Patent Application
20060024179
This invention relates to hydraulic pumps and, more particularly, to hydraulic pumps that are changed in capacity from one operating condition to another.
Two-stage hydraulic systems generally employ two hydraulic pumps. One pump is operated for low flow conditions and both pumps are operated for high flow conditions. Other two-stage pumps might control a portion of the output flow to a reservoir and a portion of the output flow to a hydraulic system during low flow conditions and both output portions to the hydraulic system during high flow conditions.
It is an object of the present invention to provide an improved two-stage hydraulic pump.
In one aspect of the present invention, the hydraulic pump has a plurality of rollers operable in slots on a rotor to provide the movement of hydraulic fluid from an input low-pressure area to an output high-pressure area.
In another aspect of the present invention, the pumps cooperate with the rotor to provide two pumping chambers and two inlet chambers.
In yet another aspect of the present invention, a control valve is incorporated to direct fluid flow from the output chamber to the desired hydraulic location.
In still another aspect of the present invention, the control valve is operable to direct a portion of the output flow to one of the input chambers thereby reducing the amount of flow going to a hydraulic system.
As seen in
When the rotor 12 is rotated in the direction of Arrow A, the rollers 16 move with the rotor 12, such that the ring 14 will force the rollers 16 inwardly as they transverse the ports outlet 20 and 22 and permit the rollers 16 to move radially outward as they traverse the inlet ports 24 and 26. The rollers 16 and the slots 18 cooperate to form a plurality of spaces or volumes 28. As the rollers 16 move inwardly, the spaces 28 decreases in size such that fluid therein is discharged through the port 22. As the rotor 12 moves the rollers 16 from a top dead center 30 toward a bottom dead center 32, a space 33 between the rotor 12 and the ring 14 steadily decreases thereby forcing fluid in this space into the port 20. Also, as the rotor 12 rotates from the bottom dead center 32 to the top dead center 30, the spaces 28 increase thereby filling with fluid while and the space 33 also increases thereby filling that space with fluid. Thus, the rotation from bottom dead center 32 to top dead center 30 is known as the inlet stroke and from top dead center 30 to bottom dead center 32 is known discharge stroke.
As seen in
In the spring set position shown, the valve 36 connects the reservoir 38 with the passage 42 and therefore the port 26. During the spring set position, the passage 34 is blocked at the valve 36. When the valve 36 is placed in the pressure set position with a control pressure at arrow 50, the valve member 46 moves against the spring 48 to provide communication between the passage 34 and the passage 42 while simultaneously disconnecting communication between the passage 40 and passage 42.
When this occurs, some of the fluid (approximately the amount discharged from the spaces 28) in the passage 34 will be directed through the valve 36 to the passage 42 and thence through the port 26, which is present at the underside or radially inward side of the rollers 16. This portion of the high-pressure fluid will operate to pressurize the radially inward portion of the rollers 16 such that it is not delivered to the hydraulic system 44 but is rather recycled through the pump 10 thereby reducing the high pressure output fluid volume of the pump 10, which is delivered to the hydraulic system 44. Thus, a two-stage pump is created.
By way of example, the two-stage pump may be designed with the following characteristics in mind. The total pump displacement being 49.26 cubic centimeters per revolution; the low flow pump displacement, that is, the inner port 22, being 21.18 cubic centimeters per revolution, thus the ratio of low flow volume to total flow volume is 43 percent. The hydraulic pump 10 includes thirteen rollers having a roller diameter of 18 millimeters and a roller length of 20 millimeters. The area between the radially outer portion of the rotor 12 and the ring 14 is 61.57 square millimeters, and the area of the inner portion between the rollers 16 and the bottom of slots 18 is 20.84 square centimeters. These numbers are given by way of example only and are not designed or considered to be limiting of the invention.
The pump 10 is also designed so that the crossover of both the inner and outer portions at top and bottom dead centers occur at the top of the sine wave, which is conventional. The output flow of a gerotor pump and/or roller type pump is generally a sine wave function. By having the crossover occur at the top of the sine wave, the lowest output flow or change in flow per degree of revolution is encountered. This will aid in quieting the pump. Also, during the crossover of the rollers occur at one-half intervals; that is, when a roller is crossing at top dead center 30 there is no crossover at bottom dead center 32 and vice versa.
As seen in
