NZ212074A - Pump housing for double acting pneumatically operated diaphragm pump - Google Patents

Description

212074 glider the provisions of Regil tlon 23 (I) the ■—f ^j*|c|flcatJon has been ante-datecf " ' 19^ Priority Date(s): Complete Specification Filed: $4 Ctass: /F. /£<?$. ■iiiitiitiiiii Publication Date: ,.

P.O. Journal, No: ..... /£?.£. iZ Patents Form No: 5 NEW ZEALAND PATENTS ACT 195 3 ' COMPLETE SPECIFICATION DIVISIONAL out■of.

Application No:' 200058 "HOUSING FOB FLUID OPERATED DOUBLE-ACTING DIAPHRAGM PUMP" We, THE COCA-COLA COMPANY, of 310 North Avenue, Atlanta, Georgia 30313, United States of America, a corporation organised and existing under the laws of the State of Delaware, U.S.A., hereby declare the invention for which . we pray that a Patent may be granted to us and the method by which it is to be performed, to be particularly described in and by the following statement: - 1 - (followed by page 1A) 2 12074 BACKGROUND OF THE INVENTION This invention relates to a fluid operated diaphragm pump utilized in a Post-mix beverage syrup dispensing system and more specifically to a housing for such a pump.

Diaphragm pumps are widely used particularly for pumping liquid solutions and highly viscous materials and are frequently used under conditions such that the viscosity of the fluid being pumped, the head of the suction side of the pump and the back pressure on the pump discharge may all vary as conditions under which the pump is operating vary. The speed of such pumps has generally been controlled by inserting an adjustable valve in the air line leading to the pump. However, this approach requires that the operation of the pump be kept under continuous observation and the valve adjusted to suit varying conditions, otherwise the speed of the pump will vary substantially depending upon the conditions of operation. For example, if the back pressure on the pump should increase or decrease for any particular reason, or if the viscosity of the liquid being pumped should vary, then the speed of operation and the quantity of liquid being pumped per unit of time will accordingly be affected. Therefore, it is highly desirable that the pump be controlled such that it operates at a substantially constant speed under varying conditions. Furthermore, it is essential that the entire pumping cycle be completed so ' Vv-- . ,V : • .... ■: *■ ' ... , ■ - ■ v : :.•' : /' 'V-r". r*\ : I: T-.v 12074 as to ensure continuous delivery of the medium being pumped at a constant consistency or concentration. In order to ensure the latter, means have been suggested such as disclosed in U.S. Patent 4,008,984 wherein 5 opposed coil springs are provided for assisting the respective valve member in the completion of its pumping cycle. The coil compression springs of identical force under the pressurized gas system assist in completion of the pumping cycle first in one direction, 10 and then by asserting a positive reversing effect when either of the springs becomes fully compressed.

Although providing a reversing mechanism for the double acting pump disclosed, there are inherent disadvantages with such a system. For example, if for some reason 15 the pressurized system is effected in such a way that a back pressure is created or established so as to inhibit or reverse the pumping cycle before it is completed, there is no means for overcoming the undesirable effect, and the fully compressed state of the spring 20 is not reached. Thus, it is possible that the pumping cycle could be reversed regardless of the presence of the compression springs, before the cycle is completed, thus effecting the efficiency, if not the complete purpose of the reciprocating pump. 25 New Zealand Patent Specification No: 194940 describes and claims a reciprocating pump and reversing mechanism therefor. •« • v. ^ V . , " ■ ■ >' :.. :;v : ■■„■=> > ;:r#v^r ; - ;v ■ : :":W.; -y-j ;■' V., >/ n , . I iiwtoi tlim'i I »«n J»nnw 2 12074 Objects and the scope of applicability of the present invention will become more apparent from the detailed description given hereinafter. It should be understood, however, that the detailed description 5 and accompanying drawings, while indicating preferred embodiments of the present invention, are given by way of illustration only since various changes and modifications within the spirit and scope of the invention will become apparent to those skilled in the art.

Any such changes and modifications should be considered to be vithin the scope of this invention.

SUMMARY OF THE INVENTION According to the present invention there is provided a housing for a fluid operated double-acting diaphragm pump comprising: (a) a one-piece molded plastic pump body including (1) a pair of spaced-apart end sections each of which includes a central circular recess, for use as a driving fluid chamber, a connecting flange surrounding said end section and extending radially outwardly from said recess, and a central shaft opening concentric to said circular recess, said end sections being located in-line on an axis passing through said shaft openings and being arranged in a plane perpendicular to said axis and each of said end sections facing outwardly away from the other end section such that said recesses open outwardly away from said pump body, ■%|t it 2 1207 4 (2) a fluid inlet manifold enclosing a fluid inlet passageway and extending between and connecting together said end sections, said inlet manifold being parallel to said axis and being located radially outwardly beyond said recesses, and terminating at each end thereof in a fluid inlet port in each of said connecting flanges and located radially outwardly from said recesses, and said fluid inlet manifold including a single fluid inlet located in-between said ends thereof, (3) a fluid outlet manifold enclosing a fluid outlet passageway and extending between and connecting together said end sections, said outlet manifold being parallel to said axis and being located radially outwardly beyond said recesses, and terminating at each end thereof in a fluid outlet port in each of said connecting flanges and located radially outwardly from said recesses, and said fluid outlet manifold including a single fluid outlet located in-between said ends thereof., and (4) a driving fluid manifold enclosing a driving fluid passageway and extending between and connecting together said end sections, said driving fluid manifold being parallel to said axis and being located radially inwardly of the peripheral edge of said recesses and terminating at each end thereof in a single driving fluid port in a respective one of said end sections and in fluid communication with the recess therein, and (b) a pair of identical, one-piece, molded plastic end caps connected one each to a respective one of said end sections, each of said end caps including (1) a central section including a circular recess concentric to said pump body recesses, for use 2 12074 as a discharge chamber, (.2) a connecting flange surrounding said central section and extending radially outwardly from said end cap recess and matingly engaging the adjacent end section connecting flange, said end cap recess facing axially inwardly toward the adjacent end section recess, (3) a fluid inlet port located in said end cap connecting flange and located radially outwardly from said end cap recess and mating with said fluid inlet port in the adjacent pump body connecting flange, and a fluid inlet passageway extending between said end cap fluid inlet port and said end cap recess to provide fluid communication therebetween, and (4) a fluid outlet port located in said end cap connecting flange and located radially outwardly from said end cap recess and mating with said fluid outlet port in the adjacent pump body connecting flange, arid a fluid outlet passageway extending between said end cap fluid outlet port and said end cap recess to provide fluid communication therebetween, and (c) means for connecting each of said pump body flanges to a respective one of said end cap flanges/ The pump comprises a pair of flexible diaphragms mounted on the respective ends of a common shaft. The outer surface of the diaphragms are in contact with the liquid to be dispensed by the system, more particularly syrup for a Post-mix beverage dispensing system.

C ■- J- :V >.v,:\ / - ' / 2 t The chamber within the pump housing contains an inner wall in which passages are provided for directing compressed air, introduced into the reciprocating pump, to the surfaces of the diaphragms.- The flow 5 of air is controlled by a reversing valve adapted so as to redirect the flow of compressed air to the respective diaphragm at the completion of each, stroke of the pump in a cyclic manner. A valve actuating member or yoke is provided which engages the shaft 10 within the inner chamber of the pump housing and travels with the pumping action of the shaft. The yoke is designed so as to engage the reversing valve during the terminal phase of the pumping stroke, thus activating the valve 2 1 207 4 -7" """* and reversing the piston action of the pump. To complete the pump reversing system, a snap-acting spring actuating means interconnected with the yoke of the shaft, is centered within the inner chamber of the housing of the pump, pivotably mounted beneath the shaft connecting the diaphragms. The valve is provided with 0-rings positioned within the valve body with respect to the air passages of the valve such that during the first half of the reciprocating cycle, pressurized gas is introduced through the respective passageways and directed to the air chamber of one of th diaphragms. At the same time, a passage is provided for exhaust gases to be released from the air chamber of the remaining diaphragm. Upon interaction with the shaft yoke and the spring mounted actuating means, the relationship of the valve openings to the pressurized gas acting on the surface of the respective diaphragm is changed at the completion of the pumping stroke so as to reverse the action of the pump. The snap-action mechanism provided precludes the sticking of the pneumatic reversing system in an intermediate position.

In operation, pressurized gas is introduced through a passageway into a valve member and is directed via a passageway within the inner wall of the pump housing to the air chamber of one of the diaphragms within the pump. As the piston action of the diaphragm forces syrup from the diaphragm chamber out the appropriate passage to the dispensing outlet, movement of the shaft also moves the remaining diaphragm in a non-pressurizing direction. This same shaft movement also engages the shaft yoke. As the shaft yoke moves, it initiates the pivotal action of a pair of snap-acting compression springs which, prior to rotating 2 120 off- center, are pushing against each other. As the springs rotate off-center, they uncoil and push the shaft and yoke along in the direction of the established movement. The action of the spring mechanism ensures that the movement of the diaphragm, initiated by the air pressure, is taken to completion by the snap action of the compression springs, while at the same time reversing the flow of pressurized air within the valve member. This procedure is then repeated as long as the dispensing outlet is open and the syrup is being (3) dispensed as a pressurized stream. When the dispersing outlet is closed, sufficient back pressure is exerted on the diaphragms to prevent shaft movement.

It has been determined in the course of the present invention that a reciprocating diaphragm pump for syrup in a Post-mix beverage dispensing system can be provided such that the liquid can be delivered under controlled pressure conditions in a reliable manner. A reversing valve is provided which includes a pair of compression springs bearing one on the other so as not to apply pressure of the bearing surfaces on the pump shaft. , / r ....... f - \ . ~i--» ■ ' ^ > 2 12074 In an alternative embodiment of the pump, the control or reversing valve, the recip rocating actuating member and the opposed coil springs are provided in a common housing or module.

This module is removably secured to the pump body adjacent to the pump shaft and can be removed as a unit for ease of repair. The module housing is preferably molded from plastic in two pieces which slide together with suitable tongue and groove elements. A top one of said pieces houses the control or reversing valve, and has a slot on the underside thereof for receiving the yoke or actuating member of the reversing mechanism. The sides of the slot form bearing surfaces parallel to the longitudinal axis of the pump shaft. In this embodiment, the yoke slides or reciprocates on these bearing surfaces defined by the slot rather than on the pump shaft. A bottom one of said two pieces comprises a support for the opposed snap-acting spring mechanism of the present invention which is sandwiched between said top and bottom pieces- The yoke or actuating member has a pair of upwardly extending spaced arms for engaging opposite ends of the control valve element when it reciprocates, and a pair of downwardly extending spaced arms for engaging a transverse pin in the pump shaft as the shaft reciprocates. A central pin in the yoke couples it to the snap-acting spring mechanism. This embodiment of the present invention also provides an improved spring mounting means for the opposed compression springs and a unique bearing structure therefor.

The pump further provides a keying or coding technique to assure proper assembly of the inlet and outlet check valves of the pump. These ( ia 2 12074 valves are disposed in cylindrical cartridges with coded protrusions on the surface thereof to be received bj complementary coded slots in the respective inlet and outlet ports. These protrusions and slots are so arranged that it is impossible to insert a cartridge into the ports backwards with respect to the proper direction of operation. Thus, replacement of the valve cartridges can be properly performed by an unskilled operator and one valve cartridge can be used as either an inlet or outlet valve.

BRIEF DESCRIPTION OF THE DRAWINGS The present invention will become more fully understood from the detailed description given hereinbelow and the accompanying drawings which are given by way of illustration only and thus are not limitative of the present invention.

Figure 1 is a cross-sectional view of a prior art form of a . pump representing the initial position of a pressure stroke in the direction indicated; Figure 1A is a top view of the pump of Figure 1, illustrating the details of the fluid input and output manifolds and the inlet and outlet valves of the pump of the present invention; Figures 2A and 2B are partial side and bottom views respectively of the pump of Figure 1, illustrating a first form of the spring reversing system thereof as they snap over center toward the r ight; Figures 3A and 3B are partial side and bottom views, respectively, of the pump of Figure 1, illustrating the spring reversing mechanism thereof immediately after the snap-over position of Figures 2A, 2B, which causes the pump shaft to reverse directions and move to the left; Figure U is h cross-sectional view of the reversing valve of the pump in the position that it occupies when the pump shaft of Figure 1 is driven to the right; Figure 5 is a cross-sectional view of the reversing valve of the pump in the position that it occupies when the pump shaft of Figure 1 is driven to the left; Figure 6 is an exploded view illustrating the details of how the yoke of the pump is mounted on the pump shaft; Figure 7 is a partial view illustrating prior art form of pump diaphragm of the pump; Figure 8 is an exploded view of a first embodiment of the pump of the present invention and reversing mechanism therefor; Figure 9 is a cross-sectional view of a fully assembled pump of the embodiment of Figure 8; Figure 10 is an exploded view of the control valve and reversing mechanism module of the present invention attached to the pump of Figure 8; Figure 11A is a side view of a check valve cartridge of the present invention illustrating coded protrusions thereon; ■:"XA Figure 1 IB is a diagrammatic view of only the protrusion configuration adjacent the right end of the cartridge of Figure 11A; Figure 11C is a diagrammatic view of only the protrusion configuration adjacent the left-hand end of the cartridge of Figure 11A; and Figure 12 is an end view of an end section of the pump of Figures 8 and 9, including inlet and outlet ports with coded groove configurations therein for selectively receiving either the front or back ends of the valve cartridge of Figure 11A.

DETAILED DESCRIPTION OF THE DRAWINGS Referring now to Figures 1 and 1A, there is seen a cross-sectional side and top view, respectively, of a prior art form of reciprocating pump generally designated 10, comprising a housing 11 having an input manifold 12A and an output manifold 12B in its top wall for carrying the syrup to be pumped from the inlet SI through the respective chambers discussed below to the pump outlet SO. Within an inner chamber 13 of the pump is positioned a shaft 14 interconnecting diaphragms 16A and 16B. An actuating member or yoke 17 with protrusions or arms 17A is slidably supported on the shaft 14 by the longitudinal bore 17B, Figure 6, passing therethrough. A reversing valve 40 is attached to the inner wall 21 of housing 11 within the inner chamber 13 of the pump. The shaft 14 is press-fit with a pin 25, which upon operation of the pump, travels with the movement of the shaft a predetermined distance before engaging an end of slot 26 provided in the yoke 17. Shaft 14 is mounted for sliding 2 1207 movement in O-ring seals OR at its respective ends. Pivotally mounted beneath the yoke and interconnected therewith is a spring actuating member 27 (Figures 2A, 2b, 3A, 3B) within the housing chamber 13. The reversing effect of the valve 40 is facilitated as a result of the interrelationship between the actuating yoke member 17 and the spring actuating means 27 and alternately directs pressurized gas introduced through passageway 22 to the respective air chambers 15A and 15B, through passageways 23 and 24, to apply pressure to the respective diaphragms 16A and 16B. The reversing valve 40 comprises a valve body 41 and spool element 42 with 0-rings 43. A more complete discussion of the operation of the reversing valve can be found below with respect to Figures 2A, 2B, 3A, 3B, 4 and 5. Each diaphragm of the pump is constructed of a flexible material, such as rubber, secured to the inner walls of the pump housing at positions 20.

In r one form of the pump, the diaphragms further include a metal or plastic piston on the outer face of the respective diaphragm and a metal retaining cap on the inner surface of the respective diaphragm, as illustrated in Figure 7 to be discussed hereinafter.

The pumping cycle of thispump and the flow of fluid therethrough can be best illustrated by reference to Figure 1A. Fluid to be pUmped is introduced through an inlet SI to input manifold 12A which extends across tlie top of the pump and communicates with fluid chambers 28 and 29 via normally closed check valves 31L, 31R. When 1 I ■ - ■ r fissesss 21 20 7 -14 the fluid pressure in input manifold 12A exceeds the pressure in either chamber 28 or 29, check valves 31L, 31R open. Since the pump is a reciprocating pump, the fluid pressures in chambers 28, 29 are always in the opposite state. That is, if the pump shaft in Figure 1A is moving to the right,chamber 28 has a higher fluid pressure than manifold 12A, and chamber 29 has a lower fluid pressure than manifold 12A.

Under these conditions, check valve 31L opens, introducing fluid into chamber 29 and check valve 31R is closed. Thus, as the pump cycles, check valves 31L, 31R alternately open and close.

Outlet check valves 32L, 32R, disposed in an output manifold 12B, function in substantially the same manner. That is, when the pressure output manifold 12B is less than the pressure in one of the respective chambers 28, 29, the check valve in that chamber opens, discharging fluid therefrom to pump outlet SO. In the above example, with the pump shaft 14 moving to the right, the pressure in chamber 28 is high, thus opening valve 32R and permitting the fluid therein to discharge via manifold 12B and pump outlet SO.

The check valves 31L, 31R, 32L, 32R are substantially identical except for the respective orientations thereof. Each is formed from rubber and includes a central stem fixedly mounted in the pump wall, and a disc-shaped seat B, which normally seats on fluid poTts C. When biased by fluid pressure to open, disc-shaped seat B flexes away from ports C, permitting fluid to pass therethrough.

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The above-described outlet check valves are disposed at the highest positions of chambers 28, 29 to preclude the formation of air pockets which could be sucked out through pump outlet SO, resulting in an uneven flow of fluid.

Figure 6 illustrates the details of actuating member or yoke 17, which is mounted for movement on shaft 14. Yoke 17 includes a pair of upstanding arms 17A described hereinbefore for engaging the valve 40 and switching the same from one state to another. A longitudinal bore 17B is provided in yoke 17 for receiving pump shaft 14. After pump shaft 14 is inserted in bore 17B, pin 25, described hereinbefore is press-fit into aperture 14A in Shaft 14. A bottom plate 17C is suitably attached to the bottom of yoke 17, thus supporting a pair of pins 39 therein. As will be discussed hereinafter, pins 39 support one pair of ends of spring members of the snap-acting mechanism illustrated in Figures 2B and 3B.

Referring now to Figure 2A, 2B, there is seen in cross-section the pump mechanism set forth in Figure 1 representing a pressure stroke of the pump in the direction indicated at the point of engagement of the pin 25 of shaft 14 with an end of slot 26 in the shaft yoke 17. At this instant, the yoke is picked up by pin 25 and begins to move with the shaft and the spring actuating member 27, connected to the yoke, begins to pass over center. The diaphragm 16 applies pressure to the liquid present in the chamber 28, which is released via check valve 32R into passageway 12 and directed out through the pump outlet SO to the respective discharge stations. Figures 2B, 3B represent the position of the diaphragm, shaft and . . „ " .. - N i 212074 -16- — yoke at the completion of the stroke, As the reversing mechanism, generally indicated 27, moves over center, there is produced a snap action effect which thrusts one arm 17A of the yoke against the protruding end of the spool 42, thus changing immediately the position of the O-rings of the valve so as to suddenly reverse the flow of pressurized air through the valve 40 at the completion of the stroke,and reverse the piston action of the pump.

Figures 2B and 3B illustrate the details of the spring reversing mechansim 27. The spring reversing mechanism in one embodiment comprises a coil spring 36 wrapped about a pin 37 and pivotally attached by way of pin 38 to the housing and pin 39 to the yoke 17. Upon engagement by the pump shaft, the yoke 17 will move in the direction of the stroke of the pump, which in turn rotates pins 37 over center about pins 38 such that the springs 36 take over and push the yoke in the direction of the established movement at a speed faster than the shaft movement, until the yoke "hits against the spool 42 of the valve mechanism so as to reverse the direction of the flow of pressurized air within the system and establish the piston action of the pump in the opposite direction. The position of the compression springs and yoke at the ends of the stroke are represented in Figure 3B. The presence of the pins 37 within the coil spring 36 prevents the spring member from buckling during the movement of the piston during the operation of the pump. Alternately, torsion springs 36T in phantom may be substituted for the coil springs herein illustrated to provide i—JfcJ^d^-'wTO^niSjrwo, M IMsS 17- 2 12 07- o o [ ■ ? : o the snap-acting actuating means of the present invention. The yoke 17 slides or is pushed along by the shaft and spring mechanism 27 of the pump, first in one direction then in a reverse direction according to the reversing action of the valve 40.

In Figures 4 and 5, there is illustrated a simplified enlarged cross-sectional view of the reversing valve 40 of the pump -which is represented herein as a spool valve comprising a valve body 41, the spool 42 having three 0-Tings 43 intermittently positioned thereon within the valve cavity 44. Within the upper area of the valve body are located air passages 45 coupled to passage 22 of Figure 1, for introducing the pressurized gas into the valve cavity 44, and 46 and 47 are coupled to passages 23, 24 of Figure 1, for directing air through the valve to the surface of the respective diaphragms of the pump. The valve 40 herein represented shows air under pressure being introduced to the valve cavity 44 through passageway 45 such that during the first half of the reciprocating cycle, the air is directed to the respective air chamber 15B, through passageway 46 and passageway 24 (see Figure 1),while at the same time remaining passageway 47 provides for exhaust gases to be released as illustrated from the air chamber of the remaining or opposite diaphragm air chamber 15A. Upon contact by the left protruding end of the spool 42 with the yoke 17 as discussed above, the spool 42 is thrust to the right such that at the end of the pumping action the 0-rings 43 shift their position as illustrated in Figure 4, and the pressurized gas is now directed in the opposite V . 3: 'f- wswkr ~r ■■•«?■■ y * 18. 2 1 7 4 c o direction so as to be introduced into the air chamber 15A of the diaphragm 16A, thus driving the pump in the opposite direction. In this position, the left end of the spool now projects from the valve cavity 44 and awaits to be engaged by an arm 17A of the shaft yoke in the reverse action of the piston.

In operation, the valve 40 alternates the air flow through the respective passages 23, 24 to the air chambers 15A, 15B of the diaphragms 16A, 16B. The compression springs 36 or 36T interconnected to the yoke continuously urge the shaft of the diaphragm pump first in one direction then the other, responsive to the location of the yoke 17 along the shaft. The pressurized air is introduced into the air chambers 15A, 15B behind the respective diaphragms 16A, 16B and drives the diaphragms so as to discharge the liquid from the diaphragm chambers. As stated above, the yoke 17 on the shaft 14 initially moves in conjunction with the movement of the shaft upon engagement of an end of slot 26 with the pin 25 in shaft 14. The compression springs 36 or 36T, which at the time of engagement are pushing against each other, with substantially no net force in a direction transverse to the pump shaft, pivot over centeT and apply a further driving force to the yoke which is then caused to move quickly by the snap-action of the springs 36 to seat the projecting portions or arms 17A of the yolce 17 against the protruding spool 42 of the valve 41.

This changes the positions of the 0-rings within the valve body and reverses the flow of pressurized air therein thus completing the first half of the cycle of the diaphragm pump. The continuous n /!■ o | ' ,***%. -r'y. «*flfc»«wsss^^ 2 12074 introduction of pressurized air into the valve 40 initiates the pumping action of the shaft mounted piston in the opposite direction, first compressing the springs 36 or 36T and then repeating the action described above in the opposite direction, the compressed springs now pushing in the opposite direction. The spring reversing mechanism ensures that the movement of either of the diaphragms initiated by the air pressure, is completed, thus preventing premature reversal of the pumping stroke or sticking of the valve 40 in a central position.

Referring now to Figure 7, there is seen in crosssection a purap construction similar to that discussed above with respect to Figures 1 and 1A, except with respect to the structure of diaphragms 16A, 16B. The diaphragms 16A and 16B further include cup-shaped plastic or metal plates 52 on the outer face of the respective diaphragm surface and cup-shaped retaining cap 54 on the inner surface of the respective diaphragms. This configuration eliminates the formation of crevices in the flexible diaphragm.

Preferably, the pump housing is constructed of a molded plastic, as herein represented in Figure 1, such that the valves are mounted through the pump and all the lines or passageways run inside the plastic housing. This construction eliminates unnecessary joints and external lines which contributes to a more reliable system. As is seen in Figure 1, the inner wall of the housing comprises one continuous member which surrounds the pump reversing system components. The outer walls of the housing 11 are also fabricated of molded plastic which provides for an overall more desirable construction of the diaphragm pumpf A? 2 1 207 Referring in detail to Figures 8 and 9, there now is/i1lustrated ah embodiment of a pump construction in accordance with the present invention. Figure 8 is an exploded view to illustrate how the pump is assembled, and Figure 9 is a cross-sectional view illustrating the pump in a fully assembled condition. The main pump body includes end sections 102 having fluid discharge chambers 105 formed therein and inlet and outlet ports 142, 144, respectively. In addition, each end section 102 has an annular groove or recess for receiving the flexible diaphragms 118 therein about the periphery thereof. The diaphragms 118 may include metal or plast piston members 119 nested therein. The end sections 102 of the main pump body also include central apertures 107 for slidably receiving the pump shaft 104 extending between and into the respective discharge chambers 105. The shaft 104 is mounted within apertures 107 by suitable 0-rings 110 and bushings 112. The ends of the pump shaft 104 are coupled to the diaphragm assembly and, more specifically, pistons 119 by retainers 114 and a suitable washer 116.

The two end sections 102 of the main pump body are molded as one piece with inlet and outlet manifold tubes 143 and 141, respectively, which connect the two end sections 102 and the respective inlet and outlet ports 142, 144, therein. Fluid inlet 139 is provided in manifold tube 143 and fluid outlet 140 is provided in manifold tube 141. Suitable connectors for flexible rubber hoses such as 132 may be secured to the respective inlet and outlets 139 and 140 by suitable 0-rings 134, screws 136 and retainer hooks 138. visf^'v Isrj'fJlWrl.iUi -ifi- ~(i ■ -.£ 2 1 20 o O A plurality of check valves to be described further hereinafter with reference to Figures 11 to 13 are provided for insertion into the inlet and outlet ports 142, 144 in the end sections 102.

These check valve cartridges include a main cylindrical body 122 with 0-rings 124 at the ends thereof and a flexible flapper type of check valve 125 including a Flexible disc on a central stem. The external surface of the cylindrical cartridges is provided with coded protrusions or bumps to be described further hereinafter with reference to Figures 11 to 13. As will become more fully apparent hereinafter, these coded protrusions 123 fit into coded slots 146 in the respective inlet and outlet chambers 142, 144, the respective configurations of the protrusions and slots being such as to preclude the insertion of the check valve cartridges into the inlet and outlet ports in the wrong direction.

Once all of the respective components such as diaphragms 118, check valve cartridges 122, pump shaft 104 and so forth are inserted into the end section 102 of the main pump body, the end caps 100 may be secured to the end sections 102 by suitable screws 126 which extend through apertures in a peripheral flange of the caps 100 into threaded apertures in the periphery of a flange extending around end sections 102. Thus, the end sections 102 of the main pump body and the end caps 100 screwed thereto define the respective discharge chambers of the pump of this embodiment of the present invention.

It should be noted at this juncture that the check valve cartridges 122 of the present invention become sandwiched between the end sections 102 of ■■■Wiisr T* ( / 2 1207 the pump body and the end caps 100 and both end sections 102 and end caps 100 are provided with coded slot configurations 146 for receiving the coded protrusions on the surface of the check valve cartridge. The end caps 100 are further provided with molded pins extending from the ends thereof disposed in a symmetrical pattern. These pins may be utilized for supporting the pump in a mounting bracket (not shown).

A control valve and reversing mechanism module 200 to be further described in connection with Figure 10 is secured to an appropriate portion of the manifold section of the pump by screws 130 adjacent to and just above the shaft 104 on a bracket 201 integral with a driving gas manifold. The gas manifold communicates with both discharge chambers and the outputs of the control valve within module 200. As illustrated in Figure 9, the control valve and reversing mechanism module 200 is disposed in operative engagement with a washer 106 fixedly secured to pump shaft 104 by retainer rings 108. As will become more fully apparent hereinafter with respect to Figure 10, the washer 106 performs a similar function to the pin 25 disposed in the pump shaft of the prior art type shown in Figure 1.

Referring in detail to Figure 10, there is illustrated an exploded view of a combined control valve and reversing mechanism module of the present invention for use with the pump of Figures 8 and 9. The module housing is generally indicated 200 and includes a top housing portion 202 and a bottom housing portion 204, the bottom housing portion 204 being slidably received within the top housing portion 202 in an assembled condition by means of slots 214 which receive tongue portions 215 V '-'X ■ A Vv! frrrr ^ .

... V • / s': ■ ! ' -v / < • •23- 2 12074 •>& o extending upwardly from the bottom housing portion 204. On the underside of bousing portion 202, there is provided a slot 210 which extends transversely across the entire top portion 202 and the side walls 212 thereof define bearing surfaces on which the edges of a yoke or actuating member to be described hereinafter may slide parallel to the pump shaft 104. The top of housing portion 202 is molded with chambers therein for receiving the control valve of the present invention which is similar in operation and construction to the control valves 40 illustrated in Figures 4 and 5 described hereinbefore. That is, the cylindrical chamber 206 is molded in housing portion 202 for receiving a plurality of interconnected bushing elements and dividing 0-rings 230 which define the different sections of the control valve body bore. The bushings include a central inlet bushing 228 which would be juxtaposed within inlet ports such as 45 of the valve of Figures 4 and 5 and outlet bushings 226 which would be juxtaposed with the outlet paths 46 and 47 of the valve of Figures 4 and 5. These bushings would include peripheral apertures in alignment with respective channels 45, 46 and 47 to permit the flow of fluid therethrough. Disposed for reciprocal sliding movement within the bushings 226 and 228 is a spool member 220 with spaced 0-rings 222 thereon of a similar construction to the spool 42 illustrated in the valve of Figure 4 and 5. This spool 220 is Tetained within the cylindrical chamber 206 and the respective bushings described hereinbefore by a screw-type retainer 224 which is screwed into one end of the chamber 206 in housing portion 202. Both retainer 224 and the opposite r 212074 end of cylindrical chamber 206 are provided with keyholetype ports 218 having enlarged wing portions 219 which permit the escape of exhaust gas during the reciprocal action of the valve. The wing portions 219 provide for better exhaust venting of the gas from the valve and assist in a self-cleaning action of the spool 220. The top housing portion (""*) 202 is further provided with an upstanding flange, including apertures 216 therein for receiving screws 130 which attach the entire module 200 to the pump assembly in communication with a suitable manifold structure 201 which supplies driving gas (2^) to either one of the pump discharge chambers on the inboard side of the diaphragms to thereby drive the pump in a reciprocating action, as described in detail hereinbefore. The supply of driving gas to the module 200 of Figure 10 is through inlet port 208 in the top housing portion 202. This inlet port 208 may be fitted with an adaptor 132, retainer hook 138 and O-ring 134 secured thereto by a screw 136 of a similar construction to the adaptors described in connection with Figure 8 hereinbefore. The provision of these adaptors enables the pump and control valve unit of Figure 10 to be connected to flexible hoses or tubes. ^ The module 200 has a reciprocating yoke or ^ actuating member therein between the top and bottom sections 202 and 204. Yoke member 240 slides in slot 210 in top section 202 on bearing surfaces provided by walls 212 thereof. Yoke or actuating member 240 is stamped from sheet metal and is configured with upstanding arms 242 at the opposite end thereof with anvil portions 241 stamped therein for engaging the opposite ends of spool valve element 220 as it o - '< 7 • t^C ":fi r 21207 o o reciprocates with the action of the pump shaft. In this regard, a pair of spaced arms 246 extend downwardly from the yoke 240 for engaging the washer 106 on the pump shaft 104, as illustrated in Figure 9. Yoke 240 is also provided with a downwardly extending pin 244 which fits into apertures 258 in the end of pins 240 of a snap-acting spring mechanism to be described hereinafter. The bottom housing portion 204 is provided with slots 264 to permit the reciprocal movement of arms 246.

The opposed compression spring snap-acting reversing mechanism utilized in the module 200 of Figure 10 includes a pair of tubular spring support sockets 248 having bores 250 therein for receiving both coil compression springs 252 and support pins 254 therefor. The springs 252 may be inserted within bores 250 and the pins 254 then inserted within the springs to provide a quick and easy assembly method of this snap-acting mechanism. Extending from the top and bottom of members 248 are pivot pins 249 which are received in aligned apertures 262 in the bottom portion 204 and the top portion 206. Thus, the socket members 248 are sandwiched between the top and bottom housing portions of the module 200 and are pivotally mounted in the apertures 262 in the respective top and bottom portions of the housing. The apertures 262 in the top housing portion 202 are not illustrated, but they are directly aligned within the slot 210 above apertures 262, illustrated in the bottom housing portion 204. The support pins 254 of this embodiment of the present invention also have a unique end bearing structure, including circular si :L^ 6 2 120" end members 256 and arcuate engaging bearing flanges 260. When assembled together, these two end bearing structures, including circular members 256 and arcuate bearing flanges 260, nest one within the other, and the respective circular end members bear against the opposed arcuate bearing flange members 260 of the opposing support spring mechanism. This structure is particularly unique and significant for increasing the life of this spring-acting mechan and also more compact in size. That is, because of this increased bearing area and nesting arrangement, the bearings have a long life. In addition, this bearing arrangement is particularly efficient and unlikely to bind or stick as the coil springs move over center in the snap-acting fashion described hereinbefore with respect to Figures 2 and 3.

All of the parts of the module 200 of Figure 10 are fabricated from plastic with the exception of yoke member 240, springs 252, spool 220 and bushings 226, 228. Of course, it is also preferable that the screws, such as 266 which hold the two housing portions together, be fabricated from metal. Of course, all parts may be plastic if desiTed. The operation of the control valve in reversing mechanism module 200 of Figure 10 should be readily apparent from the description of the prior art pumps described in conjunction with Figures 1 to 7. That is, the reciprocation of the spool 220 within the control valve bore 206 causes driving gas to be alternately provided to the discharge chambers of the pump on the inboard side of the diaphragms, depending-upon the position of the spool. This movement of one or the other of the diaphragms creates the pumping -27- 2 12074 action and simultaneously reciprocates the pump shaft, causing the shaft and the ring or bushing 150 thereon to engage one of the downwardly extending arms 246 of the yoke member 240. This, in turn, causes the yoke member 240 to reciprocate, and the pin 244 extending downwardly therefrom to apertures 258 in the ends of spring support pins 254 causes pins 254 to rotate about pins 249 of retaining sockets 248. When pins 254 and coil springs 252 thereon move over center (past a line perpendicular to the longitudinal axis of yoke 240), coil springs 252 cause the springs to snap and accelerate the yoke. The arm 242 on the trailing end then bangs against the associated end of spool 220, causing the valve to switch to its opposite bistable position. As in the spring configuration of Figures 2 and 3, the symmetrical opposed springs in a common plane precludes the occurrence of transverse forces on the bearing surfaces 212.

Thus, yoke 240 will not stick in an intermediate position of the extreme positions of travel. The bearing structure 256, 260 on the ends of pins 254 further decreases any possibility of sticking or binding of the reversing mechanism.

Preferring in detail to Figures 11 and 12, there is illustrated the novel coded valve cartridge of the present invention in conjunction with the inlet and outlet ports in which it is contained. Figure 11A sTiows a side elevational view of the valve cartridge of the present invention, including at its front end or the right end, as viewed in Figure 11A, a pair of diametrically-opposed protrusions 123F, and at the rear or left end, as viewed in Figure 11A, three spaced protrusions 123R. It should be -2 8- 2 1 /.U/ understood that the third protrusion 123R in Figure llA is not illustrated in the side view. However, the third protrusion is illustrated in Figure 11C, to be described hereinafter. In this regard, Figures 11B and 11C are diagrammatic illustrations of only the protrusion configurations of the respective right and left sides of the cartridge illustrated in Figure 11A. That is, Figure 11B illustrates two diametrically-opposed protrusions 123F and Figure 11C illustrates three spaced protrusions 123R.

Figure 12 illustrates an end section 102 of the pump of Figures 8 and 9 of the present invention and inlet and outlet ports 142 and 144, respectively. Inlet port 142 includes three spaced grooves 146R for receiving only the three-spaced protrusions 123R of the configuration of Figure 11C. Therefore, only the rear or left end of the valve cartridge of Figure 11A can be inserted into inlet port 142.

This assures that the check valve within the valve cartridge of Figure 11A cannot be inserted backwards within the inlet port 142. In a like manner, the diametrically-opposed pair of grooves 146F in outlet poTt 144 will only receive the protrusion configuration of Figure 11B which has two diametrically-opposed protrusions 123F. Therefore, only the front or right end of the valve cartridge of Figure 11A may be inserted into the outlet port 144 in the end section 102 of the pump of the present invention.

Thus, it can be clearly seen that a single valve cartridge having the protrusion coding configuration of Figure 11A may be utilized for insertion into any one of the four inlet acid outlet ports 142, 144 of the pump of the present invention; and 21207 4 it is impossible to insert the cartridges improperly.

In the preferred embodiment of the present invention, the end caps 100 of the pump of Figures 8 and 9 also have coded groove configurations for receiving the end of the valve cartridge of Figure 11A, which is not contained within the inlet and outlet ports 142, 144 of Figure 12. That is, if the cartridge of Figure 11 is inserted in the inlet port of Figure 142, the three spaced protrusions 123 are contained within that port while the diametrically-opposed protrusions 123F at the opposite end of the cartridge extend from the port 142. Therefore, a chamber 147 in end cap 100 of the pump would have a diametrically-opposed pair of slots therein for receiving the pair of diametrically-opposed protrusions 123F. In a similar manner, with the pair of diametrically-opposed protrusions 123F inserted in outlet port 144 and slot 146F, the three spaced protrusions 123R of the cartridge would extend out of outlet port 144. Thus, a chamber 149 in end cap 100 of the pump in Figure 8 would require the presence of three spaced slots to receive the protrusions 123R therein. In this manner, a double coding of the parts is achieved, so that it is impossible to insert the valve cartridges backwards into the inlet and outlet ports 142 and 144, and it is also impossible to assemble the end caps 100 to the end section 102 without having the check valve cartridges properly inserted within the inlet and outlet ports 142, 144.. • ■ ~30 " r 2 12074 The invention being thus described, it will be obvious that the same may be varied in many ways. Such variations are not to be regarded as a depatture from the spirit and scope of the present invention, and all such modifications as would be obvious to one skilled in the art are intended to be included within the scope of the following claims. 2L2074

Claims (21)

WHAT WE CLAIM IS:

1. A housing for a fluid operated double-acting diaphragm pump comprising: . (a) a one-piece molded plastics pump body including (1) a pair of spaced-apart end sections each of which includes a central circular recess, for use as a driving fluid chamber, a connecting flange surrounding said end section and extending radially outwardly from said recess, and a central shaft opening concentric to said circular recess, said end sections being located in-line on an axis passing through said shaft openings and being arranged in a plane perpendicular to said axis and each of said end sections facing outwardly away from the other end section such that said recesses open outwardly away from said pump body, (2) a fluid inlet manifold enclosing a.fluid inlet passageway and extending between and connecting together said end sections, said inlet manifold being parallel to said axis and being located radially outwardly beyond said recesses, and terminating at each end thereof in a fluid inlet port in each of said connecting flanges and located radially outwardly from said recesses, and said fluid inlet manifold including a single fluid inlet located in-between said ends thereof, (3) a fluid outlet manifold enclosing a fluid outlet passageway and extending between and connecting together said end sections, said outlet manifold being parallel to said axis and being located radially outwardly beyond said recesses, and terminating at each end thereof in a fluid outlet port in each of said connecting flanges o o '"V: • ' / ■ i' ' . .1 32 _ 2L2074 t and located radially outwardly from said recesses, and said fluid outlet manifold including a single fluid outlet located in-between said ends thereof, and (4) a driving fluid manifold enclosing a driving fluid passageway and extending between and connecting together said end sections, said driving fluid manifold being parallel to said axis and being located radially inwardly of the peripheral edge of said recesses and terminating at cacli end thereof in a single driving fluid port in a respective one of end.- ■ Xv:''-.-V; said/sections and in fluid communication,with the recess therein, and'' (b) a pair of identical, one-piece, molded plastics end caps connected one each to a respective one of said end sections, each of said end caps including (1) a central section including a circular recess concentric to said pump body recesses, for use as a discharge chamber, (2) a connecting flange surrounding said central section and extending radially outwardly from said end cap recess and matingly engaging the adjacent end section connecting flange, said end cap recess facing! axially inwardly toward the adjacent end section recess," (3) a fluid inlet port located in said end cap connecting flange and located radially outwardly ■;.*£»* I ■ r~~ / n C " 33 " 2L2074 from said end cap recess and mating with said fluid inlet port in the adjacent pump body connecting flange, and a fluid inlet passageway extending between said end cap fluid inlet port and said end cap recess to provide fluid communication therebetween, and (4) a fluid outlet port located in said end cap connecting flange and located radially outwardly from said end cap recess and mating with said fluid outlet port in the adjacent pump body connecting flange, and a fluid outlet passageway extending between said end cap fluid outlet port and said end cap recess to provide fluid communication therebetween, and (c) means for connecting each of said pump body flanges to a respective one of said end cap flanges.

2. The housing as recited in claim 1, wherein said end sections, said end section connecting flanges and said end cap connecting flanges are circular and .concentric to said axis.

3. The housing as recited in claim 1 wherein said fluid inlet manifold and said fluid outlet manifold are spaced-apart and are located on diametrically opposite sides of said pump body.

4. The housing as recited in claim 1, wherein said ' % manifold manifold fluid inlet/and said fluid outlet/are located on the same side of said pump body.

5. The housing as recited in claim 1 including an annular groove concentric to said axis in at least one of the connecting flanges of each pair of mating connecting flanges and adapted to sealingly receive an enlflxagd ' ; ' :; - v"-^; ^ -t / "-/j~ y*8& iTawxiawfr^seesetrr.^iiKiwreKynwi-.y o O - 34 - 2 120 74 circular bead of a diaphragm.

6. The housing as recited in claim 5, wherein said groove in at least one of said flanges comprises a pair of opposed mating grooves, one in each of said flanges.

7. The housing as recited in claim 6 including a pair of diaphragms, each one having an enlarged circular peripheral bead sealingly locked in a respective one of said pair of opposed grooves, each of said diaphragms defining with the respective end section a driving fluid chamber and with the respective end cap a fluid chamber for fluid to be pumped.

8. The housing as recited in claim 7 including a | reciprocatable shaft connected at each end thereof to one | each of said diaphragms and extending through said shaft | openings, and shaft sealing means in each of said shaft I openings.

| 9. The housing as recited in claim 1 including a ■ single check valve cartridge positioned one in each of said J two fluid inlet ports and positioned one in each of said | two fluid outlet ports.

10. The housing as recited in claim 9, wherein each of said check valve cartri dges is in sealing contact with each of said pump body and a respective one of said end ■ caps.

11. The housing as recited in claim 10, wherein each of said cartridges includes a pair of spaced-apart o-ring seals, and wherein one o-ring seal is in sealing contact with the port in said pump body and the other o-ring seal is in sealing contact with the port in a respective one of said end caps. f:' .'£1 . 'L -35 ~ 212074

12. The housing as recited in claim 9, wherein said check valve cartridges are identical to each other.

13. The housing as recited in claim 1, wherein each of said fluid inlet passageways and said fluid outlet passageways are formed completely inside of a respective one of said end caps, whereby there are no leakage paths directly therefrom to the outside of said housing.

14. The housing as recited in claim 1 wherein each of said end sections are substantially identical to each other, and wherein each of said end caps are substantially identical to each other.

15. A housing for a fluid operated double-acting: diaphragm pump comprising: (a) a one-piece molded plasticspump body including a pair of substantially identical, spaced-apart in-line, end sections, each having an axially outwardly facing circular recess for (.forming a driving fluid chamber, surrounded by a radially outwardly extending connecting flange, each of said recesses being concentric to the same axis and each of said end sections being oriented in a plane perpendicular to said axis, manifold means, including an inlet manifold, an outlet manifold and a driving fluid manifold, extending between and connecting said end sections together and terminating in fluid ports including an inlet port and an outlet port in each of said connecting flanges and a driving fluid port in direct fluid communication with said driving fluid recess; - 35 - 2 L2074 (b) a pair of identical, one-piece, molded plastics end caps connected one each to a respective one of said end sections, each of said end caps having an axially inwardly facing circular recess and each having a radially outwardly extending connecting flange that mates with a respective one of said end section connecting flanges for use in ' * assembling said end caps to said pump body, each of said end caps also having; an inlet port and an outlet port in each of said flanges located so as to mate with the > respective inlet and outlet ports; respectively, in the respective end section when said end caps.are connected to said pump body, and a fluid passageway extending between each of said end cap inlet and outlet ports and said end cap'-recess.,'' . (c) a single, elongated check valve cartridge, including a check valve and a cartridge body, located one in each of said two fluid inlet ports and one in each of said outlet ports, and means for sealing one end of each of said check valve cartridges to the respective port in the pump body and the other end to a respective port in the end cap, and (d) means for connecting each of said pump body connecting flanges to the connecting flange of a respective one of said end caps.

16. The housing as recited in claim 15, wherein said ' end sections, said end section connecting flanges and said end cap connecting flanges are circular and concentric to said axis. ' *' / ■h:.: ■ft. - 37 - 212074 r ^ j< i -■i

17. The housing as recited in claim 16, wherein each of said connecting flanges of said pump body includes an annular groove located radially outwardly from said outwardly facing recess, and wherein each of said flanges of each of said end caps includes a mating annular groove/ and including a pair of diaphragms, each one having an enlarged, circular, peripheral bead sealingly locked in a respective one of said mating grooves, each of said diaphragms defining with the respective end section a driving fluid chamber, and with the respective end cap a fluid chamber for fluid to be pumped.

18. The housing as recited in claim 15, wherein each of said check valve cartridges is in sealing contact with each of said pump body and a respective one of said end 'caps.

19. The housing as recited in claim 18, wherein each of said cartridges includes a pair of spaced-apart o-ring seals, and wherein one o-ring seal is in sealing contact with the port in said pump body and the other o-ring is in sealing contact with the port in a respective one of said end caps.

20. The housing as recited in claim 15, wherein said check valve cartridges are identical to each other.

21. The housing for a fluid operated double-acting diaphragm pump as claimed in claim 1, arranged, constructed and adapted to operate substantially as hereinbefore described with reference to any one of the embodiments ' '>KS^s*lown i31 2"i.cfs. 8-12 of the accompanying drawings. \:.o, y *Y t^ixcraaft^eys ' BALDWIN, SON &/CAREY