Patent Publication Number: US-8978600-B2

Title: Control methods for dual mode cooling pump

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This application is a continuation-in-part of U.S. application Ser. No. 13/509,876 filed Jan. 15, 2014. This application also claims priority to U.S. Patent Application Ser. No. 61/474,895, filed on Apr. 13, 2011, and entitled “Control System For Friction Clutch Assembly,” subsequently filed on Apr. 11, 2012, as International Application No. PCT/US12/32974. This application is also related to U.S. Patent Application Ser. No. 61/474,862, filed Apr. 13, 2011, entitled Hybrid Coolant Pump, subsequently filed on Apr. 10, 2012, as International Application No. PCT/US12/32849, U.S. Patent Application Ser. No. 61/474,876, filed on Apr. 13, 2011, entitled Pulley Assembly For A Vehicle Accessory, subsequently filed on Apr. 10, 2012, as International Application No. PCT/US12/32856, U.S. patent application Ser. No. 61/474,928, filed on Apr. 13, 2011, entitled Friction Clutch Assembly, subsequently filed on Apr. 10, 2012, as International Application No. PCT/US12/32863, and U.S. patent application Ser. No. 61/474,907, filed Apr. 13, 2011, entitled Compression Spring Member, subsequently filed on Apr. 10, 2012, as International Application PCT/US12/32876. 
    
    
     TECHNICAL FIELD 
     This invention relates to control system for engine accessories and more particularly to control methods and systems for dual mode cooling pumps and other accessories. 
     BACKGROUND 
     Water pumps are used in water cooled engines, primarily for operation of vehicles such as automobiles and trucks with internal combustion engines. The water pumps are typically driven by a belt attached to the crankshaft of the engine and thus operate at some percentage of engine speed. The pumps have an impeller that is used to circulate the engine coolant from the engine to the radiator and back in order to keep the coolant within acceptable temperature limits. 
     Efforts are being made today to reduce the power consumption of engine accessories, such as water pumps, in order to improve fuel economy and reduce emissions. It would thus be preferable if such accessories, including water pumps, could be made to operate at variable speeds or with less power in order to reduce the load on the engine and, in turn, improve fuel economy and reduce undesirable emissions from the engine. 
     SUMMARY OF THE INVENTION 
     An improved water pump is disclosed. The water pump has two modes of operation, a first mode driven mechanical, by the engine accessory belt, and a second mode operated by an electric motor, such as a brushless DC (BLDC) motor. 
     The components for the two modes of operation are contained within a housing that includes the pulley member as part of the housing. A shaft connected to the impeller of the water pump is positioned in the housing and is controlled by one mode of operation or the other, depending on certain factors. 
     The housing rotates at input speed driven by the engine accessory belt which is positioned on the pulley member. A friction clutch is provided inside the housing to selectively drive the water pump mechanically by the pulley member. A solenoid is utilized to control operation of the friction clutch. 
     The water pump is normally driven by the electric motor throughout most of its range of operation. When peak cooling is needed, the mechanical operation mode takes over and the water pump is driven directly by the pulley member. The friction clutch includes a softening spring member which minimizes the electrical power consumed by the clutch. The hybrid cooling pump has a variable speed control which results in the use of less power, the improvement of fuel economy, and the reduction of emissions. 
     The pulley assembly consists of two pieces, namely a pulley member and a clutch housing member. This configuration provides for distribution of the belt load between separate bearings minimizing overhung bearing loads. 
     A preferred control system provides for a “softer” engagement from one of the dual methods of operation to the other. The speed of the electric motor and the speed of the engine are brought closer together prior to switching from one driving mode to the other. This reduces slip and improves durability of the accessory, preferably relative to the friction members and frictional engagement. 
     The amount of electrical power supplied to the dual mode component during clutch engagement can be regulated such that the speed of the shaft rotating in the dual mode component is similar to or the same as the speed that the shaft would be rotating if only mechanical power at the engine speed is supplied. Thereafter, the electrical power can be reduced in a step or ramp fashion until the component is only being driven by mechanical power. The speed of the electrical power operation can be increased or reduced in order to be substantially the same as, or close to, the speed of the mechanical power operation. The closer the speeds are to being the same, the better will be the transition from one mode to the other, and the longer the life will be of the friction member on the friction clutch mechanism. 
     Another embodiment includes a method wherein the system includes a battery and wherein supplying electrical power comprises delivering electrical power from the battery. A capacitor could be utilized also to provide an energy storage device. Another embodiment includes a method comprising recovering energy from a first vehicle component, converting the energy to electrical power, storing the electrical power in a battery, and supplying electrical power from the battery to the dual mode component constructed and arranged to drive a second vehicle component using mechanical power and electrical power. 
     Another embodiment includes a method comprising recovering thermal energy from a vehicle component, converting thermal energy to electrical power, storing the electrical power in a battery, and supplying electrical power from the battery to the dual mode component constructed and arranged to drive a second vehicle component using mechanical power and electrical power. Another method comprises determining when an engine of the vehicle system is accelerating at first rate or greater than the first rate, and if so, then supplying electrical power to a dual mode component while the dual mode component is also being driven by mechanical power. The additional power to accomplish this could be supplied by a battery or capacitor. 
     Another embodiment includes a method of operating a vehicle system, the vehicle system including a battery and a dual mode component connect to the battery, measuring the remaining capacity of the battery to store additional energy, and if the remaining capacity is at or less than a first amount or capacity, then supplying electrical energy from the battery to the dual mode component to drive the dual mode component and to utilize a portion of the energy that was stored in the battery thereby freeing up capacity in the battery to store energy from mechanical and thermal energy recovery components. 
     Another embodiment includes a method wherein the dual mode component is being driven also by mechanical energy during the supplying electrical energy from the battery to the dual mode component to drive the dual mode component and to utilize a portion of the energy that was stored in the battery. 
     Another embodiment includes a method where the vehicle braking system is utilized to supply power back to the battery and thus to assist in operating the electric mode of the dual motor cooling pump or other accessory. 
     Also disclosed are various embodiments of products and computer program products to implement one or more of the method embodiments above. 
     Further objects, features and benefits of the invention are set forth below in the following description of the invention when viewed in combination with the drawings and claims. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  illustrates a water pump in accordance with one embodiment of the invention. 
         FIG. 2  is a cross-sectional view of the water pump shown in  FIG. 1 . 
         FIG. 3  is an exploded view of the components of the water pump as shown in  FIGS. 1 and 2 . 
         FIG. 4  illustrates a friction clutch embodiment which can be used in accordance with the present invention. 
         FIG. 5  is an exploded view of the friction clutch as shown in  FIG. 4 . 
         FIG. 6  is an embodiment of a compression spring which can be used with the present invention. 
         FIG. 7  is a side view of the compression spring member as shown in  FIG. 6 . 
         FIG. 8  is an enlarged view of a portion of the compression spring member in the uncompressed condition. 
         FIG. 9  is an enlarged view of a portion of the compression spring member in the compressed condition. 
         FIG. 10  is a load-deflection curve of an embodiment of a compression spring member for use with the present invention. 
         FIG. 11  illustrates an alternate embodiment of a compression spring member which can be used with the present invention. 
         FIG. 12  depicts another alternate embodiment of a compression spring member which can be used with the present invention. 
         FIG. 13  schematically illustrates the operating modes of a preferred embodiment of the present invention. 
         FIG. 14  schematically depicts another embodiment of a compression spring mechanism which can be used with the present invention. 
         FIGS. 15 AND 16  illustrate a planar and side view, respectively, of one of the buckling beam members utilized with the embodiment shown in  FIG. 14 . 
         FIG. 17  schematically illustrates an electromagnetic clutch mechanism. 
         FIG. 18  schematically illustrates a solenoid control system. 
         FIG. 19  is a schematic illustration of a vehicle system according to another embodiment. 
         FIG. 20  is a schematic illustration of a dual mode component for various accessories on a vehicle engine. 
     
    
    
     DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     For the purpose of promoting and understanding the principles of the present invention, reference will now be made to the embodiments illustrated in the drawings and specific language will be used to describe them. It will nevertheless be understood that no limitation as to the scope of the invention is hereby intended. The invention includes any alternatives and other modifications in the illustrated devices and described methods and further applications of the principles of the invention which would normally occur to persons of ordinary skill in the art to which the invention relates. 
     The present inventions described herein particularly relate to hybrid coolant pumps which are used to circulate the coolant in an engine, such as an automobile internal combustion engine. However, the present invention can also be used for other engine accessory devices, such as air conditioning compressors, engine oil pumps and transmission oil pumps, etc. Also, several components, mechanisms and systems described herein, including, but not limited to, the compression spring, the solenoid actuated friction clutch and/or the PWM control system, can have significant uses in other devices and systems. 
     As a coolant pump, the pump is electrically driven under most conditions. However, it also can be mechanically engaged where more cooling is required. Thus, when the vehicle is being driven under most normal conditions, the water pump is being driven and operated by the electric motor. 
     During “worst case” cooling conditions, such as when the vehicle is heavily loaded, when it is pulling a trailer, when it is going up hill in the summertime, etc., the water pump is adapted to be mechanically driven by the belt directly from the engine. This provides the necessary cooling under such circumstances. 
     In accordance with a preferred embodiment of the invention, the electric motor is a brushless DC (BLDC) motor and the motor is positioned inside a pulley assembly. The pump is also adapted to be driven mechanically when needed by the engine belt, such as a serpentine belt, attached to the crankshaft of the engine. 
     The preferred embodiment of the present invention as described herein is particularly adapted for use with trucks, passenger cars and off-highway vehicles. Since the preferred embodiment also provides variable speed control of the water pump, it uses less power from the engine and thus improves fuel economy and reduces emissions. 
     A hybrid water pump embodiment in accordance with the present invention is shown in  FIG. 1  and referred to generally by the reference numeral  20 . The hybrid water pump includes a pulley assembly  22  and a water pump housing  24 . The pulley assembly  22  has a clutch housing member  26  and a pulley member  28 . The pulley member  28  has circumferential grooves  30  for being driven by a belt (not shown). 
     A cross-sectional view of the water pump  20  is shown in  FIG. 2  and an exploded view of the components of the water pump  20  is shown in  FIG. 3 . 
     The water pump has an impeller shaft  40  which is positioned within the pulley assembly  22  and also is attached to a water pump impeller  42 . The impeller shaft  40  is held in place in the pump housing  24  by needle bearing  44  and middle bearing  84 . A coolant seal  46  is used to prevent coolant in the pump from leaking into the pulley assembly. 
     A motor stator  50  is positioned inside a stator housing  52  in the pulley assembly  22 . A nut, such as a spanner nut  54 , is used to hold the stator housing  52  to the pump housing  24 . 
     A second needle bearing  60  is positioned between the pulley member  28  and the pump housing  24  in order to allow the pulley assembly  22  to rotate freely relative to the pump housing. 
     A motor rotor  70  is positioned inside a front bearing carrier  72 , which preferably is made from an aluminum material. The motor is preferably a brushless DC (BLDC) electric motor. A solenoid member  80  is positioned immediately adjacent the front bearing carrier  72 . A friction clutch assembly  90  is positioned adjacent the front cover of the motor housing  22  and operated by the solenoid member  80 . Bearing member  84  is positioned between the bearing carrier  72  and the impeller shaft  40 . 
     A fastening member such as a hex nut  92  secures the pulley assembly  22  to the impeller shaft  40  via the front bearing  82 . As indicated particularly in  FIGS. 2 and 3 , the pulley assembly  22  consists of two pieces, namely a pulley member  28  and clutch housing  26 . This configuration provides for distribution of the belt load between the rear needle bearing  60  and the front ball bearing  82 , thereby eliminating overhung bearing loads. Consequently, the bearing loads are minimized resulting in a more durable and long-lasting product. 
     As indicated, the water pump is normally driven by the electric motor. The electric motor is electrically powered through a circuit board (not shown) connected to pin-type contact members  86 . Electrical leads and wires can be insert molded in housing  25  and lead frame  29  in order to carry the electrical signals to the electric motor stator  50  and solenoid  80 . The circuit board further communicates with the electronic control unit (ECU) of the vehicle through the vehicle communication network such as a CAN network. The pump controller circuit board could also be positioned inside the pulley assembly  22  rearward of the stator housing  52  and having a donut shape. 
     The speed of the motor and thus the water pump is selected according to the cooling required for the engine. Sensors feed relevant data to the ECU which then sends a signal to the pump controller requesting the desired speed. The pump controller then determines whether the desired speed is best achieved using the electric motor or by engaging the friction clutch and driving the impeller directly from the pulley. 
       FIG. 13  is a graph  200  schematically illustrating the functional modes of the hybrid pump. The speed of the engine is shown along the X-axis and the speed of the impeller is shown along the Y-axis in  FIG. 13 . Both speeds are shown in revolutions per minute (RPM). 
     The principal electric drive mode of the hybrid pump drive is shown at  206 . Peak torque is achieved by electric motor  208 . Full pulley drive (a/k/a “belt drive”) is shown by line  210 . Here the pump is being driven mechanically by the engine through the accessory belt. The slope of line  210  may be changed by modifying the pulley ratio between the engine crank pulley and the pump pulley member  28 . 
     An optional electrical drive area is shown at  212 . This area represents the region in which the electric motor is able to provide an “over-drive” feature where the pump can be spun at speeds greater than the mechanical input speed. The regions  214  and  216  are due to the efficiency loss in the electric drive mode from converting mechanical energy to electrical energy in the alternator and then back to mechanical energy in the electric motor. Although the pump could be operated electrically in regions  214  and  216 , it is more energy efficient for the pump to jump to the mechanical drive mode  210 . In  202 , the pump is OFF and the impeller is not rotating. In this embodiment, the pump is OFF regardless of the speed of the engine. It is also possible to drive the pump electrically when the engine is turned off. This is shown at  220 . 
     An enlarged view of the friction clutch  90  is shown in  FIG. 4 , while an exploded view of the components of the friction clutch  90  is shown in  FIG. 5 . The friction clutch  90  includes a clutch carrier member  100 , a flux plate member  102 , a compression spring member  104 , and a friction lining carrier member  106 . Pieces of friction lining material  108  are attached to its outer circumference of the carrier  106 , as shown in  FIG. 4 . The friction lining members  108  can be of any conventional friction material and can be of any size and shape. Although the friction lining material is shown with a plurality of separate members, as shown in  FIGS. 4 and 5 , the friction lining can be a single piece or any number of separate members positioned around the circumference of the friction lining carrier member  106 . 
     The friction lining material will wear over time as the hybrid pump is utilized. As this takes place, the capacity of the friction clutch  90  will increase due to the design of the compression spring member  104  which develops more force as the lining material wears. 
     An enlarged view of one embodiment of a compression spring member  104  is shown in  FIG. 6 . The spring member  104  is a “softening” spring member since the force necessary to compress it decreases over time once it reaches a certain peak. 
     The spring member  104  has a plurality of holes or openings in order to be attached to the friction lining carrier member and the clutch carrier member. In this regard, a series of four holes  110  are provided on the compression spring member  104  in order to mate with openings  112  in the friction lining carrier member  106 . A plurality of rivets  114  or the like are used to secure the compression spring member  104  to the friction lining carrier member  106 . The compression spring member can be joined to the friction lining carrier member by any conventional method, such as by welding, brazing, threaded fasteners, etc. 
     The second series of openings in the compression spring member include four openings  120 . These openings mate with corresponding post members  122  on the clutch carrier member  100 . The post members  122  are deformed or swaged over when the friction clutch assembly  90  is assembled in order to securely hold the components of the friction clutch assembly together. 
     When the friction clutch assembly  90  is in the engaged position, torque is transferred from the pulley assembly  22  through the friction lining members  108  to the friction lining carrier  106 . The friction lining carrier then transfers torque through the compression spring member  104  to the clutch carrier  100  which turns the impeller shaft. 
     The compression spring member embodiment  104  has an outer ring member  130  and an inner ring member  132 . The two ring members  130  and  132  are connected together by a plurality of connecting members  134 ,  135 ,  136  and  137 . Enlarged portions of the compression spring member  90  are shown in  FIGS. 8 and 9 . When the spring member  104  is assembled in the friction clutch assembly  90 , the outer and inner ring members  130  and  132 , respectively, are held securely in place and are fixed so they cannot be moved radially toward or away from each other during operation of the friction clutch assembly. 
     In  FIG. 8 , the compression spring member is shown in the uncompressed position. This is also shown in  FIGS. 6 and 7 . 
     When the spring member  90  is compressed to the position  142  shown in  FIG. 10 , the spring member forces the friction lining carrier member  106  and friction lining members  108  against the conical friction surface  109  ( FIG. 2 ) inside of the clutch housing member  26  causing mechanical operation of the water pump. The clutch housing member  26  can be aluminum and the conical friction surface can be thermal spray coated with a variety of materials such as low carbon steel. 
     When the friction clutch assembly  90  is energized by the solenoid  80 , the flux plate  102  is attracted to the solenoid assembly due to the force developed in the air gap between the solenoid core  81  and the flux plate. As the flux plate  102  moves toward the solenoid, the compression spring member  104  is compressed separating the friction lining carrier member  106  and friction members from their engaged positions against the inside surface of the clutch housing member  26 . In the compressed condition, the connecting members  134 ,  135 ,  136  and  137  are buckled and distorted such as in the manner schematically depicted in  FIG. 9 . In this position, the water pump is operated only by the electric motor. 
     The flux plate  102  is securely attached to the friction lining carrier  106  through tabs  107  ( FIG. 4 ). The attachment of the flux plate and friction lining carrier may be through any conventional joining technique such as spot welding, screws, rivets, or the like. 
     Axial travel of the clutch assembly is limited by the engagement of tabs  103  on the flux plate  102  within pockets  101  on the clutch carrier member  100  ( FIG. 5 ). This axial travel limit prevents the pole plate from coming into contact with the solenoid core member  81  as the pole plate rotates with impeller speed and the solenoid core is stationary. 
     The load/deflection curve of the compression spring member  104  in accordance with a preferred embodiment is shown in  FIG. 10 . As shown in  FIG. 10 , the load/deflection curve  140  reaches quickly to a maximum amount of force  140 A and then needs less force in order to continue to deflect the spring member after it is starting to buckle and deform. This is shown by the second part of the curve  140 B. This means that once the compression spring has reached point  140 A, less force is needed to further deflect the spring and thus prevent the friction clutch assembly from contacting the inside of the housing. In this regard, the clutch engaged position is shown at point  142 , the working load of the spring is indicated by line  144 , the working length of the spring is shown by line  146 , and the clutch disengaged position is shown at point  148 . Thus, once the maximum amount of force necessary to buckle or deform the spring is reached, increasingly less force is necessary in order to deflect the spring further and thus allow complete operation of the water pump by the electric motor. The softening spring member thus enables the parasitic electric power consumption of the clutch disengagement solenoid  80  to be minimized. This is accomplished by pulse width modulating (“PWM”) the current supplied to the solenoid. To disengage the solenoid the solenoid drive controller operates the solenoid drive Field Effect Transistor (“FET”) at 100% PWM so full current is supplied to the solenoid. The controller has a current sensing technology such that when the clutch seats in the fully disengaged position it is able to sense the current change indicating the clutch is disengaged. At this point, the controller drops the PWM to a smaller level such as 10%, so less current is consumed by the solenoid. Since the compression spring  104  develops much less force in this position  148  as shown in  FIG. 10  and the magnetic circuit is much more efficient as the air gap is smaller, the lower current level is still adequate to keep the clutch in the disengaged position. 
     It is quite common in automotive accessories such as air conditioning compressors, pumps, etc. to use spring engaged, electromagnetically disengaged clutches to selectively turn on and off the drive to the accessory component. This is typically done to conserve energy when the device is not needed. These devices are typically designed to be spring engaged so the accessory device is powered in the event of a control failure such as a loss of electrical power. This is done to provide “Fail-Safe” functionality meaning that the device defaults to its “on” state when it is unpowered. 
     The primary disadvantage of these “Fail-Safe” clutch designs is that they require continuous electrical power to keep the device disengaged when it is not needed. For many accessory devices this condition can constitute a large percentage of their operating life. Furthermore, these devices often require 20+ watts of electrical power, which can be a significant portion of the alternator output. On modern vehicles which employ a large number of electrical components (seat heaters, window defrosters, electric seats, and a host of other devices), it is not uncommon to exceed the maximum power capacity of the alternator. 
     A preferred embodiment of the present invention provides a means of mitigating this problem by minimizing the parasitic power consumed by electromagnetically disengaged clutches. Fundamentally this arrangement takes advantage of the physical relationship between the force developed in the air gap of a magnetic circuit and the length of the air gap. This relationship is described by the following Equation where m 1  and m 2  are the respective field strengths of the two poles of the magnetic circuit, μ is the permeability of the free space and r is the distance between the poles. 
     
       
         
           
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                   m 
                   1 
                 
                 ⁢ 
                 
                   m 
                   2 
                 
               
               
                 4 
                 ⁢ 
                 
                     
                 
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                 π 
                 ⁢ 
                 
                     
                 
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                   r 
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     From the equation it is evident that the field strength falls off with the square of the distance between the magnet poles. Furthermore, it evident from  FIG. 17  that the spring force used to engage the clutch will increase linearly when the solenoid is energized and the air gap closes. This means that the solenoid will have excess capacity in its closed position since the magnetic field strength increases with the square of distance and the counteracting spring force only increases linearly with distance. Since the field strength of the magnetic poles are related to the current flowing through the coil and the number of coil turns, it is evident that less current is required to hold the clutch in the disengaged position than what is required to pull the clutch out of engagement. Furthermore, if the clutch engagement spring is designed in such a way that the spring softens as it is compressed as described herein, this effect will be even further pronounced. 
     To capitalize on this condition, the present invention employs a PWM (Pulse Width Modulation) control system for the solenoid as shown in  FIG. 18 . The PWM control system uses a PWM Driver (typically a Field Effect Transistor and supporting circuitry) to pulse the solenoid power on and off at a very high speed, typically on the order of a few hundred hertz. Since the solenoid provides a relatively large inductance which prevents the current from changing instantaneously, this has the effect of reducing the average current delivered to the solenoid. The average current level can then be controlled by varying the duty cycle of the PWM Driver. 
     With this methodology, the PWM Driver is used to apply 100% duty cycle or full current to the solenoid to generate the maximum force in the air gap to pull the clutch out of engagement. Once the clutch is in the disengaged position, the duty cycle can be reduced to a much lower level, effectively reducing the average current supplied to the solenoid and consequently reducing the power consumption. 
     The PWM Driver can furthermore incorporate current sensing technology in such a way that a microcontroller is able to monitor the current supplied to the solenoid. This is advantageous in that a current spike will be evident on the solenoid supply line when the moving pole of the solenoid seats against the travel limit. This current spike can be used as a signal to the microprocessor that the clutch is in its retracted position and the duty cycle can be reduced. 
       FIG. 19  is a schematic illustration of a vehicle system  300  according to one embodiment. The vehicle system may include a combustion engine  312 , a radiator  314 , and a coolant pump  316  connected to the combustion engine  312  and constructed and arranged to flow coolant through coolant passages defined in the engine. Plumbing  318  is provided from the radiator to the coolant pump  316  and plumbing  320  is provided from the coolant pump  316  back to the radiator  314 . A fan  322  may be provided and positioned to force air over the radiator  314  including radiator fins to remove heat from the radiator and coolant flowing through the radiator  314 . A dual mode component  324  is provided and is constructed and arranged to be driven or powered by both mechanical power and electrical power. The dual mode component  324  in  FIGS. 19 and 20  may be connected to at least one of the coolant pump  316  or the fan  322  to operatively drive the same. In one embodiment, the coolant pump  316  and the dual mode component  324  are contained in a common housing. 
     Preferably, the dual mode component is the dual mode cooling pump  20  as described above and has the same structure, benefits and features as described above ( FIGS. 1-18 ). In accordance with the embodiments as set forth in  FIGS. 19 and 20 , the dual mode component  324  can be connected to either a coolant pump or a cooling fan and operational to drive either one. 
     In various other embodiments, the dual mode component  324  may be used to drive an air conditioning system coolant compressor pump, an engine oil pump and/or a transmission oil pump. As illustrated in  FIG. 20 , an air conditioning system coolant compressor pump propeller component  346 , an engine oil pump propeller component  348  and/or a transmission oil pump propeller component  350  may be connected to and driven by the shaft  340  of the dual mode component  324  to drive the air conditioning system coolant compressor pump, an engine oil pump and a transmission oil pump, respectively. These components also may have two or more separate drive shafts. 
     Referring again to  FIG. 19 , in one embodiment, an alternator  326  which is mechanically driven by the engine  312  may supply electrical power to the dual mode component  324 . In another embodiment, a battery  327  may supply electrical power to the dual mode component  324 . 
     In one embodiment, lost energy may be recovered from the vehicle system  300  and stored in a battery  327  so the electrical power may be supplied or delivered from the battery as desired to the electrical motor  342  of the dual mode component  324 . Both mechanical energy and thermal energy may be recovered from the vehicle system  300 . For example, the vehicle system  300  may include a plurality of brakes  328  and a mechanical energy recovery component  330  connected to the brakes  328  to recover lost mechanical energy during braking. A generator  331  may be provided to produce electrical energy from the recovered mechanical energy. An electrical converter  334  may be connected to the generator  331  and to the battery  327  to store electrical energy in the battery  327 . Similarly, a thermal energy recovery component  332  may be provided and positioned, constructed and arranged to recover thermal energy from a number of different vehicle components such as, but not limited to, the radiator  314 , engine  312  or other components producing heat such as the transmission, exhaust system, turbocharger compressors and the like. In one embodiment, the thermal recovery component may be a transducer, such as a PNP device, connected to the radiator to change thermal energy to electrical energy. 
     An electronic control module (ECM)  336  may be provided and connected to a plurality of vehicle component systems including, but not limited to, the battery  327 , electrical converter  334 , generator  331 , mechanical energy recovery component  330 , and/or thermal energy recovery component  332 , and may include hardware and software constructed and arranged to control such components including the storage and release of energy from the battery  327 . If desired, a second electronic control module (SECM)  337  may be provided and connected to the battery  327  and the dual mode component  324  to control the operation of the electrical motor  342  of the dual mode component  324 . The SECM  337  may include hardware and software constructed and arranged to carry out a variety of operating processes associated with the vehicle system  300  and the dual mode component  324 . 
     ECM  336  and SECM  337  each may receive and process input from the various sensors in light of stored instructions and/or data, and transmit output signals to various actuators. Sensors for this purpose are indicated by  346 ,  348  and  350  in  FIG. 19 . ECM  336  and SECM  337  may be operated independently of one another or SECM  337  may be a slave to ECM  336  in at least some operations and process control situations. ECM  336  and SECM  337  each may include, for example, an electrical circuit, an electronic circuit or chip, and/or a computer. In an illustrative computer embodiment, ECM  336  and SECM  337  each generally may include one or more processors, memory devices that may be coupled to the processor(s), and one or more interfaces coupling the processor(s) to one or more other devices. Although not shown, the processor(s) and other powered system devices may be supplied with electricity by a power supply, for example, one or more batteries, fuel cells, or the like. 
     The processor(s) may execute instructions that provide at least some of the functionality for the disclosed system  300  and methods. As used herein, the term instructions may include, for example, control logic, computer software and/or firmware, programmable instructions, or other suitable instructions. The processor may include, for example, one or more microprocessors, microcontrollers, application specific integrated circuits, programmable logic devices, field programmable gate arrays, and/or any other suitable type of electronic processing device(s). Processors of this type are also preferred for the dual mode cooling pump  20  as described above with reference to  FIGS. 1-18 . 
     Also, the memory device may be configured to provide storage for data received by or loaded to the engine system, and/or for processor-executable instructions. The data and/or instructions may be stored, for example, as look-up tables, formulas, algorithms, maps, models, and/or any other suitable format. The memory may include, for example, RAM, ROM, EPROM, flash, and/or any other suitable type of storage article and/or device. 
     Further, the interfaces may include, for example, analog/digital or digital/analog converters, signal conditioners, amplifiers, filters, other electronic devices or software modules, and/or any other suitable interfaces. The interfaces may conform to, for example, RS-232, parallel, small computer system interface, universal serial bus, CAN, MOST, LIN, FlexRay, and/or any other suitable protocol(s). The interfaces may include circuits, software, firmware, or any other device to assist or enable ECM  336  and SECM  337  each in communicating with other devices. 
     The methods or parts thereof may be implemented in a computer program product including instructions carried on a computer readable medium for use by one or more processors to implement one or more of the method steps. The computer program product may include one or more software programs comprised of program instructions in source code, object code, executable code or other formats; one or more firmware programs; or hardware description language (HDL) files; and any program related data. The data may include data structures, look-up tables, or data in any other suitable format. The program instructions may include program modules, routines, programs, objects, components, and/or the like. The computer program may be executed on one processor or on multiple processors in communication with one another. 
     The program(s) can be embodied on computer readable media, which can include one or more storage devices, articles of manufacture, or the like. Illustrative computer readable media include computer system memory, e.g. RAM (random access memory), ROM (read only memory); semiconductor memory, e.g. EPROM (erasable, programmable ROM), EEPROM (electrically erasable, programmable ROM), flash memory; magnetic or optical disks or tapes; and/or the like. The computer readable medium also may include computer to computer connections, for example, when data is transferred or provided over a network or another communications connection (either wired, wireless, or a combination thereof). Any combination(s) of the above examples is also included within the scope of the computer-readable media. It is therefore to be understood that the method may be at least partially performed by any electronic articles and/or devices capable of executing instructions corresponding to one or more steps of the disclosed methods. 
     Empirical models may be developed from controlling the operation of various components including, but not limited to, the dual mode components  20  and  324  and can include lookup tables, maps, and the like that may cross reference cylinder pressure with oxygen concentration. As used herein, the term “model” may include any construct that represents something using variables, such as a look up table, map, formula, algorithm and/or the like. Models may be application specific and particular to the exact design and performance specifications of any given engine system. In one example, the engine system models in turn may be responsive to engine speed and intake manifold pressure and temperature. 
     As described above with references to  FIGS. 1-20 , one embodiment of the invention includes a method of operating a vehicle cooling system including at least one dual mode component comprising supplying electrical power and mechanical power at the same time to the at least one dual mode component to drive the same. Another embodiment includes a method of operating a system including a combustion engine, a cooling system including a radiator and a fan positioned to force air onto the radiator, plumbing connected to the radiator and the engine to deliver coolant from the radiator to the engine and back to the radiator, at least one dual mode component constructed and arranged to operate using electrical and mechanical power, at least one dual mode component connected to at least one of the fan or pump to drive the same, the mechanical power being provided directly or indirectly by the engine, comprising supplying mechanical power to the dual mode component to drive the same and during rapid engine transients, such as the rapid acceleration of the vehicle, also supplying electrical power at the same time mechanical power is being supplied to the dual mode component to assist in driving the dual mode component. 
     Another embodiment includes a method of operating a vehicle system comprising a dual mode component constructed and arranged to be driven by mechanical power and electrical power, comprising controlling the dual mode component so that neither mechanical power nor electrical power is supplied during rapid engine transients and thereafter supplying both electrical power and mechanical power at the same time. 
     Another embodiment includes a method of operating a vehicle system comprising a dual mode component constructed and arranged to be driven by mechanical power and electrical power, comprising supplying only electrical power to the dual mode during rapid engine transients and thereafter supplying both electrical power and mechanical power at the same time. 
     Another embodiment includes a method of operating a vehicle system comprising a dual mode component constructed and arranged to be driven by mechanical power and electrical power, comprising supplying electrical power and mechanical power at the same time to at least one dual mode component to drive the same, and thereafter, upon deceleration of the vehicle supplying only electrical power produced from an alternator or a battery to the dual mode component. Another embodiment includes a method including operating a dual mode component for a vehicle cooling system, the vehicle system including a dual mode component including mechanical power delivery device including a clutch constructed and arranged to gradually engage and drive the dual mode component using mechanical power, the dual mode component including an electric mode for driving the dual mode component, comprising engaging the clutch to provide mechanical power to the dual mode component and supplying electrical power to the dual mode component during clutch engagement. This method reduces engagement torque of the clutch thereby increasing life of the clutch, reducing cost and preventing slippage. 
     A preferred method of operation is to synchronize the speeds of the electrical and mechanical modes of operation before switching from one to the other. In order to reduce engine “knock”, it is preferable to switch the mode of operating the cooling pump to the mode which provides the highest cooling capacity. 
     Another embodiment includes a dual mode component for a vehicle cooling system by supplying electrical power to the dual mode component to drive the same during clutch engagement to drive the dual mode component using mechanical power, wherein the amount of electrical power supplied to the dual mode component during clutch engagement is such that the speed of a shaft rotating in the dual mode component is the same as the speed that the shaft would be if the dual mode component were operated by mechanical power at the engine speed and at the time the clutch is engaged, and thereafter reducing the electrical power supplied to the dual mode component in one of a step or ramp fashion until no electrical power is being supplied to the dual mode component and the dual mode component is being driven by only mechanical power. 
     Another embodiment includes a method wherein the system includes a battery or capacitor and wherein supplying electrical power comprises delivering electrical power from the battery or capacitor. 
     Another embodiment includes a method comprising recovering energy from a first vehicle component, converting the energy to electrical power, storing the electrical power in a battery, and supplying electrical power from the battery to the dual mode component constructed and arranged to drive a second vehicle component using mechanical power and electrical power. 
     Another embodiment includes a method wherein the first vehicle component comprises a braking system. 
     Another embodiment includes a method comprising recovering thermal energy from a vehicle component, converting thermal energy to electrical power, storing the electrical power in a battery, and supplying electrical power from the battery to the dual mode component constructed and arranged to drive a second vehicle component using mechanical power and electrical power. A method of operating a vehicle system comprising determining when an engine of the vehicle system is accelerating at first rate or greater than the first rate, and if so, supplying electrical power to a dual mode component while the dual mode component is also being driven by mechanical power. 
     Another embodiment includes a method of operating a vehicle system, the vehicle system including a battery and a dual mode component connected to the battery, measuring the remaining capacity of the battery to store additional energy, and if the remaining capacity is at or less than a first amount or capacity, then supplying electrical energy from the battery to the dual mode component to drive the dual mode component and to utilize a portion of the energy that was stored in the battery thereby freeing up capacity in the battery to store energy from mechanical and thermal energy recovery components. 
     Another embodiment includes a method wherein the dual mode component is being driven also by mechanical energy during the supplying electrical energy from the battery to the dual mode component to drive the dual mode component and to utilize a portion of the energy that was stored in the battery. 
     The vehicle system may include software, hardware, actuators and switches to operate and control component as necessary to perform the various methods described above. 
     An alternate form of a compression spring  160  is shown in  FIG. 11 . In this embodiment, a series of connector members  162  are positioned between an outer ring  164  and an inner ring  166 . When compression spring member  160  is used in a friction clutch assembly, the outer and inner ring members  164  and  166  respectively, are constrained and fixed in place. The inner connecting members  162  are comprised of radial compression beams  163  and tangential flex arms  165 . When the spring is compressed, the tangential flex arms deform allowing the radial gaps  167  to close as the spring flattens. 
     Another alternate embodiment of a compression spring member which can be used with the present invention is shown in  FIG. 12 . The spring member  104 ′ is similar to spring member  104  described above, but does not have outer or inner ring members. Instead, spring member  104 ′ has a plurality of connecting members  134 ′,  135 ′,  136 ′ and  137 ′ which extend between the areas  105  of the openings  110 ′ and  120 ′. The latter openings  110 ′ and  120 ′ are the same as, in the same locations as, and for the same functions and purposes as, openings  110  and  120  in  FIGS. 4-6 . 
     When the compression spring member  104 ′ is utilized in a friction clutch assembly, the connecting members  134 ′,  135 ′,  136 ′ and  137 ′ deform and buckle similar to connecting members  134 - 137  described above providing a similar “softening” spring member. 
     Another compression spring member (not shown) can be similar to the spring member  104  in  FIG. 6 , but only comprise an inner ring member or an outer spring member (i.e. not both), together with a plurality of connecting members. 
     Another “softening” compression spring mechanism is shown in  FIG. 14 , with one of its components being shown in  FIGS. 15 and 16 . This mechanism  250  has a series of three “buckling beam” spring members  252 ,  253 ,  254 . The three beam spring members are also referred to collectively by the reference numeral  258 . As shown in  FIG. 14 , the beam members  252 - 254  are indicated as being adapted to be attached to an inner ring member  260  and an outer ring member  262 . When the beam members are used in a friction clutch mechanism, such as friction clutch member  90  described above, the ring members will be replaced by a clutch carrier member and a friction lining carrier. 
     When the beam spring members  258  are attached to outer ring members or carrier members, fastener members (not shown) will be positioned and secured in the aligned openings  270  and  280 . The fastener members can be any conventional type, but preferably are rivets. The openings can also be positioned over swagable post members in a manner as discussed above. 
     As shown in  FIGS. 15 and 16 , each of the beam spring members  252 - 254  preferably are thin pieces of spring steel material having the shape and structure shown. The beam spring members have a curved shape from a side view, as shown in  FIG. 16 , with flat areas  272 ,  274 ,  276  where the attachment holes  273 ,  275 ,  277  are located. 
     The compression spring mechanism  250 , or at least the group  258  of buckling beam spring members, can be used in the same manner and for the same purposes as the compression spring members  104 ,  104 ′ and  164  described above. The beam spring members  258  can buckle and deform under loads when the outer and inner ring members (or the clutch carrier member and friction lining carrier member) are forced toward each other in operation of the water pump. 
     As indicated above, the present invention provides a “fail safe” friction clutch design. If the electrical system of the vehicle were to fail, the solenoid would be de-energized allowing the spring  104  to engage the friction clutch assembly to the clutch housing. Therefore the pump would operate in mechanical mode with the impeller driven by the pulley through the clutch assembly. The clutch is thus engaged whenever circulation of coolant is needed. 
     Another design feature of the present invention is its modular assembly configuration. It is common for coolant pump housings to vary widely in form and configuration from application to application. In order to accommodate this wide variation of housing configurations with minimal design changes, the hybrid pump was designed so the water pump housing  24  can be easily changed while the pulley assembly  22  and the components contained within it can remain largely unchanged. 
     Although the invention has been described with respect to preferred embodiments, it is to be also understood that it is not to be so limited since changes and modifications can be made therein which are within the full scope of this invention as detailed by the following claims.