US3146720A - Pressure relief means for pump - Google Patents

Pressure relief means for pump Download PDF

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US3146720A
US3146720A US157438A US15743861A US3146720A US 3146720 A US3146720 A US 3146720A US 157438 A US157438 A US 157438A US 15743861 A US15743861 A US 15743861A US 3146720 A US3146720 A US 3146720A
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sleeve
seat
pump
wall
piston
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US157438A
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Ralph E Henry
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Dresser Industries Inc
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Dresser Industries Inc
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2562—Dividing and recombining
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2574—Bypass or relief controlled by main line fluid condition
    • Y10T137/2579—Flow rate responsive
    • Y10T137/2587—Bypass or relief valve biased open
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7781—With separate connected fluid reactor surface

Definitions

  • This invention relates to pressure relief means for a pump, and more particularly to pressure relief valve means ⁇ for a hydraulic pump of the positive displacement type.
  • the main object of the present invention is to provide in a pump pressure relief means which do not chatter and dampen or lter out vibrations.
  • Another object of the invention is to provide such pressure relief means which are adjustable so that the pressure level at which the relief means operates can be varied selectively.
  • FIG. 1 is a vertical central section through a gear pump equipped with pressure relief valve means constructed in accordance with the principles of the present invention, and showing the valve in a closed or seated position.
  • FIG. 2 is an enlarged sectional view of the pressure relief valve means shown in FG. l but illustrating the Valve in an open or unseated position, and further showing only a fragmentary part of the pump body.
  • the numeral 15 represents generally the body of a gear pump suitably formed with a lower curved wall 3 and an upper inner curved wall 9 to provide chambers for a pair of cooperatingrgears 13 and 14, and also formed to provide an inlet 11 and an outlet 12. Suitable means (not shown) cause rotation of one of the gears 13 and 14 which in cooperation with the walls 8 and 9 operate to displace positively fluid from the inlet 11 to the outlet 12.
  • an outer wall 15 is spaced from the upper inner curved wall 9 of the pump body to provide a passage 16 which at one end communicates with the outlet 12 and at its other end communicates with a cylindrical hole 18 of reduced diameter. The other end of this hole 18 is shown as communicating via the passage 19 with the inlet 11.
  • the passage 19 is formed preferablyV as shown by an outer wall Ztl and a valve housing portion 17 intermediate the walls 15 and 20. These walls 15 and 2t) and portion 17 are preferably formed integrally with the pump body 10.
  • the passages 16, 1d and 19 jointly provide a by- ⁇ pass connecting the pump inlet and outlet.
  • the pump body on the downstream side of the hole 1S is formed with a cylindrical counterbore as indicated AlCe at 21 to provide an annular seat 22 which faces toward the pump inlet 11.
  • Movable valve means are operatively associated with the seat 22.
  • Such valve means are shown as including a cylindrical sleeve member 23 slidably arranged within a bore 24 provided in the pump body portion 17 so that one end of this sleeve opposes the seat 22.
  • the inner and outer corners of the sleeve member 23 v at this end are bevelled or chamfered to provide a relatively narrow annular end face 25 which isadapted to engage abuttingly the opposing annular seat 22.
  • the sleeve member 23 is shown as provided with an internal Wall 26 which extends transversely of the member.
  • This wall is shown as having a central through hole 2S provided with an annular groove to receive an 0ring 29.
  • the O-ring 29 sealingly embraces a cylindrical stem 3).
  • One end of the stem 31B ⁇ carries a piston 31 which is relatively slidingly arranged within the sleeve member 23 and is located between the transverse wall 26 and the seat 22.
  • the space between the piston 31 and transverse wall 26 provides a chamber 32.
  • the piston 31 is shown as having a restricted opening 33 extending therethrough which establishes communication between the chamber 32 and the bypass channel constituted by the passage portions 16, 18 and 19.
  • any suitable means may be provided for securing the piston 31 to the stem.
  • the piston is removably connected to the stem and for this purpose the stem is shown as having a coaxially projecting neck 34 of reduced diameter so as to provide a forwardly facing annular shoulder 35 against which the inner face 36 of the piston 31 bears adjacent a central hole 33 provided in the piston.
  • the outer end of the reduced neck 34 is externally threaded to receive a nut 39 which bears against the outer end face 4G of the piston 31. Tightening the nut 39 clamps the piston 31 against the shoulder 35.
  • the other end of the stem 3l is shown as secured to a generally cup-shaped plug 41 having an annular wall portion 42 provided with external threads 113 adapted to be screwed into an internally threaded hole 44 provided in the pump body.
  • the hole 44 is coaxial and cornmunicates with the bore 24 for the slide valve member 23.
  • the adjusted position of the plug 41 relative to the pump body may be maintained by a lock nut 4S which is threaded on the threads 43 and bears against an outer end face 37 of the pump body portion 1.7.
  • the outer end portion of the plug 41 is shown as being enlarged and provided with an out-of-round perimetrical configuration to permit the application of a wrench or the like (not shown) to enable the plug to be rotated.
  • the adjacent end of the stem 34B is shown as having a reduced neck 46, leaving an outwardly facing shoulder 47 which engages the inner face 57 of the end wall of the plug 41.
  • the outer end portion of the neck 46 is externally threaded as indicated at 48.
  • the neck 46 extends through a counterbored hole i9 provided in the end wall of the plug 41. This counterbored hole provides an outwardly facing shoulder 5t) against which the inner end face of a nut 51 screwed onto the threaded portion 43 bears. T ightening the nut 51 clamps the stem shoulder 47 against the plug face 57.
  • a helical compression spring 52 is shown as operatively interposed between the plug 41 and sleeve member 23 so as to urge the latter toward the seat 22. Specifically, one end of the spring 52 bears against one side of the transverse wall 25 and the other end of this spring bears against the inner face 57 of the plug 41.
  • the preload on the spring 52 can be varied by adjusting lthe axial position of the plug 41 relative to the pump body portion 17.
  • the preload on the spring 52 is increased, whereas backing off or unscrewing the plug 41 partway reduces the preload on the spring.
  • the lock nut 45 is suitably loosened and then following this adjustment the lock nut is retightened.
  • the adjustable plug 41 and lock nut 45 are shown as covered by a removable cap S3 having attaching iianges 54 opposing the body end face 37.
  • a gasket S5 is shown as interposed between the flanges 54 and this face 37.
  • Removable machine screws 56 pass through holes in the attaching iianges 54 and are received in threaded recesses provided in the pump body.
  • the space between the sleeve member 23 and plug 41 which may vary in volume due to movement of the sleeve member relative to the stationary plug, is connected to the passage portion 19 by the lateral branch passage 58 formed in the body portion 17 and which intercepts the bore 24 and hole 44.
  • the piston 31 acts as a iixed wall element spaced from the seat 22, the face 40 of which is constantly exposed to the pressure in the pump outlet 12.
  • the sleeve member 23 acts as a closure member cooperable with the seat 22 and movable with respect to the iixed piston or wall element 31.
  • Another way of viewing these elements is to regard the sleeve member 23 with its transverse wall 26 as a movable cylinder member in which the piston 31 is fixed although slidable relative to the annular wall.
  • the pressure in the pump outlet 12 is transmittable to the chamber 32 formed by the opposing and spaced walls 31 and 26 through the restricted opening 33 arranged in the wall member or piston 31 and via the connected passage portions 16 and 1S. If the pressure within the chamber 32 is high enough to develop a force directed from left to right as viewed in the figures to overcome the oppositely directed force exerted by the spring 52, this spring will yield and allow the sleeve member 23 to move away from its seat 22, thereby establishing communication between the passage portions 18 and 19 and hence between the pump inlet and outlet. When the force exerted by the fluid pressure within the chamber 32 is inadequate to overcome that exerted by the spring 52, this spring will maintain the sleeve member 23 against the seat 22, as illustrated in FIG. 1.
  • the purpose of the restricted opening 33 in the wall element or piston 31 is to dampen or filter out the vibrations or pressure fluctuations in the pump outlet 12, while allowing ⁇ the more or less steady state or mean pressure to be transmitted to the chamber 32.
  • Another purpose of the restricted opening 33 in piston 31 is to act as a metering orifice in restricting the velocity of movement of sleeve 23. In order for sleeve 23 to move, fluid must be displaced through the restricted opening 33. This prevents overcontrolling and consequent pressure surges.
  • the preloading of the spring 52 is variable by adjusting the plug 41. This adjustment and hence preloading determines the pressure within the bypass channel at which the pressure relief valve member 23 will open or unseat.
  • a pump including a body having a by-pass connecting an inlet and an outlet, the combination therewith of pressure relief means comprising a seat in said by-pass, a xed piston element spaced from said seat and having two opposite sides one of which is constantly exposed to lthe pressure in said outlet and also having an opening therethrough connecting said sides, a movable cylinder member having an annular wall slidably arranged on said element and forming jointly therewith a chamber on the other side of said element communicating with said opening, and yielding means urging said member toward said seat, said member when seated blocking said by-pass but when unseated unblocking said by-pass.
  • a pump including a body having a by-pass connecting an inlet and an outlet
  • pressure relief means comprising a seat in said by-pass, movable valve means operatively associated with said seat and including a sleeve and a wall arranged transversely of and within said sleeve, yielding means urging said sleeve toward said seat, said sleeve when seated blocking said by-pass but when unseated unblocking said by-pass, and a iixed piston arranged Within said sleeve between said wall and seat to provide a chamber, said piston having an opening therethrough communicating with said chamber.
  • a pump including a body having a by-pass connecting an inlet and an outlet
  • pressure relief means comprising a seat in said by-pass, movable valve means operatively associated with said seat and including a sleeve and a wall arranged transversely of and within said sleeve and having an opening therethrough, yielding means urging said sleeve toward said seat, said sleeve when seated blocking said by-pass but when unseated unblocking said by-pass, a fixed stem extending through said opening and slidably sealed with respect to said wall, and a piston secured to said stem and arranged Within said sleeve between said wall and seat to provide a chamber, said piston having an opening therethrough communicating with said chamber.
  • a pump including a body having a by-pass connecting an inlet and an outlet, the combination therewith of pressure relief means comprising an annular seat surrounding said passage, valve means slidably arranged on said body opposite said seat and including a sleeve having an end adapted to engage said seat and also including a wall arranged transversely of and within said sleeve intermediate the ends thereof said wall having a central opening extending therethrough, a stem slidably extending through said opening, a piston secured to one end of said stem and arranged within said sleeve between said wall and seat to provide a chamber, said piston having an opening therethrough communicating with said chamber, a member adjustably mounted on said body and secured to the other end of said stem, and spring means operatively interposed between said wall and member and having a preload variable by adjustment of said member.

Description

Sept. 1., 1964 R E, HENRY 3,146,720
PRESSURE RELIEF MEANS FOR PUMP Filed Deo. 6, 1961 .'55 54' fg 23a/21,57% 7 5.a
.9 i 56 g5 Z/Zq. 20
, @WMM United States Patent O 3,146,720 PRESSURE RELIEF MEANS FOR PUlWP Ralph E. Henry, Rixford, Pa., assigner to Dresser Industries, Inc., Dallas, Tex., a corporation of Delaware Filed Dec. 6, 1961, Ser. No. 157,438 4 Claims. (Cl. 1031-42) This invention relates to pressure relief means for a pump, and more particularly to pressure relief valve means `for a hydraulic pump of the positive displacement type.
With a hydraulic pump of the positive displacement type such as a gear pump, the pressure in the outlet of the pump varies or pulses in response to the quantities or surges of the fluid positively displaced by the pump. These variations or pulsations in the pump outlet and the outlet line connected thereto cause the normal type of relief valve to chatter or oscillate rapidly and this chattering not only produces undesirable noise but also disturbs the pressure of the fluid throughout the hydraulic system connected to the pump outlet, setting up vibrations that may even break pipes.
The main object of the present invention is to provide in a pump pressure relief means which do not chatter and dampen or lter out vibrations.
Another object of the invention is to provide such pressure relief means which are adjustable so that the pressure level at which the relief means operates can be varied selectively.
Other objects of the invention are to provide such pressure relief means which are simple in construction, relatively inexpensive to incorporate in a pump, and not likely to get out of order or require repair.
Still other objects and advantages of the invention will be apparent from the following detailed description of a preferred embodiment thereof which is illustrated in the accompanying drawings wherein:
FIG. 1 is a vertical central section through a gear pump equipped with pressure relief valve means constructed in accordance with the principles of the present invention, and showing the valve in a closed or seated position.
FIG. 2 is an enlarged sectional view of the pressure relief valve means shown in FG. l but illustrating the Valve in an open or unseated position, and further showing only a fragmentary part of the pump body.
The numeral 15 represents generally the body of a gear pump suitably formed with a lower curved wall 3 and an upper inner curved wall 9 to provide chambers for a pair of cooperatingrgears 13 and 14, and also formed to provide an inlet 11 and an outlet 12. Suitable means (not shown) cause rotation of one of the gears 13 and 14 which in cooperation with the walls 8 and 9 operate to displace positively fluid from the inlet 11 to the outlet 12.
In accordance with the present invention, means are provided to relieve pressure in the outlet 12 should it rise above a predetermined level. For this purpose, an outer wall 15 is spaced from the upper inner curved wall 9 of the pump body to provide a passage 16 which at one end communicates with the outlet 12 and at its other end communicates with a cylindrical hole 18 of reduced diameter. The other end of this hole 18 is shown as communicating via the passage 19 with the inlet 11. The passage 19 is formed preferablyV as shown by an outer wall Ztl and a valve housing portion 17 intermediate the walls 15 and 20. These walls 15 and 2t) and portion 17 are preferably formed integrally with the pump body 10. The passages 16, 1d and 19 jointly provide a by-` pass connecting the pump inlet and outlet.
The pump body on the downstream side of the hole 1S is formed with a cylindrical counterbore as indicated AlCe at 21 to provide an annular seat 22 which faces toward the pump inlet 11.
Movable valve means are operatively associated with the seat 22. Such valve means are shown as including a cylindrical sleeve member 23 slidably arranged within a bore 24 provided in the pump body portion 17 so that one end of this sleeve opposes the seat 22. Preferably the inner and outer corners of the sleeve member 23 v at this end are bevelled or chamfered to provide a relatively narrow annular end face 25 which isadapted to engage abuttingly the opposing annular seat 22.
Intermediate its ends, the sleeve member 23 is shown as provided with an internal Wall 26 which extends transversely of the member. This wall is shown as having a central through hole 2S provided with an annular groove to receive an 0ring 29. The O-ring 29 sealingly embraces a cylindrical stem 3). One end of the stem 31B `carries a piston 31 which is relatively slidingly arranged within the sleeve member 23 and is located between the transverse wall 26 and the seat 22. The space between the piston 31 and transverse wall 26 provides a chamber 32. The piston 31 is shown as having a restricted opening 33 extending therethrough which establishes communication between the chamber 32 and the bypass channel constituted by the passage portions 16, 18 and 19.
Any suitable means may be provided for securing the piston 31 to the stem. As shown, the piston is removably connected to the stem and for this purpose the stem is shown as having a coaxially projecting neck 34 of reduced diameter so as to provide a forwardly facing annular shoulder 35 against which the inner face 36 of the piston 31 bears adjacent a central hole 33 provided in the piston. The outer end of the reduced neck 34 is externally threaded to receive a nut 39 which bears against the outer end face 4G of the piston 31. Tightening the nut 39 clamps the piston 31 against the shoulder 35.
The other end of the stem 3l) is shown as secured to a generally cup-shaped plug 41 having an annular wall portion 42 provided with external threads 113 adapted to be screwed into an internally threaded hole 44 provided in the pump body. The hole 44 is coaxial and cornmunicates with the bore 24 for the slide valve member 23. The adjusted position of the plug 41 relative to the pump body may be maintained by a lock nut 4S which is threaded on the threads 43 and bears against an outer end face 37 of the pump body portion 1.7. The outer end portion of the plug 41 is shown as being enlarged and provided with an out-of-round perimetrical configuration to permit the application of a wrench or the like (not shown) to enable the plug to be rotated.
The adjacent end of the stem 34B is shown as having a reduced neck 46, leaving an outwardly facing shoulder 47 which engages the inner face 57 of the end wall of the plug 41. The outer end portion of the neck 46 is externally threaded as indicated at 48. The neck 46 extends through a counterbored hole i9 provided in the end wall of the plug 41. This counterbored hole provides an outwardly facing shoulder 5t) against which the inner end face of a nut 51 screwed onto the threaded portion 43 bears. T ightening the nut 51 clamps the stem shoulder 47 against the plug face 57.
A helical compression spring 52 is shown as operatively interposed between the plug 41 and sleeve member 23 so as to urge the latter toward the seat 22. Specifically, one end of the spring 52 bears against one side of the transverse wall 25 and the other end of this spring bears against the inner face 57 of the plug 41.
It will be seen that the preload on the spring 52 can be varied by adjusting lthe axial position of the plug 41 relative to the pump body portion 17. Thus by screwing the E5 plug 41 into the body the preload on the spring 52 is increased, whereas backing off or unscrewing the plug 41 partway reduces the preload on the spring. Before making any adjustment of the plug 41, the lock nut 45 is suitably loosened and then following this adjustment the lock nut is retightened.
The adjustable plug 41 and lock nut 45 are shown as covered by a removable cap S3 having attaching iianges 54 opposing the body end face 37. A gasket S5 is shown as interposed between the flanges 54 and this face 37. Removable machine screws 56 pass through holes in the attaching iianges 54 and are received in threaded recesses provided in the pump body.
The space between the sleeve member 23 and plug 41 which may vary in volume due to movement of the sleeve member relative to the stationary plug, is connected to the passage portion 19 by the lateral branch passage 58 formed in the body portion 17 and which intercepts the bore 24 and hole 44.
From the foregoing, it will be seen that the piston 31 acts as a iixed wall element spaced from the seat 22, the face 40 of which is constantly exposed to the pressure in the pump outlet 12. Also, the sleeve member 23 acts as a closure member cooperable with the seat 22 and movable with respect to the iixed piston or wall element 31. Another way of viewing these elements is to regard the sleeve member 23 with its transverse wall 26 as a movable cylinder member in which the piston 31 is fixed although slidable relative to the annular wall.
In operation, it will be seen that the pressure in the pump outlet 12 is transmittable to the chamber 32 formed by the opposing and spaced walls 31 and 26 through the restricted opening 33 arranged in the wall member or piston 31 and via the connected passage portions 16 and 1S. If the pressure within the chamber 32 is high enough to develop a force directed from left to right as viewed in the figures to overcome the oppositely directed force exerted by the spring 52, this spring will yield and allow the sleeve member 23 to move away from its seat 22, thereby establishing communication between the passage portions 18 and 19 and hence between the pump inlet and outlet. When the force exerted by the fluid pressure within the chamber 32 is inadequate to overcome that exerted by the spring 52, this spring will maintain the sleeve member 23 against the seat 22, as illustrated in FIG. 1.
The purpose of the restricted opening 33 in the wall element or piston 31 is to dampen or filter out the vibrations or pressure fluctuations in the pump outlet 12, while allowing `the more or less steady state or mean pressure to be transmitted to the chamber 32. The smaller the transverse area of the restricted opening 33 in the wall element or piston 31 relative to the volume of lthe chamber 32, the more damping effect produced.
Another purpose of the restricted opening 33 in piston 31 is to act as a metering orifice in restricting the velocity of movement of sleeve 23. In order for sleeve 23 to move, fluid must be displaced through the restricted opening 33. This prevents overcontrolling and consequent pressure surges.
As noted hereinabove, the preloading of the spring 52 is variable by adjusting the plug 41. This adjustment and hence preloading determines the pressure within the bypass channel at which the pressure relief valve member 23 will open or unseat.
Since variations and modifications of the precise construction of the invention illustrated may occur to those skilled in the art, the scope of the invention is to be measured by the appended claims.
What is claimed is:
1. In a pump including a body having a by-pass connecting an inlet and an outlet, the combination therewith of pressure relief means comprising a seat in said by-pass, a xed piston element spaced from said seat and having two opposite sides one of which is constantly exposed to lthe pressure in said outlet and also having an opening therethrough connecting said sides, a movable cylinder member having an annular wall slidably arranged on said element and forming jointly therewith a chamber on the other side of said element communicating with said opening, and yielding means urging said member toward said seat, said member when seated blocking said by-pass but when unseated unblocking said by-pass.
2. In a pump including a body having a by-pass connecting an inlet and an outlet, the combination therewith of pressure relief means comprising a seat in said by-pass, movable valve means operatively associated with said seat and including a sleeve and a wall arranged transversely of and within said sleeve, yielding means urging said sleeve toward said seat, said sleeve when seated blocking said by-pass but when unseated unblocking said by-pass, and a iixed piston arranged Within said sleeve between said wall and seat to provide a chamber, said piston having an opening therethrough communicating with said chamber.
3. In a pump including a body having a by-pass connecting an inlet and an outlet, the combination therewith of pressure relief means comprising a seat in said by-pass, movable valve means operatively associated with said seat and including a sleeve and a wall arranged transversely of and within said sleeve and having an opening therethrough, yielding means urging said sleeve toward said seat, said sleeve when seated blocking said by-pass but when unseated unblocking said by-pass, a fixed stem extending through said opening and slidably sealed with respect to said wall, and a piston secured to said stem and arranged Within said sleeve between said wall and seat to provide a chamber, said piston having an opening therethrough communicating with said chamber.
4. In a pump including a body having a by-pass connecting an inlet and an outlet, the combination therewith of pressure relief means comprising an annular seat surrounding said passage, valve means slidably arranged on said body opposite said seat and including a sleeve having an end adapted to engage said seat and also including a wall arranged transversely of and within said sleeve intermediate the ends thereof said wall having a central opening extending therethrough, a stem slidably extending through said opening, a piston secured to one end of said stem and arranged within said sleeve between said wall and seat to provide a chamber, said piston having an opening therethrough communicating with said chamber, a member adjustably mounted on said body and secured to the other end of said stem, and spring means operatively interposed between said wall and member and having a preload variable by adjustment of said member.
References Cited in the file of this patent UNITED STATES PATENTS Re.24,892 Banker Oct. 25, 1960 168,807 Taylor Oct. 11, 1875 677,470 Richter July 2, 1901 1,285,819 Smith Nov. 26, 1918 2,013,260 Waterous et al Sept. 3 1935 2,305,518 Dunmire Dec. 15, 1942 2,437,791 Roth et al. Mar. 16, 1948 2,456,651 Schmiel Dec. 21, 1948 2,684,631 Anthony et al. July 27, 1954 2,996,013 Thompson et al. Aug. 15, 1961

Claims (1)

  1. 2. IN A PUMP INCLUDING A BODY HAVING A BY-PASS CONNECTING AN INLET AND AN OUTLET, THE COMBINATION THEREWITH OF PRESSURE RELIEF MEANS COMPRISING A SEAT IN SAID BY-PASS MOVABLE VALVE MEANS OPERATIVELY ASSOCIATED WITH SAID SEAT AND INCLUDING A SLEEVE AND A WALL ARRANGED TRANSVERSELY OF AND WITHIN SAID SLEEVE, YIELDING MEANS URGING SAID SLEEVE TOWARD SAID SEAT, SAID SLEEVE WHEN SEATED BLOCKING SAID BY-PASS BUT WHEN UNSEATED UNBLOCKING SAID BY-PASS, AND A FIXED PISTON ARRANGED WITHIN SAID SLEEVE BETWEEN SAID WALL AND SEAT TO PROVIDE A CHAMBER, SAID PISTON HAVING AN OPENING THERETHROUGH COMMUNICATING WITH SAID CHAMBER.
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Cited By (34)

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US3373689A (en) * 1966-06-08 1968-03-19 Dover Corp Positive displacement pump
US3415194A (en) * 1966-09-16 1968-12-10 Eaton Yale & Towne Pump
US4065235A (en) * 1976-06-01 1977-12-27 Tuthill Pump Company Gear pump
DE2732341A1 (en) * 1977-07-16 1979-01-25 Kloeckner Humboldt Deutz Ag Externally meshing gear pump or motor - has cylindrical outer fitting surface of housing coaxial with external driving gear wheel
US4740140A (en) * 1985-12-11 1988-04-26 Sundstrand Corporation Pump having integral switch and bypass valve
US5013220A (en) * 1989-02-22 1991-05-07 Aisin Seiki Kabushiki Kaisha Oil pump having regulator valve isolated from dynamic pressure of pumped oil
US5222576A (en) * 1991-01-10 1993-06-29 Willy Vogel Ag Central-lubrication assembly
US5277028A (en) * 1990-03-26 1994-01-11 Mercedes-Benz Ag Hydraulic flow control with temperature sensitive spring biased bypass valve
US5597291A (en) * 1994-11-22 1997-01-28 Robert Bosch Gmbh Fuel feed pump for a fuel injection pump for internal combustion engines
US6095763A (en) * 1996-06-26 2000-08-01 Robert Bosch Gmbh Fuel delivery pump with a bypass valve, for a fuel injection pump for an internal combustion engine
US6099263A (en) * 1996-06-26 2000-08-08 Robert Bosch Gmbh Fuel delivery pump with a bypass valve and an inlet check valve for a fuel injection pump for internal combustion engines
WO2002027186A1 (en) * 2000-09-27 2002-04-04 Rpm Industries, Inc. Improved engine prelubrication pump assembly
US6461118B1 (en) * 1997-07-18 2002-10-08 Rpm Industries, Inc. Oil pump by-pass valve for an internal combustion engine
US20030113217A1 (en) * 2000-05-25 2003-06-19 Josef Bachmann Regulated pump
US20030202887A1 (en) * 1997-07-18 2003-10-30 Apostolides John K. Vent for reducing seal pressure in pump assembly
US20040045609A1 (en) * 1997-10-30 2004-03-11 John Apostolides Vehicle fluid change apparatus
US6739853B1 (en) * 2002-12-05 2004-05-25 Carrier Corporation Compact control mechanism for axial motion control valves in helical screw compressors
US20040211470A1 (en) * 1997-10-30 2004-10-28 Apostolides John K. Methods and systems for performing, monitoring and analyzing multiple machine fluid processes
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US20060185737A1 (en) * 2005-01-24 2006-08-24 Matthew Williamson Pressure relief valve with debris trap
WO2009045187A1 (en) 2007-10-01 2009-04-09 Carrier Corporation Screw compressor pulsation damper
US20100202904A1 (en) * 2007-10-10 2010-08-12 Carrier Corporation Screw compressor pulsation damper
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US20110129374A1 (en) * 2008-07-22 2011-06-02 Oerlikon Leybold Vacuum Gmbh Vacuum pump in particular roots type pump
US20110297259A1 (en) * 2010-06-04 2011-12-08 Sundquist Walter W Oil pump system for an engine
US20130068328A1 (en) * 2011-09-16 2013-03-21 Caterpillar, Inc. Gerotor Pump Assembly and Engine Fluid Delivery System Using a Gerotor Pump Assembly
US20130284285A1 (en) * 2012-04-25 2013-10-31 Nordson Corporation Pressure control valve for reactive adhesives
US8984972B2 (en) 2012-07-17 2015-03-24 Cummins Ip, Inc. Power take-off system for an internal combustion engine
US20150338857A1 (en) * 2014-05-20 2015-11-26 Hamilton Sundstrand Corporation Pressure-regulating valves
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EP3267038A1 (en) * 2016-07-05 2018-01-10 Fluid-O-Tech S.r.l. Hydraulic pump and respective multifunction valve

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US3415194A (en) * 1966-09-16 1968-12-10 Eaton Yale & Towne Pump
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US4740140A (en) * 1985-12-11 1988-04-26 Sundstrand Corporation Pump having integral switch and bypass valve
US5013220A (en) * 1989-02-22 1991-05-07 Aisin Seiki Kabushiki Kaisha Oil pump having regulator valve isolated from dynamic pressure of pumped oil
US5277028A (en) * 1990-03-26 1994-01-11 Mercedes-Benz Ag Hydraulic flow control with temperature sensitive spring biased bypass valve
US5222576A (en) * 1991-01-10 1993-06-29 Willy Vogel Ag Central-lubrication assembly
US5597291A (en) * 1994-11-22 1997-01-28 Robert Bosch Gmbh Fuel feed pump for a fuel injection pump for internal combustion engines
US6095763A (en) * 1996-06-26 2000-08-01 Robert Bosch Gmbh Fuel delivery pump with a bypass valve, for a fuel injection pump for an internal combustion engine
US6099263A (en) * 1996-06-26 2000-08-08 Robert Bosch Gmbh Fuel delivery pump with a bypass valve and an inlet check valve for a fuel injection pump for internal combustion engines
US7137789B2 (en) * 1997-07-18 2006-11-21 Rpm Industries, Inc. Vent for reducing seal pressure in pump assembly
US6461118B1 (en) * 1997-07-18 2002-10-08 Rpm Industries, Inc. Oil pump by-pass valve for an internal combustion engine
US6544008B1 (en) * 1997-07-18 2003-04-08 John K. Apostolides Internal vent for reducing seal pressure in prelubrication pump assembly
US20030202887A1 (en) * 1997-07-18 2003-10-30 Apostolides John K. Vent for reducing seal pressure in pump assembly
US6988506B1 (en) 1997-10-30 2006-01-24 Rpm Industries, Inc. Fluid transfer system
US7793681B2 (en) 1997-10-30 2010-09-14 RPM Industries, LLC Methods and systems for performing, monitoring and analyzing multiple machine fluid processes
US20040045609A1 (en) * 1997-10-30 2004-03-11 John Apostolides Vehicle fluid change apparatus
US20070113894A1 (en) * 1997-10-30 2007-05-24 Rpm Industries, Inc. Methods and systems for performing, monitoring and analyzing multiple machine fluid processes
US9062575B2 (en) 1997-10-30 2015-06-23 RPM Industries, LLC Methods and systems for performing, monitoring and analyzing multiple machine fluid processes
US20040211470A1 (en) * 1997-10-30 2004-10-28 Apostolides John K. Methods and systems for performing, monitoring and analyzing multiple machine fluid processes
US6941969B2 (en) 1997-10-30 2005-09-13 Rpm Industries, Inc. Vehicle fluid change apparatus
US20050173004A1 (en) * 1997-10-30 2005-08-11 Apostolides John K. Methods and systems for performing, monitoring and analyzing multiple machine fluid processes
US6709245B2 (en) * 2000-05-25 2004-03-23 Gkn Sinter Metals Gmbh Regulated pump
US20030113217A1 (en) * 2000-05-25 2003-06-19 Josef Bachmann Regulated pump
EP1328729A1 (en) * 2000-09-27 2003-07-23 Rpm Industries, Inc. Improved engine prelubrication pump assembly
EP1328729A4 (en) * 2000-09-27 2005-01-12 Rpm Ind Inc Improved engine prelubrication pump assembly
WO2002027186A1 (en) * 2000-09-27 2002-04-04 Rpm Industries, Inc. Improved engine prelubrication pump assembly
US6853954B2 (en) 2002-09-24 2005-02-08 John K. Apostolides Methods and systems for collecting and processing data in association with machine operation and maintenance
US20040109782A1 (en) * 2002-12-05 2004-06-10 Yan Tang Compact control mechanism for axial motion control valves in helical screw compressors
US6739853B1 (en) * 2002-12-05 2004-05-25 Carrier Corporation Compact control mechanism for axial motion control valves in helical screw compressors
US20050183776A1 (en) * 2004-02-23 2005-08-25 Gerald Matranga Pressure regulator
US20060185737A1 (en) * 2005-01-24 2006-08-24 Matthew Williamson Pressure relief valve with debris trap
CN101809251B (en) * 2007-10-01 2013-07-17 开利公司 Screw compressor pulsation damper
US20100209280A1 (en) * 2007-10-01 2010-08-19 Carrier Corporation Screw compressor pulsation damper
WO2009045187A1 (en) 2007-10-01 2009-04-09 Carrier Corporation Screw compressor pulsation damper
US20100202904A1 (en) * 2007-10-10 2010-08-12 Carrier Corporation Screw compressor pulsation damper
US8459963B2 (en) 2007-10-10 2013-06-11 Carrier Corporation Screw compressor pulsation damper
US20110129374A1 (en) * 2008-07-22 2011-06-02 Oerlikon Leybold Vacuum Gmbh Vacuum pump in particular roots type pump
US8740578B2 (en) * 2008-07-22 2014-06-03 Oerlikon Leybold Vacuum Gmbh Vacuum pump in particular roots type pump
US20100283333A1 (en) * 2009-05-06 2010-11-11 Lemmers Jr Glenn C Oil pressure regulating valve for generator applications
US8485218B2 (en) 2009-05-06 2013-07-16 Hamilton Sundstrand Corporation Oil pressure regulating valve for generator applications
US20110297259A1 (en) * 2010-06-04 2011-12-08 Sundquist Walter W Oil pump system for an engine
US8801396B2 (en) * 2010-06-04 2014-08-12 Chrysler Group Llc Oil pump system for an engine
US20130068328A1 (en) * 2011-09-16 2013-03-21 Caterpillar, Inc. Gerotor Pump Assembly and Engine Fluid Delivery System Using a Gerotor Pump Assembly
US20130284285A1 (en) * 2012-04-25 2013-10-31 Nordson Corporation Pressure control valve for reactive adhesives
US9377114B2 (en) * 2012-04-25 2016-06-28 Nordson Corporation Pressure control valve for reactive adhesives
US8984972B2 (en) 2012-07-17 2015-03-24 Cummins Ip, Inc. Power take-off system for an internal combustion engine
US20150338857A1 (en) * 2014-05-20 2015-11-26 Hamilton Sundstrand Corporation Pressure-regulating valves
US10007276B2 (en) * 2014-05-20 2018-06-26 Hamilton Sundstrand Corporation Pressure-regulating valves
US10866600B2 (en) 2014-05-20 2020-12-15 Hamilton Sundstrand Corporation Pressure-regulating valves
WO2016055261A1 (en) * 2014-10-09 2016-04-14 Robert Bosch Gmbh Fluid pump, in particular for supplying fluid and regulating pressure in a fluid circuit of a slip-controllable vehicle brake system
EP3267038A1 (en) * 2016-07-05 2018-01-10 Fluid-O-Tech S.r.l. Hydraulic pump and respective multifunction valve
US11236744B2 (en) 2016-07-05 2022-02-01 Fluid-O-Tech, S.r.l. Hydraulic pump and respective multifunction valve

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