High pressure axial piston pump with multiple discharge ports

A high pressure axial piston pump displaces high pressure, high volume fluid into a 1994-2003 7.3 liter power stroke or T444E International engine. A pump housing forms a central borehole, an intake port, and two discharge ports angled about 122 degrees from each other and in fluid communication with engine. A drive shaft rotates a cylinder block about an axis of rotation. A cam is tilted at an angle relative to axis of rotation. Multiple pistons, having a cam end and a block end, reciprocate through cylinder block. The cam end is constrained to follow surface of cam. When pistons move proximally to tilted cam, the block end restricts intake of fluid, and cam end enables discharge of fluid. When pistons move distally from tilted cam, the block end enables intake of fluid, and cam end restricts passage through discharge ports. The pump is fabricated from billet aluminum material.

FIELD OF THE INVENTION

The present invention relates generally to a high pressure axial piston pump with multiple discharge ports. More so, the present invention relates to an axial piston oil pump that forcibly and variably displaces high volumes and pressures of oil into the injectors of a 7.3 liter power stroke engine or a T444E International engine manufactured from 1994 to 2003 through two discharge ports, rather than one discharge port, which feed directly into the injectors of the engines, and which are angled about 122° away from each other.

BACKGROUND OF THE INVENTION

Typically, an axial piston pump is a positive displacement pump that has a number of pistons in a circular array within a cylinder block. It can be used as a stand-alone pump, a hydraulic motor or an automotive air conditioning compressor. The axial piston pump has a number of pistons arranged in a circular array within a cylinder block which is commonly referred to as a cylinder block, rotor or barrel. This cylinder block is driven to rotate about its axis of symmetry by an integral shaft that is, more or less, aligned with the pumping pistons.

Often, axial piston pumps include a cam, referred to as a swashplate or tilt plate, against which the axial piston ends bear and around which such ends rotate with the angled surface of the swashplate. This allows a cyclic reciprocal movement of the pistons providing each cylinder with low pressure intake and high pressure discharge of hydraulic fluid on each rotation. The oil or hydraulic fluid being pumped from the axial piston pump is generally discharged through a single outlet. This feeds the fluid into oil rails, before entering the injector of the engine.

Generally, billet aluminum is fabricated in a conventional aluminum extrusion operation. In a typical manufacturing process, aluminum stock in the form of large logs, perhaps 5″ to 16″ in diameter and up to 20′ to 24′ in length are fed on a conveyor through an elongated furnace, where they are heated continuously to about 800° to 950° Fahrenheit. After heating, the logs are cut into short lengths called billets, which are fed immediately into an extruder, while the billets are hot. The extruder includes a ram that presses the billets through a die that forms the aluminum into extrusions of a desired shape. The extrusions can then be cut into desired lengths. The billets are cut to specific lengths, depending upon the particular part being extruded.

Other proposals have involved displacing fluids through an axial piston pump at high volumes and pressures. The problem with these axial piston pumps is that they do not provide enough outlets for the discharged fluid. Also, the construction material is not conducive to operate the pump with minimal noise. Self-priming can also be problematic with the prior art axial piston pumps. Even though the above cited axial piston pumps meets some of the needs of the market, a high pressure axial piston pump with two discharge ports angled at a 122° angle away from each other, which is operational with a 7.3 liter power stroke engine or T444E International engine manufactured from 1994 to 2003, and which is fabricated from integral billet aluminum material, is still desired.

SUMMARY

Illustrative embodiments of the disclosure are generally directed to a high pressure axial piston pump fabricated from billet aluminum material, and having two discharge ports disposed at an angle of about 122° away from each other, and being operational with a 7.3 liter power stroke engine or T444E International engine manufactured from 1994 to 2003.

In some embodiments, the axial piston pump comprises a pump housing that protectively encapsulates, and segregates different components of the axial piston pump. The pump housing forms a central borehole for receiving a rotatable drive shaft, an intake port for receiving a fluid, and two discharge ports for discharging the fluid into the engine. The axial piston pump further comprises a cylinder block, concentrically disposed in the pump housing. The cylinder block is defined by multiple piston chambers arranged in a circular array around the central borehole. The pump housing and the cylinder block may be fabricated from an integral billet aluminum material.

A fluid supply line, carrying a fluid such as motor oil, is in fluid communication with the intake port. The fluid supply line supplies the fluid to the intake port in the pump housing. Multiple delivery lines are arranged in fluid communication with the fluid supply line. The delivery lines carry the fluid through the pump housing, from the intake port to the discharge ports. The discharge ports are oriented about 122° away from each other along a plane, so as to optimize the volume and pressure of fluid entering the engine. Furthermore, the use of two, rather than one, discharge ports serve to discharge the fluid into the injectors of the engine at high pressures, and high volumes.

A drive shaft rotates the cylinder block about an axis of rotation. A tilted cam is disposed inside the cylinder block. The tilted cam may be fixed at a tilted angle, or may variably tilt at an angle relative to the axis of rotation. A plurality of pistons is axially disposed through the piston chambers of the cylinder block. The pistons are defined by a cam end and a block end. The cam end of the pistons is constrained to follow the surface of the tilted cam, allowing a cyclic reciprocal movement of the pistons. Thus, as the cylinder block rotates, the pistons reciprocate in a sinusoidal axial motion.

In this manner, when the pistons move proximally to the tilted cam, the block end of the piston restricts passage of the fluid through the intake port, and the cam end of the piston enables passage of the fluid through the discharge outlets. Further, when the pistons move distally from the tilted cam, the block end of the piston enables free passage of the fluid through the intake port, and the cam end of the piston restricts passage of the fluid through the discharge ports.

One objective of the present invention is to provide a high pressure axial piston pump that pumps motor oil and hydraulic fluids into a 7.3 liter power stroke engine or T444E International engine manufactured from 1994 to 2003 at high pressures and volumes.

Another objective is to provide two discharge ports that enable efficient passage of fluid to be discharged into oil rails that feed an injector, such that two discharge ports, rather than one, enable greater pressure and volume discharge of the fluids.

Another objective is to orient the discharge ports about 122° away from each other along a plane, so as to more uniformly discharge the fluid into the engine, create a self-priming mode, and optimize the volume and pressure of fluid entering the engine.

Another objective is to provide a high pressure axial piston pump configured to operate with a 7.3 liter power stroke engine or T444E International engine manufactured from 1994 to 2003.

Another objective is to enhance the structural integrity of the high pressure piston pump through construction with an integral aluminum billet material.

Yet another objective is to operate the pump with minimal noise.

Yet another objective is to operate the pump such that it operates at a high self- priming mode.

Yet another objective is to reduce the weight, size, and cost of an axial piston pump.

Yet another objective is to provide an inexpensive to manufacture high pressure axial piston pump.

DETAILED DESCRIPTION OF THE INVENTION

As referenced inFIG. 1, a high pressure axial piston pump100with multiple discharge outlets is operational with a 7.3 liter power stroke engine, or T444E International engine that is manufactured from 1994 to 2003. The high pressure axial piston pump100, hereafter “pump100” is unique in that two discharge ports106a-b,rather than one discharge port, are used for discharging a fluid110into the engine108. The use of two discharge ports106a-ballows for the displacement of high volumes and pressures of motor oil into the injectors of the engine108. Further, the disposition of the discharge ports at a 122° angle away from each other enables the axial piston pump to variably displace high volumes and pressures of motor oil into the injectors of the engine. This works to enhance self-priming of the pump100. The angled disposition of the two discharge ports106a-bis also effective for increasing the volume and rate discharge of the fluid110, which creates a more efficient engine108. The construction of the pump100from integral billet aluminum material enhances structural integrity of the pump100, and reduces noise during operation.

As illustrated inFIG. 2, the pump100comprises a pump housing102defined by an intake end200aand a discharge end200b.The pump housing102is configured to protectively house, and segregate other components described below. In one embodiment, the pump housing102has a generally cylindrical shape. Though in other embodiments, other shapes may be used. In some embodiments, the pump housing102may be fabricated from an integral billet aluminum material. As discussed below, use of billet aluminum enhances the structural integrity of the pump housing102and helps reduce operational noise.

AsFIG. 3illustrates, the pump housing102is defined by a central borehole300. The central borehole300runs concentrically through the pump housing102. In some embodiments, a rotatable drive shaft706is concentrically disposed through the central borehole300. As discussed below, the rotatable drive shaft706rotates inside the central borehole300to rotatably drive a cylinder block700.

Turning now toFIG. 4, the intake end200aof the pump housing102is defined by at least one intake port104, through which the fluid110is introduced into the pump housing102. The intake port104forms a circular aperture integral with the pump housing102. The intake port104may include a suction intake port104, since the reciprocating piston-action creates a sucking effect on the fluid. In some embodiments, a fluid supply line (not shown), which is in fluid communication with the intake port104, supplies the fluid110to the intake port104.

In addition to the fluid supply line, multiple delivery lines302a-care arranged in communication with the fluid supply line and the two discharge ports106a-b.The delivery lines302a-care arranged to carry the fluid110from the intake port104to the two discharge ports106a-b.Thus, the intake port104enables fluid110to be sucked in from the fluid supply line and into the delivery lines302a-cwithin the pump housing102. In one non-limiting embodiment, the intake port104has a diameter of about ½″.

In this regard,FIG. 10illustrates a close up view of a first delivery line302aintegral with the intake port104for carrying the fluid110from the fluid supply line into the pump housing102. Furthermore,FIG. 9is illustrative of a second delivery line carrying the fluid110through the pump housing102; and a third delivery line302ccarrying the fluid110to the two discharge ports106a-b.In other embodiments, more delivery lines may be used, depending on the required pressure and volume displacement of fluid.

In some embodiments, the fluid110may include motor oil or a hydraulic fluid known in the art for operation and lubrication of a 1994-2003, 7.3 liter power stroke engine or a T444E International engine. The fluid110may also include any petroleum based compositions. The fluid110has sufficient viscosity to flow through the various ports and delivery lines taught in the present embodiment.

AsFIG. 5references, the discharge end200bof the pump housing102is also defined by a plurality of discharge ports106a-b,through which the fluid110is discharged into the engine108. The discharge ports106a-bform circular apertures integral with the pump housing102. In one non-limiting embodiment, the discharge ports106a-bhave a diameter of about ½″.

In one non-limiting embodiment shown inFIG. 8, the discharge ports106a-bare oriented about 122° from each other along a plane800. By angling the discharge ports106a-baway from each other, rather than parallel to each other, the displacement pressure and volume of the fluid being discharged increases. This is partially because the oil rails and injectors in the engine108can be positioned further away from each other, and thereby disperse the fluid more uniformly into the inner workings of the engine108. This also works to enable a self-priming mode for the pump100.

In some embodiments, multiple delivery lines302a-cform integral relationships with the ports104,106a-b,and run through the pump housing102. The delivery lines302a-care in fluid communication with the fluid supply line to receive the fluid110, and also carry the fluid110from the intake port104to the discharge ports106a-b.In one non-limiting embodiment, the discharge ports106a-bare two discharge ports106a,106b.It is significant to note that by using two discharge ports106a-b,a greater volume and pressure displacement of the fluid110is possible. Though in other embodiments, the pump100may utilize more than two discharge ports.

In one embodiment shown inFIG. 8, the two discharge ports106a-bextend at an angle from the cylinder block700. The two discharge ports106a-bform a friction fit relationship with two oil rails (not shown) from the engine108. The oil rails are integral with the injector (not shown) of the engine108, such that fluid is displaced from the two discharge ports106a-bto the engine108. In this manner, the fluid110is efficiently guided from the discharge ports106a-bto the engine108.

In one non-limiting embodiment, the engine108is a 7.3 liter power stroke engine108or a T444E International engine108manufactured from 1994 to 2003. Though in other embodiments, the engine108may be a similar engine108, motor, or combustion apparatus that is manufactured approximately from the years 1994 to 2003.

In some embodiments, the pump housing102and the cylinder block700are fabricated substantially from an integral billet aluminum material. The billet aluminum material is configured to enhance the structural integrity of pump100, and also help reduce operational noise. Those skilled in the art will recognize that billet aluminum is fabricated in a conventional aluminum extrusion operation; whereby aluminum stock in the form of large logs, perhaps 5″ to 16″ in diameter and up to 20′ to 24′ in length, are fed on a conveyor through an elongated furnace, where they are heated continuously to about 800° to 950° Fahrenheit.

After heating, the logs are cut into short lengths called billets, which are fed immediately into an extruder, while the billets are hot. The extruder includes a ram that presses the billets through a die that forms the aluminum into extrusions of a desired shape. The extrusions can then be cut into desired lengths. The billets are cut to specific lengths, depending upon the particular part being extruded. This process creates an aluminum cylinder block that can withstand high pressures, which provides great advantage when displacing high volumes and pressures of motor oil into the injectors of the engine.

Looking now atFIG. 7, the pump100comprises a cylinder block700that is concentrically disposed in the pump housing102. In one non-limiting embodiment, the cylinder block700has a generally disc shape. As shown inFIG. 6, the drive shaft706running through the central borehole300works to rotatably drive the cylinder block700at variable speeds, so as to rotate about an axis of rotation708. In some embodiments, the rotational speed of the drive shaft706has a direct correlation with the volume and pressure of fluid110that is being displaced through the discharge ports106a-b.

In some embodiments, the cylinder block700may be defined by a plurality of piston chambers704a-cthat is arranged in a circular array around the central borehole300. The piston chambers704a-cserve to house and enable axial reciprocating movement by a plurality of pistons714a-c,as described below. The piston chambers704a-calso serve to carry the fluid110between the intake port104and the discharge ports106a-bin conjunction with the position of the pistons714a-cin the piston chamber704a-c.

In some embodiments, a rotary valve702is disposed at the block end716bof the pistons714a-c.The rotary valve702is configured to connect the piston chambers704a-cto the fluid supply line and the delivery lines302a-c.The rotational position of the rotary valve702regulates flow of fluid110through the piston chambers704a-c,the fluid supply line, and the delivery lines302a-c.

Looking again atFIG. 7, a tilted cam710is disposed inside the cylinder block700. The tilted cam710serves as a surface for the pistons714a-cto ride, so as to reciprocate in a sinusoidal axial motion. Those skilled in the art will also recognize that the tilted cam710can include a swashplate. The tilted cam710is configured to be fixedly, or variedly tilted at an angle relative to the axis of rotation708. In some embodiments, the tilted cam710is fixedly tilted at a predetermined angle relative to the axis of rotation708. In this embodiment, the tilted cam710is provided centrally with a hub on which the rotation pivot of the tilted cam710is locked. In other embodiments, the angle of the tilted cam710is variably adjusted. Those skilled in the art will recognize that altering the angle of the tilted cam710serves to increase or decrease the fluid110displacement capacity of the pump100.

As discussed above, the pump100comprises a plurality of pistons714a-c.The pistons714a-care axially disposed through the piston chambers704a-cof the cylinder block700. In this manner, the pistons714a-care operable to rotate with the cylinder block700, which is driven by the rotatable drive shaft706. In one embodiment, five pistons may be used. Though in other embodiments, more or less pistons may be used, depending on the fluid displacement requirements.

Looking back atFIG. 7, the pistons714a-care defined by a cam end716a,and a block end716b.The cam end716aof the piston714amay be wider than the block end716b,and is constrained to follow the surface712of the tilted cam710. In this manner, the cam end716arests flush on the tilted cam710while rotating with the cylinder block700. The pistons714a-crotate and simultaneously reciprocate through the piston chambers704a-cin correlation with the rotational speed of the drive shaft706. This creates a cyclic reciprocal movement of the pistons714a-c.Thus, as the cylinder block700rotates, the pistons714a-creciprocate in a sinusoidal axial motion.

This axial motion by the pistons714a-ccreates a reciprocation cycle involving fluid110being displaced through the piston chambers704a-cand discharge ports106a-b.Thus, when a pistons714amoves proximally to the tilted cam710, the block end716bof the piston714arestricts passage of the fluid110through the intake port104, and the cam end716aof the piston714aenables passage of the fluid110through the discharge ports106a-b.The piston714athen moves to reach a bottom of the reciprocation cycle, i.e., bottom-dead-center. At this position, the connection between the piston chamber704aand intake port104is closed. Shortly thereafter, the piston chamber704abecomes open to the discharge ports106a-bagain and the pumping cycle starts over.

Continuing with the reciprocation cycle of the piston714a,when the piston714amoves distally from the tilted cam710, the block end716bof the piston714aenables free passage of the fluid110through the intake port104, and the cam end716aof the piston714arestricts passage of the fluid110through the discharge ports106a-b.Thus, when the piston714ais at a top of the reciprocation cycle, i.e., top-dead-center, the connection between the trapped fluid110in the piston chamber704aand the discharge ports106a-bis closed. Shortly thereafter, that same piston chamber704abecomes open to the intake port104. As the piston714acontinues to rotate about the axis of rotation708in the cylinder block700, the piston714amoves proximally to the tilted cam710; thereby increasing the volume of the trapped piston chamber704a.As this occurs, fluid110enters the piston chamber704afrom the intake port104to fill the void.

As discussed above, adjusting the angle of the tilted cam710relative to the axis of rotation708changes the amount of fluid110displaced through the discharge ports106a-b.As the pistons714a-crotate about the axis of rotation708, the angle of the tilted cam710is varied. This tilting articulation causes the pistons714a-cto move in and out of their respective piston chambers704a-c.Thus, changing the angle of the tilted cam710causes the stroke of the pistons714a-cto be varied continuously. In some embodiments, the angle of the tilted cam710may be variably adjusted.

For example, if the tilted cam710is tilted at a sharp angle relative to the axis of rotation708, a substantially large volume of fluid110is sucked in through the intake port104and discharged through the two discharge ports106a-b.If the tilted cam710is, however, generally perpendicular to the axis of rotation708, a substantially negligible volume of fluid110is sucked in through the intake port104. In one embodiment, the tilted cam710can tilt up to 10° relative to the first end of the piston714a.As the tilted cam710tilts to press against the piston714a,the angle of the tilted cam710causes the piston714ato move in and out of their respective piston chamber704a.

In one embodiment, if the tilted cam710is perpendicular to the axis of rotation708, substantially no fluid110flows through the pump100. In another embodiment, if the tilted cam710is tilted at a sharp angle, a substantially large volume of fluid110is pump100ed.Consequently, high volume, high pressure displacement of fluid110pump100edper revolution of the drive shaft706may be varied while the pump100operates by varying both the rotation of the drive shaft706and the angle of the tilted cam710.