears  401  of rotating machine  480  have clearance holes  403  that accept bolts  405  and align with through holes  496  of mounting ear  498  of CTC body  402 . Bolts  405  are inserted through holes  496  and  403  and threaded into slip bushing  494 . When tightened, bolts  405  draw threaded slip bushings  494  against surface  407  of mounting ears  498  of CTC body  402  which in turn draws surface  409  of mounting ear  401  of rotating machine  480  against surface  411  of mounting ears  498  of CTC body  402 . Holes  492 ,  496 , and  403 , in cooperation with bolts  405  and threaded slip bushings  494 , fix rotating machine  480  to CTC body  402 . 
         [0120]    Mounting ears  413  of CTC body  402  have holes  415  that are sized to accept slip bushings  417  and align with through holes  419  in mounting ears  421  of bracket  423 . Mounting ears  425  of CTC body  402  have holes  427  that are sized to accept bolts  429  and align with through holes  419  in mounting ears  421  of bracket  423 . Bolts  429  are inserted through holes  419  and  427  and thread into slip bushings  417 . When tightened, bolts  429  draw threaded slip bushings  417  against surface  431  of mounting ears  413  of CTC body  402 , which in turn draws surface  433  of mounting ears  425  against surface  435  of mounting ears  421  of bracket  423 . Holes  415 ,  419 , and  427 , in cooperation with bolts  429  and slip bushings  417 , fix CTC body  402  to bracket  423 . Bracket  423  is fixed to mounting surface  437  with bolts  439  that align and thread into tap holes  441  in mounting surface  437 . 
         [0121]    In automotive applications the power source is typically an internal combustion engine and the power is transmitted from a crank pulley (not shown) which is fixed to the crank shaft (not shown) of the engine (not shown) to pulley  506 . In industrial applications, the power source can be an electric motor, hydraulic motor, or pneumatic motor mounted with a pulley on the main shaft to transmit power. The use of Power take offs (PTO) or other types of engine transmission auxiliary drive shafts can be equipped with pulleys to drive the rotating machine. 
         [0122]    The embodiments depicted in  FIGS. 1 ,  3  and  4  describe the CTC and rotating machine (RM) operating as two distinct assemblies joined together and aligned with appropriate hardware. Those embodiments enhance an existing rotating machine, which is particularly advantageous if the existing rotating machine cannot be replaced, or it is not desirable to be replaced, but an increased torque and/or RPM can be attained by integrating the CTC with the rotating machine (RM). 
         [0123]    Referring now to  FIGS. 5A-5E , a fourth embodiment of a CTC that integrates the CTC components with a rotating machine to produce a single CTC-RM assembly  500  is shown. Although the CTC has been integrated into a single assembly  500 , the assembly  500  still has two distinct sections: (1) an RM section, which in this embodiment is depicted as an alternator, but could also be a pump, compressor, or any other rotating machine producing output through rotation, and (2) a CTC section which enhances the functionality of the rotating machine. 
         [0124]    CTC assembly  500  comprises end bell  502 , end bell  503 , and stator  505  maintained and aligned between end bells  502  and  503  with socket head caps screws  507  and nuts  509 . The CTC portion of CTC-RM  500  comprises a shaft  504  and pulley  506 , which is fixed to shaft  504  by nut  508  pressing pulley  506  onto shaft surface  510 . Pulley  506  is also fixed to shaft  504  by key  512 . In certain applications the friction developed between pulley  506  and shaft surface  510  by nut  508  is sufficient to resist the torque being developed eliminating the need for key  512 . Press fitting or gluing pulley  506  onto shaft  504  can also be employed to fix pulley  506  adequately onto shaft  504 . Pulley  514  is maintained on shaft  504  by nut  516  pressing pulley  514  onto shaft surface  518 . Pulley  514  is also fixed to shaft  504  by key  520 . In certain applications the friction developed between pulley  514  and shaft surface  518  by nut  516  is sufficient to resist the torque being developed eliminating the need for key  520 . Press fitting or gluing pulley  514  onto shaft  504  can also be employed to fix pulley  514  adequately onto shaft  504 . 
         [0125]    End bells  502  and  503  are preferably die cast or sand cast aluminum such A356 but can manufacture from any suitable material, such as being cast from other suitable casting material such as magnesium, steel, or engineered plastic such as polyamide-imide. The end bells can alternatively be machined from a solid billet of aluminum such as 6061-T651 or other suitable material such as magnesium, steel, engineered plastic, or other appropriate material. The shaft  504  and pulleys are preferably made of the same respective materials as described for CTC assembly  300 . 
         [0126]    Front end bell  502  contains through bore  522 . Bearing bore  524  is preferably bored to a high tolerance (e.g., +0.0001 to +0.0004 inches over nominal diameter) to accept bearing  526  and is concentric with through bore  522 . Bearing  526  is maintained in bearing bore  524  by circlip  528  seated in groove  530 . Bearing  526  is located on shaft  504  between circlip  532  seated in groove  534  and circlip  536  seated in groove  513 . Surface  538  on shaft  504  between groove  534  and  513  is preferably machined to a high tolerance (e.g., +0.0000 to −0.0003) to accept bearing  526  in assembly. Shaft surface  540  is machined with sufficient clearance to allow bearing  526  to slip past surface  540  during assembly and seat on surface  538 . Rear end bell  503  contains through bore  542 . Bearing bore  544  is preferably bored to a high tolerance (e.g., +0.0001 to +0.0004 inches over nominal diameter) to accept bearing  546  and is concentric with through bore  542 . Bearing  546  is maintained in bearing bore  544  by circlip  548  seated in groove  550 . Bearing  546  is located on shaft  504  between circlip  552  seated in groove  554  and circlip  556  seated in groove  515 . Surface  558  on shaft  504  between groove  554  and groove  515  is preferably machined to a high tolerance (e.g., +0.0000 to −0.0003) to accept bearing  546  in assembly. Shaft surface  560  is machined with sufficient clearance to allow bearing  546  to slip past surface  560  during manufacture and seat on surface  558 . 
         [0127]    Through bores  522  and  542 , which align in assembly  500 , bearing bores  524  and  544 , and bearings  526  and  546  cooperate to align shaft  504  with through bores  522  and  542 . Bearing  526 , circlips  528 ,  532  and  536 , bearing  546 , circlips  548 ,  552 , and  556  cooperate to fix shaft  504  in CTC assembly  500 . Nut  508  and surface  510  fix pulley  506  on shaft  504 . Key  512  also fixes pulley  506  on shaft  504 . Nut  516  and surface  518  fix pulley  514  on shaft  504 . Key  520  also fixes pulley  514  on shaft  504 . 
         [0128]    Power is transmitted to pulley  506  from a crank pulley mounted to a power source (not shown) through belt  562 . Belt  562  in this embodiment is preferably a poly-v belt but can be a roller chain, v-belt, rope, or any other device suitable in transmitting power to pulley  506 . Pulley  506  transmits power from belt  562  to the rotating machine section of CTC assembly  500  through shaft  504 , pulley  514 , and belt  570  then to pulley  566  of the rotating machine section of CTC assembly  500 . Pulley  566  being fixed to shaft  564  by nut  568  imparts rotation to shaft  564  which in turn rotates internal components (not shown) of the rotating machine section of CTC assembly  500  producing output. Output of the rotating machine section of CTC-RM  500  can be electrical power, gas compression, fluid flow or any output generated by rotating machines. 
         [0129]    Belt  570  is preferably a synchronous or ‘cogged timing’ belt. The use of synchronous belts is well known for their capability to transmit large amounts of power relative to their cross sectional areas and ability to resist slippage. Although belt  570  in the preferred embodiment is a synchronous belt, it could also be a roller chain, v-belt, poly-v belt, rope or any other device suitable in transferring power from pulley  514  to pulley  566 . 
         [0130]    Mounting ears  574  of rear end bell  503  have holes  576  that are sized to accept threaded slip bushings  578  and align with through holes  580  in mounting ears  511  of bracket  582 . Mounting ears  584  of front end bell  502  have clearance holes  586  that accept bolts  588  and align with through holes  580  of mounting ear  511  of bracket  582 . Bolts  588  are inserted through holes  580  and  586  and thread into slip bushing  578 . When tightened, bolts  588  draw threaded slip bushings  578  against surface  590  of mounting ear  511  of bracket  582 , which in turn draws surface  592  of mounting ear  584  against surface  594  of mounting ear  511  of bracket  582 . Holes  576 ,  580 , and  586  in cooperation with bolts  588  and threaded slip bushings  578 , fix CTC-RM  500  to bracket  582 . Bracket  582  is fixed to mounting surface  501  with bolts  596  that align with tap holes  598  in mounting surface  501 . 
         [0131]    For automotive applications, mounting surface  501  could be the surface of the combustion engine itself. This is typically the case in automotive applications where CTC-RM  500  would utilize a bracket ( 582 ) to mount CTC assembly  500  to the engine. In applications where bracket  582  is relatively simple, CTC assembly  500  can be designed to fit directly to surface  501  thereby eliminating the need for bracket  582 . However, many automobile applications have complex bracket assemblies. In these instances, replacing the complex bracket is cost prohibitive, and the ability to mount CTC assembly to the existing mounting bracket is advantageous. In industrial applications, the mounting surface can be the floor, a support structure, or other piece of industrial equipment associated with the rotating machine. 
         [0132]    Referring now to  FIG. 6A-6F , collectively referred to as  FIG. 6 , a fifth embodiment of a CTC that integrates the CTC components and the rotating machine to produce a single assembly  600 . Although the CTC components have been integrated into a single unit, the assembly still has two distinct sections: (1) an RM section, which in this embodiment is depicted as an alternator but can equally apply to a pump, compressor, or any other output device produced by rotating machinery, and (2) a CTC section which enhances the functionality of the RM section. 
         [0133]    CTC assembly  600  comprises front end bell  602  and rear end bell  603 . Stator  683  is maintained and aligned between end bells  602  and  603  with socket head caps screws  685  and nuts  687 . 
         [0134]    The CTC section of CTC assembly  600  is essentially of the same design as CTC assembly  300 . It comprises shaft  604   a  and pulley  606   a , which is fixed to shaft  604   a  by nut  608   a  pressing pulley  606   a  onto shaft surface  610   a . Pulley  606   a  is also fixed to shaft  604   a  by key  612   a . In certain applications the friction developed between pulley  606   a  and shaft surface  610   a  by nut  608   a  is sufficient to eliminate the need for key  612   a . Press fitting or gluing pulley  606   a  onto shaft  604   a  can also be employed to fix pulley  606   a  adequately onto shaft  604   a . Pulley  614   a  is maintained on shaft  604   a  by nut  616   a  pressing pulley  614   a  onto shaft surface  618   a . Pulley  614   a  is also fixed to shaft  604   a  by key  620   a . In certain applications the friction developed between pulley  614   a  and shaft surface  618   a  by nut  616   a  is sufficient to eliminate the need for key  620   a . Press fitting or gluing pulley  614   a  onto shaft  604   a  can also be employed to fix pulley  606   a  adequately onto shaft  604   a.    
         [0135]    CTC assembly  600  also comprises second shaft  604   b  and pulley  606   b  which is fixed to shaft  604   b  by nut  608   b  pressing pulley  606   b  onto shaft surface  610   b . Pulley  606   b  is also fixed to shaft  604   b  by key  612   b . In certain applications the friction developed between pulley  606   b  and shaft surface  610   b  by nut  608   b  is sufficient to eliminate the need for key  612   b . Press fitting or gluing pulley  606   b  onto shaft  604   b  can also be employed to fix pulley  606   b  adequately onto shaft  604   b . Pulley  614   b  is maintained on shaft  604   b  by nut  616   b  pressing pulley  614   b  onto shaft surface  618   b . Pulley  614   b  is also fixed to shaft  604   b  by key  620   b . In certain applications the friction developed between pulley  614   b  and shaft surface  618   b  by nut  616   b  is sufficient to eliminate the need for key  620   b . Press fitting or gluing pulley  614   b  onto shaft  604   b  can also be employed to fix pulley  606   b  adequately onto shaft  604   b.    
         [0136]    End bells  602  and  603 , shafts  604  and  505  and the pulleys used in CTC assembly  600  are preferably made of the same respective materials as described for CTC assembly  500 . 
         [0137]    Front end bell  602  contains through bore  622   a . Bearing bore  624   a  is preferably bored to a high tolerance (e.g., +0.0001 to +0.0004 inches over nominal diameter) to accept bearing  626   a  and is concentric with through bore  622   a . Bearing  626   a  is maintained in bearing bore  624   a  by circlip  628   a  seated in groove  630   a . Bearing  626   a  is located on shaft  604   a  between circlip  632   a  seated in groove  634   a  and shaft surface  636   a . Surface  638   a  on shaft  604   a  between groove  634   a  and surface  636   a  is preferably machined to a high tolerance (e.g., +0.0000 to −0.0003) to accept bearing  626   a  in assembly  600 . Shaft surface  640   a  is machined with sufficient clearance to allow bearing  626   a  to slip past surface  640   a  during manufacture and seat on surface  638   a . Rear end bell  603   a  contains through bore  642   a . Bearing bore  644   a  is preferably bored to a high tolerance (e.g., +0.0001 to +0.0004 inches over nominal diameter) to accept bearing  646   a  and is concentric with through bore  642   a . Bearing  646   a  is maintained in bearing bore  644   a  by circlip  648   a  seated in groove  650   a . Bearing  646   a  is located on shaft  604   a  between circlip  652   a  seated in groove  654   a  and shaft surface  656   a . Surface  658   a  on shaft  604   a  between groove  654   a  and surface  656   a  is preferably machined to a high tolerance (e.g., +0.0000 to −0.0003) to accept bearing  646   a  in assembly  600 . Shaft surface  660   a  is machined with sufficient clearance to allow bearing  646   a  to slip past surface  660   a  during manufacture and seat on surface  658   a.    
         [0138]    Through bores  622   a  and  642   a , which align in assembly  600 , bearing bores  624   a  and  644   a , and bearings  626   a  and  646   a , cooperate to align shaft  604   a  with through bores  622   a  and  642   a . Bearing  626   a , circlips  628   a  and  632   a , surface  636   a , bearing  646   a , circlips  648   a  and  652   a , and surface  656   a  cooperate to fix shaft  604   a  in CTC-RM assembly  600   a . Nut  608   a  and surface  610   a  fix pulley  606   a  on shaft  604   a . Key  612   a  fixes pulley  606   a  on shaft  604   a . Nut  616   a  and surface  618   a  fix pulley  614   a  on shaft  604   a . Key  620   a  fixes pulley  614   a  on shaft  604   a.    
         [0139]    Front end bell  602  also contains through bore  622   b . Bearing bore  624   b  is preferably bored to a high tolerance (e.g., +0.0001 to +0.0004 inches over nominal diameter) to accept bearing  626   b  and is concentric with through bore  622   b . Bearing  626   b  is maintained in bearing bore  624   b  by circlip  628   b  seated in groove  630   b . Bearing  626   b  is located on shaft  604   b  between circlip  632   b  seated in groove  634   b  and shaft surface  636   b . Surface  638   b  on shaft  604   b  between groove  634   b  and surface  636   b  is preferably machined to a high tolerance (e.g., +0.0000 to −0.0003) to accept bearing  626   b  in assembly. Shaft surface  640   b  is machined with sufficient clearance to allow bearing  626   b  to slip past surface  640   b  during assembly and seat on surface  638   b . Rear end bell  603   b  contains through bore  642   b . Bearing bore  644   b  is preferably bored to a high tolerance (e.g., +0.0001 to +0.0004 inches over nominal diameter) to accept bearing  646   b  and is concentric with through bore  642   b . Bearing  646   b  is maintained in bearing bore  644   b  by circlip  648   b  seated in groove  650   b . Bearing  646   b  is located on shaft  604   b  between circlip  652   b  seated in groove  654   b  and shaft surface  656   b . Surface  658   b  on shaft  604   b  between groove  654   b  and surface  656   b  is preferably machined to a high tolerance (e.g., +0.0000 to −0.0003) to accept bearing  646   b  in assembly  600 . Shaft surface  660   b  is machined with sufficient clearance to allow bearing  646   b  to slip past surface  660   b  during manufacture and seat on surface  658   b.    
         [0140]    Through bores  622   b  and  642   b , which align in assembly  600 , bearing bores  624   b  and  644   b , and bearings  626   b  and  646   b , cooperate to align shaft  604   b  with through bores  622   b  and  642   b . Bearing  626   b , circlips  628   b  and  632   b , surface  636   b , bearing  646   b , circlips  648   b  and  652   b , and surface  656   b  cooperate to fix shaft  604   b  in CTC-RM assembly  600   b . Nut  608   b  and surface  610   b  fix pulley  606   b  on shaft  604   b . Key  612   b  fixes pulley  606   b  on shaft  604   b . Nut  616   b  and surface  618   b  fix pulley  614   b  on shaft  604   b . Key  620   b  fixes pulley  614   b  on shaft  604   b.    
         [0141]    Back side (smooth) idler pulley  663  is fixed to mounting ear  665  of front end bell  602  by bolt  667  inserted through pulley  663  and threaded into tapped hole  669 . The axis of tapped hole  669  is preferably parallel to the axis of shafts  604   a  and  604   b  and is located below the plane formed by the axes of shafts  604   a  and  604   b  on a vertical line mid way between shafts  604   a  and  604   b . The location of pulleys  663 ,  606   a , and  606   b  form a serpentine path for belt  671  that increases belt wrap length. Belt  671  is preferably a poly-v belt but other devices designed to work with backside idlers can also be utilized as well as roller chain, rope, or any other device suitable in transmitting power to pulleys  606   a  and  606   b.    
         [0142]    During operation belt  671  transmits power to both pulley  606   a  and  606   b  simultaneously as belt  671  travels over pulley  606   a , across idler pulley  663 , over pulley  606   b  then returning back to the engine crank pulley (not shown). Although it is advantageous to have idler pulley  663  mounted to CTC body  602 , an idler pulley can be located remotely from CTC body  602  to replicate belt wrap afforded by mounting idler pulley  663  on CTC body  602 . Belt  671  in this embodiment is preferably a poly-v belt but any other belts or devices designed to work with backside idlers may be used as well as roller chains, rope, or any other device suitable in transmitting power to pulley  606   a  and  606   b.    
         [0143]    Pulley  606   a  transmits power from belt  671 , through shaft  604   a , to pulley  614   a  then to belt  681 . Pulley  606   b  transmits power from belt  671 , through shaft  604   b , to pulley  614   b  then to belt  681 . Pulleys  606   a  and  606   b  simultaneously transmit power to belt  681 . Belt  681  drives pulley  677  of the RM portion of CTC assembly  600 . Pulley  677  is fixed to shaft  675  by nut  679  and imparts rotation to shaft  675 , which in turn rotates the internal components (not shown) of the rotating machine section of CTC assembly  600  thereby producing output. Output by rotating machine section of CTC assembly  600  can be electrical power, gas compression, fluid flow or any output generated by rotating machines. Belt  681  is preferably a synchronous or ‘cogged timing’ belt. Synchronous belts are well known for their capability to transmit large amounts of power relative to their cross sectional areas and ability to resist slippage. Although belt  681  in the preferred embodiment is a synchronous belt, it could be a roller chain, v-belt, poly-v belt, rope, or any other device suitable in transferring power from pulleys  614  and  615  to pulley  677 . 
         [0144]    Mounting ears  662  of rear end bell  603  have holes  664  that are sized to accept threaded slip bushings  666  and align with through holes  668  in mounting ears  673  of bracket  670 . Mounting ears  672  of front end bell  602  have clearance holes  674  that accept bolts  676  and align with through holes  668  in mounting ear  673  of bracket  670 . Bolts  676  are inserted through holes  668  and  674  and threaded into slip bushing  666 . When tightened, bolts  676  draw threaded slip bushings  666  against surface  678  of mounting ear  673  of bracket  670  which in turn draws surface  680  of mounting ear  672  against surface  682  of mounting ear  673  of bracket  670 . Holes  664 ,  668 , and  674  in cooperation with bolts  676  and threaded slip bushings  666 , fix CTC assembly  600  to bracket  670 . Bracket  670  is fixed to mounting surface  688  with bolts  684  that align with tap holes  686  in mounting surface  688 . CTC assembly  600  is preferably mounted in the same manner as described for CTC assembly  500 . 
         [0145]    Referring now to  FIGS. 7A-7F , collectively referred to as  FIG. 7 , a sixth embodiment of a CTC integrates the CTC components and the rotating machine RM to produce a single assembly  700 . Although the CTC has been integrated into a single unit, the assembly still has two distinct sections: (1) an RM section, which in this embodiment is depicted as an alternator but can equally apply to a pump, compressor, or any other output device produced by rotating machinery, and (2) a CTC section, which enhances the functionality of the rotating machine. CTC assembly  700  comprises front end bell  702  and rear end bell  703  a stator  705 , which is maintained and aligned between end bells  702  and  703  by socket head caps screws  707  and nuts  709 . 
         [0146]    CTC assembly  700  also comprises a shaft  704  and pulley  706 , which is fixed to shaft  704  by nut  708  compressing pulley  706  onto shaft surface  710 . Pulley  706  is also fixed to shaft  704  by key  712 . In certain applications the friction developed between pulley  706  and shaft surface  710  by nut  708  is sufficient to resist the torque being developed eliminating the need for key  712 . Press fitting or gluing pulley  706  onto shaft  704  also can be employed to fix pulley  706  adequately onto shaft  704 . Pulley  714  is maintained on shaft  704  by nut  716  pressing pulley  714  onto shaft surface  718 . Pulley  714  is also fixed to shaft  704  by key  720 . In certain applications the friction developed between pulley  714  and shaft surface  718  by nut  716  is sufficient to eliminate the need for key  720 . Press fitting or gluing pulley  714  onto shaft  704  can also be employed to fix pulley  706  adequately onto shaft  704 . 
         [0147]    End bells  702  and  703 , shafts  704  and  705  are preferably formed, respectively, of the same materials as described for CTC assembly  500 . 
         [0148]    Front end bell  702  contains through bore  722 . Bearing bore  724  is preferably bored to a high tolerance (e.g., +0.0001 to +0.0004 inches over nominal diameter) to accept bearing  726  and is concentric with through bore  722 . Bearing  726  is maintained in bearing bore  724  by circlip  728  seated in groove  730 . Bearing  726  is located on shaft  704  between pulley surface  732  and shaft surface  736 . Surface  738  on shaft  704  between surface  732  and surface  710  is preferably machined to a high tolerance (e.g., +0.0000 to −0.0003) to accept bearing  726 . In assembly pulley surface  732  and shaft surface  738  are coplanar. Rear end bell  703  contains through bore  742 . Bearing bore  744  is preferably bored to a high tolerance (e.g., +0.0001 to +0.0004 inches over nominal diameter) to accept bearing  746  and is concentric with through bore  742 . Bearing  746  is maintained in bearing bore  744  by circlip  748  seated in groove  750 . Bearing  746  is located on shaft  704  by pulley surface  752  and shaft surface  756 . Surface  758  on shaft  704  between surface  752  and surface  720  is preferably machined to a high tolerance (e.g., +0.0000 to −0.0003) to accept bearing  746 . In CTC assembly  700  pulley surface  752  and shaft surface  756  are coplanar. 
         [0149]    Through bores  722  and  742 , which align in assembly  700 , bearing bores  724  and  744 , bearings  726  and  746  cooperate to align shaft  704  in through bores  722  and  742 . Bearing  726 , circlip  728 , surface  732  and  736 , bearing  746 , surface  752  and  756  cooperate to fix shaft  704  in CTC assembly  700 . Nut  708  and surface  710  fix pulley  706  on shaft  704 . Key  712  fixes pulley  707  on shaft  704 . Nut  716  and surface  718  fix pulley  714  on shaft  704 . Key  720  also fixes pulley  714  on shaft  704 . 
         [0150]    Back side (smooth) idler pulley  762  is located on mounting ear  764  of front end bell  702  by bolt  768  inserted through idler pulley  762  threaded into tapped hole  766 . The axis of tapped hole  766  is parallel to the axis of shaft  704  and is located below and to the right of the shaft  704  axis. Poly-v (grooved) idler pulley  770  is also located on mounting ear  764  of front end bell  702  by bolt  774  inserted through idler pulley  770  threaded into tapped hole  772 . The axis of tapped hole  772  is preferably on the same horizontal plane formed by the shaft  704  axis and is located above and to the right of the axis of tapped hole  766 . Pulleys  762 ,  706 , and  707  are located to form a serpentine path for belt  774  that increases belt wrap over pulley  706 . During operation belt  774  transmits power to pulley  706  as belt  774  travels over pulley  706 , across idler pulley  762 , over idler pulley  770  then returning back to the engine crank pulley (not shown). Belt  774  is preferably a poly-v belt, but any belts or other devices designed to work with backside idlers may be used as well as roller chains, rope, or any other device suitable in transmitting power to pulley  706 . 
         [0151]    Pulley  702  transmits power from belt  774  to the rotating machine section of CTC assembly  700  through shaft  704 , pulley  714 , and belt  782  then to pulley  778  of the rotating machine section of CTC assembly  700 . Pulley  778  is fixed to shaft  776  by nut  780  and imparts rotation to shaft  776  of the rotating machine section of CTC assembly  700  which in turn rotates internal components (not shown) of rotating machine section of CTC assembly  700  producing output. Output by the rotating machine section of CTC assembly  700  can be electrical power, gas compression, fluid flow or any output generated by rotating machines. 
         [0152]    Idler pulleys  762  and  770  can be located remotely from front end bell  702  thereby replicating similar belt wrap around pulley  706 . 
         [0153]    In automotive applications the power source is typically an internal combustion engine and the power is transmitted from a crank pulley (not shown) which is fixed to the crank shaft (not shown) of the engine (not shown) to pulley  706 . In industrial applications, the power source can be an electric motor, hydraulic motor, or pneumatic motor mounted with a pulley on the main shaft to transmit power. The use of Power take offs (PTO) or other types of engine transmission auxiliary drive shafts can be equipped with pulleys to drive the rotating machine. Belt  782  in this embodiment is a synchronous or ‘cogged timing’ belt. The use of synchronous belts is well known for their capability to transmit large amounts of power relative to their cross sectional areas and ability to resist slippage. Although belt  782  in the preferred embodiment is a synchronous belt, it could also be a roller chain, v-belt, poly-v belt, rope, or any other device suitable in transferring power from pulley  714  to pulley  778 . 
         [0154]    Mounting ears  784  of rear end bell  703  have holes  786  that are sized to accept threaded slip bushings  788  and align with through holes  790  in mounting ears  711  of bracket  792 . Mounting ears  794  of front end bell  702  have clearance holes  796  that accept bolts  798  and align with through holes  790  of mounting ear  711  of bracket  792 . Bolts  798  are inserted through holes  790  and  796  and thread into slip bushing  788 . When tightened, bolts  798  draw threaded slip bushings  788  against surface  713  of mounting ear  711  of bracket  792  which in turn draws surface  715  of mounting ear  794  against surface  717  of mounting ear  711  of bracket  792 . Holes  786 ,  790 , and  796 , in cooperation with bolts  798  and threaded slip bushings  788 , fix CTC assembly  500  to bracket  792 . Bracket  792  is fixed to mounting surface  713  with bolts  715  that align with tap holes  717  in mounting surface  713 . 
         [0155]    CTC assembly  700  would preferably be mounted in the same manner as CTC assembly  500 . 
         [0156]    Referring now to  FIGS. 8A-8F , collectively referred to as  FIG. 8 , a seventh embodiment of a CTC assembly  800  comprises a twin shaft CTC body  802 , a first shaft  804   a , and pulley  806   a , which is fixed to shaft  804   a  by nut  808   a  pressing pulley  806   a  onto shaft surface  810   a . Pulley  806   a  is also fixed to shaft  804   a  by key  812   a . In certain applications the friction developed between pulley  806   a  and shaft surface  810   a  by nut  808   a  is sufficient to eliminate the need for key  812   a . Press fitting or gluing pulley  806   a  onto shaft  804   a  can also be employed to fix pulley  806   a  adequately onto shaft  804   a.    
         [0157]    Pulley  814   a  is maintained on shaft  804   a  by nut  816   a  pressing pulley  814   a  onto shaft surface  818   a  Pulley  814   a  is also fixed to shaft  804   a  by key  820   a . In certain applications the friction developed between pulley  814   a  and shaft surface  818   a  by nut  816   a  is sufficient to eliminate the need for key  820   a . Press fitting or gluing pulley  814   a  onto shaft  804   a  can also be employed to fix pulley  806   a  adequately onto shaft  804   a.    
         [0158]    CTC  800  also comprises second shaft  804   b , and pulley  806   b  which is fixed to shaft  804   b  by nut  808   b  pressing pulley  806   b  onto shaft surface  810   b . Pulley  806   b  is also fixed to shaft  804   b  by key  812   b . In certain applications the friction developed between pulley  806   b  and shaft surface  810   b  by nut  808   b  is sufficient to eliminate the need for key  812   b . Press fitting or gluing pulley  806   b  onto shaft  804   b  can also be employed to fix pulley  806   b  adequately onto shaft  804   b . Pulley  814   b  is maintained on shaft  804   b  by nut  816   b  pressing pulley  814   b  onto shaft surface  818   b . Pulley  814   b  is also fixed to shaft  804   b  by key  820   b . In certain applications the friction developed between pulley  814   b  and shaft surface  818   b  by nut  816   b  is sufficient to eliminate the need for key  820   b . Press fitting or gluing pulley  814   b  onto shaft  804   b  can also be employed to fix pulley  806   b  adequately onto shaft  804   b    
         [0159]    CTC body  802  is preferably die-cast or sand-cast aluminum such A356 but other suitable casting materials such as magnesium, steel, or engineered plastic such as Polyamide-Imide. Alternatively, CTC body can be machined from a solid billet of aluminum such as 6061-T651 or other suitable material such as magnesium, steel, engineered plastic, or other appropriate material. Shafts  804   a  and  804   b  and the pulleys are preferably manufactured, respectively, from the same materials as described for CTC assembly  500 . 
         [0160]    Twin shaft body  802  contains through bore  822   a . Bearing bore  824   a  is preferably bored to a high tolerance (e.g., +0.0001 to +0.0004 inches over nominal diameter) to accept bearing  826   a  and is concentric with through bore  822   a . Bearing  826   a  is maintained in bearing bore  824   a  by circlip  828   a  seated in groove  830   a . Bearing  826   a  is located on shaft  804   a  between circlip  832   a  seated in groove  834   a  and shaft surface  836   a . Surface  838   a  on shaft  804   a  between groove  834   a  and surface  836   a  is preferably machined to a high tolerance (e.g., +0.0000 to −0.0003) to accept bearing  826   a  in assembly. Shaft surface  840   a  is machined with sufficient clearance to allow bearing  826   a  to slip past surface  840   a  during assembly and seat on surface  838   a.    
         [0161]    Twin shaft body  802  also contains bearing bore  844   a , which is preferably bored to a high tolerance (e.g., +0.0001 to +0.0004 inches over nominal diameter) to accept bearing  846   a  and is concentric with through bore  822   a . Bearing  846   a  is maintained in bearing bore  844   a  by circlip  848   a  seated in groove  850   a . Bearing  846   a  is located on shaft  804   a  between circlip  852  seated in groove  854   a  and shaft surface  856   a . Surface  858   a  on shaft  804   a  between groove  854   a  and surface  856   a  is preferably machined to a high tolerance (e.g., +0.0000 to −0.0003) to accept bearing  846   a  in assembly. Shaft surface  860   a  is machined with sufficient clearance to allow bearing  846   a  to slip past surface  860   a  during assembly and seat on surface  858   a.    
         [0162]    Through bore  822   a , bearing bores  824   a  and  844   a , and bearings  826   a  and  846   a  cooperate to align shaft  804   a  with through bore  822   a . Bearing  826   a , circlips  828   a  and  832   a , surface  836   a , bearing  846   a , circlips  848   a  and  852   a , surface  856   a  cooperate to fix shaft  804   a  in CTC-RM assembly  800 . Nut  808   a  and surface  810   a  fix pulley  806   a  on shaft  804   a . Key  812   a  fixes pulley  806   a  on shaft  804   a . Nut  816   a  and surface  818   a  fix pulley  814   a  on shaft  804   a . Key  820   a  also fixes pulley  814   a  on shaft  804   a.    
         [0163]    CTC body  802  also contains through bore  822   b . Bearing bore  824   b  is preferably bored to a high tolerance (e.g., +0.0001 to +0.0004 inches over nominal diameter) to accept bearing  826   b  and is concentric with through bore  822   b . Bearing  826   b  is maintained in bearing bore  824   b  by circlip  828   b  seated in groove  830   b . Bearing  826   b  is located on shaft  804   b  between circlip  832   b  seated in groove  834   b  and shaft surface  836   b . Surface  838   b  on shaft  804   b  between groove  834   b  and surface  836   b  is preferably machined to a high tolerance (e.g., +0.0000 to −0.0003) to accept bearing  826   b  in assembly. Shaft surface  840   b  is machined with sufficient clearance to allow bearing  826   b  to slip past surface  840   b  during assembly and seat on surface  838   b . Bearing bore  844   b  is preferably bored to a high tolerance (e.g., +0.0001 to +0.0004 inches over nominal diameter) to accept bearing  846   b  and is concentric with through bore  822   b.    
         [0164]    CTC body  802  also contains bearing  846   b , which is maintained in bearing bore  844   b  by circlip  848   b  seated in groove  850   b . Bearing  846   b  is located on shaft  804   b  between circlip  852   b  seated in groove  854   b  and shaft surface  856   b . Surface  858   b  on shaft  804   b  between groove  854   b  and surface  856   b  is preferably machined to a high tolerance (e.g., +0.0000 to −0.0003) to accept bearing  846   b  in assembly. Shaft surface  860   b  is machined with sufficient clearance to allow bearing  846   b  to slip past surface  860   b  during assembly and seat on surface  858   b.    
         [0165]    Through bore  822   b , bearing bores  824   b  and  844   b  and bearings  826   b  and  846   b  cooperate to align shaft  804   b  with through bores  822   b . Bearing  826   b , circlips  828   b  and  832   b , surface  836   b , bearing  846   b , circlips  848   b  and  852   b , and surface  856   b  cooperate to fix shaft  804   b  in CTC assembly  800 . Nut  808   b  and surface  810   b  fix pulley  806   b  on shaft  804   b . Key  812   b  also fixes pulley  806   b  on shaft  804   b . Nut  816   b  and surface  818   b  fix pulley  814   b  on shaft  804   b . Key  820   b  also fixes pulley  814   b  on shaft  804   b.    
         [0166]    CTC body  802  also comprises stanchion  805  with left mounting ears  807   a  with through holes  809   a  and right mounting ears  807   b  with through holes  809   b . Stanchion  805  can be an integral part of the CTC body  802  or can be fabricated separately and joined to CTC body  802  with bolts (not shown) or welded to CTC body  802 . If stanchion  805  is to be fabricated separately, it is preferable it be fabricated from the same material used to fabricate CTC body  802 . 
         [0167]    In assembly, mounting ears  862   a  of rotating machine  873   a  have holes  864   a  that are sized to accept threaded slip bushings  866   a  and align with left mounting ears  807   a  through holes  809   a  of stanchion  805 . Mounting ears  872   a  of rotating machine  873   a  have clearance holes  874   a  that accept bolts  876   a  and also align with left mounting ears  807   a  through holes  809   a  of stanchion  805 . Bolts  876   a  are inserted through holes  809   a  and  874   a  and threaded into slip bushing  866   a . When tightened, bolts  876   a  draw threaded slip bushings  866   a  against surface  878   a  of left mounting ears  807   a  of stanchion  805 , which in turn draws surface  880   a  of mounting ear  872   a  of rotating machine  873   a  against surface  882   a  left mounting ears  807  of stanchion  805 . Holes  864   a ,  809   a , and  874   a  in cooperation with bolts  876   a  and threaded slip bushings  866   a , fix rotating machine  873   a  to stanchion  805 . 
         [0168]    In assembly, mounting ears  862   b  of rotating machine  873   b  have holes  864   b  that are sized to accept threaded slip bushings  866   b  and align with left mounting ears  807   b  through holes  809   b  of stanchion  805 . Mounting ears  872   b  of rotating machine  873   b  have clearance holes  874   b  that accept bolts  876   b  and also align with left mounting ears  807   b  through holes  809   b  of stanchion  805 . Bolts  876   b  are inserted through holes  809   b  and  874   b  and threaded into slip bushing  866   b . When tightened, bolts  876   b  draw threaded slip bushings  866   b  against surface  878   b  of left mounting ears  807   b  of stanchion  805 , which in turn draws surface  880   b  of mounting ear  872   b  of rotating machine  873   b  against surface  882   b  left mounting ears  807   b  of stanchion  805 . Holes  864   b ,  809   b , and  874   b  in cooperation with bolts  876   b  and threaded slip bushings  866   b , fix rotating machine  873   b  to stanchion  805 . 
         [0169]    Mounting ears  384  of CTC body  802  have holes  886  that are sized to accept slip bushings  888  and align with through holes  890  in mounting ears  892  of bracket  894 . Mounting ears  896  of CTC body  802  have holes  898  that are sized to accept bolts  883  and align with through holes  890  in mounting ears  892  of bracket  894 . Bolts  883  are inserted through holes  890  and  898  and threaded into slip bushings  888 . When tightened, bolts  883  draw threaded slip bushings  888  against surface  885  of mounting ears  884 , which in turn draws surface  887  of mounting ears  896  against surface  889  of mounting ears  892  of bracket  894 . Holes  886 ,  890 , and  898  in cooperation with bolts  883  and slip bushings  888 , fix CTC body  802  to bracket  894 . Bracket  894  is fixed to mounting surface  891  with bolts  893  that align with tap holes  895  in mounting surface  891 . 
         [0170]    CTC-RM assembly  800  is affixed to a power source as previously described with respect to CTC assembly  500 . 
         [0171]    Back side (smooth) idler pulley  863  is located on mounting ear  865  of CTC body  802  by bolt  869  inserted through idler pulley  863  threaded into tapped hole  867 . The axis of tapped hole  867  is preferably parallel to the axis formed by shafts  804   a  and  804   b  and located below the plane formed by the axis of shafts  804   a  and  804   b  on a line midway between shafts  804   a  and  804   b . The location of tapped hole  867  is best seen in  FIG. 8B . Pulleys  863 ,  806   a , and  806   b  are located to form a serpentine path for belt  871  that increases belt wrap angle and belt contact arc length over pulleys  806   a  and  806   b . During operation belt  871  transmits power to both pulley  806   a  and  806   b  simultaneously as belt  871  travels over pulley  806   a , across idler pulley  863 , over pulley  806   b  then returning back to the engine crank pulley (not shown). Although it is advantageous to have idler pulley  863  mounted to CTC body  802 , an idler pulley can be located remotely from CTC body  802  to replicate belt wrap around pulleys  806   a  and  806   b  afforded by mounting idler pulley  863  on CTC body  802 . 
         [0172]    Pulley  806   a  transmits power from belt  871  to rotating machine  873   a  through shaft  804   a , pulley  814   a , and belt  881   a , and then to pulley  887   a  of rotating machine  873   a . Pulley  887   a  being fixed to shaft  875   a  by nut  879   a  imparts rotation to shaft  875   a , which in turn rotates internal components (not shown) of rotating machine  873   a  producing an output. Output at rotating machine  873   a  can be electrical power, gas compression, fluid flow or any output generated by rotating machines. 
         [0173]    Pulley  806   b  transmits power from belt  871  to rotating machine  873   b  through shaft  804   b , pulley  814   b , and belt  881   b , and then to pulley  887   b  of rotating machine  873   b . Pulley  887   b  being fixed to shaft  875   b  by nut  879   b  imparts rotation to shaft  875   b , which in turn rotates internal components (not shown) of rotating machine  873   a  producing an output. Output at rotating machine  873   b  can be electrical power, gas compression, fluid flow or any output generated by rotating machines. 
         [0174]    Rotating machines  873   a  and  873   b  can produce different outputs and are not required to have the same functionality. For example, rotating machine  873   a  could be an alternator while rotating machine  873   b  could be an air compressor. 
         [0175]    Belts  881   a  and  881   b  in this preferred embodiment are synchronous or ‘cogged timing’ belts. The use of synchronous belts is well known for applications where their capability to transmit large amounts of power relative to their cross sectional areas is advantageous. Although belts  881   a  and  881   b  in the preferred embodiment are synchronous belts they could instead be roller chains, v-belts, poly-v belts, ropes, or any other device suitable in transferring power from pulley  814   a  to pulley  887   a  and  814   b  to pulley  877   b.    
         [0176]    In automotive applications, mounting surface  891  would be the surface of the combustion engine itself. This is typically the case in automotive applications wherein the rotating machine, in this example an alternator, would use a bracket ( 894 ) to maintain alternator (rotating machine  873 ) to the engine. In applications where bracket  894  is relatively simple in design, CTC  800  can mount directly to the engine using tapped holes  895  thereby eliminating the need for bracket  894 . However, when automobile applications have complex bracket assemblies to which many accessories are mounted, replacing the complex bracket becomes cost prohibitive. In that case, the CTC may be mounted to the existing bracket. 
         [0177]    Although the present invention has been described in conjunction with various exemplary embodiments, the invention is not limited to the specific forms shown, and other embodiments of the present invention may be created without departing from the spirit of the invention. Variations in components, materials, values, structure, and other aspects of the design and arrangement may be made in accordance with the present invention as expressed in the following claims and legal equivalents thereof.