US20150300334A1

US20150300334A1 - Rotary drive linear rod displacement pump

Info

Publication number: US20150300334A1
Application number: US14/257,994
Authority: US
Inventors: Steve Smith
Original assignee: Individual
Current assignee: Individual
Priority date: 2014-04-21
Filing date: 2014-04-21
Publication date: 2015-10-22

Abstract

A rotary drive linear rod displacement pump includes a pump housing supporting a plurality of radially spaced linear rod displacement pump segments. A rotor supporting a plurality of roller cam followers is rotatably coupled to the pump segments and is driven by a source of rotary power. As the rotor is driven, the cam followers articulate the pump segments.

Description

FIELD OF THE INVENTION

This invention relates generally to pumps and particularly to those operated in response to a rotary power drive source.

BACKGROUND OF THE INVENTION

Pumps comprise one of the most common well developed and well known type of basic machines. The essential function of a pump is the displacement and movement or pressurization of a fluid. The majority of pumps may be divided into a basic classification as either reciprocating or rotary action pumps. Reciprocating pumps typically utilize one or more cylinders together with appropriate valves for controlling fluid flow to and from the cylinders. Each cylinder within the reciprocating pump is fitted with a moving piston which in turn is coupled to a crank mechanism or the like for imparting piston movement within the cylinder. Most reciprocating pumps are coupled to a rotary, or linear drive power source.
One of the oldest types of reciprocating pumps is often referred to in the art as a “rod pump”. Rod pumps are characterized by providing use in high pressure or fluid metering applications. Typically rod pumps utilize a fluid cylinder having a closed end bore within which a pump rod is moved. The open end of the fluid cylinder bore supports a pressure seal against the pump rod for maintain pressure within the cylinder bore. Pumping is accomplished by initially drawing the rod from the cylinder bore which in turn draws an infill of the pumping fluid into the bore. Thereafter, the pump rod is forced into the fluid filled bore displacing a portion of the fluid and producing a pressurized movement of the fluid. This type of pump is characterized in that there is no piston or piston seal required.
U.S. Pat. No. 6,398,514 issued to Smith et al sets forth a DOUBLE-ACTING ROD PUMP having a plurality of rod pumps supported within a drive apparatus which moves the pump rods in opposition to each other within respective cylinder bores. The operation reverses during the next cycle of operation allowing the previously filled cylinders to discharge fluid under pressure while the remaining cylinders are filled. This reversed opposed operation of the plurality of rod pumps produces a virtually continuous flow.
In contrast, rotary pumps are generally characterized as apparatus in which input power is coupled to a rotating shaft which in turn is coupled to a rotating pump mechanism within the pump body. The pump body defines a chamber or cavity within which a fluid movement or displacement device is rotated by the power input shaft. Perhaps the most pervasive type of rotary pump may be generally described as an impeller, or gear, type pump. In such pumps, a rotor is rotatably supported within the pump chamber and is driven by the input power shaft to rotate. The rotor in turn supports a plurality of blades which are sized and configured in general correspondence to the interior surface of the pump chamber. As the input drive power rotates the rotor, the fluid is carried by the impeller blades within the pump chamber and is driven from the chamber under pressure. Simultaneously, the outward movement of the driven fluid from the chamber produces a draw which causes additional fluid to flow into the chamber. The pump operation is more or less continuous.
Another type of rotary pump is typically referred to as a turbine or vane-type pump. The turbine or vane pump utilizes a housing defining an interior chamber which is typically cylindrical in shape. A plurality of static blades or vanes are supported in radial disposition upon the interior surface of the chamber. An armature, also supporting a plurality of vanes or blades is rotatably supported within the chamber. The static blades and the rotating blades of the armature are spaced to facilitate free rotation of the armature. A source of rotating power is coupled to the armature to drive the armature usually at high speed.
Still another type of rotary action pump is referred to generally as a peristaltic type pump. Peristaltic pumps are often referred to as “hose pumps” so described because they utilize a elongated flexible tubing or hose within which fluid is disposed. The tubing is typically looped in one or more helical loops within a housing chamber. Inside the helical loops a rotor is operative to push fluid through the helical hose tubing as the rotor rotates. In most peristaltic pumps the rotor supports a plurality of rollers which are forced against the helical tubing or hose.
U.S. Pat. No. 6,296,460 issued to Smith sets forth a ROTARY CAVITY PUMP having a pump housing which supports a plurality of pump segments each having a raised pump cavity enclosed by a resilient diaphragm sealed to the pump cavity. A compression plate supports a plurality of rollers against the pump segments. The compression plate is rotatable with respect to the pump housing to move the rollers across the pump segments deforming the diaphragms and expelling fluid from the pump segments. Fluid passages couple each pump cavity to a source of fluid and a fluid output. As each roller rolls across each diaphragm to expel fluid from the pump segment, the resilience of the diaphragm draws the fluid into the pump segment behind the roller to refill the pump segment.
While the above described prior art pumps have been the subject of substantial refinement and development and have in some measure enjoyed commercial success, there remains nonetheless a continuing need in the art for ever more improved rotary drive pumps.

SUMMARY OF THE INVENTION

Accordingly, it is a general object of the present invention to provide an improved rotary drive pump. It is a more particular object of the present invention to provide a highly efficient rotary drive pump which utilizes displacement pump apparatus and which produces a substantially ripple free fluid flow.
In accordance with the present invention, there is provided, a rotary drive linear rod displacement pump comprising: a pump housing; a plurality of displacement pump segments, supported by said pump housing, each including a pump cam follower; a plurality of valve portions, supported by said pump housing, each including a valve cam follower; and a rotor supporting a plurality of roller cams in contact with said valve cam followers and said pump cam followers for actuating said pump as said rotor rotates.

BRIEF DESCRIPTION OF THE DRAWINGS

The features of the present invention, which are believed to be novel, are set forth with particularity in the appended claims. The invention, together with further objects and advantages thereof, may best be understood by reference to the following description taken in conjunction with the accompanying drawings, in the several figures of which like reference numerals identify like elements and in which:

FIG. 1 sets forth a perspective view of a rotary drive linear rod displacement pump constructed in accordance with the present invention;

FIG. 2 sets forth a perspective view of the present invention rotary drive linear rod displacement pump having the rotor housing removed therefrom;

FIG. 3 sets forth a perspective view of the present invention rotary drive linear rod displacement pump showing the rotor apparatus in transparent view;

FIG. 4 sets forth a perspective view of the present invention rotary drive linear rod displacement pump having the rotor housing and rotor removed therefrom;

FIG. 5 sets forth a perspective view of the present invention rotary drive linear rod displacement pump having the plunger plate and pump valve plate removed therefrom;

FIG. 6 sets forth a perspective view of the present invention rotary drive linear rod displacement pump having the upper seal plate removed therefrom;

FIG. 7 sets forth a perspective view of the present invention rotary drive linear rod displacement pump showing the pump segments and valve segments together with the fluid manifold;

FIG. 8 sets forth a simplified top view the present invention rotary drive linear rod displacement pump showing the arrangement of the pump segments and valve segments;

FIG. 9 sets forth a section view of the present invention rotary drive linear rod displacement pump taken along section lines 9-9 in FIG. 8;

FIG. 10 sets forth a partial section view of the present invention rotary drive linear rod displacement pump taken along section lines 10-10 in FIG. 8;

FIGS. 11A through 11E set forth sequential section views of the present invention rotary drive linear rod displacement pump illustrating the operational cycle of the pump; and

FIGS. 12A through 12E set forth simplified drawings illustrating the rotational operation of the rotor and cams upon the pump segments and valve segments of the present invention rotary drive linear rod displacement pump.

DESCRIPTION OF THE PREFERRED EMBODIMENTS OF THE INVENTION

FIG. 1 sets forth a perspective view of a rotary drive linear rod displacement pump constructed in accordance with the present invention and generally referenced by numeral 10. Pump 10 is fabricated using a plurality of plates which are joined by a plurality of fasteners to provide the combined housing for pump 10. It will be apparent to those skilled in the art however that the present invention rotary drive linear rod displacement pump may be fabricated utilizing a different number of plate segments and a different arrangement of plate segments without departing from the spirit and scope of the present invention. It will also be apparent to those skilled in the art that, in its preferred form, pump 10 utilizes plates which are formed of appropriate material such as high strength metal or the like. However, once again, it will be understood by those skilled in the art that other materials such as carbon fiber materials or other high strength exotic materials may be utilized without departing from the spirit and scope of the present invention. The important aspect in fabricating pump 10 is the combined structure of plates forms a pump housing 11 suitable for operating in the manner described below. Thus, pump housing 11 of pump 10 includes a rotor housing 13 joined to a plunger plate 14 which in turn is joined to a pump valve plate 15. Pump housing 11 further includes an upper seal plate 16 joined to a lower seal plate 17 together with a seal support plate 18. Finally, housing 11 of pump 10 is completed by the attachment of a fluid plate 19 together with a valve plate 20 and a manifold 21. Pump 10 further includes a generally cylindrical mounting flange 12 which defines a plurality of apertures utilized in securing pump 10 to a suitable support surface (not shown).
In further accordance with the present invention, pump 10 includes an input power shaft 26 which, in the manner described below in greater details, extends through appropriate bores formed in mounting flange 12 and rotor housing 13 to support a rotatable rotor (seen in FIG. 9). As is also better seen in FIG. 11, plates through 21 are secured by a plurality of bolts 24 and 25. As is seen in FIG. 10, upper bolts 24 extend downwardly through rotor housing 13 together with plates 14, 15, 16, 17 and 18 into fluid plate 19 while lower bolts 25 extend upwardly through manifold 21 and valve plate 20 into fluid plate 19. Of importance with respect to the present invention is the function by which upper bolts 24 and lower bolts 25 (seen in FIG. 11) cooperate to maintain the security and integrity of pump housing 11. Pump housing 11 further supports an input fluid coupling 22 and an output fluid coupling 23. The position and orientation of input fluid coupling 22 and output fluid coupling 23 are set forth in greater detail. However, suffice it to note here that in the normal operation of pump 10, fluid is drawn into pump 10 through input 22 and is expelled outwardly under pressure from fluid output 23. In addition, in the anticipated use of the present invention pump, input shaft 26 is operatively coupled to a conventional source of rotational power (not shown). It will be equally apparent to those skilled in the art that rotary drive linear rod displacement pump 10 may be fabricated in a wide range of sizes to suit particular needs to capacity and flow rates without departing from the spirit and scope of the present invention.
For purposes of illustration, FIGS. 2 through 7 set forth sequential perspective views of pump 10 as successive portions are removed from the combined pump structure in order to facilitate the description and illustration of the structure and operation of the present invention pump. In addition, the structure in each of FIGS. 2 through 7 has been simplified to avoid unduly cluttering the figures an allow illustration of the various system components. More specifically, FIG. 2 sets forth pump housing 11 of pump 10 having rotor housing 13 removed. Thus, plunger plate 14, pump valve plate 15, upper and lower seal plates 16 and 17, seal support plate 18, fluid plate 19, valve plate 20 and manifold 21 remain as previously described. With rotor housing 13 removed, input shaft 26 is shown supporting a keeper 32 together with a pair of bearings 30 and 31. Also now seen in FIG. 2 with the removal of rotor housing 13 is rotor 40 secured to input shaft 26 by means set forth below in FIG. 9 in greater detail. Suffice it to note here that rotor 40 is secured to input shaft 26 and thus rotates therewith. Thus, as input shaft 26 is rotated in the direction indicated by arrow 35, rotor 40 is rotated correspondingly in the direction indicated by arrow 34. Plunger plate 14 supports a plurality of pump and cam plungers, such as plunger 50, each supported within a respective cylindrical sleeve guide such as sleeve guide 60 supporting plunger 50. Rotor 40 further supports a plurality of cam plungers such as cam rollers 70, 71 and 72 shown in FIG. 2. As will be described below in greater detail, the plurality of cam rollers supported upon rotor 40 are operative to move the pluralities of plungers supported within the interior of pump housing 11. In the view shown in FIG. 2, cam rollers 70, 71 and 72 are moving toward plunger 50 and are operative to depress cam follower 50 downwardly within sleeve guide 60. The entire operation of rotor 40 and the plurality of cam rollers which it supports in actuating the plurality of plungers supported within pump housing 11 is described below in greater detail. However, suffice it to note here that rotor 40 is rotated in the direction indicated by arrow 34 with respect to pump housing 11, the cooperation of cam rollers and plungers within pump operates the valve and pump segments shown and described below in greater detail.
FIG. 3 sets forth the perspective view shown in FIG. 2 in which rotor 40 is shown in phantom line depiction in order to illustrate the plurality of cam followers supported within rotor 40. Thus, as described above, pump 10 includes pump housing 11 supporting plunger plate 14, pump valve plate 15, upper and lower seal plates 16 and 17, seal support plate 18, fluid plate 19, valve plate 20 and manifold 21. As is also described above, rotor 40 is joined to input shaft 26 which in turn is sealed by a lip seal 32 and is supported by bearings 30 and 31. Plunger plate 14 supports a plurality of cam plungers, such as plunger 50, supported within a corresponding plurality of sleeve guides, such as sleeve guide 60. Rotor 40 includes an inner hub 41 supporting a plurality of cam rollers 83 through 90 (seen in FIG. 12A). Rotor 40 further includes an outer wall 42 which supports a plurality of cam followers 70 through 81 (seen in FIG. 13A). As mentioned above, and as is described below in greater detail, as rotor 40 is rotated by power applied to input shaft 26, the pluralities of cam followers supported against inner hub 41 and outer wall 42 are operative upon the plurality of plungers supported by plunger plate 14 to provide the pump operation described below in greater detail.
FIG. 4 sets forth the perspective view of pump 10 having rotor 40 and shaft 26 together with bearings 30 and 31 and lip seal 32 removed therefrom. With rotor 40 removed, FIG. 4 shows the positions of the various plungers supported within plunger plate 14.
As is described below in greater detail, pump 10 utilizes a plurality of pump segments operative in combination with a corresponding plurality of valve segments. Each portion of pump 10 utilizes the operative pair of a pump segment together with a valve segment. Accordingly, and as is seen in FIG. 4, plunger plate 14 supports three dome-shaped plungers operative upon the valve portions of pump 10. The valve portion plungers are referenced by numerals 50, 51 and 52 and are slidably supported within a corresponding plurality of sleeve guides 60, 61 and 62. As is better seen in FIG. 12A, valve plungers 50, 51 and 52 are evenly spaced upon plunger plate 14 and occupy the surface portions of plunger plate 14 nearest the outer edge thereof. Also best seen in FIG. 12A, pump plungers 55, 56 and 57 are equally spaced upon plunger plate 14 and are positioned inwardly toward the center portion of plunger plate 14. Correspondingly, pump cam followers 55, 56 and 57 are slidably supported within sleeve guides 65, 66 and 67. Returning to FIG. 4, it will be apparent that as rotor 40 (seen in FIG. 3) supporting its plurality of cam followers (also seen in FIG. 3) is caused to rotate upon the upper surface of plunger plate 14, plungers 50 through 52 are operative to actuate the valve mechanisms within pump 10. Also seen and also understood, as rotor 40 supporting its plurality of cam followers is rotated upon the surface of plunger plate 14, pump plungers 55, 56 and 57 are also operated. By means shown below in greater detail, the rotation of rotor 40 upon the plungers causes the valves and pump segments within pump 10 to be operated and thereby produce the pumping action described below.
FIG. 5 sets forth a perspective view of pump 10 having plunger plate 14 and pump valve plate 15 removed therefrom. With plunger plate 14 and pump valve plate 15 removed, a second plurality of guide sleeves operative to slidably support the pump rods and valve rods is shown. More specifically, sleeve guide 90 supports the valve rod coupled to plunger 50 while sleeve guide 91 supports the valve rod coupled to plunger 51. Similarly, sleeve guide 92 supports the valve rod coupled to plunger 52. Also shown, sleeve guide 95 supports the pump rod coupled to plunger 55 while sleeve guide 96 supports the pump rod coupled to plunger 56 and sleeve guide 97 supports the pump rod coupled to plunger 57. FIG. 5 also shows a plurality of return springs operative upon plungers 50 through 52 and plungers 55 through 57.
FIG. 6 shows the perspective view of pump 10 having upper seal plate 16 removed therefrom. As described above, pump 10 includes a manifold 21, a valve plate 20, a fluid plate 19, a seal support plate 18 and a lower seal plate 17. As is also described above, pump 10 includes a plurality of valve plungers 50, 51 and 52 supported within sleeve guides 60, 61 and 62. Also described above, pump 10 includes a plurality of pump plungers 55, 56 and 57 slidably supported within sleeve guides 65, 66 and 67. Further described above, pump 10 includes a plurality of guides 90, 91 and 92 supporting the valve rods coupled to valve plungers 50, 51 and 52 respectively together with guides 95, 96 and 97 supporting the pump rods coupled to pump plungers 55, 56 and 57. FIG. 6 also shows a plurality of seals 100, 101 and 102 encircling the valve rods coupled to valve plungers 50, 51 and 52 respectively. FIG. 6 also shows a plurality of seals 105, 106 and 107 encircling the pump rods coupled to pump plungers 55, 56 and 57.
FIG. 7 sets forth a perspective view of manifold 21 together with the major operative components of the present invention pump valve and pump segments. As described above, a plurality of valve plungers 50, 51 and 52 are supported within sleeve guides 60, 61 and 62 respectively. A plurality of guides 90, 91 and 92 support the valve rods coupled to valve plungers 50, 51 and 52. As is also described above, pump 10 includes a plurality of pump plungers 55, 56 and 57 supported within respective sleeve guides 65, 66 and 67. Sleeve guides 95, 96 and 97 further support the pump rods coupled to pump plungers 55, 56 and 57.
Pump 110 further includes a plurality of spring ball check valves 115, 116 and 117 operative in combination with each of the pump segments. Pump 10 further includes a plurality of valve seats 110, 111 and 112 operative in combination with valve ball ends 120, 121 and 122.
Manifold 21 defines and input fluid channel 27 and an output fluid channel 28. Fluid channels 27 and 28 are separated by a pair of O- ring seals 47 and 48. An aperture 37 formed within input channel 27 of manifold 21 is coupled to input coupling 22. Similarly, an aperture 38 is formed within output channel 28 and is coupled to output coupling 23. Thus during normal pump operation, en input flow of fluid flows through input coupling 22 through aperture 37 to fill input channel 27. Similarly, during pump operation, fluid under pressure flows outwardly through output channel 28 through aperture 38 and output coupler 23.
FIG. 8 sets forth a top view of plunger plate 14 showing the relative positions of valve plungers 50 through 52 together with pump plungers 55 through 57. As mentioned above, valve plungers 50 through 52 are supported within sleeve guides 60 through 62 respectively while pump plungers 55 through 57 are supported within respective sleeve guides 65 through 67.
FIG. 9 sets forth a section view of pump 10 taken along section lines 9-9 in FIG. 8. As described above, pump housing 11 is formed of a stacked array of rotor housing 13, plunger plate 14, pump valve plate 15, upper and lower seal plates 16 and 17, seal support plate 18, fluid plate 19, valve plate 20 and manifold 21. As is also described above, rotor housing 13 further supports a mounting flange 12 within which in input shaft 26 is rotatably supported by a pair of bearings 30 and 31. Rotor 40 is joined to input shaft 26 and is rotatable within rotor housing 13. Rotor 40 further supports a plurality of cam followers in the manner set forth above in FIG. 3 which includes cam followers 84 and 88 as well as cam followers 73 and 79. Pump 10 includes a valve segment formed by combination of a valve plunger 52 movably supported within a sleeve guide 62. The valve segment further includes an elongated valve rod 82 extending downwardly from valve plunger 52. Valve rod 82 further supports a valve ball 122 at the lower end thereof. A sleeve guide 92 is supported within pump valve plate 15 and provides a guide for valve rod 82. A pair of rod seals 102 and 103 encircle valve rod 82 and are supported within upper seal plate 16 and lower seal plate 17 respectively. Fluid plate 19 defines a fluid chamber 125 within which a valve seat 112 is supported. Valve plate 20 defines a fluid chamber 83 extending downwardly from valve seat 112. Manifold 21 defines an input fluid channel 27 (better seen in FIG. 7) which is in communication with fluid passage 83.
The valve segment of pump 10 shown in FIG. 9 is depicted in its valve open condition characterized by the position of valve ball 122 above and away from valve seat 112. This open condition allows fluid to flow from input channel 27 upwardly through fluid passage 83 past valve seat 112 into fluid chamber 125. A fluid passage is formed in fluid plate 19 (better seen in FIG. 11A) which facilitates fluid coupling to a pump segment in the manner shown in FIGS. 11A through 11E below. A pair of valve springs are operatively coupled to valve plunger 52 to position valve plunger 52 and valve rod 82 in the normally open position shown. The valve segment is moved to a closed valve condition when a cam follower such as cam follower 73 is moved upon plunger 52 forcing valve rod 82 and valve ball 122 downwardly. Valve ball 122 moves against valve seat 112 under these circumstances and closes the fluid flow coupling passage.
FIG. 9 also shows a pump segment supported within housing 11 which includes a pump plunger 56 supported within sleeve guide 66 which in turn is supported within plunger plate 14. A pump rod 86 is coupled to pump plunger 56 and extends downwardly through a guide 96 which in turn is supported within pump valve plate 15. Pump rod 86 extends downwardly through a pair of seals 106 and 108 supported within seal plates 16 and 17 respectively. Fluid plate 19 defines a fluid chamber 45 within which a valve seat 105 is supported. Valve plate 20 defines a fluid chamber 46 in communication with fluid chamber 45 through valve seat 105. A valve spring 127 and valve ball 126 are captivated within fluid chamber 46 against the underside valve seat 105. The resulting combination of seat 105, valve ball 126 and spring 127 forms a check valve operative to limit fluid transfer to flow from chamber 46 into chamber 45. Fluid chamber 46 is in communication with output channel 28 formed in manifold 21. The operation of the pump segment within pump 10 is set forth below in FIG. 11A through 11E. Suffice it to note here that the pump segment provides a rod displacement pump operative when a cam follower exserts force against pump plunger 56 forcing pump rod 86 downwardly into fluid chamber 45. The displacement of fluid from chamber 45 overcomes the force of valve spring 127 moving valve ball 126 away from seat 105 and allowing fluid to flow downwardly through fluid chamber 46 into output fluid channel 28.
FIG. 10 sets forth a partial section view of a portion of the present invention pump taken along section lines 10-10 in FIG. 8. Of importance to note in FIG. 10 is the extension of upper bolt 24 downwardly to be received within threaded bore 34 formed in fluid plate 19. Similarly, lower bolt 25 extends upwardly to be received within the lower portion of threaded bore 34 in fluid plate 19. The cooperation of upper bolts 24 and lower bolts 25 each threadably coupled within threaded bore 34 secures the integrity of housing 11.
FIG. 11A through 11E set forth sequential views of a section view of the present invention pump taken along section lines 11-11 in FIG. 8. While the section views shown in FIGS. 11A through 11E are somewhat simplified to aid in discussion, they provide sequential views showing the operation of the cooperating pump segment and valve segment of the present invention rotary drive linear rod displacement pump. Thus with concurrent reference to FIGS. 11A through 11E, plunger plate 14, pump valve plate 15, upper seal plate 16, lower seal plate 17, seal support plate 18, fluid plate 19, valve plate 20 and manifold 21 are joined together in the above-described manner. Plunger plate 14 supports a valve plunger 50 received within a sleeve guide 60. Plunger plate 14 further supports a guide 95 while upper seal plate 16 supports a seal 105. Lower seal plate 17 supports a seal 109. Fluid plate 19 further defines a fluid chamber 119 within which a valve seat 130 is supported. Valve plate 20 defines a fluid chamber 133 within which a valve ball 131 and a spring 132 are captivated. Manifold 21 defines an output fluid channel 28 (better seen in FIG. 7) which is in communication with fluid chamber 133. A pump rod 88 is coupled to pump plunger 55 and extends downwardly through guide 95, seal 105 and seal 109. The lower end of pump rod 88 extends into fluid chamber 119. A return spring 89 is operatively coupled between pump rod 88 and cam follower 55 to urge pump rod 88 and pump cam follower 55 upwardly. The check valve formed by the combination of ball 131 and spring 132 forms a normally closed valve in which ball 131 is urged against seat 130.
Pump valve plate 15 supports a sleeve guide 90. Upper seal plate 16 supports a seal 100 while lower seal plate 17 supports a seal 104. Fluid plate 19 defines a fluid chamber 136 within which a valve seat 110 is supported. Valve plate 20 defines a fluid chamber 137 which is in communication with input fluid channel 27 formed in manifold 21. An elongated valve rod 114 is operatively coupled to valve plunger 50 and extends downwardly through guide 90, seal 100 and seal 104. The lower end of valve rod 114 extends further into fluid chamber 136 and supports a valve ball 120 at its lower end. Fluid plate 19 supports a valve seat 110. Valve plate 20 defines a fluid chamber 137 which is in fluid communication with chamber 136 and input fluid channel 27 (seen in FIG. 7). A spring 118 is operatively coupled between pump valve plate 15 and valve rod 114 to urge valve rod 114 upwardly against valve cam follower 50 which in turn raises valve plunger 50.
With specific reference to FIG. 11A, pump 10 assumes the initial position in which both pump rod 88 and valve rod 114 have been forced downwardly to their lowered positions. It should be noted that the position shown in FIG. 11A corresponds to the positions for the cam followers shown in FIG. 12A in which plungers 55 and 50 are both forced downwardly by cam followers 73 and 83 respectively. Returning to FIG. 11A, with pump rod 88 in its downward position, the fluid volume within chamber 119 is at its minimum volume. Correspondingly, the downward position of valve rod 114 forces valve ball 120 against seat 110 closing chamber 136 and isolating it from chamber 137 and input fluid channel 127. Thereafter, as rotor 40 (seen in FIG. 12A) rotates to move cam followers 73 and 83 away from valve plunger 50 and pump plunger 55, spring 89 moves pump rod 88 upwardly while spring 118 moves valve rod 114 upwardly. The upward movement of valve rod 114 withdraws valve ball 120 from seat 110 allowing fluid coupling between passages 136 and 137 into input fluid channel 27. Concurrently, the upward movement of pump rod 88 provided by spring 89 increases the fluid volume of fluid chamber 119 which in turn draws fluid upwardly from input fluid channel 27 into fluid chamber 137 and further upwardly through fluid chamber 136. Fluid then flows through fluid passage 135 into fluid chamber 119 filling fluid chamber 119 as pump rod 88 rises to the intermediate position shown in FIG. 11B.
FIG. 11B shows the configuration of pump and valve segments within pump 10 at an intermediate point as pump rod 88 and valve rod 114 continue to rise. This configuration corresponds to FIG. 12B which shows cam followers 73 and 83 moving off of plungers 50 and 55 respectively. Returning to FIG. 11B, the continued upward movement of pump rod 88 continues the expansion of fluid chamber 119 which in turn allows continued fluid draw upwardly from input channel 27 through fluid chambers 137 and 136 and ultimately into fluid chamber 119 through fluid passage 135.
FIG. 11C shows the pump configuration as pump rod 88 and valve rod 114 assume their upper most positions. This configuration in turn corresponds to FIG. 12C in which cam follower 73 has moved away from plunger 50 and cam follower 83 has moved away from plunger 55. In the configuration shown in FIG. 11C, fluid chamber 119 is filled with fluid drawn upwardly from input fluid channel 27. It will be noted in FIG. 11C that ball 131 is forced against valve seat 130 closing the valve at the bottom end of fluid chamber 119. It will also be noted that valve ball 120 is withdrawn from valve seat 110. Thus, the entire fluid chamber arrangement is at this point filled with fluid drawn upwardly by the upward movement of pump rod 88.
FIG. 11D shows the configuration of the present invention pump as rotor 40 continues rotating to the position shown in FIG. 12D. As set forth therein, cam follower 72 has moved upon plunger 50 which again forced cam rod 114 downwardly forcing valve ball 120 against valve seat 110. This closure isolates fluid chamber 136 from fluid chamber 137 and input channel 27. As the rotation of rotor 40 continues to the position shown in FIG. 12E, cam follower 89 moves upon pump plunger 55 driving pump rod 88 downwardly into fluid chamber 119. The insertion of the lower end of pump rod 88 into filled fluid chamber 119 creates a displacement of fluid within chamber 119. This in turn produces a fluid pressure within fluid chamber 119 causing the pump to assume the configuration shown in FIG. 11E.
FIG. 11E shows the configuration of pump 10 as pump plunger 55 and pump rod 88 are driven downwardly by the force of cam follower 89 (seen in FIG. 12E). This fluid pressure forces valve ball 131 away from valve seat 130 opening the check valve and forcing fluid under pressure downwardly through fluid chamber 133 into output fluid channel 28 within manifold 21. This pressurized fluid flow into output channel 28 in turn produces an outward fluid flow from the pump. As rotor 40 continues to rotate, cam follower 89 moves across and away from pump plunger 55 and the system assumes the configuration represented by FIGS. 11A and 12A. In the absence of fluid pressure, valve ball 131 is forced upwardly against seat 130 by spring 132 returning the entire system to the configuration shown in FIG. 11A which results from the rotor position shown in FIG. 12A.
FIGS. 12A through 12E set forth sequential top views of pump 10 having rotor housing 13 removed. The sequential views of FIGS. 12A through 12E provide somewhat simplified views to best facilitate an understanding of the operation of the present invention pump. Accordingly, certain structural features of pump 10 are omitted from the figures such as upper bolts 24. Furthermore, FIGS. 12A through 12E show the positions of rotor 40 which correspond to the sequential pump section views shown in FIGS. 11A through 11E.
Accordingly and with concurrent reference to FIGS. 12A through 12E, pump 10 includes housing 11 having plunger plate 14 thereon. Plunger plate 14 supports, sleeve guides 60 through 62 and 65 through 67. Sleeve guides 60 through 62 support valve cam followers 50 through 52 while sleeve guides 65 through 67 support pump cam followers 55 through 57.
Rotor 40 is driven by input shaft 26 and includes an inner hub 41 and an outer wall 42. Hub 41 supports a plurality of cam followers 83 through 90 in a radially equally spaced array. Cam followers 84, 86, 88 and 90 are positioned higher upon hub 41 and are solely operative to limit the upward travel of pump plungers 55, 56 and 57. Cam followers 83, 85, 87 and 89 are positioned at lower positions on hub 41 to interact with pump plungers 55, 56 and 57. Cam followers 70 through 81 are supported by wall 42 and are arranged in groups of three in an equally radially spaced array. Cam followers 70 through 81 interact with vale plungers 50, 51 and 52 as rotor 40 is rotated.
With specific reference to FIG. 12A, rotor 40 is shown at the start of a pump cycle for the portion of pump 10 formed by the combination of the pump segment driven by pump plunger 50 and valve plunger 55. It should be noted that the remaining portions of pump 10 formed by the pump and valve segments driven by pump plungers 56 and 57 together with valve cam plungers 51 and 52 operate in the same manner as described below. In effect, pump 10 includes three pump portions simultaneously driven by rotor 40. It will also be noted that these three pump portions operate in interleaved sequences due to the radial arrangement of the cam followers on rotor 40. This provides interleaved pump cycles which minimizes, and virtually eliminates pressure ripple in the pump output.
In the position shown in FIG. 12A, cam follower 73 is forcing valve plunger 50 downwardly while cam follower 83 is forcing pump plunger downwardly causing the valve and pump segments to assume the positions in FIG. 11A. Thus, both valve rod 114 and pump rod 88 are at their lowest positions.
As rotor 40 rotates in the direction indicated by arrow 140, rotor 40 reaches the position shown in FIG. 12B. Cam followers 73 and 83 are moving away from the high points of valve plunger 50 and pump plunger 55. This allows valve rod 114 and pump rod 88 to begin rising to the positions shown in FIG. 11B. This in turn opens the valve and draws fluid into the pump segment.
As rotor 40 continues to rotate, it reaches the position shown in FIG. 12C in which valve plunger 50 is free of any cam follower and rises to the full height shown in FIG. 11C. Correspondingly, raised cam follower 90 limits the upward travel of the pump plunger to the maximum travel position shown in FIG. 11C. The pump potion is at this point fully filled.
As rotor 40 rotates to the position shown in FIG. 12D, cam follower 72 forces valve plunger 50 downwardly to the position shown in FIG. 11D which closes the pump valve as shown therein. The pump segment remains the same, that is, filled with fluid and pump rod 88 raised.
As rotor 40 continues to rotate, it reaches the position shown in FIG. 12E. At this point, cam followers 72, 71 and 70 have continued to depress valve plunger 50 maintaining the valve in the closed position shown in FIG. 11E. However, during the rotation of rotor 40 from the position shown in FIG. 12D to that shown in FIG. 12E, cam follower 89 depresses pump plunger 55 which drives pump rod 88 downwardly as shown in FIG. 11E. This provides the displacement pumping action of the present invention pump.
This cycle is repeated for each of the pump portions as rotor 40 is driven by a power source coupled to input shaft 26. It will be apparent to those skilled in the art that while the embodiments set forth herein show a pump having three pump portions in combination, Pumps having different numbers of pump potions may be utilized without departing from the spirit and scope of the present invention.
While particular embodiments of the invention have been shown and described, it will be obvious to those skilled in the art that changes and modifications may be made without departing from the invention in its broader aspects. Therefore, the aim in the appended claims is to cover all such changes and modifications as fall within the true spirit and scope of the invention.

Claims

1. A rotary drive linear rod displacement pump comprising:

a pump housing;

a plurality of displacement pump segments, supported by said pump housing, each including a pump plunger;

a plurality of valve portions, supported by said pump housing, each including a valve plunger; and

a rotor supporting a plurality of cam followers in contact with said valve plungers and said pump plungers for actuating said pump as said rotor rotates.

2. A rotary drive continuous flow linear rod displacement pump comprising:

a pump housing;

a plurality of linear rod displacement pump segments, supported by said pump housing and each including a pump plunger for actuating each of said linear rod displacement pump segments;

a plurality of valve segments, supported by said pump housing, each including a valve plunger for actuating each of said valve segments; and

a rotor, supported for rotation with respect to said pump housing, supporting a plurality of cam followers actuating said linear rod displacement pump segments and said valve segments as said rotor is caused to rotate.

3. The rotary drive continuous flow linear rod displacement pump set forth in claim 2 wherein each of said linear rod displacement pump segments include:

a fluid chamber; and

a pump rod movable within said fluid chamber between a withdrawn position allowing fluid to be received into said fluid chamber and an inserted position displacing fluid and expelling it from said fluid camber.

4. The rotary drive continuous flow linear rod displacement pump set forth in claim 3 wherein said pump housing includes a fluid manifold defining a fluid input accumulating channel in fluid communication with said plurality of valve segments and a fluid output accumulating channel in fluid communication with said plurality of linear rod displacement pump segments.

5. The rotary drive continuous flow linear rod displacement pump set forth in claim 4 wherein said fluid input accumulating channel includes a fluid input for coupling to a supply of fluid and wherein said fluid output accumulating channel includes a fluid output for discharging fluid from said rotary drive continuous flow linear rod displacement pump.

6. The rotary drive continuous flow linear rod displacement pump set forth in claim 5 wherein said plurality of linear rod displacement pump segments and said plurality of valve segments are supported by said pump housing in a radially spaced arrangement whereby each of said plurality of linear rod displacement pump segments and said plurality of valve segments are actuated sequentially as said rotor is caused to rotate.

7. The rotary drive continuous flow linear rod displacement pump set forth in claim 6 wherein said plurality of linear rod displacement pump segments and said plurality of valve segments are operatively coupled in associated pairs in which fluid flow into said fluid chamber of each linear rod displacement pump segment flows through its associated valve segment.

8. A rotary drive linear rod displacement pump comprising:

a pump housing having a plunger plate supporting a plurality of pump plungers movable with respect to said plunger plate and a plurality of valve plungers movable with respect to said plunger plate;

a plurality of displacement pump segments, supported by said pump housing, each actuated by one of said pump plungers;

a plurality of valve portions, supported by said pump housing, each actuated by one of said valve plungers; and

a rotor supporting a plurality of cam followers contacting and depressing said valve plungers and said pump plungers as said rotor is caused to rotate.

9. The rotary drive continuous flow linear rod displacement pump set forth in claim 8 wherein said plurality of linear rod displacement pump segments and said plurality of valve segments are operatively coupled in associated pairs in which fluid flow into said fluid chamber of each linear rod displacement pump segment flows through its associated valve segment.

10. The rotary drive linear rod displacement pump set forth in claim 9 wherein said displacement pump segments each include:

a fluid chamber formed in said housing;

a pump rod, coupled to a pump plunger, supported for movement between a withdrawn position and an inserted position relative to said fluid chamber; and a discharge output; and

a pump rod spring urging said pump rod and its coupled pump plunger toward said withdrawn position,

said pump plunger moving said pump rod from said withdrawn position to said inserted position as said cam followers contact said pump plunger during rotation of said rotor.

11. The rotary drive linear rod displacement pump set forth in claim 10 wherein said valve segments each include:

a valve rod supported within said pump housing coupled to a valve plunger;

a valve closure moveable between an open condition allowing fluid to flow into said fluid chamber and a closed condition preventing fluid flow from said fluid chamber; and

a valve rod spring urging said valve rod and its coupled valve plunger toward said open condition;

said valve plunger moving said valve rod from said open condition to said closed condition as said cam followers contact said valve plunger during rotation of said rotor.

12. The rotary drive continuous flow linear rod displacement pump set forth in claim 11 wherein said plurality of displacement pump segments and said plurality of valve segments are supported by said pump housing in a radially spaced arrangement whereby each of said plurality of rod displacement pump segments and said plurality of valve segments are actuated sequentially as said rotor is caused to rotate.