High pressure fuel pump

Information

  • Patent Grant
  • 6460407
  • Patent Number
    6,460,407
  • Date Filed
    Monday, August 10, 1998
    25 years ago
  • Date Issued
    Tuesday, October 8, 2002
    21 years ago
Abstract
A number of embodiments of direct injected V-type outboard motors provided with a very effective fuel supply system wherein the number of components can be significantly reduced as well as the elimination of many of the flexible conduits normally employed. This also permits the fuel system to be assembled as a relatively unitary assembly that can be then affixed to the engine. The arrangement is such that purging of the system from vapors during shutdowns is easily accomplished and the system can be purged without complicated construction. Furthermore, the system can be pressure tested by an arrangement where the low pressure system can bypass the high pressure system when the engine is not operating so as to be pressurized for testing purposes. However, when the high pressure system operates, then the bypass line will be closed by the shunting valve arrangement. The direct injection system permits operation with two cycle engines even under low load and speed conditions by using residual gasses to assist in fuel vaporization. The high pressure pump and its drive are also provided with a cooling system.
Description




BACKGROUND OF THE INVENTION




This invention relates to a fuel supply system for direct injection engines and more particularly to an improved high pressure fuel pump for an outboard motor incorporating a direct injection system.




As is well known, in all fields of engine design there is an increasing emphasis on obtaining more effective emission control, better fuel economy and, at the same time, continued high or higher power output. This trend has resulted in the substitution of fuel injection systems for carburetors as the engine charge former. In order to obtain still further improvements, direct fuel injection systems are being considered. These systems inject fuel directly into the combustion chamber and thus have significant potential advantages.




In many applications, the incorporation of direct injection is relatively straightforward. However, in connection with outboard motors, the very compact nature of the outboard motor renders this further sophistication in engine design difficult to obtain. The problems in connection with direct fuel injection systems for outboard motors is related primarily to the space that is.




These problems arise, in part, because of the number of components required for fuel injection and the very nature of some of these components. For example, with manifold injection systems for outboard motors, it has been the practice to provide a fuel injection system that includes at last the following components:




a low pressure fuel pump,




a high pressure fuel pump,




a pressure regulator,




a vapor separator; and




a fuel rail for delivering the fuel to the injectors.




The use of a vapor separator is required primarily because of the confined space and the fact that fuel vapors or air in the fuel, conditions primarily resulting from heat, can cause erratic injection and poor performance.




For the same reasons, it has also been the practice to position the high pressure fuel pump in the vapor separator so as to permit it being cooled and to minimize the amount of heat that is generated in the system and to remove the heat from the fuel that is delivered to the injectors. This also saves space. However, this necessitates the use of an electrically operated fuel pump. Such pumps have limited capacity in the pressure which they can generate.




With direct injection systems, however, the fuel must be injected directly into the combustion chamber. This means that the pressure into which the fuel is injected is higher than with manifold injection systems wherein the pressure is at substantially atmospheric or even below. Electric pumps are not totally capable of supplying such high pressures. Thus engine driven, mechanical pumps are required.




In conjunction with the use of these mechanical pumps, the pump configuration may at times require the use of a transmission to drive the pump. That is, the type of pump employed may have its axis positioned in a position that is not parallel to the axis of rotation of the engine output shaft. Thus, bevel gear transmission or other mechanical transmissions may be required in order to transmit the drive from the engine output shaft or another shaft driven by it and the pump input shaft.




Both the mechanical pump itself and the driving transmission can generate heat. Unless this heat is dissipated externally in another fashion, the heat may actually be transmitted to the fuel and cause vapor problems.




It is, therefore, a principal object of this invention to provide an improved high-pressure fuel pump for an internal combustion engine and particularly one that is utilized in conjunction with an outboard motor.




It is a still further object of this invention to provide an improved high-pressure fuel pump and drive therefor for a fuel injection system wherein the fuel pump is cooled externally.




It is a still further object of this invention to provide an improved high-pressure fuel pump for a fuel injection system for an internal combustion engine that shares a cooling system with the engine cooling system.




SUMMARY OF THE INVENTION




This invention is adapted to be embodied in a fuel injection system for an internal combustion engine. The engine is provided with a cooling jacket that is supplied with cooling water. A fuel injection system is provided for the engine and this includes fuel injectors for injecting fuel directly into the cylinders of the engine. A fuel supply system supplies high-pressure fuel to the fuel injection system. This includes a high-pressure pump and a transmission for driving the high-pressure pump from an engine output shaft. A cooling jacket is provided for at least one of the high-pressure pump and its transmission and coolant delivered to the engine cooling jacket is also supplied to this fuel pump cooling jacket.











BRIEF DESCRIPTION OF THE DRAWINGS





FIG. 1

is a multi-part view showing: in the lower right-hand portion, an outboard motor embodying the invention; in the lower left-hand portion, a rear elevational view of the outboard motor with portions removed and other portions broken away and shown in section so as to more clearly show the construction of the engine; and in the upper view, a partially schematic cross sectional view of the engine of the outboard motor with its induction and fuel injection system shown in part schematically. The ECU for the motor links the three views together.





FIG. 2

is an enlarged cross-sectional view taken through a portion of one of the cylinders of the engine of this embodiment and shows in detail the fuel injection spray pattern relative to the scavenging air flow and the residual charge.





FIG. 3

is a cross-sectional view taken along a plane that passes through the scavenge and exhaust ports and is generally perpendicular to the claim of FIG.


2


.





FIG. 4

is a top plan view of the power head showing the engine in solid lines and the protective cowling in phantom.





FIG. 5

is a view looking in the same direction as

FIG. 5

, but with the accessories, including the high pressure fuel pump, removed and with the engine broken away and shown in section.





FIG. 6

is a side elevational view of the power head showing the engine in solid lines and the protective cowling in phantom, and is taken in the direction of the arrow


6


in FIG.


4


.





FIG. 7

is a rear elevational view of the engine and is taken generally in the direction of the arrow


7


in FIG.


4


.





FIG. 8

is an enlarged top plan view, looking in the same direction as

FIG. 4

, but shows only the high pressure pump and its association with the main fuel delivery system.





FIG. 9

is a view looking in the same direction as FIG.


7


and shows those components of the fuel supply system illustrated in FIG.


8


.





FIG. 10

is an enlarged top plan view showing the high pressure fuel pump with the drive pulley thereof being shown in phantom.





FIG. 11

is a view looking in the direction of the arrow


11


in FIG.


10


and showing a part of the fuel pump drive and cooling system broken away and shown in cross-section.





FIG. 12

is a top plan view showing the main fuel manifold.





FIG. 13

is a cross-sectional view taken along a plane perpendicular to the plane of FIG.


12


and passing through the center of the main fuel manifold.





FIG. 14

is a cross-sectional view taken along the line


14





14


of FIG.


12


.





FIG. 15

is an elevational view showing the side of the main fuel rail that mounts to the fuel injectors.





FIG. 16

is a cross-sectional view taken through a plane perpendicular to the plane of FIG.


15


and passing through the center of the fuel delivery passage.





FIG. 17

is a cross-sectional view taken along the line


17





17


of FIG.


16


.





FIG. 18

is an enlarged cross-sectional view showing one of the connectors for connecting the main fuel manifold to one of the fuel rails.





FIG. 19

is a top plan view of the mounting bracket for the high pressure fuel injection pump.





FIG. 20

is a view of the mounting bracket looking in the direction of the arrow


20


in FIG.


19


.





FIG. 21

is a view of the mounting bracket looking in the direction of the arrow


21


in FIG.


19


.





FIG. 22

is a view, in part similar to the lower left hand side view of

FIG. 1

, and shows a second embodiment of the invention.





FIG. 23

is a view, in part similar to the lower left hand view of FIG.


1


and to

FIG. 2

, and shows a third embodiment of the invention.





FIG. 24

is a view, in part similar to the lower left hand view of FIG.


1


and

FIGS. 22 and 23

, and shows a fourth embodiment of the invention.





FIG. 25

is a rear elevational view, in part similar to

FIG. 7

, and shows a fifth embodiment of the invention.











DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS




The general overall environment in which the invention is practiced and certain details of the engine will be described initially by reference to FIG.


1


. In the lower right hand view of this figure, an outboard motor constructed and operated in accordance with an embodiment of the invention is depicted in side elevational view and is identified generally by the reference numeral


31


.




The entire outboard motor


31


is not depicted in that the swivel bracket and clamping bracket that are associated with the drive shaft housing, indicated generally by the reference numeral


32


, are not illustrated. This is because these components are well known in the art and the specific method by which the outboard motor


31


is mounted to the transom of an associated watercraft is not necessary to permit those skilled in the art to understand or practice the invention.




The outboard motor


31


includes a power head, indicated generally by the reference numeral


33


, that is positioned above the drive shaft housing


32


and which includes a powering internal combustion engine, indicated generally by the reference numeral


34


. This engine


34


is shown in more detail in the remaining two views of this figure and will be described shortly by reference thereto.




The power head


33


is completed by a protective cowling which includes a main cowling member


35


. This main cowling member


35


is detachably connected to a lower tray portion which is also not shown in this figure and which encircles an upper portion of the drive shaft housing


32


.




Positioned beneath the drive shaft housing


32


is a lower unit


36


in which a propeller


37


, which forms the propulsion device for the associated watercraft, is journaled.




As is typical with outboard motor practice, the engine


34


is supported in the power head


33


so that its crankshaft


36


(see the upper view) rotates about a vertically extending axis. This is done so as to facilitate connection of the crankshaft


36


to a drive shaft which depends into the drive shaft housing


32


and which drives the propeller


37


through a conventional forward, neutral, reverse transmission contained in the lower unit


36


.




The details of the construction of the outboard motor and the components which are not illustrated may be considered to be conventional or of any type known to those wishing to utilize the invention disclosed herein. Those skilled in the art can readily refer to any known constructions with which to practice the invention.




Referring now in detail to the construction of the engine


34


still by primary reference to

FIG. 1

, in the illustrated embodiment, the engine


34


is of the V6 type and operates on a two stroke, crankcase compression principle. Although the invention is described in conjunction with an engine having this cylinder number and cylinder configuration, it will be readily apparent that the invention can be utilized with engines having other cylinder numbers and other cylinder configurations. Some features of the invention, however, have particular utility in connection with V-type engines.




Also, although the engine


34


will be described as operating on a two stroke principle, it will also be apparent to those skilled in the art that certain facets of the invention can be employed in conjunction with four stroke engine. In fact, some features of the invention also an be employed with rotary type engines.




The engine


34


is comprised of a cylinder block


38


that is formed with a pair of cylinder banks


39


and


41


. Each of these cylinder banks is formed with three vertically spaced, horizontally extending cylinder bores


42


. Pistons


43


reciprocate in these cylinder bores


42


. The pistons


43


are, in turn, connected to the upper or small ends of connecting rods


44


. The big ends of these connecting rods are journaled on the throws of the crankshaft


36


in a manner that is well known in this art.




The crankshaft


36


is journaled in a suitable manner for rotation within a crankcase chamber


45


that is formed in part by a crankcase member


46


that is affixed to the cylinder block


38


in a suitable manner. As is typical with two cycle engines, the crankshaft


36


and crankcase chamber


45


are formed with seals so that each section of the crankcase that is associated with one of the cylinder bores


42


will be sealed from the others. This type of construction is well known in the art.




A cylinder head assembly, indicated generally by the reference numeral


47


, is affixed to the end of each of the cylinder banks


39


and


41


that are spaced from the crank case chamber


45


. These cylinder head assemblies


47


are shown in more detail in FIG.


2


and are comprised of a main cylinder head member


48


that defines a plurality of recesses


49


in its lower face. Each of these recesses


49


cooperate with the respective cylinder bore


42


and the head of the piston


43


to define the combustion chambers of the engine. When the pistons


43


are at their top dead center position, the cylinder head recesses


49


form the major portion of the combustion chamber. For that reason, the reference numeral


49


will be used, at times, to identify the combustion chamber per se.




A cylinder head cover member


50


completes the cylinder head assembly. The cylinder head members


48


and


50


are affixed to each other and to the respective cylinder banks


39


and


41


in a suitable, known manner.




Referring again primarily to

FIG. 1

, an air induction system, indicated generally by the reference numeral


51


is provided for delivering an air charge to the sections of the crankcase chamber


46


associated with each of the cylinder bores


42


. This communication is via an intake port


52


formed in the crankcase member


46


and registering with each such crankcase chamber section.




The induction system


51


includes an air silencing and inlet device, shown schematically in this figure and indicated by the reference numeral


53


. The actual construction of this air line device appears partially in

FIGS. 4 and 6

. In actual physical location, this device


53


is contained within the protective cowling at the forward end thereof and has a rearwardly facing air inlet opening


54


through which air is inducted. Air is admitted into the interior of the protective cowling in a known manner, and this is primarily through a pair of rearwardly positioned air inlet openings that appear only in phantom in

FIG. 6

of the drawings where they are identified at Ai and have a construction as is generally well known in the art.




Referring again back to

FIG. 1

, the air inlet device


53


supplies the inducted air to a plurality of throttle bodies


55


, each of which has a throttle valve


56


provided therein. These throttle valves


56


are supported on throttle valve shafts. These throttle valve shafts are linked to each other for simultaneous opening and closing of the throttle valves


56


in a manner that is well known in this art.




As is also typical in two cycle engine practice, the intake ports


52


have provided in them reed-type check valves


57


. These check valves permit the air to flow into the sections of the crankcase chamber


45


when the pistons


43


are moving upwardly in their respective cylinder bores. However, as the pistons move downwardly, the charge will be compressed in the sections of the crankcase chamber


45


. At that time, the reed type check valve


57


will close so as to permit the charge to be compressed.




The charge which is compressed in the sections of the crankcase chamber


45


is then transferred to the combustion chambers


49


through a scavenging system which appears best in

FIGS. 2 and 3

. This scavenging system is of the Schnurl type and includes a pair of main scavenge passages


58


that are positioned on diametrically opposite sides of a plane L containing the axis A of the respective cylinder bore


42


. These main scavenge passages


58


terminate in main scavenge ports


59


so as to direct a scavenging air flow as indicated by the arrows S in

FIGS. 2 and 3

.




In addition, an auxiliary scavenge passage


61


is formed between the main scavenge passages


58


and terminates in an auxiliary scavenging port


62


which also provides scavenging air flow indicated by the arrows S. Thus, during the scavenging stroke, the intake charge will be transferred to the combustion chambers


49


for further compression as the pistons


43


move upwardly from their bottom dead center position so as to close the scavenge ports


59


and


63


and further compress the charge.




Continuing to refer primarily to

FIGS. 2 and 3

, a spark plug


64


is mounted in the cylinder head assembly


47


for each cylinder bore and has its respective spark gap


65


disposed substantially on the cylinder bore axis A. The spark plug


64


is fired under the control of an ECU, shown schematically in FIG.


1


and identified by the reference numeral


66


. This ECU receives certain signals, as will be described, for controlling the time of firing of the spark plugs


64


in accordance with any desired control strategy.




The spark plugs


64


fire a fuel air charge that is formed by mixing fuel directly with the intake air via a fuel injector, indicated generally by the reference numeral


67


. The fuel injectors


67


are electrically operated and mounted directly in the cylinder head in a specific location, as will be described, so as to provide optimum fuel vaporization under all running conditions.




Fuel is supplied to the fuel injectors


67


by a fuel supply system, indicated generally by the reference numeral


68


and which will be described first by reference to FIG.


1


and particularly the upper and lower left hand portions thereof.




The fuel supply system


68


is comprised of a main fuel supply tank


69


that is provided in the hull of the watercraft with which the outboard motor


31


is associated. Fuel is drawn from this tank


69


through a conduit


71


by means of a plurality of low pressure pumps


72


. These low pressure pumps


72


may, for example, be operated by the variations in pressure in the sections of the crankcase chamber


45


, and thus provide a relatively low pressure.




A quick disconnect coupling is provided in the conduit


71


and also a fuel filter


73


is positioned in this conduit at an appropriate location. Specific locations for these components are shown in later, more detailed views.




From the low pressure pump


72


, fuel is supplied to a vapor separator


74


which is mounted, in a manner which will be described later, on the engine or within the protective cowling at an appropriate location. This fuel is supplied through a line


75


. At the vapor separator end of the line


75


, there is provided a float valve that is operated by a float


76


so as to maintain a uniform level of fuel in the vapor separator


74


.




A higher pressure, electric fuel pump


77


is provided in the vapor separator


74


and pressurizes fuel that is delivered through a fuel supply line


78


to a high pressure pumping apparatus, indicated generally by the reference numeral


79


. A low pressure regulator


81


is positioned in the line


78


at the vapor separator


74


and limits the pressure that is delivered to the high pressure pump


79


by dumping the fuel back to the vapor separator


74


.




The high pressure fuel delivery system


79


includes a high pressure pump


82


that has a construction which will be described in more detail later by reference to FIG.


11


. It includes a pump drive shaft to which a driving pulley


83


is affixed. This driving pulley


83


is driven from a pulley, to be described, mounted on the crankshaft


36


by means of a drive belt


84


.




Fuel is supplied from the high pressure pump


82


to a main fuel manifold


85


that is mounted on the engine and which has a construction which will be described in more detail later. This will be done by primary reference to

FIGS. 7-9

and


12


-


14


. The main fuel manifold


85


, in turn, delivers fuel to a pair of vertically extending fuel rails


86


. This connection and the manner of delivery of fuel will be described later by particular reference to

FIGS. 15-18

. The fuel rails


86


deliver fuel to the fuel injectors


67


in a manner which will be described later by detailed reference to FIG.


2


.




The pressure in the high pressure delivery system


79


is regulated by a high pressure regulator


87


which dumps fuel back to the vapor separator


74


through a pressure relief line


88


in which a fuel heat exchanger or cooler


89


is provided.




Referring again primarily to

FIGS. 1-3

, after the fuel charge has been formed in the combustion chambers


49


by the injection of fuel from the fuel injectors


67


, the charge is fired by firing the spark plugs


64


. The strategy by which the injection timing and duration is controlled by the ECU


66


, as well as the control for the timing of firing of the spark plug


64


will be described in more detail shortly.




Once the charge burns and expands, the pistons


43


will be driven downwardly in the cylinder bores until the pistons reach a position indicated at


43




e


in FIG.


2


. At this time, an exhaust port


91


will be uncovered so as to open the communication with an exhaust passage


92


formed in the cylinder block


38


. It should be noted that the exhaust port


91


and exhaust passage


92


are formed diametrically opposite the auxiliary scavenge passage


61


and its scavenge port


63


. However, the exhaust port


91


opens earlier and closes later than all of the scavenge ports


59


and


63


.




The exhaust gases flow through the exhaust passages


92


to collector sections


93


of respective exhaust manifolds that are formed within the cylinder block


38


in a manner to be described in more detail later by reference to FIG.


5


. These exhaust manifold collector sections


93


communicate with exhaust passages formed in an exhaust guide plate


94


on which the engine


34


is mounted, as clearly seen in the lower left hand view of FIG.


1


.




A pair of exhaust pipes


95


depend from these exhaust guide exhaust passages into an expansion chamber


96


formed in the drive shaft housing


32


. From this expansion chamber


96


, the exhaust gases are discharged to the atmosphere through a suitable exhaust system. As is well known in outboard motor practice, this may include an underwater, high speed exhaust gas discharge and an above the water, low speed exhaust gas discharge. Since these types of systems are well known in the art, a further description of them is not believed to be necessary to permit those skilled in the art to practice the invention.




Although any type of desired control strategy can be employed for controlling the time and duration of fuel injection from the injector


67


and timing of firing of the spark plug


64


, it will be apparent from the following description that there is some significance in injector timing to improve good fuel vaporization under difficult running conditions. This will be described in more detail later by particular reference to

FIGS. 2 and 3

. However, a general discussion of some engine conditions that may be sensed and some other ambient conditions that can be sensed for engine control will follow. It is to be understood, however, that those skilled in the art will readily understand how various control strategies can be employed in conjunction with the components of the invention that will be described in more detail.




Preferably, the control for the fuel air ratio includes a feed back control system. Thus, a combustion condition or oxygen sensor


97


is provided that senses the in cylinder combustion conditions by sensing the residual amount of oxygen in the combustion products at a time near the time when the exhaust port


91


is opened. This is accomplished through a sensor port


97




p


as seen in FIG.


5


. This output and air fuel ratio signal are indicated schematically at


98


to the ECU


66


.




There is provided also associated with the crankshaft


36


a crank angle position sensor which when measuring crank angle versus time and output an engine speed signal, indicated schematically at


99


. Engine load, as determined by throttle angle of the throttle valves


56


, is sensed by a throttle position sensor which outputs a throttle position or load signal


101


to the ECU


66


.




There is also provided a pressure sensor


102


in the line connected to the pressure regulator


87


. This pressure sensor


102


outputs the high pressure fuel signal to the ECU


66


, which signal is indicated schematically at


103


. At other times than during normal engine running, the sensor


102


may be utilized for another purpose, as will be described later.




There also may be provided a trim angle sensor


104


(see the lower right hand side view of

FIG. 1

) which outputs a trim angle signal


105


to the ECU


66


.




The sensed conditions are merely some of those conditions which may be sensed for engine control.




The ECU, as has been noted, outputs signals to the fuel injector


67


and spark plug


64


for their respective control. These control signals are indicated schematically in

FIG. 1

at


106


and


107


, respectively.




It has been noted that when the engine is shut off, it is desirable to release the high pressure that may exist in the fuel supply system and specifically in the main fuel manifold


85


and fuel rails


86


. To this end, there is provided an electrically operated pressure release valve


108


that is mounted in a bypass line


109


that extends from the main fuel manifold


85


back to the return line


87


bypassing the pressure regulator


87


. When this valve


108


is opened upon the cessation of engine operation via a control signal


111


from the ECU


66


, the fuel pressure in the system will be relieved by dumping fuel back to the vapor separator


74


.




The mounting of the fuel injector


68


and its positioning and injection strategy in order to obtain good running, particularly under the difficult low speed low load condition will now be described by primary references to

FIGS. 2 and 3

. First, it will be noted that the main cylinder head member


48


is formed with an opening


112


that is complimentary and receives a main body portion


113


of the fuel injector


67


. At its lower end, the injector opening


112


receives a seal


114


that sealingly engages the injector around its discharge nozzle portion


115


.




A retainer member


116


has an opening


117


that cooperates with a shoulder


118


formed on the injector body and secures the injector


68


to the cylinder head in this relationship. The nozzle portion


115


extends into a smaller diameter opening


119


formed at the lower periphery of the opening


102


and is located in an area that is preferably disposed in a relatively narrow range above the exhaust port


91


as shown in FIG.


3


.




The injector nozzle has a conical spray pattern indicated as an S in

FIGS. 2 and 3

which preferably is disposed so that the fuel spray will penetrate the combustion chamber and will come into contact with residual exhaust gas patches R


1


, R


2


and R


3


that exist during low speed and low load running conditions when the piston


43


is moving toward top dead center position and after the scavenged ports


59


and


63


and the exhaust port


91


have closed. This is preferably at a relatively short angle before top dead center position of the piston and something in the range of about 3 to 10 degrees of crank rotation before top dead center.




Under this running condition there is little time for the fuel to vaporize before the spark plug is fired. Thus by utilizing the heat of the residual gasses vaporization can be obtained to insure good and complete combustion. Thus, the injected spray will pass through the residual exhaust gases which will still be highly. Thus, the residual heat of combustion will help in vaporizing the injected fuel for the next firing cycle and thus will insure that a stoichiometric mixture is present at the gap of the spark plug


65


at the time of firing.




Under high speed high load conditions, fuel injection may be done at something more like 90° before top dead center so as to insure the supply of adequate fuel for combustion.




Having thus described the general overall system, the high pressure fuel supply system


79


will now be described in more detail by reference to the remaining figures of this embodiment. It should be noted that this high pressure system


79


including the high pressure fuel pump


83


, the main fuel manifold


85


and the fuel rails


86


are designed so as to be connected substantially rigidly together as a unit. This facilitates mounting on the engine and also reduces the number of flexible hoses, which can cause problems with leakage and wear.




The description of the components will begin with the overall construction of those components which are basically assembled together and initially by reference to

FIGS. 6-11

. As may be seen in these figures, a driving pulley


121


is affixed to the upper end of the crankshaft


36


to drive the drive belt


84


, as previously noted. As may be best seen in

FIG. 11

, the high pressure pump assembly


83


is comprised of two major components. These comprise a transmission


122


and the pump and pump valving bodies, indicated generally by the reference numeral


123


.




Continuing to refer primarily to

FIG. 11

, the transmission portion


122


is comprised of a housing assembly that includes a main housing member


124


in which a pump drive shaft


125


is journaled by means of a plain bearing


126


and a ball bearing


127


. The ball bearing


127


is mounted in an end portion of the housing assembly


124


which is closed by a closure plate


128


so as to define a fuel pump cooling jacket


129


.




The fuel pump cooling jacket


129


receives cooling water from an engine cooling jacket, indicated generally by the reference numeral


131


through a conduit


132


. As is known in the marine field, the water for cooling is drawn from the body of water in which the watercraft is operating and returned thereto after having passed through the respective cooling jackets. A suitable return conduit (not shown) is also provided to return that cooling water that has been circulated through the fuel pump cooling jacket water jacket


129


.




Because the pump drive pulley


82


and drive belt


84


are in proximity to the cowling air inlets Ai (

FIG. 4

) the pump and drive will be cooled by the air flow caused by their movement.




An input shaft


133


is journaled in the housing member


124


and has the driving pulley


82


affixed to its upper end. A pair of intermeshing bevel gears


134


transmit the drive from the intake shaft


133


to the pump drive shaft


125


. This type of transmission can generate some heat and the cooling jacket


129


and air flow previously referred to assists in dissipating that heat and ensuring that the high pressure fuel pump


83


and particularly the pumping unit


123


will be cooled so as to not heat the fuel that is delivered to the injection system. This will ensure against vapor being generated in the fuel system.




The transmission housing


124


is connected by means of an intermediate member


135


to a flange


136


of the main high pressure pump body


123


by means of threaded fasteners


137


. The pump body has a nose piece through which the pump shaft


138


extends so as to be coupled by a splined coupling or coupling of another type to the pump drive shaft


125


.




These shafts rotate about a generally horizontally extending axis indicated at PL which extends transversely across the upper portion of the engine


34


in an area that is disposed above and partly depending into the valley formed between the cylinder banks


39


and


41


.




The pump body, indicated generally by the reference numeral


141


, is formed with a plurality of tapped openings to receive fasteners for attachment to a support plate and also to the main fuel manifold


85


in a manner which will be described shortly. As may be seen, the pump body


141


is formed with an inlet opening


142


that is adapted to receive a fitting connected to one end of the fluid conduit which has been indicated schematically as


78


in

FIG. 1. A

pair of tapped openings


143


permit attachment of this fitting so that fuel can be delivered to the high pressure pump.




A pump discharge fitting


144


is formed below this inlet fitting and is positioned so as to be attached, in a manner to be described, directly to the main fuel manifold


85


so as to limit the necessity for a separate, external conduit. Tapped openings


145


receive fasteners for this purpose.




In accordance with another feature that assists in minimizing the number of external conduits required, the high pressure regulator


87


previously referred to is actually built directly into the pump body


141


. A small L-shaped fitting member


146


(

FIGS. 7 and 8

) is attached to a pressure sensing inlet fitting


147


formed in the pump body


41


so as to transmit the fluid pressure from the main fuel manifold


85


to the pressure regulator


87


.




The return conduit


88


from the high pressure regulator


87


is connected to a relief fitting opening


148


formed in the pump body


141


vertically above the pressure regulator inlet opening


147


. Thus, the number of external conduit is still further reduced by this arrangement that incorporates the regulator


87


directly into the body


141


of the high pressure pump assembly


83


. The vertical spacing of the various fittings also assist in the relief of air back toward the vapor separator


74


when the engine has shut down and is again started up.




The construction of the main fuel manifold


85


will now be described by principal reference to

FIGS. 12-14

. This main fuel manifold


85


is comprised of a generally rectangular metal body member


151


that is formed with a through drilling


152


. This drilling


152


is closed at its outer ends by end plug


153


.




The side of the body


151


is provided with a first fitting member, indicated at


154


and which is shown in most detail in FIG.


14


. This member


154


has an opening


155


that is adapted to be received in fluid communication with the high pressure pump outlet fitting


144


. Through a connector of the type shown in

FIG. 18

or only employing an O-ring seal therebetween. Thus, no external conduit are required for this communication. The fitting


154


has a cross drilling


156


that permits the high pressure fuel to communicate with the manifold passage or drilling


152


.




The upper surface of the manifold body


155


and the surface which extends transversely to the surface in which the fitting


154


is received receives a further fitting


156


, which fitting has an opening


157


so as to couple to the L-shaped connector


156


to communicate the pressure in the manifold passage


152


with the pressure regulator as aforenoted by the same measures as used in the connection to the high pressure pump outlet


144


.




At the ends of the manifold


151


and on the under surface thereof, there are provided a pair of fittings


158


which have openings


159


so as to receive a coupling to provide a connection to the fuel rails


86


, as will be described shortly by reference to FIG.


18


.




The construction of the main fuel rails


86


will now be described by particular reference to

FIG. 15-17

. Like the fuel manifold


85


, the main fuel rails


186


are formed from rectangular metal bodies


161


. A drilled passageway


162


extends vertically through these bodies from their upper ends to their lower ends. The lower ends thereof are closed by a closure plug


163


. The upper end is provided with a counterbored opening


164


that receives a coupling member as will be described later by reference to

FIG. 18

which may be the same as the type coupling member employed to connect the high pressure fuel pump outlet


144


with the inlet fitting


155


of the main fuel manifold


85


. These couplings cooperate with the fitting openings


159


of the main fuel manifold


85


as will also be described.




In the area where each of the fuel injectors


67


of the respective cylinder bank lie, the fuel rail body


161


is provided with a drilled passageway


165


which penetrates far enough into the body


161


to intersect the drilling


162


without having to be plugged at its outer end. These drillings


165


receive elastic sleeves


166


having openings


167


that are complementary to fuel nozzle portions


168


of the fuel injectors


67


so as to deliver fuel to them as seen in FIG.


2


.




Drilled openings


169


also extend through the fuel rail


86


and the body


161


thereof to receive threaded fasteners


171


so as to affix the fuel rail


186


rigidly to the injector mounting elements


161


and, accordingly, to the cylinder head assemblies


47


.




The couplings that are employed between the main fuel manifold


85


and the fuel rails


86


as well as those which may be employed between the high pressure fuel pump


83


and the main fuel manifold


85


as well as between the fitting


146


and the pressure regulator portion of the high pressure fuel pump


83


will now be described by particular reference to FIG.


18


.





FIG. 18

shows specifically the connection between the main fuel manifold


85


and one of the fuel rails


86


. There is provided a cylindrical coupling member


172


that is provided with a central bore


173


and which is also formed with a pair of seal receiving grooves


174


at its opposite ends. Each of these grooves


174


receives a respective O-ring


175


and a nylon backup member


176


so as to provide a leak-tight connection between these elements and one which does not require threaded fittings.




In order to hold the main fuel manifold


85


in position relative to the fuel rails


86


, a structure as shown in

FIG. 9

is employed. This is comprised of an L-shaped bracket


177


that is abuttingly engaged with the surfaces of the fuel manifold


85


and the fuel rails


86


and fixed to them by threaded fasteners


178


. As a result, this provides a unitary assembly which will ensure that the components are held together in sealed relationship without requiring threaded fittings or flexible conduits.




This entire assembly is then mounted on the mounting bracket shown in most detail in

FIGS. 19-21

and which is indicated generally by the reference numeral


179


. This mounting bracket


179


may be formed from a suitable high strength lightweight material such as an aluminum or aluminum alloy.




This member has a horizontally extending surface


181


with a pair of forwardly extending tabbed portions


182


which define an opening between them. The portion


181


is adapted to underlie the main fuel manifold


85


. The main fuel manifold


85


is provided through openings


186


that are adapted to receive threaded fasteners


187


as seen in FIG.


9


. These threaded fasteners are threaded into tapped openings formed on mounting bosses


188


that extend upwardly from the mounting plate surface


181


.




As best seen in

FIG. 8

, the high pressure fuel pump assembly


79


has one rearward opening and a pair of forward openings. One of these openings overlies a further boss


191


formed on the mounting plate portion


181


. The other openings overlie a pair of openings


192


that are formed on the extending portions


182


of the mounting plate


179


. Threaded fasteners


193


pass through these openings so as to secure the high pressure pump assembly


79


also to the mounting plate


179


.




Finally, the mounting plate


179


has a depending rib


194


that is provided for reinforcing purposes and which has a plurality of ribs


195


that extend beneath the surface


181


to add rigidity in this area.




A pair of forwardly positioned apertures


196


are formed in the forwardmost portion of the mounting plate projections


182


and receive threaded fasteners for fixing the mounting plate


182


to the upper surfaces of the cylinder banks


39


and


41


, respectively, so as to provide a secure mount for the pump assembly and manifold on the engine.




Referring now primarily to

FIGS. 5 and 7

, the mounting for certain of the control elements including the ECU


66


will be described. As may be seen in this Figure, the valley between the cylinder bank is closed by a closure plate


198


which also partially encloses the exhaust manifold in part by the cylinder block. A further cover plate


199


encloses this closure plate


198


to form a water jacket


201


through which cooling water may be passed so as to cool the exhaust system.




Mounted on the cover plate


199


by means that include elastic isolators


202


is mounting board


203


which carries the ECU


66


. In addition, a solenoid coil driver arrangement


204


may be mounted on the outer side of the ECU in this area. This solenoid coil driver arrangement drives the solenoid associated with the fuel injector


86


for opening the valves. In addition, this assembly may be attached at its upper end to the mounting bracket


179


through threaded fasteners that pass through apertures


204


(

FIG. 20

) formed in the flange portion


194


thereof.




The spark coils for firing the spark plug


64


, are indicated by the reference numeral


205


and are mounted on the adjacent side of the mounting plate


203


so as to minimize the length of wiring and makes the electrical connections more secure.




It has been mentioned that there is a desire to be able to pressure test the system. This is accomplished with utilization of only the single pressure gauge


102


and is done by means of a check valve arrangement as best shown in FIG.


1


and particularly the upper view thereof. It should be noted that the conduit


78


leading from the high pressure electric fuel pump


77


to the higher pressure, mechanical fuel pump


83


includes a branch passage


206


, which bypasses the inlet and outlet sides of the high pressure pump


83


. This conduit


206


extends in essence between the pump inlet and outlet fittings


142


and


145


as shown in FIG.


11


and may be located within the pump body


141


.




A check valve


207


is provided in this bypass conduit


206


that permits flow to pass around the high pressure pump


83


. However, there is provided a further check valve


208


in the outlet side of the high pressure pump


83


between it and the discharge of the conduit


206


. This is also preferably located within the pump body


141


.




Thus, when the high pressure pump


83


is operating, the check valve


208


will open and force the check valve


207


closed so that no fluid pressure will be lost. However, by stopping the engine and running the electric pump


77


, the fluid will flow through the conduit


78


and bypass conduit


206


to close the check valve


208


and provide a pressure signal at the sensor


102


. This may be used to check the integrity of the lower pressure fuel system.




During normal engine running, the pressure sensor


102


will indicate that the high pressure side is not leaking and thus, the system can be used and checked with a single pressure tap. In the embodiment as thus far described, the main fuel manifold


85


has extended transversely across the upper surface of the fuel rails


86


.

FIG. 22

shows another embodiment in the invention which is the same as that already described except for the relationship between the main fuel manifold


85


and the fuel rails


86


. For that reason, only this single view, which is a reduced scale view similar to the lower left hand portion of

FIG. 1

, is believed necessary to permit those skilled in the art to practice the invention. In this embodiment, the main fuel manifold is shorter in length and is joined to the fuel rails


86


through their sides rather than through their upper ends.





FIG. 23

shows another embodiment wherein the manifolding arrangement similar to that utilized in

FIG. 22

is employed. In this embodiment, however, a transfer manifold


251


having a construction like the earlier main fuel manifold


85


but which is not a main fuel manifold connects the bottom of the two fuel rails


86


as seen in FIG.


23


. The high pressure fuel pump


83


, therefore, delivers fuel to one of the fuel rails


86


through its upper inlet fittings and the pressure regulator inlet is dispose at the upper end of the other fuel rail.





FIG. 24

shows another embodiment that differs from those already described and in the manifolding arrangement. In this embodiment, fuel is supplied to a main fuel manifold


85


that is positioned at the lower end of the construction between the lower ends of the fuel rails


86


. A cross manifold


261


is also provided between the upper ends of the manifolds. High pressure fuel is supplied to the main fuel manifold


85


through a delivery manifold


262


which communicates directly with the high pressure fuel pump outlet.





FIG. 25

shows a final embodiment of this invention and in this embodiment, the vapor separator


74


is mounted on the back of the mounting plate for the control body.




Thus, from the foregoing description, it should be readily apparent that the described embodiment of the invention provides a very effective fuel supply system for an outboard motor wherein the number of components can be significantly reduced as well as the elimination of many of the flexible conduits normally employed. This also permits the fuel system to be assembled as a relatively unitary assembly that can be then affixed to the engine. The arrangement is such that purging of the system from vapors during shutdowns is easily accomplished and the system can be purged without complicated construction. Furthermore, the system can be pressure tested by an arrangement where the low pressure system can bypass the high pressure system when the engine is not operating so as to be pressurized for testing purposes. However, when the high pressure system operates, then the bypass line will be closed by the shunting valve arrangement as shown in FIG.


1


. The high pressure pump and its drive are also provided with a cooling system.




Of course, the foregoing description is that of preferred embodiments of the invention. Various changes and modifications may be made without departing from the spirit and scope of the invention, as defined by the appended claims.



Claims
  • 1. A fuel injected multi-cylinder internal combustion engine said engine being provided with a cooling jacket supplied with coolant, a fuel injection system for said engine and including fuel injectors for injecting fuel directly into said cylinders of said engine, a fuel supply system for supplying high-pressure fuel to said fuel injection system including a high-pressure pump and a transmission for driving said high-pressure pump from an engine output shaft, a fuel pump cooling jacket for at least one of said high-pressure pump and said transmission, and means for delivering the coolant from said engine cooling jacket to said fuel pump cooling jacket.
  • 2. A fuel injected multi-cylinder engine as set forth in claim 1 wherein the transmission comprises a bevel gear transmission.
  • 3. A fuel injected multi-cylinder engine as set forth in claim 2 wherein the fuel pump cooling jacket is formed in a wall of a transmission case containing the bevel gear transmission.
  • 4. A fuel injected multi-cylinder engine as set forth in claim 2 wherein the bevel gear transmission comprises an input shaft having a first bevel gear and journalled about a vertical axis and driven by an output shaft of said engine and a second bevel gear in mesh with said first bevel gear and fixed to a horizontally extending pump drive shaft.
  • 5. An outboard motor including a fuel injected multi-cylinder engine as set forth in claim 4 said outboard motor comprised of a power head consisting of the multi-cylinder internal combustion engine having an output shaft and a surrounding protective cowling and a driveshaft housing and lower unit containing a propulsion device within said lower unit depending from said power head, said engine being mounted within said protective cowling so that said output shaft rotates about a vertically-extending axis, a lower end of said output shaft being coupled to a drive shaft that depends into said drives shaft housing and lower unit for driving said propulsion device, a plurality of fuel injectors each of which injects fuel directly into a respective one of said cylinders, said high pressure fuel pump being contained within said protective cowling and disposed at an upper end of said engine and driven off an upper end of said output shaft through said transmission.
  • 6. An outboard motor as set forth in claim 5, wherein a transmission input shaft is driven from the output shaft by a belt drive.
  • 7. An outboard motor as set forth in claim 6, wherein the engine is of a V-type and has a pair of cylinder banks each containing at least one combustion chamber and wherein the cylinder banks define a valley therebetween.
  • 8. An outboard motor as set forth in claim 7, wherein the high pressure pump is disposed in the valley and above the cylinder banks.
  • 9. An outboard motor as set forth in claim 8, wherein the high pressure pump delivers fuel to a main fuel manifold.
  • 10. An outboard motor as set forth in claim 9, wherein the main fuel manifold supplies fuel to a pair of fuel rails each associated with a respective one of the cylinder banks.
  • 11. An outboard motor as set forth in claim 10, wherein the engine is a crankcase compression, two-cycle, internal combustion engine.
  • 12. An outboard motor as set forth in claim 11, wherein the main cowling member defines an air inlet opening for admitting air to the engine induction system in proximity to the pump drive belt.
Priority Claims (1)
Number Date Country Kind
9-216839 Aug 1997 JP
US Referenced Citations (8)
Number Name Date Kind
3633411 Bass et al. Jan 1972 A
4494507 Yasuhara Jan 1985 A
4850911 Nakahama et al. Jul 1989 A
5367998 Shiohara et al. Nov 1994 A
5373820 Sakamoto et al. Dec 1994 A
5476402 Nakai et al. Dec 1995 A
5637792 Kimura et al. Jun 1997 A
5806473 Kometani et al. Sep 1998 A