Abstract:
The present invention is directed to a dual fuel system and a dual fuel system assembly where liquid LPG and diesel are mixed and then distributed via the common rail to the combustion chambers. The liquid fuel mixture remains in a liquid state and under pressure for introduction to the combustion chambers. With the preferred embodiment of the dual fuel system, only minor changes are required to the diesel engine without altering the manufactures specifications and voiding the manufacturer&#39;s warranties. The resultant combustion of the liquid fuel mixture provides a cleaner emission and relatively cheaper vehicle operational costs.

Description:
FIELD OF INVENTION 
       [0001]    The present invention relates to diesel engines and fuel systems for diesel engines. The present invention has particular but not exclusive application for use with trucks. 
       BACKGROUND OF THE INVENTION 
       [0002]    Trucks and in particular long haul trucks use large volumes of diesel fuel in transporting goods. As the price of diesel increases, the cost of freighting goods also increases. While at least part of the increase in costs is passed on to the end consumer, market forces have caused the truck operator to absorb much of the additional costs thereby reducing their profit margin. Consequently alternative fuel sources have been investigated. 
         [0003]    LPG (Liquid Petroleum Gas) has been used as an alternative fuel source for diesel engines. While LPG is stored under pressure (approximately 150 psi) in the tank which maintains the LPG in a liquid state, LPG is usually used in a gaseous state at pressures well below 140 psi which is the pressure required to maintain LPG in a liquid state. 
         [0004]    LPG has also been used with diesel in dual fuel systems. In US2005205021 a separate set of injectors introduce gaseous LPG into the combustion chamber, whereas in U.S. Pat. No. 5,408,957, U.S. Pat. No. 4,520,766, JP1318755 and GB1252458, gaseous LPG is mixed with air prior to introducing the air mixture to the combustion chamber. 
         [0005]    The problem with using LPG as the sole fuel source for diesel engines is that the engines need substantial modification to overcome the reduction in lubricity with the use of LPG and the ability to provide the combustion of the LPG. Modification of engines is a major expense and voids the warranties from the engine manufacturer. Even with LPG and diesel dual fuel systems, diesel engines need to be modified to allow the introduction of LPG into the combustion chamber. 
       OBJECT OF THE INVENTION 
       [0006]    It is an object of the present invention to provide an alternative dual fuel system that overcomes at least in part the abovementioned problems. 
       SUMMARY OF THE INVENTION 
       [0007]    The present invention arose from taking an alternative approach by understanding the effects of pressure on LPG and developing a different solution to dual fuel systems using pressurized LPG and without substantially modifying the diesel engine. 
         [0008]    In one aspect the present invention broadly resides in a dual fuel system for use by an internal combustion diesel engine including 
         [0009]    a fuel tank to store pressurized liquefied gas; 
         [0010]    a proportioning valve means operatively connected to the fuel tank and adapted to control the flow of the liquefied gas; and 
         [0011]    a mixing chamber operatively connected to the proportioning valve and adapted to mix a proportioned flow of the liquefied gas and a proportioned flow of diesel to form a liquid fuel mixture, wherein the liquid fuel mixture remains under pressure and is introduced into a combustion chamber of the diesel engine. 
         [0012]    In another aspect the present invention broadly resides in a dual fuel system assembly for installation with an internal combustion diesel engine including 
         [0013]    a fuel tank to store pressurized liquefied gas; 
         [0014]    a proportioning valve means operatively connectable to the fuel tank and adapted to control the flow of the liquefied gas; and 
         [0015]    a mixing chamber operatively connectable to the proportioning valve and adapted to mix a proportioned flow of the liquefied gas and a proportioned flow of diesel to form a liquid fuel mixture, wherein in use the assembly can provide the liquid fuel mixture to a combustion chamber of the diesel engine. 
         [0016]    The proportioning valve means preferably includes a flow control valve operatively controlled by an electronic control board. The electronic control board preferably controls the flow control valve in response to processed information from the vehicle electronic control unit. 
         [0017]    Preferably the diesel fuel is pressurized prior to entering the mixing chamber. The diesel fuel is preferably pressurized by an inline pump and the fuel is stored within a pressurized tank prior to use. Preferably the supply of pressurized diesel fuel to the mixing chamber is regulated by a flow control valve that is operatively controlled by an electronic control board. The electronic control board is preferably controlled by the vehicle electronic control unit that receives and processes information to provide a relevant signal to the electronic control board. 
         [0018]    The liquefied gas is preferably filtered before the proportioning valve with an inline filter. 
         [0019]    Preferably the LPG tank, proportioning valve means and mixing chamber are linked by a gas pipeline. 
         [0020]    The pipeline between the LPG tank and proportioning valve preferably includes at least one closeable valve. In a preferred embodiment there is a one-way non-return valve and a closeable valve within the line between the LPG tank and the proportioning valve means. 
         [0021]    The dual fuel assembly may be fitted prior to delivery of a diesel engine vehicle or fitted as an after market kit. 
         [0022]    The liquefied gas may be LPG, propane, natural gas or compressed natural gas. 
         [0023]    Preferably the liquefied gas tank stores LPG under pressure of about 150 psi but above its vapor pressure of 80 psi. 
         [0024]    In a further aspect the invention broadly resides in an internal combustion diesel engine with dual fuel system including 
         [0025]    a first tank to store pressurized liquefied gas; 
         [0026]    a second tank to store pressurized diesel; 
         [0027]    a first proportioning valve means operatively connected to the first tank and adapted to control the flow of the liquefied gas; 
         [0028]    a second proportioning valve means operatively connected to the second tank and adapted to control the flow of the diesel; 
         [0029]    a mixing chamber operatively connected to the first proportioning valve means and second proportioning valve means, said mixing chamber is adapted to mix a proportioned flow of the liquefied gas and a proportioned flow of diesel to form a liquid fuel mixture, and 
         [0030]    distribution means for distributing the liquid fuel mixture to each internal combustion chamber, wherein an engine processor controls the proportioning of the fuels by regulating the respective proportioning valve means in accordance with demand. 
         [0031]    The abovementioned preferred embodiments for the features of the dual fuel system and dual fuel system assembly also apply for this aspect of the invention. 
         [0032]    The second tank preferably receives pressurized diesel via an inline filter and pump from a diesel fuel tank. 
         [0033]    The second proportioning valve means preferably includes a flow control valve operatively controlled by an electronic control board. The electronic control board preferably controls the flow control valve in response to processed information from the vehicle electronic control unit. The vehicle electronic control unit receives and processes input regarding the demand of fuel by the engine. 
         [0034]    Preferably there is an accelerometer means that measures the acceleration of the vehicle and whether the vehicle is traveling up or down an incline. Input from the accelerometer means preferably operatively regulates the diesel and liquefied gas flow control valves via the respective electronic control boards. The accelerometer inputs are preferably processed by the electronic control unit. 
         [0035]    The ratio of LPG to diesel may vary between 50:50 and 90:10 respectively. More preferably the ratio of LPG to diesel is approximately 70:30 respectively. Preferably any ratio is suitable providing the engine components are not prematurely worn because of lack of lubricity and the manufacturer&#39;s warranties are not voided and the calorific value of the fuel is sufficient to allow the engine to produce an acceptable amount of power and torque. 
         [0036]    The liquid fuel mixture is preferably pumped to a common rail operable under high pressure so that the liquid fuel mixture remains in a liquid state. The phrase common rail in the specification includes common rails and fuel rails. Preferably, the common rail is connected to an injector for each combustion chamber and the fuel mixture is distributed to each of the injectors for combustion in accordance with the manufacturer&#39;s specifications. 
         [0037]    Preferably the fuel mixture is filtered prior to distribution in the common rail. 
         [0038]    Excess unburnt fuel mixture is preferably collected in a overflow tank and returned to the mixing chamber for combustion in the combustion chamber. More preferably, excess fuel mixture is returned via a fuel temperature sensor to a fuel pressure limiter then to an overflow valve and a pressure limiting valve. Excess fuel is then preferably passed through a fuel cooler and maintained under pressure in a pressurized tank for subsequent reintroduction into the mixing chamber. 
         [0039]    Preferably there is a separate line from the diesel tank to the supply pump and subsequently to the common rail for the engine to use diesel as the sole fuel source. 
         [0040]    In another aspect the invention broadly resides in a method of using the above mentioned dual fuel system for an internal combustion diesel engine including 
         [0041]    proportioning flow of liquefied gas from the first tank with the first proportioning valve means; 
         [0042]    proportioning flow of diesel from the second tank with the second proportioning valve means; 
         [0043]    mixing proportioned fuels to form a liquid fuel mixture in the mixing chamber; 
         [0044]    distributing the liquid fuel mixture from the mixing chamber to each of the combustion chambers. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0045]    In order that the present invention can be more readily understood and put into practical effect, reference will now be made to the accompanying drawings wherein: 
           [0046]      FIG. 1  is a diagrammatic view of the preferred embodiment of the dual fuel system for diesel engines; 
           [0047]      FIG. 2  is a diagrammatic top view of the mixing chamber using Swage Lock proportioning valves as an alternative to the electronic control system; and 
           [0048]      FIG. 3  is a diagrammatic side view of the mixing chamber using Swage Lock proportioning valves as an alternative to the electronic control system. 
       
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
       [0049]    With reference to  FIG. 1 , there is shown a dual fuel system  10  for a diesel engine for trucks. Diesel is introduced from a service station pump at atmospheric pressure into tank  11 . In a first pathway, diesel is drawn from tank  11  along pipe  30  via an inline filter  12  by fuel feeder pump  13 . Fuel feeder pump  13  operates at a pressure of approximately 30 psi. The inline filter  12  is a glass filter that removes contaminants. The diesel fuel is subsequently pumped by supply pump  15  to the common rail  16  for entry into the combustion chamber via injectors  18 . With the first pathway, diesel is used as the sole fuel source for combustion within the combustion chamber of the engine. 
         [0050]    In a second pathway, diesel is drawn from tank  11  by secondary fuel feeder pump  20  along pipe  31 . The diesel from tank  11  is filtered by the inline filter  12  as it is being drawn by the secondary fuel feeder pump  20 . From the secondary fuel feeder pump  20 , diesel is passaged through a non-return valve  17  to a secondary diesel pressure tank  21 . The pressure within the secondary diesel pressure tank  21  is maintained at approximately 100 psi. The secondary diesel pressure tank  21  has an approximately 43 litre capacity. The secondary diesel pressure tank  21  has a pressure switch  22  which electrically controls the secondary fuel feeder pump  20  thereby maintaining the desired pressure. The secondary diesel pressure tank  21  also has a bleed valve to bleed any air within the line  31  and secondary diesel pressure tank  21 . There is also a line  32  between the fuel feeder pump  13  and the secondary diesel pressure tank  21  to enable diesel passaging line  30  to enter the secondary diesel pressure tank  21 . There is a non-return valve  27  in line  32  that prevents diesel from the secondary diesel pressure tank  21  passaging to the fuel feeder pump  13 . 
         [0051]    Pressurized diesel from the secondary diesel pressure tank  21  is passaged along line  33  to the mixing chamber  28 . The flow of pressurized diesel along line  33  is controlled by a diesel flow control valve  24 . The diesel control valve  24  is electrically operated by a diesel electronic controller  25  which in turn is actuated by the electronic control unit  26 . The electronic control unit  26  processes information regarding revolutions per minute of the engine from a crank angle sensor. Pressurized diesel passes through the diesel flow control valve  24  and enters the mixing chamber  28  at a pressure of approximately 100 psi. 
         [0052]    LPG is introduced into tank  43  from a service station pump where the tank  43  is filled under the pressure of approximately 150 psi in liquid state. LPG is stored under pressure at 150 psi in liquid state. Liquid LPG passes through pipe  34  via shut off valve  44 , in line filter  45 , solenoid valve  48  and non-return valve  49  to an LPG flow control valve  50 . The LPG flow control valve  50  is electrically operated by a LPG electronic controller  51  which is actuated by the electronic control unit  26 . Pressurized liquid LPG enters the mixing chamber  28  at approximately 100 psi. 
         [0053]    Both the pressurized diesel and liquefied LPG enter the mixing chamber  28 . The mixing chamber  28  is shown in both  FIGS. 2 and 3 . As an alternative to the electronic control flow valve system, ¼ NPT Swage Lock Proportioning Valves  60  can be used and are preferably locked at a predetermined ratio setting. 
         [0054]    The mixing chamber  28  is substantially spherical with the proportioning valves  60  are positioned spatially diagonally opposite each other. The mixing chamber  28  has an internal wire mesh  61  to facilitate mixing of the fuels. The mixed fuel is discharged via outlet  62  and excess mixed fuel is reintroduced via inlet  63 . 
         [0055]    A preferred ratio of fuels is 30% diesel and 70% LPG. However, there is a range of ratios from 10% diesel and 90% LPG to 90% diesel and 10% LPG. Ratios of fuel blends which use less than 30% diesel can be achieved where the lubricity of the fuel mix is increased. In particular, low sulphur diesel which undergoes additional filtration treatment has reduced lubricity and fuel blends below a diesel percentage of 30% requires additional lubricity in order to maintain engine components. 
         [0056]    Apart from regulating the diesel and LPG flow control valves  24 ,  50 , in response to engine revolutions per minute, the flow control valves  24 ,  50  are also regulated by accelerometer inputs which provide information regarding traveling up and down inclines. The accelerometer inputs are processed by the electronic control unit  26 . 
         [0057]    From the mixing chamber  28  the liquid fuel mixture is drawn through a secondary fuel filtration unit  54  by the supply pump  15 . From the secondary fuel filtration unit  54 , the liquid fuel mixture is drawn into the supply pump  15  and pumped to the common rail  16  at high pressure. The common rail  16  distributes the liquid fuel mixture to the injectors  18  of each combustion chamber (not shown). Only one injector  18  is shown in  FIG. 1  by way of example. There is also a fuel pressure sensor  55  associated with the common rail  16 . 
         [0058]    Excess fuel mixture that is not burnt is returned from each injector  18  via a fuel temperature sensor  56 . Excess fuel mixture associated with the common rail  16  is returned via pressure limiter  57 . Excess fuel mixture is piped to the overflow valve  58  through pressure limiting valve  59 , fuel cooler  64  to the mixed fuel pressure tank  65 . The mixed fuel pressure tank  65  has a bleed valve  66  which allows removal of air from the fuel lines and tank  65 . From the mixed fuel pressure tank  65 , the fuel mixture is drawn up into the mixing chamber  28  for return to the common rail  16  and combustion chambers. 
       Emission Test Results 
       [0059]    By way of providing support for the dual fuel system of the current invention, emission tests were conducted by an independent third party, Brisbane City Council and the results were analyzed by Gilmore Engineers Pty Ltd. Two tests were conducted when the vehicle used diesel only and LPG/diesel (at a ratio of 70% LPG and 30% diesel). The diesel only test (test 2969) was conducted on 27 Mar. 2007 using the DT80 short test. The LPG/diesel test (test 3262) was conducted on 17 May 2007 using the DT80 short test. The same vehicle was used for both tests. The vehicle was an ISUZU (950 FVR) truck with a vehicle test mass of 13000 kg. The DT80 short test was a series of rapid accelerations and decelerations interspersed with idling and is designed to evaluate vehicle emissions during typical “real world” stop start operating modes and conditions. 
         [0060]    The emission test results are summarized below: 
         [0000]    
       
         
               
               
               
               
               
             
               
               
               
               
               
             
           
               
                   
                   
               
               
                   
                   
                 DIESEL ONLY 
                 LPG/DIESEL 
                 DNEPM 
               
               
                   
                 UNITS 
                 (Test 2969) 
                 (Test 3262) 
                 Limits 
               
               
                   
                   
               
             
             
               
                   
               
             
          
           
               
                 NO x   
                 g/kWh 
                 6.211 
                 0.380 
                   
               
               
                 (Nitrous 
                 g/km · t 
                 0.707 
                 0.686 
                 1.5 
               
               
                 Oxide) 
               
               
                 PM LLSP 
                 mg/kWh 
                 80.194 
                 26.325 
               
               
                 (Particulate 
                 mg/km · t 
                 9.126 
                 2.831 
                 50 
               
               
                 Matter) 
               
               
                 Average 
                 % 
                 4.623 
                 2.382 
                 25 
               
               
                 Opacity 
               
               
                   
               
             
          
         
       
     
         [0061]    Based on these results, an engine under the DT80 short test driving cycle using the LPG/diesel fuel mixture has significantly lower opacity, significantly lower particulate emissions, and lower NO x  emissions on a per km basis in comparison with diesel. 
         [0062]    The NO x  emissions using the LPG/diesel mixture are only 45.7% of that allowable by the DNEPM (Diesel Vehicle Emission National Environment Protection Measure) limits. Particulate matter emissions are only 5.7% of that allowable by DNEPM limits and average opacity is 9.5% of that allowable by DNEPM limits. In summary, the emission levels using LPG/diesel mixture are substantially lower than that allowable by DNEPM limits. 
       ADVANTAGES 
       [0063]    The preferred embodiment of the dual fuel system has the advantage that LPG can be mixed with diesel at comparatively high ratios and used as a liquid fuel mixture in the combustion chamber. Unlike other dual fuel systems, the diesel manufacturer&#39;s specifications are not altered and manufacturer&#39;s warranties are maintained. The advantage of the preferred embodiment arises from mixing liquid LPG and diesel to form a liquid fuel mixture which can be distributed via the common rail to the combustion chambers. Other dual fuel systems use LPG in a gaseous state often introducing LPG with the induction air. 
         [0064]    The advantage of the dual fuel system of the preferred embodiment is that only minor changes are required to the diesel engine, a cleaner emission is produced and less frequent servicing including oil changes is required. The dual fuel system of the preferred embodiment takes advantage of the relative cheapness and abundant supply of LPG compared with diesel and petrol fuels. This relative cheapness can be translated into operational cost savings for vehicles with diesel engines. 
       VARIATIONS 
       [0065]    It will of course be realised that while the foregoing has been given by way of illustrative example of this invention, all such and other modifications and variations thereto as would be apparent to persons skilled in the art are deemed to fall within the broad scope and ambit of this invention as is herein set forth. 
         [0066]    Throughout the description and claims this specification the word “comprise” and variations of that word such as “comprises” and “comprising”, are not intended to exclude other additives, components, integers or steps.