Patent Application
20240035495
The present disclosure generally relates to high pressure fluid systems, such as high pressure pumps and intensifiers. In particular, the present disclosure relates to hydraulic pistons and heads that dampen or prevent hydraulic surge that may otherwise occur during operation of a high pressure pump.
Precision cutting for industrial and commercial purposes is often accomplished through the use of a waterjet system that directs a high speed stream of water at a material surface to be cut. Waterjet systems pressurize water to 15,000 psi or greater and convert that pressure to a fluid stream traveling at speeds in excess of Mach 2. This high velocity stream, often mixed with an abrasive, is capable of slicing through hard materials such as metal and granite with thicknesses of more than a foot.
The pumps operating within a waterjet system include plungers that reciprocate within a high pressure chamber to pressurize a fluid in the chamber, and can further include check valves to allow fluids into and out of the high pressure chamber. The pumps typically include seals between the plunger and an inner wall of the chamber and between the check valve and the inner wall of the chamber to prevent high pressure fluid from leaking out of the chamber.
The high pressure fluid flows through a check valve body to an outlet check valve. If the pressure of the fluid is greater than a biasing force provided by high-pressure fluid in an outlet area acting on a downstream end of the outlet check valve, the high pressure fluid overcomes the biasing force, and passes through the outlet check valve to the outlet area. Typically, a pump has multiple cylinders, and pressurized fluid from the outlet area of each pump is collected in an accumulator. High-pressure fluid collected in this manner is then selectively used to perform a desired function, such as generating a fluid jet to process (e.g., cut) a workpiece.
Referring to
The check valve assembly 30b has check valves 33 for admitting unpressurized fluid into the pressure vessel 20 during an intake stroke of the plunger and allowing pressurized fluid to exit the pressure vessel 20 after a power stroke of the plunger 30a. Both inserts 30 are held in position relative to the pressure vessel 20 by a yoke 12 that includes end caps 13 secured with threaded rods 15 that bias the end caps 13 toward the pressure vessel 20.
Two seal assemblies 40 (shown as a dynamic seal assembly 40a and a static seal assembly 40b) may seal a gap 21 between the inserts 30 and an inner wall of the bore 22 to prevent fluid from leaking from the pressure vessel 20. The dynamic seal 40a seals a portion of the gap 21 between the reciprocating plunger 30a and the inner wall 25, and the static seal 40b seals a portion of the gap 21 between the stationary check valve body 30b and the inner wall 25. A sleeve 14 adjacent the inner wall 25 between the seal assemblies 40 reduces the volume of the gap 21.
In some known high pressure pumps, hydraulic oil forces a hydraulic piston to move in a first direction, referred to as a “stroke.” At the end of the stroke, the hydraulic piston stops its movement in the first direction, and then reverses to begin movement in a second direction that is opposite the first direction. The inertia of the hydraulic piston may result in impact of the hydraulic piston and another component of the high pressure pump (e.g., a hydraulic head) that is adjacent the hydraulic piston at the end of its stroke.
Such an impact may result in hydraulic oil (e.g., trapped within a front pocket of the hydraulic piston) being subjected to a sudden pressure surge. This pressure surge may result in damage or failure of components of the high pressure pump (e.g., locating pins, retaining springs, plunger, etc.). The risk of this damage or failure may increase significantly if a check valve mounted within the hydraulic piston is damaged such that hydraulic fluid is permitted to leak into the front pocket of the hydraulic piston within which the plunger may be secured. The pressure surge within the front pocket may result in ejection of the plunger from the pocket.
The present disclosure is directed to pressure relief structures and components that provide passage for trapped hydraulic oil (e.g., within a front pocket of a hydraulic piston) so as to prevent a sudden pressure surge.
According to one embodiment, a hydraulic piston includes a body, a pocket, and a hydraulic surge dampener. The body extends along an axis from a front surface of the body to a rear surface of the body, and the body includes a shoulder portion and a neck portion. The shoulder portion has a first cross-sectional dimension measured in a first direction that is perpendicular to the axis. The neck portion extends out from the shoulder portion along a second direction that is parallel to the axis, and the neck portion has a second cross-sectional dimension measured in the first direction, wherein the second cross-sectional dimension is less than the first cross-sectional dimension.
The pocket extends into the neck portion along a third direction that is opposite the second direction. The pocket enters the neck portion through an opening in the front surface, which is spaced from the shoulder portion by the neck portion. At least a portion of the pocket is bounded by an inner surface of the neck portion. The hydraulic surge dampener forms at least one passage that extends from the pocket, through the neck portion via an opening in the inner surface, and exits the neck portion via an opening in an outer surface of the neck portion that faces away from the inner surface.
According to one embodiment, a hydraulic head includes a body, a bore, and a hydraulic surge dampener. The bore extends through the body along an axis, and the body includes a shoulder portion and a neck portion. The shoulder portion has a first cross-sectional dimension measured in a first direction that is perpendicular to the axis. The neck portion extends out from the shoulder portion along a second direction that is parallel to the axis, and the neck portion has a second cross-sectional dimension measured in the first direction, wherein the second cross-sectional dimension is less than the first cross-sectional dimension. The hydraulic surge dampener forms at least one passage that extends from the bore, through the neck portion via an opening in an inner surface of the neck portion, and exits the neck portion via an opening in an outer surface of the neck portion. At least a portion of the bore is bounded by the inner surface of the neck portion, and the outer surface faces away from the bore.
According to one embodiment, a high pressure pump includes a hydraulic chamber, a hydraulic piston, and a hydraulic head. The hydraulic chamber has at least one port that provides entry for hydraulic fluid into an interior cavity of the hydraulic chamber. The hydraulic piston is movable within the interior cavity along a first direction and a second direction that is opposite the first direction.
The hydraulic piston includes a piston body that extends along a piston axis from a front piston surface of the piston body to a rear piston surface of the piston body. The piston axis is parallel to the first direction and the second direction, and the piston body includes a piston shoulder portion and a piston neck portion. The piston shoulder portion has a first cross-sectional dimension measured in a third direction that is perpendicular to the piston axis. The piston neck portion extends out from the piston shoulder portion along the first direction, and the piston neck portion has a second cross-sectional dimension measured in the third direction, wherein the second cross-sectional dimension is less than the first cross-sectional dimension.
The hydraulic piston includes a pocket extends into the piston neck portion along the second direction, and the pocket enters the piston neck portion through an opening in the front piston surface, which is spaced from the piston shoulder portion in the first direction by the piston neck portion. At least a portion of the pocket bounded by an inner surface of the piston neck portion.
The hydraulic head includes a head body and a bore that extends through the head body along a head axis, and the head body includes a head shoulder portion and a neck shoulder portion. The head shoulder portion has a third cross-sectional dimension measured in the third direction. The head neck portion extends out from the head shoulder portion along the second direction, and the head neck portion has a fourth cross-sectional dimension measured in the third direction, wherein the fourth cross-sectional dimension is less than the third cross-sectional dimension.
The hydraulic surge dampener forms either a first passage that extends from the pocket, through the piston neck portion via an opening in the inner surface of the piston neck portion, and exits the piston neck portion via an opening in an outer surface of the piston neck portion that faces away from the inner surface of the piston neck portion, or a second passage that extends from the bore, through the head neck portion via an opening in an inner surface of the head neck portion, and exits the head neck portion via an opening in an outer surface of the head neck portion that faces away from the bore, or both the first passage and the second passage.
In the drawings, identical reference numbers identify similar elements or acts. The sizes and relative positions of elements in the drawings are not necessarily drawn to scale. For example, the shapes of various elements and angles are not drawn to scale, and some of these elements are arbitrarily enlarged and positioned to improve drawing legibility. Further, the particular shapes of the elements as drawn are not intended to convey any information regarding the actual shape of the particular elements, and have been solely selected for ease of recognition in the drawings.
In the following description, certain specific details are set forth in order to provide a thorough understanding of various disclosed embodiments. However, one skilled in the relevant art will recognize that embodiments may be practiced without one or more of these specific details, or with other methods, components, materials, etc.
Unless the context requires otherwise, throughout the specification and claims which follow, the word “comprise” and variations thereof, such as, “comprises” and “comprising” are to be construed in an open, inclusive sense, that is as “including, but not limited to.”
Reference throughout this specification to “one embodiment” or “an embodiment” means that a particular feature, structure or characteristic described in connection with the embodiment is included in at least one embodiment. Thus, the appearances of the phrases “in one embodiment” or “in an embodiment” in various places throughout this specification are not necessarily all referring to the same embodiment. Furthermore, the particular features, structures, or characteristics may be combined in any suitable manner in one or more embodiments.
As used in this specification and the appended claims, the singular forms “a,” “an,” and “the” include plural referents unless the content clearly dictates otherwise. It should also be noted that the term “or” is generally employed in its sense including “and/or” unless the content clearly dictates otherwise.
Reference herein to two elements “facing” or “facing toward” each other indicates that a straight line can be drawn from one of the elements to the other of the elements without contacting an intervening solid structure. The term “aligned” as used herein in reference to two elements along a direction means a straight line that passes through one of the elements and that is parallel to the direction will also pass through the other of the two elements. The term “between” as used herein in reference to a first element being between a second element and a third element with respect to a direction means that the first element is closer to the second element as measured along the direction than the third element is to the second element as measured along the direction. The term “between” includes, but does not require that the first, second, and third elements be aligned along the direction.
Recitation of ranges of values herein are merely intended to serve as a shorthand method of referring individually to each separate value falling within the range including the stated ends of the range, unless otherwise indicated herein, and each separate value is incorporated into the specification as if it were individually recited herein. All methods described herein can be performed in any suitable order unless otherwise indicated herein or otherwise clearly contradicted by context.
The headings and Abstract of the Disclosure provided herein are for convenience only and do not interpret the scope or meaning of the embodiments.
Referring to
The check valve assembly 60 may include one or more check valves 64 (e.g., respective ones of the check valves 64 admitting unpressurized fluid into the pressure vessel 52, specifically the bore 56, during an intake stroke of the plunger 58, and allowing pressurized fluid to exit the pressure vessel 52 after a power stroke of the plunger 58). The high pressure pump 50 may include an end cap 66 that secures the check valve assembly 60 in position relative to the pressure vessel 52. Similarly, the high pressure pump 50 may include a hydraulic head 68 securable relative to the pressure vessel 52 opposite the check valve assembly 60 and the end cap 66 along the length L.
The high pressure pump 50 may include seals between components of the pump 50 to prevent fluid from leading from the pressure vessel 52. For example, the pump 50 may include a dynamic seal 70 that forms a liquid impermeable barrier between the pressure vessel 52 and the hydraulic head 68. The pump 50 may include a static seal 72 that forms a liquid impermeable barrier between the pressure vessel 52 and the check valve assembly 60. The static seal 72 may include respective passages into the bore 56 for the check valves 64 of the check valve assembly 60. The pump 50 may include a sleeve 74 adjacent an inner wall 76 of the pressure vessel 52, the sleeve 74 being positioned so as to act as a buffer between the reciprocating plunger 58 and the body 54 of the pressure vessel 52.
The high pressure pump 50 may be a double acting pump, (e.g., as shown in the illustrated embodiment). The double acting high pressure pump 50 may include a plurality of the plungers 58 and a plurality of pressure vessels 52, with respective ones of the plurality of the plungers 58 reciprocating within respective ones of the bores 56 of the plurality of pressure vessels 52. Alternatively, the high pressure pump 50 may be a single acting pump that includes only a single plunger 58 reciprocating within a bore 56 of a single pressure vessel 52.
As shown, the high pressure pump 50 may include a hydraulic pressure chamber 80. The hydraulic pressure chamber 80 may include a chamber body 82 and a bore 84 extending through the chamber body 82. As shown, the bore 84 may extend through the chamber body 82 along a length of the hydraulic pressure chamber 80, and the length of the hydraulic pressure chamber 80 may be parallel to the length L of the pressure vessel 52 when the hydraulic pressure chamber 80 is secured to the pressure vessel 52. An inner surface 86 of the hydraulic pressure chamber 80 may face the bore 84 and form an interior cavity 88 of the hydraulic pressure chamber 80.
The hydraulic pressure chamber 80 may include a first port 90 that provides passage for a hydraulic fluid (e.g., hydraulic oil) to enter interior cavity 88. As shown in
The hydraulic pressure chamber 80 may include a second port 96 that provides passage for the hydraulic fluid to exit the interior cavity 88. As shown in
The plunger 58 (e.g., a first plunger 58a) may be carried by the hydraulic piston 62 such that movement of the hydraulic piston 62 results in corresponding movement of the first plunger 58a. As shown, the first plunger 58a may pass through the bore 56 (e.g., a first bore 56a) of the pressure vessel 52 (e.g., a first pressure vessel 52a). As the first plunger 58a advances within the first bore 56a, fluid (e.g., water) within the first bore 56a is pressurized and exits via one of the check valves 64 (e.g., a first check valve 64a) of the check valve assembly 60 (e.g., a first check valve assembly
The pressurized fluid may then exit the high pressure pump 50 (e.g., as indicated by arrow 100) and be delivered to a system 102 (e.g., a waterjet cutting head) that uses the pressurized water (e.g., to form a waterjet that processes a workpiece).
In the embodiment in which the high pressure pump 50 is a double acting pump, a second plunger 58b may be carried by the hydraulic piston 62 such that movement of the hydraulic piston 62 results in corresponding movement of the second plunger 58b. As shown, the second plunger 58b may withdraw through a second bore 56b of a second pressure vessel 52b). As the second plunger 58b withdraws through the second bore 56b, fluid (e.g., water) enters the second bore 56b via one of the check valves 64 (e.g., a second check valve 64b) of the check valve assembly 60 (e.g., a second check valve assembly 60b).
The high pressure pump 50 may include a proximity sensor 104 that senses the hydraulic piston 62 as the hydraulic piston 62 approaches the end of a stroke (e.g., a power stroke for the first pressure vessel 52a as shown in
Due to the inertia of the moving hydraulic piston 62, the change in direction of movement of the hydraulic piston 62 may not be instant. Thus, during operation of the high pressure pump 50, the hydraulic piston 62 may impact another component of the high pressure pump that is adjacent the hydraulic piston 62 at the end of its stroke. As shown, the hydraulic head 68, for example a first hydraulic head 68a positioned between the first pressure vessel 52a and the hydraulic pressure chamber 80, may be impacted by the hydraulic piston 62.
Impact of the hydraulic piston 62 with another component of the high pressure pump 50 may result in hydraulic fluid (e.g., a portion of which may be trapped within a pocket 108 of the hydraulic piston 62) being subjected to a sudden pressure surge. This pressure surge may result in damage or failure of components of the high pressure pump 50 (e.g., locating pins, retaining springs, the plunger 58, etc.).
The hydraulic piston 62 may include one or more check valves 110 that provide passage for hydraulic fluid within the pocket 108 to pass through a portion of the hydraulic piston 62 and exit into a portion of the interior cavity 88 opposite the pocket 108 (i.e., the portion of the interior cavity 88 that is “behind” the hydraulic piston 62 with respect to its direction of movement, or the portion of the interior cavity 88 between the hydraulic piston 62 and a second hydraulic head 68b. However, the check valve 110 may be insufficient to prevent damage caused by impact of the hydraulic piston 62 with another component of the high pressure pump 50. Additionally, the check valve 110 may become damaged, which may greatly increase the risk of damage to the high pressure pump 50 caused by impact of the hydraulic piston 62. The hydraulic piston 62, according to one embodiment, may be devoid of the check valve 110.
The high pressure pump 50 may include one or more hydraulic surge dampeners 17 that may reduce or eliminate the sudden pressure surge described above and the potential damage associated with such a sudden pressure surge. After the change in direction of the hydraulic piston 62 is complete (i.e., such that the hydraulic piston 62 travels away from the first hydraulic head 68a and the first pressure vessel 52a, and (when the high pressure pump 50 is a double acting pump) travels towards the second hydraulic head 68b and the second pressure vessel 52b. As the hydraulic piston 62 travels away from the first hydraulic head 68a (or the hydraulic head 68 when the high pressure pump 50 is a single acting pump), the first plunger 58a withdraws from the first bore 56a of the first pressure vessel 52a.
During the withdrawal of the first plunger 58a from the first pressure vessel 52a, low pressure fluid (e.g., water) may enter the first bore 56a (e.g., via the second check valve 64b of the first check valve assembly 60a). As the hydraulic piston 62 advances towards the second pressure vessel 52b, the second plunger 58b advances within the second bore 56b thereby pressurizing fluid (e.g., water) within the second bore 56b. The pressurized fluid exits the second pressure vessel 52b via one of the check valves 64 (e.g., the first check valve 64a) of the second check valve assembly The pressurized fluid may then exit the high pressure pump 50 (e.g., as indicated by arrow 101) and be delivered to a system (e.g., the system 102) that uses the pressurized water.
The high pressure pump 50 may include a second proximity sensor 104b that senses the hydraulic piston 62 as the hydraulic piston 62 approaches the end of a stroke (e.g., a power stroke for the second pressure vessel 52b as shown in
Referring to
According to one embodiment, the passage 112 extends along a direction (e.g., a first direction D1) that is angularly offset (i.e., non-parallel) with respect to the direction along which the hydraulic piston 62 reciprocates within the hydraulic pressure chamber 80 (e.g., a second direction D2). The first direction D1 and the second direction D2 may be angularly offset by an angle greater than zero degrees. According to one embodiment, the first direction D1 and the second direction D2 may be angularly offset by an angle greater than thirty degrees. According to one embodiment, the first direction D1 and the second direction D2 may be angularly offset by an angle greater than seventy-five degrees. According to one embodiment, the first direction D1 and the second direction D2 may be perpendicular or angularly offset by about ninety degrees (e.g., between 85 degrees and 95 degrees).
According to one embodiment, the hydraulic piston 62 may be radially symmetrical about the central axis 116. As shown the central axis 116 may be parallel to the second direction D2. The hydraulic piston 62, according to one embodiment, may include a neck portion 118 that has a first cross-sectional dimension J1 that is less than a second cross-sectional dimension J2 of a shoulder portion 120 of the hydraulic piston 62. The first cross-sectional dimension J1 and the second cross-sectional dimension J2 may each be measured along a direction perpendicular to one or both of the central axis 116 and the second direction D2. As shown, the first cross-sectional dimension J1 and the second cross-sectional dimension J2 may each be measured along the first direction D1.
The pocket 108 may enter the neck portion 118 through an opening 121 (e.g., formed in the front surface 117). The front surface 117 may be spaced from the shoulder portion 120 along the length of the hydraulic piston 62 (e.g., in a direction parallel to the second direction D2) by the neck portion 118. The opening 121 may face in a direction that is parallel to a direction of travel of the hydraulic piston 62 while it reciprocates within the hydraulic pressure chamber 80.
As shown, the check valve 110 may form a passage that extends from the pocket 108, through the shoulder portion 120 (e.g., entering via an opening 123 in a base surface 125 at which the pocket 108 terminates), and exits the body 114 (e.g., the shoulder portion 120) via an opening 131 in a rear surface 133 of the shoulder portion 120 that faces away from the neck portion 118.
As shown, the hydraulic piston 62 may be a double acting piston that includes the shoulder portion 120 positioned between two neck portions 118 that each extend out from the shoulder portion 120 in opposite directions. Alternatively, the hydraulic piston 62 may be a single acting piston that includes only one neck portion 118 extending out from the shoulder portion 120. The description herein of the hydraulic piston 62 refers to both single acting and double acting pistons, unless specified to the contrary.
The neck portion 118 may include an inner surface 122 that forms or bounds at least a portion of the pocket 108. The pocket 108 may extend into the body 114 of the hydraulic piston 62 and terminate therewithin. The pocket 108 may be sized to receive a portion of the plunger 58. The plunger 58 may be secured within the pocket 108 (e.g., via one or more fasteners 126 (e.g., pins, screws, rivets, etc.) inserted through respective fastener receiving holes 128.
The passage 112 formed by the hydraulic surge dampener 17 may extend from the inner surface 122, through the neck portion 118 (e.g. entering via an opening 127 in the inner surface 122), and exit the body 114 of the hydraulic piston 62 through an outer surface 124 of the neck portion 118 (e.g., exiting via an opening 129 in the outer surface 124). As shown, the outer surface 124 may be opposite the inner surface 122 such that the outer surface 124 faces away from the pocket 108 (e.g., with respect to the first direction D1). The respective passages 112 formed by the through holes 130 may be linear, or they may be non-linear (e.g., curved, or including multiple angularly offset linear segments). According to one embodiment, the through holes 130 may be linear such that a radial ray extending perpendicularly from the axis 116 intersects both the opening 127 in the inner surface 122 and the opening 129 in the outer surface 124 of one of the at least one passages 112.
As shown in
The first number of through holes may be a different size (e.g., smaller as shown, or larger) than the second number of through holes. The first number of through holes may be radially spaced (e.g., equidistantly from adjacent ones) about the central axis 116 at a first position along the length of the hydraulic piston 62. The second number of through holes may be radially spaced (e.g., equidistantly from adjacent ones) about the central axis 116 at a second position along the length of the hydraulic piston 62. For example each of the first number of through holes may be farther from the shoulder portion 120 than each of the second number of through holes is from the shoulder portion 120. According to one embodiment, the first number of through holes may extend through a portion of the neck portion 118 with a cross-sectional diameter that is different from (e.g., larger than as shown, or smaller than) a cross-sectional diameter of a portion of the neck portion 118 through which the second number of through holes extends through.
As shown in
When the hydraulic piston 62 is mounted within the hydraulic pressure chamber 80, the surface 134 may be closer to the hydraulic head 68 than any other portion of the hydraulic piston 62. The surface 134 may be the “leading surface” with respect to the direction of movement of the hydraulic piston 62 during at least a portion of a stroke of the plunger 58.
The surface 134 may be flat (e.g., normal with respect to the second direction D2), with the exception of the one or more grooves 132. Similar to the one or more through holes 130 described above, each of the one or more grooves 132 may form respective passages 112 extending from the inner surface 122, through/across the neck portion 118, and exiting the body 114 of the hydraulic piston 62 through the outer surface 124 of the neck portion 118. The grooves 132 may be linear, as shown, or they may be non-linear (e.g., curved, or including multiple angularly offset linear segments). According to one embodiment, the grooves 132 may be linear such that a radial ray extending perpendicularly from the axis 116 intersects both the opening 127 in the inner surface 122 and the opening 129 in the outer surface 124 of one of the at least one passages 112.
According to one embodiment, the opening 127 may be a shape (e.g., an arc, curve, series of linear segments, etc.) with an open perimeter. Similarly, the opening 129 may be a shape (e.g., an arc, curve, series of linear segments, etc.) with an open perimeter. Thus, the passage 112 formed by the groove 132 may be an open passage that is only partially (i.e., not entirely) surrounded by the body 114 (e.g., the neck portion 118) of the hydraulic piston 62.
As shown in
As shown in
Still referring to
In operation, as the hydraulic piston 62 approaches the end of its stroke (i.e., transitions from movement in one direction to movement in the opposite direction), hydraulic fluid may be present in the pocket 108 of the approaching side of the hydraulic piston 62. As pressure inside the pocket 108 increases (e.g., due to impact or a near impact of the hydraulic piston 62 with another component of the high pressure pump 50, such as the hydraulic head 68), the hydraulic fluid present in the pocket 108 travels along the passage(s) 122 provided by the hydraulic surge dampener 17 to exit the pocket 108. The hydraulic fluid may exit the passage(s) 122 and enter the interior cavity 88 of the hydraulic pressure chamber 80, which the hydraulic fluid may exit (e.g., via the second port 96. The hydraulic fluid may exit the passage(s) 122 and enter the interior cavity 88 of the hydraulic pressure chamber 80, where the hydraulic fluid may assist in the transition of the direction of movement of the hydraulic piston 62.
Referring to
For example, a surface 136 may form an end of the hydraulic head 68 (e.g., the hydraulic head 68 may be devoid of a portion that extends beyond the surface 136 with respect to one component of the second direction D2). The surface 136 may be part of a neck portion 138 of the hydraulic head 68 (similar to the front surface 117 of the neck portion 118 of the hydraulic piston 62 as described above), as shown in
The neck portion 138 may be positioned inside interior cavity 88 of the hydraulic pressure chamber 80 when the high pressure pump 50 is in operation. The hydraulic surge dampener 17 of the hydraulic head 68 may include one or more through holes 139 (e.g., similar to the through holes 130 as described above), as shown in
Referring to
Referring to
Referring to
Referring to
According to one embodiment, both the hydraulic piston 62 and the hydraulic head 68 may include portions of the hydraulic surge dampener 17. The portions may include corresponding grooves 132 and 140 that are aligned with each other such that the grooves 132 and 140 cooperatively define the passages 112 when the hydraulic piston 62 impacts the hydraulic head 68. According to one embodiment, the portions of the hydraulic surge dampener 17 carried by the hydraulic piston 62 and the hydraulic head 68 may be offset or different such that they define separate passages 112.
Other components of the high pressure pump 50 (e.g., any component that directly faces or could come into contact with the reciprocating hydraulic piston 62) may include the hydraulic surge dampener 17 as described above.
Referring to
The high pressure pump 50 may include the hydraulic head 68 secured to the hydraulic pressure chamber 80 such that the neck portion 118 faces the neck portion 138. The high pressure pump 50 may include the hydraulic head 68 secured to the hydraulic pressure chamber 80 such that the neck portion 138 is positioned within the interior cavity 88. The high pressure pump 50 may include the hydraulic head 68 secured to the hydraulic pressure chamber 80 such that the axis 116 is coincident with the axis 148. According to one embodiment, the pocket 108 may be radially symmetrical about the axis 116, and the bore 146 may be radially symmetrical about the axis 148.
In general, in the following claims, the terms used should not be construed to limit the claims to the specific implementations and embodiments disclosed in the specification and the claims, but should be construed to include all possible implementations and embodiments along with the full scope of equivalents to which such claims are entitled. Accordingly, the claims are not limited by the disclosure.
