EP1775469A2 - Pompe - Google Patents

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Publication number
EP1775469A2
EP1775469A2 EP06255287A EP06255287A EP1775469A2 EP 1775469 A2 EP1775469 A2 EP 1775469A2 EP 06255287 A EP06255287 A EP 06255287A EP 06255287 A EP06255287 A EP 06255287A EP 1775469 A2 EP1775469 A2 EP 1775469A2
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EP
European Patent Office
Prior art keywords
pump
discharge
actuating
cylinder
fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Application number
EP06255287A
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German (de)
English (en)
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EP1775469A3 (fr
Inventor
Eric Swan Stamper
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Individual
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Individual
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Publication date
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Publication of EP1775469A2 publication Critical patent/EP1775469A2/fr
Publication of EP1775469A3 publication Critical patent/EP1775469A3/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/12—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air
    • F04B9/129—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers
    • F04B9/131—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers with two mechanically connected pumping members
    • F04B9/133—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by a double-acting elastic-fluid motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/22—Arrangements for enabling ready assembly or disassembly

Definitions

  • the present invention relates to a pump.
  • the present invention relates to a reciprocating pump.
  • Pumps are commonly used in hydraulic systems for the supply of fluid under pressure.
  • single piston reciprocating pumps are known, which, in operation, draw fluid in during part of a cycle of the pump, and discharge fluid during another part of the cycle.
  • Such pumps provide an intermittent flow output, which may be undesirable.
  • Dual-piston reciprocating pumps are also known, which provide a substantially constant fluid output.
  • Such pumps include opposed pistons, which are successively actuated, such that during discharge of one of the pistons, the other piston is being charged, and vice versa. Joining the two outlets of the pistons into a common fluid line facilitates constant fluid flow into the line (during the cycle of the pump), giving a constant flow output.
  • These reciprocating dual-piston pumps are typically mechanically driven, for example using a rotating cam arrangement to drive the pistons.
  • the pumps may be fluid operated, with an actuating fluid supplied to the pump to drive the pistons in a reciprocating fashion.
  • One such type of pump is pneumatically actuated and includes a main actuating piston.
  • the actuating piston is mounted between and coupled to the discharge pistons and is pneumatically controlled for reciprocating motion, to alternately charge and discharge the pistons.
  • valve assembly in this manner inhibits maintenance of and access to the valve assembly should it require changing out. For example, in existing pump and valve assemblies, it is often difficult to replace various seals, which tend to deteriorate relatively quickly over time.
  • a reciprocating pump comprising:
  • the sleeve can be changed out for maintenance or replacement with different diameter sleeves, to alter the nature of the fluid discharge.
  • the pump operates by reciprocating the actuating piston within the actuating cylinder, which causes the discharge piston to correspondingly reciprocate within the sleeve.
  • a fluid volume is drawn into the sleeve by the discharge piston, and is then forced out of the sleeve and the discharge cylinder at pressure.
  • the volume of fluid drawn in and expelled in each cycle is controlled by the operating diameter of the sleeve; i.e.
  • a relatively large diameter sleeve provides for discharge of a relatively large volume of fluid
  • a relatively small diameter sleeve provides for discharge of a relatively small volume of fluid, but at a higher pressure. It will therefore be understood that, in combination with the discharge piston, the sleeve defines a maximum operating volume of the discharge cylinder.
  • the discharge piston is removably or releasably coupled to the actuating piston. This facilitates removal and replacement of the piston, such that a range of discharge pistons may be provided, each of which corresponds to a different diameter sleeve. This may also facilitate maintenance.
  • the discharge cylinder is removably or releasably coupled to the actuating cylinder.
  • the discharge cylinder can be detached and the discharge piston replaced with a new piston, together with appropriate seals and a desired sleeve, which correspond to the chosen size of the new piston.
  • the pump additionally comprises:
  • the pump can achieve a substantially constant fluid output.
  • the first and second sleeves may be independently replaceable and may have different operating diameters.
  • the output of discharged fluid may be balanced to achieve relatively high-pressure and high-flow volume; this may be achieved by combining a relatively high volume, low pressure flow from one discharge cylinder (using a relatively large diameter sleeve) with a relatively low volume, high pressure flow from the other piston (using a relatively small diameter sleeve). Accordingly, this may facilitate control of the physical characteristics, such as pressure and flow rate, of the fluid discharged from the pump.
  • the pump may provide separate, independent fluid outputs from the two cylinders, which may therefore have different flow characteristics.
  • the second discharge sleeve has an operating diameter equal to the operating diameter of the first discharge sleeve.
  • the second discharge piston is removably coupled to the actuating piston.
  • the second discharge cylinder may also be removably attached to the actuating cylinder.
  • first and second discharge cylinders are located at opposing first and second ends of the pump. This facilitates effective transfer of force from the actuating piston to the discharge pistons.
  • the pump may further include a seal for sealing between the sleeve and the discharge cylinder.
  • the pump may comprise first and second seals for sealing between the first and second discharge pistons and the respective sleeves. This may prevent leakage of fluid between the pistons and the sleeves.
  • the diameters of the first and second discharge pistons are matched to the respective diameters of the first and second sleeves, for slideable movement of the discharge pistons within the sleeves.
  • the sleeve may be tubular, and may form part of a removable cartridge, which may comprise the sleeve and the seal.
  • the cartridge or the pump may further comprise a locking collar, which may comprise threads for engaging with mating threads provided in the discharge cylinder.
  • the locking collar may serve for locating and securing the sleeve against movement relative to the discharge cylinder, in use.
  • the actuating piston operates in response to a fluid pressure force provided by an actuating fluid.
  • the actuating fluid is a gas, and may be a pneumatic fluid, particularly, compressed air.
  • the actuating fluid is a liquid.
  • the pump comprises a main valve assembly for controlling supply of actuating fluid to the actuating piston.
  • the main valve assembly may be adapted for controlling supply of actuating fluid successively to one end of the actuating cylinder acting on one face of the actuating piston, whilst permitting discharge of actuating fluid from the other end of the actuating cylinder acting on an opposite face of the actuating piston.
  • the actuating fluid acts successively on opposing faces of the actuating piston, to cause the reciprocating movement.
  • the main valve assembly may comprise a valve housing and a reciprocating shuttle valve, which may control the flow of actuating fluid to the actuating cylinder depending upon a position of the shuttle valve in the housing.
  • the main valve assembly and in particular the valve housing and the shuttle valve, is provided separately from the actuating cylinder. This allows the shuttle valve to be maintained and changed out without a need to dismantle other pump components.
  • the actuating cylinder may comprise a plurality of fluid flow ports for fluid communication between the actuating cylinder and the main control valve assembly.
  • the actuating cylinder comprises a pair of main flow ports, for the flow of actuating fluid in to and out of the cylinder.
  • the main flow ports may act as inlets or outlets depending on a direction of movement of the actuating piston.
  • the main actuating cylinder flow ports may be in fluid communication with the main valve assembly through main valve assembly flow ports, for the flow of fluid between the actuating cylinder and the main valve assembly.
  • the shuttle valve In a first position, the shuttle valve may facilitate supply of actuating fluid to a first end of the actuating cylinder and discharge from a second end, to facilitate movement of the actuating piston in a first direction.
  • the shuttle valve In a second position, the shuttle valve may facilitate supply of actuating fluid to the second end and discharge from the first end, for movement of the actuating piston in a second, opposite direction. This may provide the desired reciprocating motion of the actuating piston.
  • the actuating cylinder includes a pair of pilot valves for controlling operation of the main valve assembly.
  • the pilot valves may be provided at opposite ends of the actuating cylinder, and may each include a valve pin protruding into the actuating cylinder for opening the pilot valves.
  • the pilot valves may be biased toward a closed position, and the actuating piston may be adapted to open the pilot valves via mechanical interaction between the actuating piston and the pilot valves, optionally with the pin of each valve.
  • the pilot valves may permit selective fluid bleed from the main valve housing.
  • each pilot valve may selectively permit fluid bleed from a respective end of the main valve housing.
  • opening of one of the pilot valves may facilitate movement of the shuttle valve between its first and second positions, to thereby switch supply of actuating fluid between the main valve assembly and the actuating cylinder.
  • the pilot valves may selectively open the main valve housing to atmosphere, to permit fluid bleed, through respective bleed ports.
  • a first pilot valve may be coupled to a first end of the main valve housing, and a second pilot valve to a second, opposite end of the valve housing, by corresponding fluid lines.
  • the pilot valves may each also be coupled to a fluid pressure source. Actuation of the first pilot valve may supply fluid to the first end of the valve housing, to move the shuttle valve in a first direction. Actuation of the second pilot valve may supply fluid to the second end of the valve housing, to move the shuttle in a second, opposite direction.
  • the position of the pins relative to the actuating cylinder may be adjustable, or the pins may be adjustable in length.
  • the distance of travel of the actuating piston can be altered to correspondingly change the duration of successive discharge and draw-in phases from first and second ends of the pump.
  • the main valve assembly further comprises a flow input valve coupled to the valve housing, for controlling supply of actuating fluid to the assembly.
  • the flow input valve may be needle valve, and may be adjustable for controlling the supply of fluid to the main valve assembly and thus to the actuating piston. This may facilitate variation of an operating characteristic of the pump, such as output fluid pressure or flow rate.
  • a sleeve for a reciprocating pump wherein the sleeve is adapted to be releasably mounted in a discharge cylinder of the pump, to thereby define an operating diameter of the discharge cylinder.
  • the sleeve is further adapted to receive a discharge piston of the pump, the discharge piston coupled to an actuating piston of the pump and mounted for reciprocating movement within the sleeve to successively draw fluid into and discharge fluid from the cylinder.
  • the sleeve is for a reciprocating pump according to the first aspect of the invention.
  • a method of changing output flow from a pump comprising the steps of:
  • the method comprises the steps of:
  • FIG 1 there is shown a longitudinal, cross-sectional view of a pump in accordance with an embodiment of the present invention, the pump indicated generally by reference numeral 10.
  • the pump 10 is illustrated in more detail in Figures 2 and 3, which also show a main valve assembly 80 of the pump 10, and which show the pump 10 at various stages in a cycle of operation.
  • the pump 10 comprises an actuating cylinder 12 and an actuating piston in the form of an air drive flange 16, which is mounted for reciprocating movement within the actuating cylinder 12.
  • the pump also comprises a discharge cylinder 52a which is provided in a hydraulic end housing 38a, and a sleeve in the form of a cartridge 40a which is releasably mounted within the discharge cylinder 52a, to thereby define an operating diameter 42a of the cylinder.
  • a discharge piston 30a is coupled to the flange 16 and mounted for reciprocating movement within the sleeve 40a, to discharge fluid from the discharge cylinder 52a.
  • the pump 10 is operated to pump a fluid by controlling reciprocating movement of the flange 16 within the actuating cylinder 12. This is achieved by controlling the supply of actuating fluid (in this case, compressed air) to the actuating cylinder 12, as will be described in more detail below.
  • actuating fluid in this case, compressed air
  • the discharge piston 30a by virtue of its connection to the flange 16, is reciprocated back and forth within the sleeve 40a during movement of the flange 16, and thus repeatedly charges the discharge cylinder 52a (drawing fluid in through a check valve in an inlet 56a) and discharges the cylinder 52a (expelling the fluid through a check valve in an outlet 58a).
  • the sleeve 40a is releasably mounted within the discharge cylinder 52a, which facilitates maintenance and/or replacement.
  • the sleeve 40a may be replaced with a sleeve of a different internal diameter, which enables the flow characteristics of the pump to be adjusted. For example, by replacing the sleeve 40a with a sleeve of a smaller internal diameter, a smaller volume of fluid is drawn into the discharge cylinder 52a on each cycle of the discharge piston 30a.
  • the diameter of the replacement sleeve 40a is smaller, the resultant pressure of the discharged fluid is higher; this is due to the corresponding smaller piston area defined by the replacement sleeve, which will be described below.
  • the pump 10 is a dual-piston reciprocating pump, for supplying a substantially constant fluid output, and includes two discharge pistons 52a, 52b at opposite ends 32 and 34 of the pump. Like components of the pump components at the end 32 with those at the end 34 share the same reference numerals, but with the suffix 'a' generally replaced with the suffix 'b'.
  • the air cylinder 12 includes end caps 14a,b and a drive shaft 18 is provided which extends along a longitudinal axis of the cylinder 10 and through apertures 20a,b in the end caps 14a,b.
  • the air drive flange 16 is connected to the portion 22 of the shaft 18 within the cylinder 12, and seals 24 are provided around the outer circumference of the flange 16.
  • the discharge pistons 30a,b are connected to the drive shaft 18 via threaded connections 36a,b thereby allowing the pistons to be readily changed out.
  • Hydraulic end housings 38a,b are connected to each end 32,34 of the pump, and are threadably connected to the end caps so that they can be removed easily for access to components of the pump.
  • the hydraulic end housings 38a,b define the discharge cylinders 52a,b and are aligned with the longitudinal axis of the pump, such that the drive shaft 18 with pistons 30a,b are able to slideably move relative to the discharge cylinders.
  • the housings 38a,b include respective end portions or caps 50a,b.
  • the hydraulic end housings 38a,b receive the sleeves or cartridges 40a,b, which have hydraulic seals 44a,b that seal between the cartridges 40a,b and the outer surface of the pistons 30a,b.
  • the diameter 42a,b defined by the cartridges 40a,b match that of the pistons 30a,b such that the pistons fit snugly and slideably within the cartridges.
  • a maximum, operating volume of the discharge cylinders 52a,b are defined by front surfaces 54a,b of the pistons 30a,b, the inner surfaces of the cartridges 40a,b, and end portions 50a,b of the hydraulic end housings and depend upon the extent of movement of the pistons relative to the cartridges.
  • the inlets 56a,b enable fluid to be drawn in from an external reservoir (not shown), whilst the discharge pistons 30a,b move in a direction away from the respective first and second ends 32,34 of the pump.
  • the outlets 58a,b facilitate discharge of high-pressure fluid from the cylinders 52a,b under the force of the pistons 30a,b.
  • the pump 10 is modular and the detachable hydraulic end housings 38a,b allow easy access to the pistons 30a,b and hydraulic seals 44a,b. This facilitates cleaning/maintenance and replacement without having to fully dismantle the pump 10.
  • pistons and cartridges also allows pistons of different sizes to be selected and installed with ease, in situ, and without requirement to change other pump components.
  • different cartridges 40a,b provided with different size internal bores are inserted into the end housings 38a,b with internal diameters corresponding to the outer diameters of the desired pistons 30a,b.
  • a piston may be changed out and replaced with a different piston as required by a user for a particular application.
  • a smaller piston may be required to provide high-pressure, low-flow-rate output.
  • the provision of different cartridge or insert sizes removes the need to provide pumps with different specifications for different jobs or purposes.
  • the air cylinder is additionally provided with ports 57a,b extending through the cylinder end caps 14a,b. As will be described, the ports 57a,b provide a fluid connection to ends 26 and 28 of the air cylinder 12 for driving the pump 10.
  • the pump 10 is shown in an operational configuration, connected to a main valve assembly 80.
  • air is supplied to the air cylinder 12 under the control of the valve assembly 80, which comprises a valve housing 98 and a shuttle valve 100.
  • the shuttle valve 100 is mounted for reciprocating movement within the housing 98, and is provided with a number of flanges 102 having outer surfaces 104 which carry seals 106.
  • the flanges 102 of the shuttle valve 100 defines a series of annular chambers 82, 84, 90 and 92 between the shuttle valve and the valve housing 98, which serve for controlling air flow, as will be described below.
  • the valve assembly 80 also includes an adjustable needle valve 83, through which air enters the valve assembly for driving the pump 10. Air enters the valve assembly 80 via a port 81, and flows into the chamber 82. In the portion of the pump cycle depicted in Figure 2, the air provided to chamber 82 exits through a port 85 and flows into the air cylinder 12 via a pipe 94a and the port 57a. This air enters the end 26 of the cylinder 12 under pressure, and exerts a pressure force on the drive flange 16. Simultaneously, the end 28 of the air cylinder 12 is open to atmosphere, via the port 57b, a pipe 94b, a port 87 in the valve housing 98 and an exhaust port 89 (which opens on to the annular chamber 84).
  • a pressure differential is thereby created across the flange 16, which then moves towards the second end 34 of the pump.
  • the piston 30b connected to the drive shaft 18 acts against the fluid in the chamber 52b, providing a high-pressure output from outlet 58b.
  • the pressure of the air provided to the air cylinder 12 is typically between 2 and 12 bar (approximately 30 to 175 psi), whilst the output pressure is in the region of 60,000 psi.
  • the pump 10 also comprises two pilot valves 60a,b which are biased closed, and which are opened via mechanical activation of valve pins 66a,b from inside the air cylinder 12.
  • the length of the pins 66a,b is adjustable and the pins 66a,b protrude into the cylinder ends 26 and 28.
  • the flange 16 strikes the valve pin 66b of the pilot valve 60b and, when the pin is depressed, the valve is opened.
  • the pilot valves 60a,b are connected via pipes 96a,b to ports 88a,b of the flow valve. Air is supplied to the pipes from a common pressure source (not shown) through ports 86a,b of the valve assembly 80 and annular end chambers 90 and 92 respectively. Air pressure in these pipes 96a,b and the chambers 90 and 92 determine the position of the shuttle valve 100 within the valve housing 98. In the position of Figure 2, the pressure in the chamber 90 is held at a higher level than that in the chamber 92 by the closed pilot valve 60b, creating a pressure differential across the shuttle valve 100 holding it in the Figure 2 position.
  • valve 60b When the valve 60b is opened, through contact between the flange 16 and the valve pin 66b, the air in the pipe 96b is vented to atmosphere through a pilot hole (not shown) which is opened by this movement of the valve pin 66b.
  • the pressure in pipe 96b and chamber 90 thus reduces to near atmospheric pressure, urging the shuttle 100 towards the now-low pressure chamber 90, driven by the higher pressure of air in chamber 92, moving the shuttle 100 to the position shown in Figure 3.
  • the pump is shown following movement of the shuttle 100 to the opposite end of the valve housing 98.
  • the chamber 82 of the valve assembly 80 opens onto the port 87, such that air is now provided to the end 28 of the air cylinder 12 through port 57b.
  • air is supplied to the cylinder end 28 and forces the flange 16 and piston 30 to move toward the first end 32 of the pump 10.
  • air exits the cylinder end 26 via port 57a and pipe 94a and back to the valve assembly 80.
  • the return air enters port 85 and exhausts to the atmosphere through a port 126.
  • the pilot valve 62b is released and closes, locking the shuttle 100 in the position of Figure 3.
  • the different internal diameters 42a,b of the sleeves 40a,b result in different flow characteristics of the discharged fluid.
  • a larger volume of fluid is discharged from the cylinder 52a on each cycle of the piston 30a than on each cycle of the piston 30b.
  • the smaller piston area of the piston 30b results in a higher pressure output from the discharge cylinder 52b.
  • the present invention provides a number of other advantages.
  • the pins 66a,b for triggering the switching of the stroke direction of the pump are adjustable in length. This allows the stroke length of the pump in either direction to be adjusted, i.e. arranging the pins to protrude further into the air cylinder 12 will shorten the stroke length.
  • the valves containing these pins may be unscrewed to insert appropriate length pins 66a,b or the lengths of the pins could be adjusted externally without needing to unscrew the valve. In either case, the pins and stroke length can be adjusted easily without dismantling the pump or providing a different size cylinder, which would otherwise be necessary.
  • FIG 5 there is shown a longitudinal, cross-sectional view of a reciprocating pump in accordance with an alternative embodiment of the present invention, the pump indicated generally by reference numeral 10'.
  • the pump 10' Like components of the pump 10' with the pump 10 of Figs 1 to 4 share the same reference numerals, with the addition of the suffix'. Only significant differences between the pump 10' and the pump 10 will be described in detail herein.
  • the pump 10' includes pilot valves 60'a and 60'b which govern the position of a shuttle valve 100', in a similar fashion to the valves 60a, 60b of the pump 10.
  • end caps 14'a and 14'b of an actuating cylinder 12' include bleed vents 108a, 108b which open on to bores 110a, 110b in which the respective valves 60'a, 60'b are mounted.
  • the bleed vent 108a is coupled to a fluid outlet line 112a which is in fluid communication with a chamber 90' of the valve assembly 80'.
  • the bleed vent 108b is coupled by a fluid outlet line 112b to a chamber 92' at an opposite end of the valve 80'.
  • valves 60'a and 60'b are coupled via fluid supply lines 96'a and 96'b to a common pilot pressure source (not shown).
  • Ports 86'a and 86'b of the shuttle valve 80' carry one-way valves (not shown), and permit exhaust of air from the chambers 92' and 90', respectively.
  • the pump 10 operates as follows. In use and during movement of a flange 16' of the pump 10' to the right, as shown in Figure 5, the flange 16' comes into contact with a pin 66'b of the pilot valve 60'b. This causes the valve 60'b to open, thereby permitting fluid communication between the pilot pressure source and the chamber 92', through the supply line 96'b and the outlet line 112b. The valve 60'a is closed, and the fluid supplied to chamber 92' causes the shuttle valve 100' to move to the right, exhausting the air in chamber 90' through the port 86'b. In a similar fashion to the valve assembly 80 of the pump 10, this switches flow into the actuating cylinder 12', and reverses the flange 16'.
  • the pump 10' includes sleeves 40'a and 40'b which are of similar internal diameters, and thus illustrates a situation where it is desired to have similar discharge from each discharge piston 30'a and 30'b. Additionally, Figure 5 illustrates clamping bolts 116 which secure the cylinder flanges 14'a, 14'b together.
  • FIG 6 there is shown a longitudinal, cross-sectional view of a main valve assembly forming part of a reciprocating pump in accordance with a further alternative embodiment of the present invention, the main valve assembly indicated generally by reference numeral 80".
  • the valve assembly 80'' typically forms part of a pump similar to the pump 10' shown in Figure 5, and thus may replace the valve assembly 80'.
  • the valve assembly 80'' is shown in Figure 6 and described, the remaining components of the pump being as shown in Figure 5. Only the differences between the assemblies 80" and 80' will be described herein in detail, and like components of the valve assembly 80" with the valve assemblies of Figs 1 to 4 and Fig 5 share the same reference numerals, with the addition of the suffix ".
  • the valve assembly 80" includes a shuttle 100" of slightly different shape to the shuttle 100' of the valve assembly 80'.
  • the shuttle 100" includes shoulders 118, 120 which abut end caps 122, 124 respectively at each extreme extent of travel of the shuttle 100".
  • These end caps 122, 124 are threadably coupled to a housing 98" of the valve assembly 80", in a similar fashion to the valve assemblies shown in Figures 1 to 5. This permits removal of the shuttle 100" for maintenance/replacement.
  • the shoulders 118, 120 define maximum extents of movement of the shuttle 100", and thus the position of the shuttle 100" in relation to the various ports 85"; 86''a,b; 87"; and 88"a,b.
  • end cap 124 defines an outlet 126 from an end chamber 128 which is of larger diameter than similar vent or bleed ports from the valve assemblies shown in Figures 1 to 5. This provides improved exhaust of air from the chamber 128 in use of the valve assembly 80". Operation of the valve assembly 80" is otherwise as described in relation to the valve assembly 80' of Figure 5.
  • FIGS. 7 and 8 there are shown longitudinal, cross-sectional views of a main valve assembly forming part of a reciprocating pump in accordance with a preferred embodiment of the present invention, the valve assembly indicated generally by reference numeral 80''' and shown in the Figures at respective opposite extents of travel of a shuttle 100''' of the valve assembly.
  • valve assembly 80''' is provided as part of a reciprocating pump similar to that shown in Figure 5, save that the valve assembly 80' has been replaced with the valve assembly 80"'.
  • the remaining components of the pump have been omitted, for ease of illustration.
  • valve assembly 80"' and the previously described valve assemblies will be described herein in detail.
  • Like components of the valve assembly 80''' with the valve assemblies of Figs 1 to 4, Fig 5 or Fig 6 share the same reference numerals, with the addition of the suffix"'.
  • a housing 98"' of the valve assembly 80"' includes a number of flow ports 130a and 130b (two of each shown) spaced around a circumference of the housing 98"'.
  • Outer seal rings 132a, 132b are mounted on the housing 98 in abutment with a central flange 134, and are secured by bolts (not shown) which extend through passages 136a,b and engage in the flange 134.
  • the seal rings 132a,b define main flow ports (not shown) similar to the ports 85" and 87'' of the valve assembly 80". These main flow ports open onto annular chambers 138a,b between the seal rings 132a,b and the housing 98"', as do the flow ports 130a, 130b.
  • valve assembly 80''' This provides fluid communication between the valve assembly 80''' and the cylinder of the pump (such as the cylinder 12' of the pump 10' shown in Figure 5).
  • This arrangement of the flow ports 130a,b spaced around the circumference of the housing 98"', and of the main flow ports opening onto the annular chambers 138a,b provides enhanced flow of air to and from the cylinder in use of the valve assembly 80"'.
  • end caps 122''' and 124"' of the valve assembly 80"' have enlarged outlets 126"'a, 126"'b, to provide enhanced flow of exhaust air.
  • the shuttle 100"' also includes a number of exhaust ports 140 and 142 (five of each shown) spaced around a circumference of the shuttle valve, to enhance flow of exhaust air.
  • the shuttle 100"' includes a throughbore 144 which provides for fluid communication between the exhaust ports 140, 142 and the respective outlets 126"'a,b. The shuttle 100''' is shown following movement to the opposite extent of its travel in Figure 8.
  • valve assembly 80 iv of a reciprocating pump in accordance with a further alternative embodiment of the present invention
  • valve assembly 80 iv is provided as part of a reciprocating pump similar to that shown in Figure 5, save that the valve assembly 80' has been replaced with the valve assembly 80 iv .
  • the remaining components of the pump have been omitted, for ease of illustration.
  • valve assembly 80 iv and the previously described valve assemblies will be described herein in detail.
  • Like components of the valve assembly 80 iv with the assemblies of Figs 1 to 4, Fig 5, Fig 6 or Figs 7 and 8 share the same reference numerals, with the addition of the suffix iv
  • valve assembly 80 iv is essentially the same as the valve assembly 80"', save that the internal diameter of the shuttle 100"' throughbore 144 is 3 ⁇ 4", whereas a throughbore 144 iv of the shuttle 100 iv is 1" to provide enhanced air flow. Additionally, internal diameters of end caps 122 iv and 124 iv have been enlarged to account for the larger diameter shuttle 100 iv . Operation of the valve assemblies 80''' and 80 iv is otherwise as described in relation to the valve assembly 80' of Figure 5.
  • the end housings may be detached, allowing the piston to be unscrewed and replaced with a different diameter piston to suit desired needs.
  • Cartridges provided in the housing that compliment the piston and house the hydraulic seals can similarly be unscrewed, removed and replaced. Such replacement can be carried out with ease and with the pump in situ, as part of a larger system. Hydraulic seals can be easily accessed, maintained and replaced.
  • the present pump mitigates the need to dismantle the pump or to change out the entire pump with a new pump when different pump characteristics are required. This saves costs relating to the purchase of parts and operational downtime for repair and maintenance.
  • the discharge pistons may be directly threadably coupled to the actuating piston, such that the entire piston is released from the actuating piston when it is desired to changeover for a discharge piston of a different diameter.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP06255287A 2005-10-14 2006-10-13 Pompe Withdrawn EP1775469A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GBGB0520878.0A GB0520878D0 (en) 2005-10-14 2005-10-14 Improved pump

Publications (2)

Publication Number Publication Date
EP1775469A2 true EP1775469A2 (fr) 2007-04-18
EP1775469A3 EP1775469A3 (fr) 2009-03-04

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WO2019239105A1 (fr) 2018-06-15 2019-12-19 Combined Pumps Limited Pompe alternative
GB2637475A (en) * 2023-12-21 2025-07-30 Combined Pumps Ltd Drainage port for a transfer pump and a method of using the same

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WO2014032758A1 (fr) * 2012-08-29 2014-03-06 Eisenmann Ag Pompe haute pression à quatre soupapes
CN104583597A (zh) * 2012-08-29 2015-04-29 艾森曼欧洲公司 四阀高压泵
CN104583597B (zh) * 2012-08-29 2016-11-09 艾森曼欧洲公司 四阀高压泵
RU2624093C2 (ru) * 2012-08-29 2017-06-30 Айзенманн Се Четырехклапанный насос высокого давления
WO2019239105A1 (fr) 2018-06-15 2019-12-19 Combined Pumps Limited Pompe alternative
GB2637475A (en) * 2023-12-21 2025-07-30 Combined Pumps Ltd Drainage port for a transfer pump and a method of using the same

Also Published As

Publication number Publication date
US20070128053A1 (en) 2007-06-07
GB0520878D0 (en) 2005-11-23
EP1775469A3 (fr) 2009-03-04

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