United States Patent (19)
`Pacht
`
`(54) HIGH PRESSURE FLUID DELIVERY
`SYSTEM
`75) Inventor: Amos Pacht, Houston, Tex.
`(73) Assignee: Partek Corporation of Houston,
`Houston, Tex.
`(21) Appl. No.: 853,113
`22 Filed:
`Nov. 21, 1977
`51) Int. Cl. .........
`... F04B 39/14; F04B 21/02
`52 U.S. C. ..................................... 417/454; 417/539
`58) Field of Search ............... 417/454, 571, 901, 568,
`417/539
`
`(56)
`
`References Cited
`U.S. PATENT DOCUMENTS
`l/1951
`Collins ................................. 417/454
`2,537,742
`8/1952 Towler et al. ....................... 417/569
`2,604,855
`3,212,280 10/1965 Thomas et al. ...................... 417/901
`3,220,202 11/1965 Goltzmann .......................... 417/901
`3,323,467
`6/1967 Heinz ................................... 417/454
`3,348,570 10/1967 Nealy ................................ 137/454.6
`3,373,695
`3/1968 Yohpe .................................. 417/454
`3,709,638
`1/1973
`Iguchi.................................. 417/454
`3,746,483
`7/1973
`Hindel .................................. 417/571
`3,811,801
`5/1974 Buse et al. .....
`... 417/454
`3,870,439
`3/1975 Stachowiak .......
`... 417/454
`3,916,771 11/1975 Nendzig ............
`... 417/568
`4,140,979
`2/1979 Mulvey ................................ 417/454
`FOREIGN PATENT DOCUMENTS
`793057 4/1958 United Kingdom..................... 417/539
`Primary Examiner-William L. Freeh
`
`(11)
`(45.
`
`4,277,229
`Jul. 7, 1981
`
`Attorney, Agent, or Firm-Hubbard, Thurman, Turner,
`Tucker & Glaser
`ABSTRACT
`57
`A high pressure fluid delivery system including an im
`proved reciprocating pump is disclosed. The pump has
`a fluid cylinder block, with a stuffing box mounted on
`one side and a suction manifold on the other. A cylindri
`cal passage extends into the fluid cylinder block from
`the stuffing box side of the block to receive a plunger
`which is mounted in the stuffing box. A cylindrical
`chamber, coaxial with the passage, extends from the
`passage to the suction manifold side of the fluid cylinder
`block. In the suction manifold, a suction port leads to
`the cylindrical chamber of the fluid cylinder block.
`The cylindrical chamber holds a suction valve, with a
`valve seat and a valve guide. A discharge valve and
`valve seat are provided in a cylindrical opening extend
`ing from the chamber to an outer wall of the fluid cylin
`der block. A plug or cover in the cylindrical opening
`holds the discharge valve elements in place and serves
`as a guide for the discharge valve. An opening in the
`cover communicates with a discharge port for the
`pump, formed in the fluid cylinder block.
`The suction and discharge valve elements of the pump
`may be accessed by removing, respectively, the suction
`manifold and the discharge valve cover. The suction
`valve seat and its guide, and the discharge valve seat, all
`are tapped for engagement by a threaded disassembly
`tool to remove these elements.
`
`17 Claims, 6 Drawing Figures
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`Vulcan
`Ex. 1056
`Page 1 of 13
`
`

`

`U.S. Patent
`U.S. Patent
`
`Jul. 7, 1981
`Jul. 7, 1981
`
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`Vulcan
`Ex. 1056
`Page 2 of 13
`
`

`

`U.S. Patent Jui. i, i98i
`U.S. Patent Jul. 7, 1981
`
`Sheet 2 of 2
`Sheet 2 of 2
`
`4,277,229
`4,277,229
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`Vulcan
`Ex. 1056
`Page 3 of 13
`
`

`

`1.
`
`30
`
`HIGH PRESSURE FLUID DELIVERY SYSTEM
`BACKGROUND OF THE INVENTION
`This invention relates to a high pressure fluid deliv
`ery system having an improved reciprocating pump.
`High pressure fluid delivery systems with reciprocat
`ing pumps are used to create a high pressure water jet,
`as for cleaning. Examples of the pumps can be found in
`10
`U.S. Pat. Nos. 3,870,439 to Stachowiak et al and
`3,373,695 to Yohpe. Hydraulic pressures in excess of
`10,000 psi may be present in various sections of these
`pumps, subjecting their parts to significant stresses.
`Accordingly, durability and ease of maintenance when
`necessary are important considerations in the design of
`15
`such a pump. Moreover, the high pressures require a
`considerable input of energy to the pump, so that it is
`highly desirable to increase the efficiency of the pump.
`As will be described below, the present pump has fea
`tures which provide improved durability, maintainabil
`20
`ity and efficiency compared with existing pumps such as
`those of the Stochowiak et al and Yohpe patents.
`SUMMARY OF THE INVENTION
`in accordance with the present invention, there is
`25
`provided a high pressure fluid delivery system with a
`reciprocating pump assembly. The pump assembly in
`cludes a fluid cylinder block with a stuffing box
`mounted at one side thereof and a suction manifold
`mounted at the other side. A cylindrical bore in the
`stuffing box holds a plunger sliding toward the cylinder
`block. A cylindrical passage extends into the fluid cylin
`der block from the stuffing box side thereof to receive
`one end of the piston. A first cylindrical chamber, of a
`larger diameter than the passage, extends from the pas
`35
`sage to the suction manifold side of the fluid cylinder
`block. The suction manifold has a suction port leading
`to the chamber of the fluid cylinder block. The suction
`valve is positioned in the cylindrical chamber in line
`between the cylindrical bore in the stuffing box and the
`suction port.
`A second cylindrical chamber also extends perpen
`dicular to the first cylindrical chamber, from the cham
`ber to an outer wall of the fluid cylinder block. A first
`portion of the opening near the cylindrical chamber has
`45
`a first diameter. A second portion, farther from the
`chamber than the first portion, has a second diameter,
`larger than the first diameter. The discharge valve is
`positioned in the second cylindrical chamber between
`the first cylindrical chamber and a discharge port.
`When the piston is moved away from the fluid cylin
`der block, the discharge valve is closed and fluid can be
`drawn from the suction port through the suction valve.
`When the piston is moved toward the fluid cylinder
`block, the suction valve is closed, and fluid is driven
`through the discharge valve into the discharge port.
`In a preferred embodiment of the invention, the suc
`tion and discharge valve seats and the suction valve
`guide, each have a tapped hole therein for engagement
`by a threaded disassembly tool for removal.
`60
`The pump structure of the present invention pos
`sesses certain advantages as compared with existing
`pumps such as those of the Yohpe and Stachowiak et al
`patents. The first advantage has to do with the forces to
`which the parts of the various pumps are subjeced dur
`65
`ing operation.
`When the plunger is driven into the fluid cylinder
`block, a high pressure is applied to the interior walls of
`
`4,277,229
`2
`the fluid cylinder block, that is, in the cylindrical open
`ing and chamber formed in the block. In addition, the
`pressure is exerted on the valve seats of the suction and
`discharge valves and against the stuffing box, tending to
`force all of these away from the fluid cylinder block. In
`turn, the bolts and threaded connections holding the
`pump assemblies together are subjected to large forces.
`In the pump of the present invention each of the
`valve seats is configured with a long, narrow shape that
`has a small area subject to the high fluid pressure experi
`enced during compression. By contrast, the valve seats
`in the Yohpe device are broader, each having a larger
`area encompassed within the sealing ring associated
`therewith and subject to the fluid pressure. Accord
`ingly, the valve seats of the Yohpe device are subject to
`larger total fluid forces than in the present pump. The
`contrast is even greater with respect to the pump at
`Stachowiak et al which has one large valve seat piece
`serving both the suction and discharge valves. Here the
`area subject to fluid pressure is greater still. As a conse
`quence in the Stachowiak et al pump, bolts holding a
`manifold and the valve seat piece to the fluid cylinder
`block have a very large force applied to them and of
`necessity must be relatively large. This adds expense as
`well as danger of bolt breakage from over or under
`torquing.
`In the pump of the present invention, the sealing area
`around the plunger, at the interface of the stuffing box
`and fluid cylinder block, is small as compared with
`conventional pumps and therefore is subject to less
`force tending to cause a separation of the stuffing box
`and fluid cylinder block at the interface. Thus, sealing
`problems associated with the high pressures employed
`are reduced substantially in the pump structure of the
`present invention.
`The introduction of narrow valve elements, closely
`fitted into the chambers of the pump of the invention
`presents the problem of removing them if maintenance
`is required. In accordance with the present invention,
`the valve elements may be readily removed using the
`threaded disassembly tool. Thus, provision for use of
`the disassembly tool is an important factor permitting
`particular valve elements to be advantageously em
`ployed in the pump of the present invention.
`The present pump also exhibits improved efficiency
`compared with existing pumps. The relative placement
`of the suction valve, discharge valve and plunger suc
`ceeds in minimizing the chamber sizes in the fiuid cylin
`der block, as compared, for example, with all the pumps
`shown in the Yohpe and Stachowiak, et al patents. The
`small sizes of these chambers result in an increased
`volumetric efficiency, particularly when the plunger of
`the pump is operated with a relatively short stroke.
`The present pump has yet another advantage, in that
`its structure is modularized by having, as separate com
`ponents, the fluid cylinder block, stuffing box and suc
`tion manifold. In case of fatigue, these can be replaced
`separately. In addition, they can be manufactured sepa
`rately, each suited to its own requirements. For exam
`ple, the suction manifold, operating at low pressure
`need not be made of extremely strong material.
`By reducing the fatigue and sealing problems associ
`ated with prior pumps used for the high pressures for
`which the present pump is designed, manufacturing and
`maintenance problems are also reduced. Also, the ar
`rangement of the respective valve chambers in the fluid
`
`50
`
`55
`
`Vulcan
`Ex. 1056
`Page 4 of 13
`
`

`

`10
`
`15
`
`4,277,229
`3
`4.
`cylinder block permits relatively easy manufacture as
`Stuffing box 14 is mounted with one end against the
`compared to the pumps of the prior art.
`side of a fluid cylinder block 36. Adapting plate 38 bears
`As contrasted with the prior art, the present inven
`against the other end of the stuffing box. Screws 40 pass
`tion does not have a separate discharge manifold at
`through adapting plate 38 and are screwed into fluid
`tached to its fluid cylinder block. As a result, an acces
`cylinder block 36, to hold stuffing box 14 in place. A
`sory such as a pressure safety head disclosed herein can
`ring seal 42 seals around the plunger 12 at the interface
`be mounted directly to the fluid cylinder block. This
`of stuffing box 14 and fluid cylinder block 36.
`avoids the multiple efforts of machining the fluid cylin
`Attached to the other side of fluid cylinder block 36
`der block to accept a discharge manifold and machining
`is a suction manifold 44. Manifold 44 is held in place by
`the manifold to accept accessories.
`screws 46 passing through it and fastened into fluid
`These and other features and advantages will become
`cylinder 36. A suction port 48 leads to fluid cylinder
`apparent from a consideration of the description of the
`block 36.
`preferred embodiment which follows.
`In the fluid cylinder block 36, there is a cylindrical
`passage 50 which forms an extension of the plunger
`BRIEF DESCRIPTION OF THE DRAWINGS
`bore 15 in stuffing box 14. As illustrated in the FIG
`FIG. 1 is a schematic diagram of a high pressure
`URE, one end of the plunger 12 is received into the
`water blasting system utilizing the pump of this inven
`passage 50. Coaxial with the passage 50 (and plunger
`bore 15), and somewhat larger in diameter than passage
`tion.
`FIG. 2 is a cross section of a pump according to the
`50, is a cylindrical chamber 52. At the end of chamber
`invention.
`52, which is next to suction manifold 44 is a suction
`20
`FIG. 3 is a perspective view of the suction valve and
`valve seat 54. The valve seat 54 is generally tubular in
`valve guide of the pump in FIG. 1.
`shape, with the outer surface 56 conforming to the wall
`FIG. 4 is an elevation view of a disassembly tool used
`of chamber 52. The cylindrical inner surface 58 of valve
`with the valve elements of the pump of FIG. 1.
`seat 54 functions as a guide for a suction valve 60 which
`FIG. 5 is an elevation view of a disassembly tool
`is positioned therein as shown in FIG. 3. Near suction
`25
`applied to the packing gland of the pump of FIG. 2 with
`manifold 44, the inner surface 58 of the valve seat is
`a section of the tool broken away.
`tapped with threads 62. The threads 62 are used for use
`FIG. 6 is a cross section of a pressure safety head in
`with disassembly tool 64 illustrated in FIG. 3 and de
`the pump of FIG. 2.
`scribed below. A ring seal 66 encircles a fluid flow path
`formed by suction port 48 and suction ring seal 68 and
`DESCRIPTION OF THE PREFERRED
`backup ring 67 around valve seat 54 seal between the
`EMBODIMENT
`valve seat and the wall of the chamber 52.
`Referring now to FIG. 1, a high pressure fluid deliv
`As illustrated in FIG, 2 valve seat 54 includes a circu
`ery system for water blasting is illustrated as including,
`lar tapered seating surface 54a and valve member 60
`as is well known in the art, a high pressure pump 10
`includes a circular, tapered seating surface 60a adapted
`to engage surface 54a in a sealing relationship as shown
`connected to a source of water (not shown) and a
`"dump' gun 11 connected by a hose 11a to the outlet of
`in FIG. 2. In accordance with the teachings of U.S. Pat.
`pump 10. High pressure water from dump gun 11 may
`No. 3,986,523 assigned to the assignee of this invention,
`be used, for example, to clean the surface of an object.
`it is preferred that these sealing surfaces (and those on
`The pump 10 is powered by a driving source M such as
`the discharge valve to be described) be maintained as
`an electric motor or gasoline engine.
`small as possible for the pressures employed to issue
`FIG. 2 shows the internal construction of a pump 10
`proper seating and reduce the forces required to move
`according to the invention. In the operation of pump 10,
`the valve members to and from their sealing positions.
`the motion of a plunger 12 draws fluid from a suction
`Suction valve member 60 is shown in FIG. 3 re
`manifold 44 and forces it into a discharge port 100.
`moved from its valve seat 54. Also seen in FIG. 3 is a
`Preferably, the pump 10 has several, for example, three
`suction valve guide 70, which as seen in FIG. 2, fits
`plungers like plunger 12, side by side, each with its
`between valve seat 54 and the end of chamber 52 that is
`adjacent passage 50. Both the valve 60 and guide 70 are
`associated valves, like valves 60 and 90 shown in FIG.
`2. The operations of the plungers are combined by con
`symmetrically located with respect to the cylindrical
`necting all of them to force water into one common
`axis of the inner surface 58 of valve seat 54. Valve 60 has
`50
`discharge port, namely port 100.
`a disc portion 72, perpendicular to the cylindrical axis,
`Plunger 12 has a threaded connection 13 for connec
`which stops fluid flow through valve seat 54 when the
`tion to a driving source (not shown in FIG. 2) which
`disc portion presses against the end of the valve seat.
`reciprocates the plunger along the longitudinal axis
`Three guide ribs 74 project from the disc portion 72 into
`thereof. Plunger 12 moves in bore 15 of a stuffing box
`valve seat 54. The edges 76 of the guide ribs engage
`55
`14, in contact with bushing 16 and packing 18. Packing
`inner surface 58 of valve seat 54 to guide motion of the
`18 is compressed by packing spring 20 pressing on front
`valve 60 along its axis.
`packing ring 22. Packing 18 is held in place by rear
`The suction valve guide 70 has a base 78 shaped by
`packing ring 24 (which includes a bushing surface) and
`three curved sides 80. The base 78 is penetrated by a
`packing gland 26, which is secured in stuffing box 14 by
`tapped hole 82 for use with the disassembly tool 64 to be
`60
`threads 28. Lubrication is provided through fitting 30,
`described in connection with FIG. 3. When valve guide
`tube 32 and opening 34 in packing ring 24.
`70 is in chamber 52, vertex portions 84 of base 78 lie
`It is preferred that the support for plunger 12 in bore
`against the wall of the chamber. There is a substantial
`15 be relatively long between the front bushing 16 and
`space between the curved sides 80 and the wall of the
`rear packing ring 24 to insure relatively long life of the
`chamber 52, which permits fluid flow through the
`65
`plunger. For example, for a plunger having a 1' diame
`chamber past base 78. Fluid also flows through hole 82.
`ter and being approximately 11' long, the support be
`Guide arms 86 project along the wall of chamber 52
`tween bushings is about 4''.
`from vertex portions 84 of the base 78. As can be seen in
`
`40
`
`30
`
`35
`
`45
`
`Vulcan
`Ex. 1056
`Page 5 of 13
`
`

`

`5
`
`15
`
`4,277,229
`5
`6
`FIG.1, the guide arms 86 are located between the wall
`easily withdrawn. Then the small end 130 of tool 64
`of chamber 52 and the disc portion 72 of suction valve
`may be screwed into the tapped hole 82 of suction valve
`60. In this position, they bound the path of disc portion
`guide 70 to pull the valve guide out of chamber 52. In
`72 of the suction valve as the valve moves back and
`this case, bushing 134 is slid to collar 132 where it may
`forth in seat 54. A spring 88 between the base 78 of
`be impacted in order to break loose the valve guide.
`valve guide 70 and disc portion 72 of valve 60 urges the
`To remove the parts of the discharge valve, valve
`valve toward the closed position against the end of
`cover 116 is removed by turning hexagonal head 117.
`Spring 126 and discharge valve 90 should then come
`valve seat 54.
`A discharge valve 90 and associated apparatus is
`out easily. The small end 130 of disassembly tool 64 is
`inserted through cylindrical opening 92 and through the
`installed in a cylindrical opening 92 which extends from
`chamber 52 to an outer wall 94 of fluid cylinder block
`interior of discharge valve seat 104, to be screwed into
`36, perpendicular to chamber 52. Different parts of
`threads 108 of the valve seat. Bushing 134 is slid against
`opening 92 are of different sizes. A first portion 96, near
`collar 132 where it may be struck to dislodge valve seat
`104 from the walls of opening 92.
`chamber 52 has a relatively small diameter. A second
`portion, 97, further away from chamber 52, has a rela
`FIG. 5 shows packing gland 26 and a tool, indicated
`tively larger diameter than portion 96. A third portion,
`generally by the reference numeral 138, for attaching
`and removing the packing gland from pump 10. As can
`98, still further away from chamber 52, has a slightly
`greater diameter than portion 92. Adjacent to cylindri
`be seen in FIG. 2, packing gland 26 is fastened into
`cal opening 92 is formed the discharge port 100 of the
`stuffing box 14 by means of threads 28. As seen in both
`pump. The discharge port is in open communication in
`FIGS. 2 and 5, packing gland 26 has grooves 140,
`the area 101 with the cylindrical opening 92.
`spaced about the circumference of that portion thereof
`Discharge valve 90, which is of the same general
`which protrudes from the stuffing box. These grooves
`configuration as suction valve 60, is seated on discharge
`are engaged by tool 138 to screw the packing gland into
`valve seat 104. Valve seat 104 which is generally cylin
`and out of the stuffing box.
`drical in shape has a part with a smaller diameter lo
`The tool 138 includes a handle 142 with two arcuate
`25
`cated in portion 96 of opening 92 and a larger part held
`arms 144 extending from one end. In a hollow 146 in
`against end wall 99 of portion 97. Just as the outer sur
`handle 142, is a ratchet pin 148 with face 149 generally
`parallel to side walls 150 of a groove engaged by the
`face of valve seat 104 has different diameters, so does
`the inner surface 106. The smaller part, near chamber 52
`tool 138. Another face 151 of pin 148 lies at an oblique
`is tapped with threads 108 for use with disassembly tool
`angle to the groove walls 150. A spring 152 urges pin
`30
`148 against packing gland 26. Roll pins 153 engage
`64 of FIG. 3. The larger part of inner surface 106 holds
`guide ribs 110 of discharge valve 90. Discharge valve 90
`handle 142, preventing rotation of ratchet pin 148 with
`is closed when the disc portion 111 thereof bears against
`respect to the longitudinal axis of handle 142 and also
`limiting the motion of pin 148 along that axis,
`the end of valve seat 104 which is toward outer wall 94,
`The interface between valve seat 104 and portion 97 of
`Tool 138 is shown as it would be used for removing
`35
`opening 92 is sealed by a sealing ring 112 and a backup
`packing gland 26 from the pump. Pressure can be ap
`plied to handle 142 to push it in a counter clockwise
`ring 113 around the outer surface of the valve seat.
`Holding valve seat 104 in place is a threaded dis
`direction until face 149 of ratchet pin 148 engages one of
`charge valve plug or cover 116. Cover 116 is fastened
`the sides 150 of grooves 140. Then torque can be ap
`by threads 118 into fluid cylinder block 36 and has
`plied through handle 142 to gland 26 via face 149 bear
`40
`formed on it a hexagonal head 117 to allow removal of
`ing on side 150 of one of the grooves 140. After handle
`the cover. Sealing ring 120 and backup ring 121, around
`142 has been turned a convenient distance, it may be
`cover 116, seal the cover 116 against portion 98 of open
`pulled back in the clockwise direction. In this direction
`ing 92. A cylindrical cavity 122 is formed in the part of
`of rotation, face 151 of ratchet pin 148 cams off the
`the cover 116 that bears against valve seat 104. Exit 124
`grooves 140, so that handle 142 may be easily turned
`45
`provides fluid communication between the cavity 122
`back to a new starting position. From the new position,
`and discharge port 100. Thus cavity 122 is a path for
`it is once again rotated counter-clockwise to apply
`torque to packing gland 26. Thus, pin 148 engages
`fluid flow to the discharge port, while the walls of the
`cavity serve as a valve guide. A spring 126, between the
`grooves 140 in a ratchet manner, allowing handle 142 to
`top wall of cavity 122 and disc portion 111 of valve 90,
`be turned through an arc which is convenient. All the
`urges the discharge valve toward its closed position.
`while, arms 144 maintain the engagement of ratchet pin
`148 with packing gland 26.
`FIG. 4 shows a disassembly tool 64 used in mainte
`nance of the pump 10. The tool 64 has a shaft 127 with
`When tool 138 is applied in a reversed orientation
`with face 149 of pin 148 upward in the drawing, it may
`threads formed on a large end 128 thereof and a small
`be used to fasten packing gland 26 to the pump. In that
`end 130. Fixed to the shaft 127 are collars 132 and 133
`near the large and the small end, respectively. Shaft 127
`reverse application, torque is transmitted to the packing
`is fitted through a hole 135 in a bushing 134 which is
`gland when handle 142 is rotated in the clockwise direc
`free to slide along the shaft.
`tion.
`The disassembly tool 64 is used to remove various
`FIG. 6 shows the details of a pressure safety head,
`parts of the pump 10 as follows. To gain access to the
`indicated generally by reference numeral 154. Head 154
`60
`components of the suction valve 60, suction manifold 44
`includes a body 155 fastened by threads 156 into an
`is removed by removing screws 46. The large end 128
`aperture 157 in fluid cylinder block 36. Aperture 157 is
`of disassembly tool 64 is screwed into threads 62 of
`in communication with discharge port 100, and conduit
`suction valve seat 54 to pull the valve seat from cham
`158 within body 155 directs fluid from the port 100 into
`ber 52. Bushing 134 is slid against collar 133 where the
`the safety head 154. A disc-shaped frangible partition
`65
`bushing may be struck with a hammer to dislodge valve
`159 is seated in body 155 across conduit 158. Partition
`seat 54 from the fluid cylinder block 36. After the valve
`159 is shaped to protrude outward from conduit 158.
`seat has been removed, the valve 60 and spring 88 are
`Ring 160 bears against partition 159 to hold it in place,
`
`50
`
`55
`
`Vulcan
`Ex. 1056
`Page 6 of 13
`
`

`

`O
`
`25
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`4,277,229
`8
`7
`fluid not displaced by plunger 12 is mainly that enclosed
`and the ring, in turn, is held in place by plug 161 fas
`by discharge valve seat 104 and in the portion of cham
`tened by threads to body 155. A passage 162 formed in
`the interior of the ring 160 and plug 161 leads to down
`ber 52 where valve guide 70 is located. That is, the fluid
`is in the valve parts, but does not occupy substantial
`wardly directed vent tubes 163. There can be more than
`spaces interconnecting the valves, as in the referenced
`the two vent tubes shown distributed around passage 5
`Yohpe patent, for example. In addition, the configura
`162. Attached to the top of plug 161 by threads is a
`tion is such that plunger 12 can move to a portion imme
`cover or deflector or guard 164 surrounding the vent
`diately adjacent valve guide 70; therefore, no wasted
`tubes 163.
`space is associated with the plunger path. Moreover, the
`Aperture 157 and conduit 158 direct high pressure
`fluid from discharge port 100 to partition 159. The pas
`valve elements of pump 10 have relatively small cross
`sections compared with those found in conventional
`sage 162 on the other side of partition 159 is at atmo
`spheric pressure. With the protruding shape of partition
`pumps; hence, the volume of fluid contained in these
`elements is relatively small.
`159, the pressure of the fluid behind it is applied more or
`Some of the improvements provided by pump 10
`less uniformly across the partition. The thickness of the
`partition is chosen so that the partition will rupture, if 15
`relate to stresses on the parts of the pump during opera
`tion. The present pump is designed to reduce the area
`the pressure in conduit 158 exceeds a selected safe limit.
`exposed to the high pressures as much as possible with
`This could happen, for example, if the discharge path
`way downstream from the pump became accidentally
`out imposing flow restrictions that would be detrimen
`tal to the operation of the pump. For example, when the
`occluded. Were the partition 159 to rupture, the fluid
`from the discharge port 100 would flow through con
`plunger 12 is driven into fluid cylinder block 36, pres
`20
`sures in the range of 13,000 to 15,000 psi may be experi
`duit 158 and passage 162 and be vented through tubes
`enced in passage 50, chamber 52 and cylindrical open
`163 to the atmosphere. Guard 164 would serve to de
`ing 92. This pressure is exerted on suction valve seat 54,
`flect and disperse the vented fluid in a downward direc
`tion to reduce the opportunity for damage and injury
`discharge valve seat 104 and stuffing box 14, tending to
`force all of these away from fluid cylinder block36. The
`from the vented flow.
`After a venting occurs, partition 159 can be replaced
`force on suction valve seat 54 is, in turn, exerted against
`without removing safety head 154 from fluid cylinder
`suction manifold 44 and screws 46. Part of the force on
`discharge valve seat 104 is transmitted to discharge
`block 36. Plug 161 can be unscrewed from the body 155,
`and ring 160 removed along with the ruptured partition
`valve cover 116. The hydraulic force on stuffing box 14
`is carried by screws 40. Thus, by minimizing the sealing
`159 to replace it. .
`In the operation of the pump 10, the plunger 12 is
`areas within which the forces referred to are applied, (as
`pulled in a direction away from the fluid cylinder block
`represented by seals 42,66, 67, 112 and 120), the present
`36 to draw fluid into the pump. The pressures produced
`invention effectively reduces the stresses on the mount
`ing bolts and other parts of the pump.
`by this motion of the plunger tends to pull valve 60
`Compared with the valve seats of conventional
`towards the plunger, when the force exerted by spring
`pumps, valve seats 54 and 104 are configured with a
`88 is overcome. The discharge valve 90, aided by the
`relatively long and narrow shape that exposes only a
`force of spring 126 is closed and remains so during the
`relatively small area to the high fluid pressure. A pre
`suction stroke, however, valve 60 opens off seat 54.
`Fluid is drawn from suction port 48, through the inte
`ferred value for the diameter of the suction valve seat 54
`at ring seal 66 is 1 inches. The diameter of discharge
`rior of valve seat 54 and into the portion of chamber 52 40
`occupied by valve guide 70. Fluid flows past the valve
`valve seat 104 at sealing ring 112 is 1 inches, while the
`diameter of discharge valve cover 116 at sealing ring
`guide 70, between the curved sides 80 and the wall of
`120 is 1 inches. The outer diameter of ring seal 42
`chamber 52, and through the hole 82, into passage 50
`around plunger 12 is about 1 inches.
`and the portion of bore 15 vacated by the plunger 12.
`When plunger 12 is moved toward fluid cylinder 45
`The force exerted on one of the parts, such as one of
`the valve seats, is the product of the hydraulic pressure
`block 36, the tendency of both valves 60 and 90 is to be
`pushed away from the plunger. Thus, suction valve 60
`and the area subject to the pressure. Therefore, a part
`having a smaller area exposed to the pressure is subject
`is pushed closed against its valve seat 54, aided by the
`force of spring 88. Discharge valve 90 is forced open,
`to a smaller total force. For example, in the case of the
`away from its valve seat 104, against the force of spring 50
`suction valve seat 54, a smaller force is transmitted from
`126. Fluid flows from bore 15 and passage 50, through
`the inside of chamber 52 to the suction manifold 44 and
`hole 82 and the spaces between the curved sides of
`to screws 46.
`The design of pump 10 achieves quite a dramatic
`suction valve guide 70 and the wall of chamber 52. The
`decrease in the forces exerted on its parts, compared to
`fluid then flows between the guide arms 86 of suction
`conventional pumps. For example, a pump manufac
`valve guide 70, into the inner part of discharge valve 55
`tured according to the Yohpe patent referred to above,
`seat 104, then through cavity 122 and exit 124 thereof
`operating at 10,000 psi hydraulic pressure requires that
`and out the discharge port 100.
`The design of pump 10 has features which result in
`the fastening screws be tightened with 200-300 ft. lbs. of
`improved efficiency. When the plunger 12 pushes
`torque. By contrast, pump 10 can operate at 20,000 psi,
`against fluid in the pump at very high pressures, there is
`with the screws 40 and 46 requiring only to be tightened
`some compression of the fluid. Since the object of the
`to 50 ft. lbs. of torque. As a result, less and easier mainte
`pump is to move the fluid, energy is wasted when it
`nance is required of pum