Pumps – Three or more cylinders arranged in parallel – radial – or... – Radial cylinders
Reexamination Certificate
1999-08-03
2001-06-26
Freay, Charles G. (Department: 3746)
Pumps
Three or more cylinders arranged in parallel, radial, or...
Radial cylinders
C417S470000
Reexamination Certificate
active
06250893
ABSTRACT:
PRIOR ART
The invention relates to a radial piston pump for a high-pressure fuel supply in fuel injection systems of internal combustion engines, in particular in a common rail injection system. A drive shaft which is supported in a pump housing and is embodied eccentrically or has cam-like protrusions in the circumferential direction, and having a plurality of pistons, disposed radially in a given cylinder chamber relative to the drive shaft, are movable radially back and forth by rotation of the drive shaft in the respective cylinder chamber.
However, it should be noted that the present invention can be employed not only in a radial piston pump but also in high-pressure pumps, especially with demand-based quantity regulation.
In an internally supported radial piston pump of the type referred to at the outset, the base of each of the pistons has contact with the drive shaft. The pistons are set successively into a reciprocating motion by the eccentricity of the drive shaft or by the cam-like protrusions on the drive shaft. However, the rotating drive shaft exerts not only forces in the radial direction relative to the drive shaft on the pistons, or in other words in the longitudinal direction of the pistons, but also transversely to the pistons. These transverse forces generate a moment on the respective piston.
Within the scope of the present invention, it has been found that the piston base, which has contact with the drive shaft or with a ring disposed between the drive shaft and the piston base, was damaged during operation. This was particularly true for a piston whose base is formed by a plate that is secured to the piston by a cage and is pressed against the ring by a spring. In this particular piston, breakage of the cage occurred frequently. The damage to the piston base occurred to an increased extent when the cylinder chambers were partly filled. The damage to the piston base is disadvantageous because proper operation of the radial piston pump is no longer assured if the piston base or especially the cage breaks.
It is therefore the object of the invention to furnish a radial piston pump which overcomes the above-discussed disadvantages. In particular, damage to the piston base, such as cage breakage, is to be prevented, so that proper operation of the radial piston pump is assured even under partial filling conditions. The radial piston pump of the invention should withstand a pump pressure of up to 2000 bar.
This object is attained by the radial piston pump disclosed hereinafter. Particular types of embodiment of the invention also are disclosed.
A radial piston pump for high-pressure fuel supply in fuel injection systems of internal combustion engines, in particular in a common rail injection system. The piston pump has a drive shaft which is supported in a pump housing and is embodied eccentrically or has cam-like protrusions in the circumferential direction. Further a plurality of pistons, are disposed radially in a given cylinder chamber relative to the drive shaft, which are movable radially back and forth by rotation of the drive shaft in the respective cylinder chamber. The above object is attained in that one transverse force absorbing device is disposed between each piston and the drive shaft. The damage to the piston base is caused by the moments acting on the pistons. The transverse force absorbing device absorbs the forces acting crosswise to the pistons. This has the advantage that only forces in the longitudinal direction are now brought to bear on the pistons. This means that practically no moments act on the pistons. This reduces the load exerted by the drive shaft on the pistons considerably. Thus even at peak pressures of up to 2000 bar, a long service life of the pistons is assured.
One special type of embodiment of the invention is characterized in that the transverse force absorbing device is movable back and forth in the same direction as the associated piston. This assures that forces in the radial direction from the drive shaft, that is, in the longitudinal direction of the pistons, can be output to the pistons to the transverse force absorbing device. This assures the reciprocating motion of the pistons of the radial piston pump that is necessary for pump operation.
A further particular type of embodiment of the invention is characterized in that the transverse force absorbing device is guided in a respective bore in the housing that extends in the same direction as the associated cylinder chamber. The guidance, even at high pump pressures and rapid load changes, makes a reciprocating motion of the transverse force absorbing device possible. In particular, canting of the transverse force absorbing device in the cylinder chamber is averted.
A further particular type of embodiment of the invention is characterized in that the transverse force absorbing device is a cup tappet with a cup-shaped body. Within the scope of the present invention it has been found that a cup tappet is especially highly suitable for absorbing the transverse forces. Other forms that perform the same function are equally conceivable.
A further particular type of embodiment of the invention is characterized in that the bottom of the cup tappet is formed by a force absorbing plate. The force absorbing plate is in contact with the drive shaft and can have a variable thickness, depending on the load. The surface of the force absorbing plate can be especially treated, in order to assure high wear resistance.
A further particular type of embodiment of the invention is characterized in that the force absorbing plate is connected to a guide ring by the cup-shaped body. The guide ring slides in the cylinder chamber. The face in contact with the cylinder chamber can be especially treated, to minimize the frictional forces. The guide ring assures that the transverse force absorbing device will not become canted in the cylinder chamber. The dimensions of the guide ring depend on the pump pressure and on the number of load changes per unit of time.
A further particular type of embodiment of the invention is characterized in that a plurality of openings are provided in the cup-shaped body. The openings serve the purpose of pressure equalization and assure that even if the full stroke is utilized, there will be only a minimal pressure difference between the chamber surrounding the drive shaft and the respective cylinder chamber. As a result, the increase in Hertzian stress in the useful stroke remains slight, and in the intake stroke, complete filling of the element is assured.
A further particular type of embodiment of the invention is characterized in that the pistons are each pressed by a spring against the associated force absorbing plate of the cup tappet. By means of the spring force, the piston is moved toward the drive shaft, so that fuel is aspirated. It is also possible for the force absorbing plate of the cup tappet to be pressed against the drive shaft by a spring. In that case, however, it would be necessary for the force absorbing plate to be connected to the piston, to assure the aspiration of fuel. If the piston is acted upon directly by the spring force, then this connection between the force absorbing plate and the piston can be omitted. This variant has the advantage that a radial piston pump designed in this way can be produced simply and economically. Also in this variant, it is readily possible to apply the present invention to known radial piston pumps.
A further particular type of embodiment of the invention is characterized in that the force absorbing plate is embodied in slightly crowned fashion on the side oriented toward the drive shaft. The convex embodiment of the force absorbing plate serves to reduce the area of contact between the drive shaft and the force absorbing plate. This advantageously reduces the moment brought to bear on the cup tappet by the drive shaft. In the design of the force absorbing plate, the elastic deformation of the cup tappet must be taken into the account.
A further particular type of embodiment of the invention is characte
Freay Charles G.
Greigg Edwin E.
Greigg Ronald E.
Robert & Bosch GmbH
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