CA1040005A - High-pressure plunger pump - Google Patents
High-pressure plunger pumpInfo
- Publication number
- CA1040005A CA1040005A CA213,548A CA213548A CA1040005A CA 1040005 A CA1040005 A CA 1040005A CA 213548 A CA213548 A CA 213548A CA 1040005 A CA1040005 A CA 1040005A
- Authority
- CA
- Canada
- Prior art keywords
- plunger
- pressure
- suction
- pump according
- valve element
- 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.)
- Expired
Links
Classifications
-
- 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
- F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
- F04B19/02—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00 having movable cylinders
- F04B19/022—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00 having movable cylinders reciprocating cylinders
-
- 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
- F04B53/007—Cylinder heads
Abstract
A B S T R A C T
A high pressure plunger pump is provided. The pump has a centrally arranged pressure valve and a sleeve like element mounted slidably between the cylinder and the plunger, subjected to spring pressure and enclosing the pump pressure chamber. The sleeve like element is carried exclusively by the plunger and stop means are provided for limiting sliding movement of the sleeve like element towards a rearward end of the cylinder, away from the pressure valve. Multiple cylinder embodiments are also disclosed.
A high pressure plunger pump is provided. The pump has a centrally arranged pressure valve and a sleeve like element mounted slidably between the cylinder and the plunger, subjected to spring pressure and enclosing the pump pressure chamber. The sleeve like element is carried exclusively by the plunger and stop means are provided for limiting sliding movement of the sleeve like element towards a rearward end of the cylinder, away from the pressure valve. Multiple cylinder embodiments are also disclosed.
Description
104~}005 The invention relates to a high-pressure plunger pump having a centrally arranged pressure valve, and a sleeve-like element mounted slidably between the cylinder and the plunger, subjected to spring pressure, and enclosing the pump pressure chamber.
In one known pump of this kind, the suction-valve element is guided externally by the cylinder, which means that at high pressures there is a danger of the suction-valve element jamming in the cylinder. In addi-tion to this, there is an accumulation of heat in the transition area between the suction-valve element and the cylinder wall. This known suction-valve element must be machined internally and externally.
It is the purpose of the invention to design a high-pressure plunger pump of the type mentioned above in a manner such that the efficiency is in-creased, the reliability is improved, and the structure is simplified.
According to the invention, there is provided a high pressure plunger pump having a pumping unit comprising: a housing defining a suction chamber with an open end; a pump head extending over and closing the open end of the suction chamber, the pump head and housing engaging one another along a dividing plane; a retainer for securing said head to said housing;
a pressure valve in the pump head, having an inlet opening in said dividing plane and a valve element normally closing said opening, an end face of the valve element lying lsubstantially in said dividing plane; a collector chamber in the pump head communicating with the suction chamber through the pressure valve; a plunger mounted in said housing for reciprocation within the suction chamber, the plunger being concentrically arranged relative to the pressure valve inlet opening and valve element and having a forward dead centre position in which a forward face of the plunger is disposed sub-stantially in said divisional plane; a sleeve like suction valve element carried on said plunger for sliding movement thereon and spring biased to a closed position where an annular forward end face of the suction valve ele-ment is engaged with a suction valve seat on the pump head, lying in the ~.~ - 1 -.~
~L04~1~Q5 dividing plane and surrounding the pressure valve inlet opening.
Since the suction-valve element is guided on the plunger, the outer surface of the element re~uires no machining. It is impossible for the element to jam in the cham~er. In operation the element is washed by suction fluid. I'he heat produced during the compression stroke is trans-ferred from the element directly to the suction fluid.
The suction stroke of the suction-valve element, and thus the opening and closing times thereof, may be determined by a stop associated with the element.
The suction-valve element may be fitted to the plunger in a manner such that a high-pressure seal forms within the suction valve as an hydro-static seal. During the suction stroke, the suction valve is opened by the returning plunger as a result of the fluid friction arising in the seal.
During the compression stroke, fluid in the suction chamber is drawn into the gap between the plunger and the suction-valve element and supports the sealing action.
While the unit is in operation, the retention of the pump head to the housing may be adjusted according to the hydraulic pressure present in the pump head.
The object of the application may be used not only as a plunger pump, but also as an homogenizing unit for cream, pastes, and the like, or for the purpose of accelerating polymerization processes.
Various exemplary embodiments of the invention are described here-inafter and are illustrated in the drawings attached hereto, wherein:
Figure 1 is a longitudinal section through th~ pressure and suction chambers of a pump;
Figure 2 is a view in the direction of arrow II in Figure l;
Figure 3 is a detail of Figure 1 in cross section;
Figure 4 shows another embodiment in longitudianl section;
Figure 5 is a variant of the design in Figure 4;
~04~ 5 Figure 6 is a view in the ~irection of arrow VI in Figure 5;
Figure 7 shows an example of the U-shaped retainer shown in Figure 1 for the pump head;
Figure 8 is a section through an additional anchorage between the pump-head and pump-housing;
Figure 9 shows another embodiment of the pump in which the suction-valve element is in two parts;
Figur0 10 is a variant of the design in Figure 9;
Figure 11 shows another embodiment of a high-pressure plunger pump in longitudinal section;
Figure 12 shows a detail, in section, of the design according to Figure 11, to an enlarged scale.
In the pump shown in Figure 1, pump housing 26 has a suction chamber 61 to which suction fluid flows through a passage 60. A plunger 46 enters this suction chamber through a low-pressure seal 4, the plunger being driven, for example, by means of a crankshaft, a connecting rod, and a crosshead.
The drawing shows the plunger at forward dead centre, i.e. at the end of the compression stroke.
It may be gathered from the illustration that the pump has very little dead space at the forward dead-centre position.
The pump head 27 is secured to the pump housing 26 by means of a U-shaped retainer 28. To this end, the legs of the U-shaped retainer are provided with anchoring rims 29 engaging behind anchoring projections 30 on housing 26.
Figure 1 shows a dove-tail type of joint between housing 26 and retainer 28. The latter may be pushed onto the housing from the side, to-gether with pump head 27.
Pump head 27 is aligned with retainer 28 by means of centering pins 31.
~O~ 5 In the embodiment according to Figures 1 and 2, after the pump head and the retainer have been slid onto pump housing 26, toggle-bar screws 32 are tightened, threaded shanks 33 thereof passing through threaded holes in the central web 34 of the retainer and bearing against pump head 27. This presses pump head 27 against end-face 35 of housing 26 and presses anchoring rims 29 against anchoring projections 30. The seal between pump head 29 and end-face 35 of the housing is achieved by means of a sealing ring 35a.
Thus toggle-bar screws 32, 33 produce a prestress between the pump head, the retainer, and the pump housing, and this is present at all times.
As a variant of the design illustrated in Figures 1 and 2, it is also possible to replace toggle-bar screws 32, 33 with eccentrics 3-7 (Figures 5 and 6) mounted to pivot about axes 39 in recesses 38 in central web 34 of retainer 28, the said eccentrics being actuated by means of handles 40, Anchoring rims 29 on retainer 28 may extend over the whole width of the retainer. It is, however, also conceivable, as shown in Figure 7, to make the rims in sections, thus producing a plurality of hooks in spaced relationship to each other.
It is also unnecessary for a dove-tail type of attachment to be 2Q provided between the anchoring rims and the anchoring projections. Instead, the anchorage may be designed as shown in Figure 8. In this case, the coop-erating surfaces of anchoring rims 22a and anchoring projections 30a are at right angles to the wall of the pump housing.
~ alve seat 41 of pressure valve 42, and valve seat 43 of suction-valve element 44, lie in the area of the parting plane between pump housing 26 and pump head 27. Should the valve seats require refinishing, this may be carried out quite easily after removal of the pump head.
During the suction stroke of plunger 46, under the action of a spring 47 pressure valve element 45 closes the pressure-valve aperture, thus defining one end of collector chamber 48 provided in pump head 27 for the .~ - 4 -~' 10~05 medium being delivered. At the end facing the valve aperture, collector chamber 48 has an aperture which is closed off by a piston 49 arranged to slide in the collector chamber and acting upon central web 34 of retainer 28.
The pressure in the collector chamber defines the pressure applied by piston 49 to the central web 34 of retainer 28.
Thus, when the pump is in operation, a clamping force dependent upon the pressure in collector chamber 48 is superimposed upon the pre-load produced by toggle-bar screws 32, 33 or eccentrics 37, 40.
Pressure-valve element 42 has a pin 50, the free end of which is adapted to-slide in a blind bore 51. An angled passage 52 is provided in the pin for the purpose of equalizing the pressure between the piston chamber formed by the blind bore and the free end of the pin, and collector chamber 48.
Return spring 47 surrounding pin 50 rests with one end on piston 49.
The embodiments illustrated in the drawings have three plungers 46 and therefore three collector chambers 48 in pump head 27. These collector chambers are connected together through a bore 53, through which pressure equalization is effected within the pump head.
A sleeve-like suction~valve element 44 is slidably mounted on the plunger 46 and consists of two cylindrical sleeves 54, 55 which are joined together by shrinkage or auto frettage. Rear edge 56 of sleeve 54 forms a supporting surface for the end of return spring 57 of suction-valve element 44. During the suction stroke of plunger 46, the suction-valve element follows the movement of the plunger against the action of spring 57, rear edge 58 of sleeve 55 comes up against a stop surface 59. This stop 59 limits the stroke of suction-valve element 44, which is less than the maximal travel of spring 57. During the suction stroke of the pump, the medium being delivered is drawn through a housing aperture 60 into suction chamber 61 of the pump, whence it passes to the space defined by suction-valve element 44 . - .
~04000S
and plunger 46, which forms the pressure chamber during the compressîon stroke of the pump.
Thus in the object of the application, it is only suction-valve element 44 that is subjected to alternating loads during the suction and com-pression strokes.
The cross-sectional area of the pressure chamber, of diameter dl, is larger than the cross-sectional area of the suction-valve seat, of dia-meter d2, so that an additional closing force is produced for the suction valve, during the compression stroke, by the pressure of water on the differential area.
During the suction stroke, a negative pressure occurs in the inter-nal chamber of the suction-valve element 44. This negative pressure, in conjunction with the slight initial pressure in the pump suction chamber, allows a force to act upon the valve element, which force assists the valve as it moves in the opening direction.
It is also possible to provide plunger 46, and the inner surface of the suction-valve element associated therewith, with a micro-labyrinth seal in which the labyrinth recess in the plunger are in staggered relation-ship to the divisions in the suction-valve element. Relative movement between the plunger and the suction-valve element produces vortexing of the delivery medium, and this intensifies the sealing action between the plunger and the suction-valve element.
In the embodiment according to Figure 4, inside diameter d3 of low-pressure seal 4, and the corresponding diameter of the plunger end which does not enter the suction-valve element are larger than diameter dl of the other part of the plunger.
This plunger configuration i s an advantage in the case of a high-pressure plunger pump equipped with a plurality of plungers operating in a chronologically staggered relationship to each other. During the compression stroke of one plunger, end-face 22 of the plunger, produced by enlarged s~
~o~ooos diameter d3, delivers suction fluid from suction chamber 2, through a pass-age into the suction chambers of the other plungers. This improves the over-all suction ratio.
Slidably mounted on the plunger 5 is a sleeve-like suction-valve element 6, with which a biasing spring 7 is associated. One end of spring 7 rests against rear end 8 of the suction-valve element, while the other end rests against a flange 9 on a sleeve 10 secured in the pump housing 1.
Sleeve 10 extends into the interior of cylindrical helical spring 7 with the front end-face 11 of the sleeve limiting the return stroke of the suction-valve element 6.
The sleeve-like design of the suction-valve element makes it easy, from the production point of view, to produce a dimensionally stable suction-valve element which does not change shape under the loads associated with the compression stroke. Thus the sealing gap between the suction-valve element and the plunger retains its predetermined size.
In the embodiment according to Figures 9 and lO, suction-valve elements 85, 85a and 85b are made in two parts. In the design according to Figure 9, the suction-valve element has a sleeve 87 guided on plunger 86 and a valve part 88. A spring 90 is provided between valve part 88 and sleeve 87.
Sleeve 87 is arranged between pump head 9O and rear plunger guide 91 with a certain amount of play. Sleeve 87 has slots 92 adjacent pump head 90. In this embodiment, the suction-valve element is surrounded by an annu-lar screen 93.
During the return stroke of the plunger, a vacuum is formed within the suction-valve element, and this opens valve part 88 by compressing spring 89. If there is any initial pressure in suction chamber 94, this increases the force acting to open valve part 88.
In the design according to Figure lO, valve part 88b is carried on sleeve 87b. Spring 89b, arranged between sleeve 87b and valve part 88b, has 10~ 5 one end bearing against a stop ring 95 secured to sleeve 87b. The other end of spring 89b bears against rear end-face 96 of valve part 88b.
The designs according to Figures 9 and 10 are suitable for both horizontal and vertical pumps.
In the embodiment according to Figures 11 and 12, pump housing 101, in which a plurality of plungers 102 may be arranged side by side, is connected to pump head 104 by means of laterally insertable bars 103.
The pump housing has a suction chamber iO5 to which suction fluid is delivered through a passage 106. Plunger 102 en~ers the suction chamber through a seal 107, the plunger being driven by a crankshaft, a connecting rod, and a crosshead.
Suction-valve element 108 is carried entirely on the plunger.
Associated with the suction-valve element is a spring 109 which endeavours to keep the said element in the closed position shown in Figure 14, During the suction stroke, the force of spring 109 must be overcome by suction-valve element 108. The suction stroke is limited by a stop 1~ which co-operates with rear end-face 111 of the suction-valve element.
Plunger 102 has a rod part 112 and a sleeve 113 enclosing the rod part.
2n In the forward area of plunger 102, rod part 112 has a reduced diameter forming an annular space 114 defined peripherally by sleeve 113.
This annular space is connected through a transverse passage 115, and a pass-age 116 lying on the longitudinal axis of the plunger, with pump pressure chamber 117, formed by suction-valve element 108. In this embodiment, passage 116 passes through a threaded stud, extending from the front face of rod part 112, onto which a nut 118 is screwed in order to secure a stop plate 119 for the front annular surface of sleeve 113. Seat 120 of the suc-tion valve, and seat 121 of pressure valve element 122, are arranged on a valve-seat ring 123. This valve-seat ring, which is mounted in a recess in pump head 104, can easily be replaced after the pump head has been removed ..~
~04~ S
from the pump housing.
A sealing ring 124 is provided, adjacent the rear end of the annular space, 114 between rod part 112 and sleeve 113 of the plunger.
Figure 12 shows the sealing gap 125 between suction-valve element 108 and sleeve 113 of plunger 102, to an enlarged scale.
The pressure in pressure chamber Pl decreases, in sealing,gap 125, in the direction of the drive-end of the plunger, reaching a valve P2 in the end _ g _ ~L04QO(~S
area of annular space 114.
Since annular space 114 is slightly staggered towards the drive-end, in relatlon to the front end of the plunger, the pressure in the sealing gap associated with annular space 114 is lower, during the compression stroke, than the pressure in annular space 114, which coincides with the pressure in pressure chamber 117. This deforms sleeve 113, as shown in dotted lines in Figure 15, leading to a reduction in the cross section of sealing gap 125.
The deformation of the plunger sleeve, induced by the pressure of the medium being delivered, lies within the elastic limit of the sleeve, so that when the pressure drops, the sleeve again assumes its normal shape. This ensures a satisfactory seal between the plunger and the suction-valve element in the case of plunger pumps operating at very high pressures, of 1000 bars and more, for example.
In one known pump of this kind, the suction-valve element is guided externally by the cylinder, which means that at high pressures there is a danger of the suction-valve element jamming in the cylinder. In addi-tion to this, there is an accumulation of heat in the transition area between the suction-valve element and the cylinder wall. This known suction-valve element must be machined internally and externally.
It is the purpose of the invention to design a high-pressure plunger pump of the type mentioned above in a manner such that the efficiency is in-creased, the reliability is improved, and the structure is simplified.
According to the invention, there is provided a high pressure plunger pump having a pumping unit comprising: a housing defining a suction chamber with an open end; a pump head extending over and closing the open end of the suction chamber, the pump head and housing engaging one another along a dividing plane; a retainer for securing said head to said housing;
a pressure valve in the pump head, having an inlet opening in said dividing plane and a valve element normally closing said opening, an end face of the valve element lying lsubstantially in said dividing plane; a collector chamber in the pump head communicating with the suction chamber through the pressure valve; a plunger mounted in said housing for reciprocation within the suction chamber, the plunger being concentrically arranged relative to the pressure valve inlet opening and valve element and having a forward dead centre position in which a forward face of the plunger is disposed sub-stantially in said divisional plane; a sleeve like suction valve element carried on said plunger for sliding movement thereon and spring biased to a closed position where an annular forward end face of the suction valve ele-ment is engaged with a suction valve seat on the pump head, lying in the ~.~ - 1 -.~
~L04~1~Q5 dividing plane and surrounding the pressure valve inlet opening.
Since the suction-valve element is guided on the plunger, the outer surface of the element re~uires no machining. It is impossible for the element to jam in the cham~er. In operation the element is washed by suction fluid. I'he heat produced during the compression stroke is trans-ferred from the element directly to the suction fluid.
The suction stroke of the suction-valve element, and thus the opening and closing times thereof, may be determined by a stop associated with the element.
The suction-valve element may be fitted to the plunger in a manner such that a high-pressure seal forms within the suction valve as an hydro-static seal. During the suction stroke, the suction valve is opened by the returning plunger as a result of the fluid friction arising in the seal.
During the compression stroke, fluid in the suction chamber is drawn into the gap between the plunger and the suction-valve element and supports the sealing action.
While the unit is in operation, the retention of the pump head to the housing may be adjusted according to the hydraulic pressure present in the pump head.
The object of the application may be used not only as a plunger pump, but also as an homogenizing unit for cream, pastes, and the like, or for the purpose of accelerating polymerization processes.
Various exemplary embodiments of the invention are described here-inafter and are illustrated in the drawings attached hereto, wherein:
Figure 1 is a longitudinal section through th~ pressure and suction chambers of a pump;
Figure 2 is a view in the direction of arrow II in Figure l;
Figure 3 is a detail of Figure 1 in cross section;
Figure 4 shows another embodiment in longitudianl section;
Figure 5 is a variant of the design in Figure 4;
~04~ 5 Figure 6 is a view in the ~irection of arrow VI in Figure 5;
Figure 7 shows an example of the U-shaped retainer shown in Figure 1 for the pump head;
Figure 8 is a section through an additional anchorage between the pump-head and pump-housing;
Figure 9 shows another embodiment of the pump in which the suction-valve element is in two parts;
Figur0 10 is a variant of the design in Figure 9;
Figure 11 shows another embodiment of a high-pressure plunger pump in longitudinal section;
Figure 12 shows a detail, in section, of the design according to Figure 11, to an enlarged scale.
In the pump shown in Figure 1, pump housing 26 has a suction chamber 61 to which suction fluid flows through a passage 60. A plunger 46 enters this suction chamber through a low-pressure seal 4, the plunger being driven, for example, by means of a crankshaft, a connecting rod, and a crosshead.
The drawing shows the plunger at forward dead centre, i.e. at the end of the compression stroke.
It may be gathered from the illustration that the pump has very little dead space at the forward dead-centre position.
The pump head 27 is secured to the pump housing 26 by means of a U-shaped retainer 28. To this end, the legs of the U-shaped retainer are provided with anchoring rims 29 engaging behind anchoring projections 30 on housing 26.
Figure 1 shows a dove-tail type of joint between housing 26 and retainer 28. The latter may be pushed onto the housing from the side, to-gether with pump head 27.
Pump head 27 is aligned with retainer 28 by means of centering pins 31.
~O~ 5 In the embodiment according to Figures 1 and 2, after the pump head and the retainer have been slid onto pump housing 26, toggle-bar screws 32 are tightened, threaded shanks 33 thereof passing through threaded holes in the central web 34 of the retainer and bearing against pump head 27. This presses pump head 27 against end-face 35 of housing 26 and presses anchoring rims 29 against anchoring projections 30. The seal between pump head 29 and end-face 35 of the housing is achieved by means of a sealing ring 35a.
Thus toggle-bar screws 32, 33 produce a prestress between the pump head, the retainer, and the pump housing, and this is present at all times.
As a variant of the design illustrated in Figures 1 and 2, it is also possible to replace toggle-bar screws 32, 33 with eccentrics 3-7 (Figures 5 and 6) mounted to pivot about axes 39 in recesses 38 in central web 34 of retainer 28, the said eccentrics being actuated by means of handles 40, Anchoring rims 29 on retainer 28 may extend over the whole width of the retainer. It is, however, also conceivable, as shown in Figure 7, to make the rims in sections, thus producing a plurality of hooks in spaced relationship to each other.
It is also unnecessary for a dove-tail type of attachment to be 2Q provided between the anchoring rims and the anchoring projections. Instead, the anchorage may be designed as shown in Figure 8. In this case, the coop-erating surfaces of anchoring rims 22a and anchoring projections 30a are at right angles to the wall of the pump housing.
~ alve seat 41 of pressure valve 42, and valve seat 43 of suction-valve element 44, lie in the area of the parting plane between pump housing 26 and pump head 27. Should the valve seats require refinishing, this may be carried out quite easily after removal of the pump head.
During the suction stroke of plunger 46, under the action of a spring 47 pressure valve element 45 closes the pressure-valve aperture, thus defining one end of collector chamber 48 provided in pump head 27 for the .~ - 4 -~' 10~05 medium being delivered. At the end facing the valve aperture, collector chamber 48 has an aperture which is closed off by a piston 49 arranged to slide in the collector chamber and acting upon central web 34 of retainer 28.
The pressure in the collector chamber defines the pressure applied by piston 49 to the central web 34 of retainer 28.
Thus, when the pump is in operation, a clamping force dependent upon the pressure in collector chamber 48 is superimposed upon the pre-load produced by toggle-bar screws 32, 33 or eccentrics 37, 40.
Pressure-valve element 42 has a pin 50, the free end of which is adapted to-slide in a blind bore 51. An angled passage 52 is provided in the pin for the purpose of equalizing the pressure between the piston chamber formed by the blind bore and the free end of the pin, and collector chamber 48.
Return spring 47 surrounding pin 50 rests with one end on piston 49.
The embodiments illustrated in the drawings have three plungers 46 and therefore three collector chambers 48 in pump head 27. These collector chambers are connected together through a bore 53, through which pressure equalization is effected within the pump head.
A sleeve-like suction~valve element 44 is slidably mounted on the plunger 46 and consists of two cylindrical sleeves 54, 55 which are joined together by shrinkage or auto frettage. Rear edge 56 of sleeve 54 forms a supporting surface for the end of return spring 57 of suction-valve element 44. During the suction stroke of plunger 46, the suction-valve element follows the movement of the plunger against the action of spring 57, rear edge 58 of sleeve 55 comes up against a stop surface 59. This stop 59 limits the stroke of suction-valve element 44, which is less than the maximal travel of spring 57. During the suction stroke of the pump, the medium being delivered is drawn through a housing aperture 60 into suction chamber 61 of the pump, whence it passes to the space defined by suction-valve element 44 . - .
~04000S
and plunger 46, which forms the pressure chamber during the compressîon stroke of the pump.
Thus in the object of the application, it is only suction-valve element 44 that is subjected to alternating loads during the suction and com-pression strokes.
The cross-sectional area of the pressure chamber, of diameter dl, is larger than the cross-sectional area of the suction-valve seat, of dia-meter d2, so that an additional closing force is produced for the suction valve, during the compression stroke, by the pressure of water on the differential area.
During the suction stroke, a negative pressure occurs in the inter-nal chamber of the suction-valve element 44. This negative pressure, in conjunction with the slight initial pressure in the pump suction chamber, allows a force to act upon the valve element, which force assists the valve as it moves in the opening direction.
It is also possible to provide plunger 46, and the inner surface of the suction-valve element associated therewith, with a micro-labyrinth seal in which the labyrinth recess in the plunger are in staggered relation-ship to the divisions in the suction-valve element. Relative movement between the plunger and the suction-valve element produces vortexing of the delivery medium, and this intensifies the sealing action between the plunger and the suction-valve element.
In the embodiment according to Figure 4, inside diameter d3 of low-pressure seal 4, and the corresponding diameter of the plunger end which does not enter the suction-valve element are larger than diameter dl of the other part of the plunger.
This plunger configuration i s an advantage in the case of a high-pressure plunger pump equipped with a plurality of plungers operating in a chronologically staggered relationship to each other. During the compression stroke of one plunger, end-face 22 of the plunger, produced by enlarged s~
~o~ooos diameter d3, delivers suction fluid from suction chamber 2, through a pass-age into the suction chambers of the other plungers. This improves the over-all suction ratio.
Slidably mounted on the plunger 5 is a sleeve-like suction-valve element 6, with which a biasing spring 7 is associated. One end of spring 7 rests against rear end 8 of the suction-valve element, while the other end rests against a flange 9 on a sleeve 10 secured in the pump housing 1.
Sleeve 10 extends into the interior of cylindrical helical spring 7 with the front end-face 11 of the sleeve limiting the return stroke of the suction-valve element 6.
The sleeve-like design of the suction-valve element makes it easy, from the production point of view, to produce a dimensionally stable suction-valve element which does not change shape under the loads associated with the compression stroke. Thus the sealing gap between the suction-valve element and the plunger retains its predetermined size.
In the embodiment according to Figures 9 and lO, suction-valve elements 85, 85a and 85b are made in two parts. In the design according to Figure 9, the suction-valve element has a sleeve 87 guided on plunger 86 and a valve part 88. A spring 90 is provided between valve part 88 and sleeve 87.
Sleeve 87 is arranged between pump head 9O and rear plunger guide 91 with a certain amount of play. Sleeve 87 has slots 92 adjacent pump head 90. In this embodiment, the suction-valve element is surrounded by an annu-lar screen 93.
During the return stroke of the plunger, a vacuum is formed within the suction-valve element, and this opens valve part 88 by compressing spring 89. If there is any initial pressure in suction chamber 94, this increases the force acting to open valve part 88.
In the design according to Figure lO, valve part 88b is carried on sleeve 87b. Spring 89b, arranged between sleeve 87b and valve part 88b, has 10~ 5 one end bearing against a stop ring 95 secured to sleeve 87b. The other end of spring 89b bears against rear end-face 96 of valve part 88b.
The designs according to Figures 9 and 10 are suitable for both horizontal and vertical pumps.
In the embodiment according to Figures 11 and 12, pump housing 101, in which a plurality of plungers 102 may be arranged side by side, is connected to pump head 104 by means of laterally insertable bars 103.
The pump housing has a suction chamber iO5 to which suction fluid is delivered through a passage 106. Plunger 102 en~ers the suction chamber through a seal 107, the plunger being driven by a crankshaft, a connecting rod, and a crosshead.
Suction-valve element 108 is carried entirely on the plunger.
Associated with the suction-valve element is a spring 109 which endeavours to keep the said element in the closed position shown in Figure 14, During the suction stroke, the force of spring 109 must be overcome by suction-valve element 108. The suction stroke is limited by a stop 1~ which co-operates with rear end-face 111 of the suction-valve element.
Plunger 102 has a rod part 112 and a sleeve 113 enclosing the rod part.
2n In the forward area of plunger 102, rod part 112 has a reduced diameter forming an annular space 114 defined peripherally by sleeve 113.
This annular space is connected through a transverse passage 115, and a pass-age 116 lying on the longitudinal axis of the plunger, with pump pressure chamber 117, formed by suction-valve element 108. In this embodiment, passage 116 passes through a threaded stud, extending from the front face of rod part 112, onto which a nut 118 is screwed in order to secure a stop plate 119 for the front annular surface of sleeve 113. Seat 120 of the suc-tion valve, and seat 121 of pressure valve element 122, are arranged on a valve-seat ring 123. This valve-seat ring, which is mounted in a recess in pump head 104, can easily be replaced after the pump head has been removed ..~
~04~ S
from the pump housing.
A sealing ring 124 is provided, adjacent the rear end of the annular space, 114 between rod part 112 and sleeve 113 of the plunger.
Figure 12 shows the sealing gap 125 between suction-valve element 108 and sleeve 113 of plunger 102, to an enlarged scale.
The pressure in pressure chamber Pl decreases, in sealing,gap 125, in the direction of the drive-end of the plunger, reaching a valve P2 in the end _ g _ ~L04QO(~S
area of annular space 114.
Since annular space 114 is slightly staggered towards the drive-end, in relatlon to the front end of the plunger, the pressure in the sealing gap associated with annular space 114 is lower, during the compression stroke, than the pressure in annular space 114, which coincides with the pressure in pressure chamber 117. This deforms sleeve 113, as shown in dotted lines in Figure 15, leading to a reduction in the cross section of sealing gap 125.
The deformation of the plunger sleeve, induced by the pressure of the medium being delivered, lies within the elastic limit of the sleeve, so that when the pressure drops, the sleeve again assumes its normal shape. This ensures a satisfactory seal between the plunger and the suction-valve element in the case of plunger pumps operating at very high pressures, of 1000 bars and more, for example.
Claims (24)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A high pressure plunger pump having a pumping unit comprising:
a housing defining a suction chamber with an open end;
a pump head extending over and closing the open end of the suction chamber, the pump head and housing engaging one another along a dividing plane;
a retainer for securing said head to said housing;
a pressure valve in the pump head, having an inlet opening in said dividing plane and a valve element normally closing said opening, an end face of the valve element lying substantially in said dividing plane;
a collector chamber in the pump head communicating with the suction chamber through the pressure valve;
a plunger mounted in said housing for reciprocation within the suction chamber, the plunger being concentrically arranged relative to the pressure valve inlet opening and valve element and having a forward dead centre position in which a forward face of the plunger is disposed substantially in said divisional plane;
a sleeve like suction valve element carried on said plunger for sliding movement thereon and spring biased to a closed position where an annular forward end face of the suction valve element is engaged with a suction valve seat on the pump head, lying in the dividing plane and surrounding the pressure valve inlet opening.
a housing defining a suction chamber with an open end;
a pump head extending over and closing the open end of the suction chamber, the pump head and housing engaging one another along a dividing plane;
a retainer for securing said head to said housing;
a pressure valve in the pump head, having an inlet opening in said dividing plane and a valve element normally closing said opening, an end face of the valve element lying substantially in said dividing plane;
a collector chamber in the pump head communicating with the suction chamber through the pressure valve;
a plunger mounted in said housing for reciprocation within the suction chamber, the plunger being concentrically arranged relative to the pressure valve inlet opening and valve element and having a forward dead centre position in which a forward face of the plunger is disposed substantially in said divisional plane;
a sleeve like suction valve element carried on said plunger for sliding movement thereon and spring biased to a closed position where an annular forward end face of the suction valve element is engaged with a suction valve seat on the pump head, lying in the dividing plane and surrounding the pressure valve inlet opening.
2. A high-pressure plunger pump according to claim 1 including a helical spring having one end bearing against a rear end of the suction-valve element and an opposite end resting upon a flange on a cylindrical sleeve secured to the pump housing, a front face of said sleeve forming the stop means for said suction valve element.
3. A high-pressure plunger pump according to claim 1 characterized in that the plunger extends into said cylinder through a low-pressure seal in the rearward end of the suction chamber.
4. A high-pressure plunger pump according to claim 1, 2 or 3 charac-terized in that said plunger and an internal surface of said suction valve element are provided with a micro-labyrinth seal; and in that divisions of labyrinth recesses in the plunger differ from, and are staggered in relation to divisions of labyrinth recesses in the suction valve element.
5. A high-pressure pump according to claim 3 including a plurality of pumping units wherein each plunger includes a first part on which said suc-tion valve element is mounted and a second part extending through said seal, said second part having a larger diameter than said first part, the suction chambers of said units being connected by a passage.
6. A high-pressure plunger pump according to claim 1, characterized in that the retainer is of substantially U-shaped crossed section, encloses the pump head on three sides, and engages, with anchoring means provided at the ends of the U-legs, behind anchoring projections on the pump housing.
7. A high-pressure plunger pump according to claim 6, characterized in that the anchoring means and the anchoring projections comprise rims extending along the retainer and pump housing, transversely of its cylinder.
8. A high-pressure plunger pump according to claim 7 wherein said rims are divided into sections spaced apart transversely of said cylinder.
9. A high-pressure pump according to claim 1 including a piston mounted slidabl y in said collector chamber and engaging said retainer through an aperture in said head at an opposite end of said chamber from said pressure valve.
10. A high-pressure plunger pump according to claim 9 wherein said pressure valve element has a valve head and a pin projecting therefrom, a free end of said pin being slidably mounted in a blind bore in said piston, and said pin having a passage therethrough to equalize pressure between the collector chamber and the blind bore.
11. A high-pressure plunger pump according to claim 10 including a return spring surrounding said pin and having its opposite ends resting against said piston and said valve head respectively.
12. A high-pressure plunger pump according to claim 1, characterized in that said retainer clamps said pump head to said pump housing by means of screws carried by the retainer and acting upon said pump head.
13. A high-pressure plunger pump according to claim 1 characterized in that said retainer clamps said pump head to said housing by means of eccentrics mounted on the retainer and engaging said pump head.
14. A high-pressure plunger pump according to claim 1 having a plurality of pumping units with the individual collector chambers of the units connected together by a passage.
15. A high-pressure plunger pump according to claim 1 characterized in that the suction valve element consists of two cylindrical sleeves connected together.
16. A high-pressure plunger pump according to claim 1 wherein the internal diameter of the suction valve element and the diameter of the pressure valve openings are equal.
17. A high-pressure plunger pump according to claim 1 characterized in that the suction valve element comprises two parts, a sleeve carried on the plunger and a valve part mounted slidably on said sleeve, a spring being arranged between said two parts.
18. A high-pressure plunger pump according to claim 17 characterized in that the sleeve extends, with a small amount of play, between said forward end of said suction chamber and a rear plunger guide at the rearward end of said cylinder, and is provided with slots adjacent said forward end.
19. A high-pressure plunger pump according to claim 18 characterized in that the sleeve is surrounded by a cylindrical screen.
20. A high-pressure plunger pump according to claim 1 characterized in that the plunger consists of a plunger rod and a plunger sleeve surround-ing said plunger rod and defining therewith an annular space peripherally closed by said plunger sleeve, said annular space communicating with a pump pressure chamber through at least one passage.
21 A high-pressure plunger pump according to claim 20 characterized in that the annular space is provided in a forward part of the plunger.
22. A high-pressure plunger pump according to claim 20 or 21 charac-terized in that a sealing ring is arranged between the plunger rod and the plunger sleeve, adjacent a rear end of the annular space.
23. A high-pressure plunger pump according to claim 20 characterized in that the plunger rod has a threaded stud extending from its front end face, a stop plate for the front end of the plunger sleeve surrounding said stud and a nut securing said stop plate on said plunger.
24. A high-pressure plunger pump according to claim 23 characterized in that the plunger rod has a central passage passing through the threaded stud, from which transverse passages branch off to open into the annular space.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE2411546A DE2411546C3 (en) | 1974-03-11 | 1974-03-11 | High pressure plunger pump |
| DE19742445696 DE2445696B2 (en) | 1974-09-25 | 1974-09-25 | HIGH PRESSURE PUMP |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1040005A true CA1040005A (en) | 1978-10-10 |
Family
ID=25766771
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA213,548A Expired CA1040005A (en) | 1974-03-11 | 1974-11-13 | High-pressure plunger pump |
Country Status (9)
| Country | Link |
|---|---|
| JP (1) | JPS5738789B2 (en) |
| AT (1) | AT338623B (en) |
| BR (1) | BR7501303A (en) |
| CA (1) | CA1040005A (en) |
| CH (1) | CH584841A5 (en) |
| ES (1) | ES434465A1 (en) |
| FR (1) | FR2264195A1 (en) |
| IT (1) | IT1033855B (en) |
| NL (1) | NL7501024A (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6464187B2 (en) * | 2014-03-31 | 2019-02-06 | サウディ ベーシック インダストリーズ コーポレイション | Process for preparing ethylene copolymers in a tubular reactor |
| DE102022205716A1 (en) | 2022-06-03 | 2023-12-14 | Volkswagen Aktiengesellschaft | Aluminum die-cast part with at least one cavity, in particular for a motor vehicle, and method for treating such an aluminum die-cast part |
-
1974
- 1974-10-31 AT AT879874A patent/AT338623B/en not_active IP Right Cessation
- 1974-11-01 CH CH1467974A patent/CH584841A5/xx not_active IP Right Cessation
- 1974-11-12 FR FR7439917A patent/FR2264195A1/en active Granted
- 1974-11-12 JP JP13038574A patent/JPS5738789B2/ja not_active Expired
- 1974-11-13 CA CA213,548A patent/CA1040005A/en not_active Expired
-
1975
- 1975-01-29 NL NL7501024A patent/NL7501024A/en unknown
- 1975-02-04 IT IT1243975A patent/IT1033855B/en active
- 1975-02-05 ES ES434465A patent/ES434465A1/en not_active Expired
- 1975-03-05 BR BR7501303A patent/BR7501303A/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| NL7501024A (en) | 1975-09-15 |
| CH584841A5 (en) | 1977-02-15 |
| IT1033855B (en) | 1979-08-10 |
| FR2264195B1 (en) | 1978-05-05 |
| ES434465A1 (en) | 1976-12-16 |
| JPS5738789B2 (en) | 1982-08-17 |
| JPS50122703A (en) | 1975-09-26 |
| ATA879874A (en) | 1976-12-15 |
| FR2264195A1 (en) | 1975-10-10 |
| BR7501303A (en) | 1975-12-09 |
| AT338623B (en) | 1977-09-12 |
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