Patent Application
20210140426
This application relates to a fluid end cartridge for use in a high pressure water pump.
High pressure water pumps are known, and may operate at pressures up to 55,000 psi. These pumps may be used to perform water jetting operations such as surface preparation, cutting, cleaning, coating removal, and other operations. These pumps typically use a fluid cylinder having reciprocating plungers to force the fluid out of an applicator at extremely high pressure. As the plungers reciprocate within the fluid cylinder, the fluid cylinder and components thereof cycle between atmospheric and maximum system pressure.
A cartridge assembly for use in a high pressure pump according to an exemplary aspect of the present disclosure includes, among other things, a cartridge housing. A bore extends through the cartridge housing from a valve end to a packing end. A valve assembly is arranged in the valve end of the bore and configured to abut a valve seat. The bore has a constant diameter between the valve assembly and the packing end. The cartridge assembly is designed to be used in a fluid pump at a fluid pressure of at least 30,000 psi.
In another aspect of this disclosure, a cartridge assembly for use in a high pressure pump includes, among other things, a cartridge housing. A bore extends through the cartridge housing from a valve end to a packing end. A valve assembly is arranged in the valve end of the bore and configured to abut a valve seat. A retainer flange is removably secured to the cartridge housing at an end of the cartridge housing.
These and other features of the present invention can be best understood from the following specification and drawings, the following of which is a brief description.
The drawings can be briefly described as follows:
The frame plate 22 may contain multiple inlets circumferentially spaced about the cartridge 21 in communication with the plenum 24. The valve 30 is mounted within a recess in the valve seat 26. A valve guide 42 is arranged within the housing 28. The valve 30 is biased against the valve seat 26 by a valve spring 38 to close off the flow of water from the plenum 24. The valve spring 38 is arranged radially inward of the valve guide 42. In one example the valve seat 26 may be formed of two portions, an outer valve seat portion 26A and an inner valve seat portion 26B, and the cartridge housing 28 may be formed of two portions, an outer housing 28A and an inner housing 28B. In other embodiments, the valve seat 26 and the cartridge housing 28 may each be formed from a single piece. A bore 40 extends through the inner housing 28B and receives the plunger 32. The bore 40 extends generally along the axis A. A plurality of seals 80, such as o-rings, may be arranged near an outer diameter of the valve seat 26.
A packing spring 44 is arranged within the bore 40. The packing spring 44 may be arranged between the valve guide 42 and a bushing 46, for example. The bushing 46 has a length along the axis A that may be longer than a diameter of the plunger 32, for example. A packing assembly 48 and backup ring 50 may be arranged along the bore 40. This arrangement eliminates the need for a shoulder within the bore 40. That is, the bore 40 has a constant diameter along substantially its entire length. In this example, the bore 40 is tapered at one end but otherwise exhibits a constant diameter along its entire length. The bore 40 extends from a valve end 51 to a packing end 52. In one example, the bore 40 has a constant diameter between the valve guide 42 and the packing end 52 beyond the packing assembly 48. At no point along the inner housing 28B does the inner housing 28B contact the plunger 32.
In one example, the frame plate has a major inner diameter 60 of about 3.757 inches and a minor inner diameter 62 of between about 3.255 and 3.257 inches. The valve seat 26 has an outer diameter of about 3.755 inches. The valve seat 26 has an outer diameter 64 of between about 3.754 and 3.756 inches. In another example, the valve seat outer diameter 64 may be between 3.700 and 3.756 inches. The cartridge housing 28 has a major outer diameter 66 of about 3.7552 inches and a minor outer diameter 68 of about 3.2534 inches. The cartridge housing major outer diameter 66 may be between about 3.750 and 3.760. The cartridge housing minor outer diameter 68 may be between about 3.243 and 3.253. In a further embodiment, the cartridge housing minor outer diameter 68 is about 3.248. The disclosed dimensions illustrate the referenced parameters within 10% of the desired values. In another example, the referenced parameters are within 5% of the desired values, and in another example, the reference parameters are within 2% of the desired values. In some examples, the dimensions are within 0.001 inches of the disclosed values. In an example, a difference between the cartridge housing major outer diameter 66 and the cartridge housing minor outer diameter 68 is about 0.5 inches. A ratio of the cartridge housing outer diameter 66 and the cartridge housing minor diameter 68 is about 1.15. The frame plate major inner diameter 60 is slightly larger than the cartridge housing major outer diameter 66 and the valve seat outer diameter 64 to accommodate a tolerance in assembling these components. The frame plate minor inner diameter 62 is slightly larger than the cartridge housing minor outer diameter 68. The aforementioned ratios and dimensions, both individually and combined, provide a low-cost design which exhibits improved performance, especially at substantially high operating pressures, such as in pumps designed to operate between 30,000 and 55,000 psi. In an example, the cartridge assembly is designed to be used at pressures between 35,000 and 50,000 psi. In a further example, the cartridge assembly is designed to be used at about 40,000 psi.
The discharge valve assembly 34 includes a discharge valve 70 biased within a discharge manifold 72 by a discharge valve spring 74. The discharge valve assembly 34 is biased to a closed position by the discharge valve spring 74. The discharge manifold 72 is secured to the cartridge 21 at a discharge end and houses the discharge passage 36. The discharge manifold 72 may be secured to the frame plate 22 and/or the valve seat 26 with fasteners 78. The fasteners 78 may be screws, for example. A seal 76, such as an o-ring, may be arranged between the discharge manifold 72 and the valve seat 26.
A retainer flange 82 is mounted at an end 85 of the cartridge 21. The retainer flange 82 is secured to the cartridge 21 with bolts 84. A lock washer may be used at the bolts 84. This arrangement may allow for easier access to the inside bore surface, which may allow particular processes to enhance the inside surface and may reduce manufacturing cost.
The disclosed cartridges 21, 121 eliminate a shoulder within the bore of known cartridges. This design instead utilizes a suction valve stop and guide trapped between the cartridge and the valve seat. This arrangement allows the force of the packing spring 44 and the suction valve spring 38 to act on the valve guide 42 and valve seat 26, respectively. Elimination of the shoulder from the bore may reduce cost and stress within the cartridge. The disclosed cartridge and pump design may produce more horsepower in a smaller package than known pumps.
Although the different examples have the specific components shown in the illustrations, embodiments of this disclosure are not limited to those particular combinations. It is possible to use some of the components or features from one of the examples in combination with features or components from another one of the examples.
One of ordinary skill in this art would understand that the above-described embodiments are exemplary and non-limiting. That is, modifications of this disclosure would come within the scope of the claims. Accordingly, the following claims should be studied to determine their true scope and content.
This application claims the benefit of U.S. Provisional Application No. 62/933,710, filed on Nov. 11, 2019.
| Number | Date | Country | |
|---|---|---|---|
| 62933710 | Nov 2019 | US |
