HK1069618A - Double acting simplex plunger pump with bi-directional valves - Google Patents

Description

Double-acting single-plunger pump with two-way valve

Background

The present invention provides a unique bi-directional fluid valve apparatus having a wide variety of applications, particularly for use with a double acting single piston pump as disclosed in the prior U.S. patent nos. 5,173,039 and 5,183,396, the entire contents of which are incorporated herein by reference. A one-way valve 66 is disclosed in fig. 11 of these two patents, while fig. 4 shows one-way valves 66 and 67, the one-way valves 66 and 67 being reversed to provide the two-way valve function. Check valves 66 and 67 are relatively expensive compared to the unique check valves provided herein.

Disclosure of Invention

The present invention provides an improved reversible check valve for use in a two-way fluid valve apparatus having the following advantages over the check valves 66 and 67 shown in U.S. patents '039 and' 396: the prior art check valve has sufficient utility, but its four parts make it quite expensive, at least twenty times more expensive than the unique check valve taught by the present application, and is further characterized by its incredible simplicity, reversibility, versatility, faster response, efficiency, quiet operation, and adaptability to provide variation in fluid flow rate through a family of valve components, each having a different preselected axial length to vary the axial stroke of the component, thereby adjusting a predetermined flow rate, or varying the flow rate of fluid flowing through the valve.

Broadly, the present invention provides a reversible, bi-directional fluid valve apparatus for use in conjunction with a cap member having a planar manifold-engaging surface and a manifold member having a planar surface. The two components are joined together by the planar surfaces in an abutting relationship. Each member has an identical bore generally perpendicular to the abutting flat surface, the bores being axially aligned, and each member has an identical recess surrounding the respective bore and forming a shoulder having an axial end surface spaced the same preselected distance from the abutting surface. The shoulders have the same preselected transverse dimension. The valve apparatus further includes a valve member having two axial ends with a flat surface on a first of said axial ends, the axial ends having preselected transverse dimensions greater than said preselected transverse dimensions of the shoulders positioned relative to said flat surfaces thereof, said flat surfaces abutting an axial end face of one of said shoulders. The valve member further includes at least two axially extending and circumferentially spaced ribs on a second axial end surface thereof. Each rib has the same preselected axial length and terminates in an end surface. The ribs are positioned so that their end faces are axially aligned with and spaced a preselected distance from the axial end face of the other shoulder. The valve apparatus further includes a hollow coil spring device positioned within the recess aligned with the aperture and having two ends: the first end is sized to engage the other shoulder and the second end of the same size is sized to engage the second axial end of the valve member located on the rib. (not segmented here, next segment follows here) the spring means is chosen such that it biases the flat surface of the valve member against the axial end face of one of the shoulders to provide the function of a shut-off valve. Furthermore, the spring means is selected so as to be compressible under force to allow the valve to travel axially a limited distance to a position in which said end surface of said rib engages with the axial end surface of the other shoulder to provide a predetermined area of function for opening the valve.

To a more limited extent, the above-mentioned valve device is characterized in that the bore, the recess, the shoulder and the valve member all have a circular cross-section, and the spring means are cylindrical with a circular cross-section.

To a more limited extent, this unique valve apparatus can be used in conjunction with a double-acting single-plunger pump apparatus to provide an improved pump.

Drawings

FIG. 1 is a partial cross-sectional view of a portion of a double acting single piston pump;

FIG. 2 is an enlarged view of the unique valve structure shown in FIG. 1;

FIG. 2A is a representation of the one-way valve shown in FIG. 2, wherein the spring 47 has been compressed, i.e., under the force of a fluid, to allow fluid to flow therethrough;

figure 3 is an isometric view of an example of a unique valve component. The figure also shows three mutually perpendicular reference axes: x, Y and Z, respectively, hereinafter sometimes referred to as longitudinal, transverse and vertical;

FIG. 4 is a view of the apparatus shown in FIG. 2 as seen along section line 4-4;

FIG. 5 is a view of the apparatus shown in FIG. 2 as seen along section line 5-5;

FIG. 6 is a view of an alternative configuration of a valve member;

FIG. 7 is a representation of the valve apparatus shown in FIGS. 1 and 2, but with the valve member reversed so as to act as a fluid check valve in a flow direction opposite to that controlled by the apparatus of FIGS. 1 and 2;

FIG. 8 is a side view of the exterior of a complete double acting single piston pump;

FIG. 9 is a view of the first and second integrated combination gasket and cover member as seen along section line 9-9 of FIG. 8;

FIG. 10 is a view of the manifold member as seen along section line 10-10 of FIG. 8;

FIG. 11 is a top view of a preferred embodiment of the valve member of the present invention; and

figure 12 is a side view of the valve member shown in figure 11.

Detailed Description

In fig. 1, reference numeral 10 generally designates a double-acting single-plunger pump including a manifold 12, and first and second integral combinations of a gasket and cover or body member, only one of which 18 is shown in fig. 1. The body 18 has two spaced apart and parallel surfaces 18A and 18B, which serve as a motor end face engagement surface and a pump manifold engagement surface, respectively. A recess 19 is provided in the body 18 for receiving one end of a cylindrical plunger 20, the recess 19 having a circular cross-section and a longitudinal axis between and parallel to the parallel surfaces 18A and 18B.

The plunger is capable of reciprocating along its longitudinal axis by an eccentric comprising a drive shaft 21 from a motor (not shown) and an eccentric 22 housed within an inner race of a bearing 23, the bearing 23 being disposed within a recess 20' in the plunger 20, all as discussed in detail in the above-mentioned patent. A guide sleeve 24 and a gasket 24' are provided to provide guidance, lubrication and sealing for the plunger 20. The guide bush and the packing are held by a sheet metal member 25. The axial end of the longitudinally extending bore 19 is indicated by reference numeral 19 'and the bore 19 is connected to a vertically extending bore 27, the bore 27 extending normal to the surface 18A and terminating at an end 27', best shown in figure 1.

Each body member has a pair of laterally spaced parallel bores, of which only the bore 27 of one of the body members 18 is shown in fig. 1 by way of illustration. Each pair of apertures is hereinafter referred to as a "set" of first and second laterally spaced pump ports; also, each pump port is in connected relation to the recess 19 so that fluid drawn by the reciprocating plunger 20 flows through the pump port, as will be described in more detail below. Fig. 9 shows two similar bodies 118 and 118 ' as an assembly, with four pump ports 127 ' -127 ' (similar to pump port 27) shown in phantom, each of which is covered in this view by a valve member 135 ' -135 ' described below. Fig. 9 thus shows two sets of laterally spaced pump ports that are longitudinally spaced.

The manifold 12 has a longitudinal axis and a bottom planar surface 12A, the bottom planar surface 12A being adapted to be abutted by the pump manifold engagement surface 18A of the cover member. (lower section here) the manifold further comprises first and second laterally spaced manifold inlet/outlet apertures extending longitudinally from the first end to the second end, parallel to the longitudinal or X-axis; one of these inlet/outlet apertures 14 is shown in fig. 1, and reference is made to fig. 5 of the aforementioned U.S. patent 5S183,396, where a pair of similar inlet/outlet apertures 55 and 66 are shown in fig. 5. Referring also to FIG. 10, manifold inlet/outlet apertures 114' and 114 "are shown in FIG. 10. The manifold further includes first and second longitudinally spaced sets of laterally spaced pump ports connecting the manifold inlet/outlet ports to the bottom planar surface of the manifold; only one of the last-mentioned pump ports 50 is shown in fig. 2, but four similar pump ports are shown in fig. 10, wherein the pump ports are designated by the reference numerals 50 '-150'.

Each pump port of the body and the manifold port are surrounded by concentrically positioned annular recesses such as recesses 30 and 45 shown in fig. 2.

Each recess forms an annular shoulder, such as shoulders 31 and 46 of fig. 2. Each annular shoulder has an axial end face (e.g., surface 31 'and surface 46' of fig. 2) spaced a preselected distance from the pump manifold engagement surface 18A and the bottom planar surface 12A, respectively; this preselected size is indicated by the designation "d" in fig. 2A. Furthermore, the shoulders have substantially the same or equal outer diameter, i.e. transverse dimension.

The combination seal and cover member 18 is connected to the manifold member 12 as shown in fig. 1, and the flat bottom surface 12A of the manifold abuts the pump manifold engagement surface 18A of the combination seal and cover member by suitable means such as machine screws 13 in cooperation with threaded means (not shown). The joined components 12 and 18 have vertically (Z-axis) oriented bores surrounding recesses and shoulders that are aligned or aligned in respective axial directions, as shown in fig. 2. For example, when abutted as shown in FIG. 2, recesses 30 and 45 form a combined recess volume for accommodating a valve assembly. Prior to assembly of the manifold 12 with the aforementioned cover components, the unique valve components are positioned as an assembly within the combined recess formed by the assembled components. More specifically, as shown in FIGS. 2-5, the unique valve assembly includes a valve member 35 having a circular cross-section with two axial ends 36 and 39; and a flange 37 having a diameter greater than the outer diameter of the annular shoulder. As shown in FIG. 2, the valve member 35 has a bottom planar surface 36, i.e., a planar surface at its first axial end, and at least two ribs extending axially and circumferentially spaced apart at its second axial end 39. For stability, three ribs are provided in the illustrated embodiment, as best shown in FIG. 3. The above-mentioned flange 37 is shown on the first axial end; inside the flange 37 is a reduced diameter hub or shoulder 38, the reduced diameter being preselected to fit within a coil spring 47 as will be discussed below. Projecting or extending axially from the wheel hub 38 are posts or ribs 40, 41 and 42 circumferentially spaced from one another and terminating in flat surfaces 40 ', 41 ' and 42 ', respectively. These ribs all have the same preselected axial length ending at the above-mentioned end surfaces 40 ', 41 ' and 42 '. When the valve member 35 is positioned within the annular recess, it should be noted that the posts 40-42 are axially aligned (along the Z-axis) with the axial end surface 46' of the shoulder 46 of the manifold 12.

The components 12 and 18 have a suitable gasket or equivalent surrounding each aligned hole, for example, fig. 2 shows a pair of aligned opposed annular recesses 48' and 48 "to form a housing for the annular" 0 "ring 48.

Each pump comprises four identical hollow cylindrical coil springs; one of which 47 is shown in fig. 1 and 2, the springs being respectively seated in said combined annular recesses concentric with the hole. Each spring having two ends sized to fit snugly around the first end of one of the annular shoulders; this is shown in fig. 2, in which a spring 47 is a sliding fit around a shoulder 46 of the manifold 12. The second end of the spring is sized to fit snugly around the spaced ribs 40-42; this is also shown in figure 2 and more particularly slidingly surrounds hub 8 as shown in figure 3.

By way of illustration, the valve arrangement may operate as a one-way valve, and this is the preferred application in the disclosed double-acting single-plunger pump. More specifically, as shown in FIG. 2, the valve member 35 is at rest, sealing the pump port 27 under the pressure in the pump port 50.

Fig. 2A shows the valve 35, as shown, with the valve 35 moving upward away from the surface 31' of the shoulder 31 under sufficiently high pressure in the pump port 27. When this pressure exceeds a preselected level, the spring 47 is then compressed under the applied force of the pressure acting on the lower or first axial end surface 36 of the valve 35. The valve 35 travels upwardly a finite distance YY, as shown in fig. 2, and operation terminates when the valve end faces 40 ', 41' and 42 'abut an axial end face 46' of the shoulder 46. It can be seen that the flow of fluid is out through the pump port 27, and thus radially around all sides of the valve 35, through the coil spring 47 and struts 40-42, and thus upwardly through the pump port 50, as indicated by the letter F and its corresponding arrows.

Thus, broadly speaking, the valve arrangement shown in fig. 1 and 2, etc. acts as a check valve whose operating point is a function of the spring characteristic to compress under a greater pressure applied to the underside 36 of the valve member to permit fluid flow.

The dimensions of the recess and the valve member are important to the operation of the valve to control fluid flow. The first critical dimension is the axial length of the valve, i.e. the distance from the flat surface located on one axial end of the valve to the end face of the rib or strut of the valve; an example of this axial length is indicated by "XX" in FIG. 2A. The second critical dimension is the distance from the abutment surfaces 12A and 18A to the axial end of the shoulder; see label "d" in FIG. 2A. The axial distance between the axial ends 31 'and 46' of the opposing shoulders 31 and 46 is 2d when the parts 12 and 18 are connected as shown. When the valve member having an axial length XX is positioned as shown in fig. 2, a gap or spacing "YY" is formed between the axial end surface of the rib and the axial end surface of the opposing shoulder. Dimension YY thus defines the maximum axial travel for the valve, as shown in fig. 2A; this is important as will be appreciated by those skilled in the art. In an optimal design, "YY" would be selected to provide a desired fluid flow rate; this unnecessary additional axial stroke may cause a reduction in response time without further increase in flow if the actual "YY" is larger than necessary. Thus, the selection of dimension "YY" provides a means for obtaining a precise flow rate, which provides a powerful design tool for valve designers.

Another variable is the fan width of the ribs relative to the circumferential spacing of the ribs; as shown in FIG. 2A, the fluid flow path F flows out of the pump port 27, into the combining recess, across between the coil springs 47, and into the manifold port 50 between the ribs.

Fig. 7 shows how the valve member 35 and its associated spring are reversed from the position shown in fig. 2 and 2A to provide the same check valve function and other functions as previously described, but in the case of reversal.

Fig. 11 and 12 illustrate a preferred form or embodiment of the valve member, wherein the entire valve member is designated 135, and includes a cylindrical valve member having a circular cross-section with a diameter greater than the outer diameter of the annular shoulder. More specifically, the valve member 135 has a flange 137 with a diameter greater than the outer diameter of the shoulder, such as shoulder 31 and first axial end 136. Annular shoulder 138 has a preselected outer diameter 138D that is preselected to be a snug fit within coil spring 47. The annular shoulder 138 has a limited axial length, and the annular shoulder 138 acts as a support for at least two axially extending and circumferentially spaced ribs; three ribs 140, 141 and 142 are shown. The second axial end 139 of the valve 135 is shown in fig. 11. Ribs 140 and 142 each have the same preselected axial length and terminate at end surface 145. The diameter of the annular shoulder 135 and the diameter of the circumferentially spaced ribs 140 and 142 are selected to be substantially the same as the axial end surface of the shoulder, such as the shoulder surface 31' shown in FIG. 2.

The pump cap, manifold and valves 35 and 135 may be made of any suitable material, such as plastic or metal.

In FIG. 9, four preferred valve members 135 are shown in place in the bodies 118 and 118 ', designated by reference numerals 135 ', 135 ", 135 '" and 135 "", respectively. More specifically, at the right end of the apparatus shown in FIG. 9, the valve 135 'is positioned with the flat surface 136' exposed to the viewer, and the laterally spaced valve 135 '"associated therewith is positioned so that the rib or post and the second axial surface 139' face the viewer.

Also at the left end of the apparatus shown in fig. 9, the valve 135 "is positioned with the flat surface 136" exposed to the audience, and the laterally spaced valves 135 "" associated therewith are positioned so that the ribs or posts and the second axial surface 139 "face the audience.

Figure 10 shows the flat bottom surface of the manifold as viewed along section line 10-10 of figure 8. First and second laterally spaced manifold inlet/outlet apertures 114' and 114 "are shown in phantom extending longitudinally from a first end to a second end and parallel to the longitudinal axis X. A first set of laterally spaced pumping ports 150 'and 150' "is shown at the right end of the drawing and a second set of laterally spaced pumping ports 150" and 150 "" is shown at the left end of the drawing. Thus, for the manifold, FIG. 10 shows first and second sets of laterally spaced pump ports that connect the manifold inlet/outlet ports to the planar bottom surface. Each pump port of the body and the manifold port are concentrically positioned by an annular recess. Thus, for the manifold, the recesses are respectively designated by reference numerals 140 '-145 "", which in turn respectively form shoulders 146' -146 "".

Illustratively, the pump ports 150' -150 "" are positioned so as to be precisely aligned with the valves and pump ports depicted in the body of FIG. 9.

Fig. 6 shows another alternative construction of the valve member, which can be used in the devices shown in fig. 8-10. In addition, the cover member 218 has a flat surface adapted to abut the flat surface of the manifold member 212. The cover member has a recess 60 and the manifold member has a recess 70 concentric with the pump ports 227 and 250, respectively, and defining shoulders 61 and 71, respectively, with opposite axial surfaces 62 and 72 of the shoulders 61 and 71, respectively, being curved to match the curvature of one axial end 81 of the valve member 80, which valve member 80 may be made of a suitable material such as plastic or rubber. In the cross-sectional view of fig. 6, a valve 80 is shown having a curved surface 81 as previously described for abutting the curved axial end surface of shoulder 61 as shown in fig. 6, (or curved surface 72 if the device is inverted). Valve member 80 also has an axially extending annular shoulder 81 ', annular shoulder 81' being formed by annular groove 82 to provide a seat for one end of spring 147. Spring 147 is shown as a coil spring with one end seated in annular recess 82 and the other end abutting an axial end or bottom of recess 70, as shown in fig. 6. As shown in FIG. 6, valve 80 is moved upwardly so that spring 147 is compressed by the fluid pressure applied to surface 81 of valve 80, thereby providing a clearance or flow space for fluid to flow upwardly through pump port 227 as shown, from there around valve member 80, through coil spring 147 to flow outwardly through pump port 250. The upward travel of the valve 80 is limited by one or more axially extending struts 84, the struts 84 extending axially from a base line 83 located on the valve 80 and having ends abutting the curved valve seating surfaces 72 and 62.

In summary, the present invention provides a unique reversible valve member that can be combined with the same apertures, recesses, shoulders, and shoulder axial end faces described above. The biasing and centering spring has a dual function: they simultaneously act as spring retainers allowing the valve to run axially a limited amount while retaining or stabilizing the valve against running in the transverse (X and Y axes). In addition, the spring is preselected to have a desired stiffness so as to compress to achieve the aforementioned axial travel at a preselected pressure in the bore adjacent the valve.

The annular shoulder is also multi-functional. While one opposing shoulder serves as a seat (retainer) for one end of the coil spring, the other opposing shoulder serves as a valve seat. Further, the axial end face of the shoulder serves to limit the amount of axial travel of the valve to the dimension YY, taking into account the given axial length XX of the valve, and the overall axial dimension 2d between the opposing axial end faces of the opposing shoulder.

Illustratively, the minimum number of ribs or struts located on the valve member is two; while the preferred embodiment of the invention shown in the drawings comprises three struts or ribs spaced apart at approximately equal distances along the circumference; this provides stability in valve operation. Of course, more than three ribs may be used; this would be within the scope of the present invention.

While the preferred embodiments of the invention have been illustrated, it will be appreciated by those skilled in the art that changes could be made without departing from the inventive concept. Accordingly, the invention is to be limited only by the scope of the following claims.

Claims (12)

1. A bi-directional fluid valve apparatus comprising the following:

a. a cover member having a flat manifold engaging surface;

b. a manifold member having a planar surface with which said manifold member is connected in abutting relation to said cover member, each of said members having an aperture generally perpendicular to said abutting planar surface, said apertures being axially aligned, and each of said members having a recessed portion surrounding the respective aperture, and each of said members forming a shoulder having an axial end surface spaced from said abutting surface by the same preselected distance, said annular shoulders having generally equal preselected transverse dimensions;

c. a valve member having two axial ends with a flat surface on a first of said axial ends, the axial ends having a preselected transverse dimension greater than said preselected transverse dimension of said shoulders, said shoulders being positioned relative to said flat surfaces, said flat surfaces abutting said axial end surface of one of said shoulders; and at least two axially extending and circumferentially spaced ribs on a second axial end face, each of said ribs having the same preselected axial length and terminating in a distal end surface, said ribs being positioned such that said end faces are axially aligned with and spaced a preselected distance from said axial end face of the other of said shoulders; and

d. a hollow coil spring device mounted in said recess in alignment with said aperture and having two ends: the first end being dimensioned to engage said other shoulder and the second end being dimensioned to engage said at least two circumferentially spaced ribs and said second axial end of said valve member, said spring means being selected such that it will bias said flat surface of said valve member (i) towards said axial end surface of one of said shoulders to provide the function of closing the valve, and (ii) compress under force to allow said valve member to travel axially a limited distance to a position where said end surface of said rib engages the axial end surface of said other shoulder to provide the function of opening the valve.

2. A valve apparatus according to claim 1, further characterized in that said bore, recess, shoulder and valve member are of circular cross-section and said spring means is cylindrical with a circular cross-section.

3. The valve apparatus of claim 1, wherein said spring means maintains and stabilizes said valve member against lateral movement.

4. A bi-directional fluid valve apparatus incorporating:

a cover member having a flat manifold engaging surface; and

manifold members having a planar surface with which said manifold members are connected in abutting relation to said cover members, each of said members having an aperture generally perpendicular to said joining planar surface, said apertures being axially aligned, and each of said members having a recessed portion surrounding the respective aperture, and each of said members forming a shoulder having an axial end surface spaced a same preselected distance from said abutting surface, said annular shoulders having generally equal preselected transverse dimensions; the valve apparatus includes:

a. a valve member having two axial ends, a flat surface on a first of said axial ends, an axial end having a preselected transverse dimension greater than said preselected transverse dimension of said shoulders, said shoulders being positioned relative to said flat surfaces, said flat surfaces abutting said axial end surface of one of said shoulders, at least two axially extending and circumferentially spaced ribs on a second of said axial end surfaces, each of said ribs having the same preselected axial length and terminating in an end surface, said ribs being positioned such that said end surfaces are axially aligned with and spaced a preselected distance from said axial end surface of the other of said shoulders; and

b. a hollow coil spring device positioned within said recess aligned with said aperture and having two ends: the first end being dimensioned to engage said other shoulder and the second end being dimensioned to engage said at least two circumferentially spaced ribs and said second axial end of said valve member, said spring means being selected such that it will bias said flat surface of said valve member (i) towards said axial end surface of one of said shoulders to provide the function of closing the valve and (ii) compress under force to allow axial travel of said valve member away from the axial end surface of one of said shoulders to provide the function of opening the valve.

5. A valve arrangement according to claim 4, further characterized in that said bore, recess, shoulder and valve member are of circular cross-section and said spring means is cylindrical with a circular cross-section.

6. A valve arrangement according to claim 5, wherein said preselected distance between said terminal end surface of said rib and said axial end surface of said other shoulder is selected to limit said axial travel of said valve member to obtain an optimum flow rate while minimizing the axial travel range of said valve member.

7. The valve apparatus of claim 4, wherein said spring means maintains and stabilizes said valve member against lateral movement.

8. A double acting single piston pump comprising the following parts:

a. a combined gasket and cover member having a flat manifold-engaging surface;

b a manifold member having a planar surface with which said manifold member is connected in abutting relation to said seal gasket and cover member, each of said members having a circular bore which is generally perpendicular to said abutting planar surface, said bores being axially aligned, and each of said members having an annular recess concentrically disposed with the respective bore, and each of said members forming an annular shoulder having an axial end face which is spaced the same preselected distance from said abutting surface, said annular shoulders having generally equal preselected outer diameters;

c. a cylindrical poppet valve member having a flat surface at a first axial end thereof and a preselected diameter greater than the outer diameter of said annular lands, said lands being positioned relative to said flat surfaces, said flat surfaces abutting said axial end surface of one of said lands, at least two axially extending and circumferentially spaced ribs on a second axial end surface, each of said ribs having the same preselected axial length and terminating in an end surface, and said ribs being positioned such that said flat end surface is axially aligned with and spaced a preselected distance from said axial end surface of the other annular land; and

d. a hollow coil spring device positioned within said recess concentrically disposed with said bore and having two ends: the first end is dimensioned for a snug fit around said other annular shoulder and the second end is dimensioned for a snug fit around said at least two circumferentially spaced ribs and for engagement with said second axial end of said poppet member, said spring means being selected such that it will bias said flat surface of said poppet member (i) against said axial end surface of one of said annular shoulders to provide the function of closing the valve and (ii) compress under force to allow said poppet member to travel axially a limited distance to a position where said flat end surface of said rib engages with the axial end surface of said other annular shoulder to provide the function of opening the valve.

9. A double acting single piston pump comprising the following parts:

a. first and second integrated combination gaskets and cover members, each of said members comprising: (i) a unitary body having two spaced parallel surfaces for respectively serving as a motor end face engaging surface and a pump manifold engaging surface, (ii) a recess in said body for receiving a cylindrical plunger, said recess having a circular cross-section and a longitudinal axis between and parallel to said spaced parallel surfaces, (iii) a set of first and second laterally spaced pump ports in said body, each pump port extending from said pump manifold engaging surface into said body and in connected relation to said plunger receiving recess;

b. a manifold having: a longitudinal axis; a bottom planar surface adapted to be abutted by the pump manifold engagement surface; first and second laterally spaced manifold inlet/outlet apertures extending longitudinally from a first end to a second end and parallel to said longitudinal axis; and first and second laterally spaced sets of circumferentially spaced pump ports connecting said manifold inlet/outlet port to said bottom planar surface, said pump port and said manifold port of each said body being surrounded by a concentrically positioned annular recess forming an annular shoulder having an axial end face spaced a preselected distance from said pump manifold engaging surface and said planar surface, respectively, and said annular shoulders having substantially equal outer diameters;

c. connecting means connecting said component to said manifold such that said bottom planar surface abuts said pump manifold engaging surface of said component and said two sets of first and second pump ports of said component, said surrounding recesses being aligned with said first and second sets of longitudinally spaced pump ports and said surrounding recesses in said manifold, respectively;

d. four identical cylindrical valve members, each having: a circular cross-section having a diameter greater than the outer diameter of the annular shoulder; a flat surface at a first axial end thereof; and at least two axially extending and circumferentially spaced ribs on a second axial end thereof, each of said ribs having the same preselected axial length and terminating in an end face, said valve members being positioned in said annular recesses respectively so that said flat surfaces of two of said four valves abut said axial end faces of said annular lands in said manifold and so that said flat surfaces of the other two of said valves abut said axial surfaces of said annular lands in said members, said end faces of said ribs being aligned with and spaced a preselected distance from said axial end faces of said adjacent annular lands;

e. four hollow cylindrical coil spring means respectively positioned within said annular recesses concentrically disposed with said bore, each coil spring having two ends: the first end being sized to be a snug fit around one of said annular shoulders and the second end being sized to be a snug fit around at least two circumferentially spaced ribs and engaging said second axial end of said valve member, said spring means having preselected characteristics so as to bias said flat surface against the adjacent axial end surface of said shoulder to provide the function of closing the valve and so as to permit said valve member to axially travel a limited distance under force to a position where said end surface of said rib engages the adjacent axial end surface of said shoulder to provide the function of opening the valve.

10. A bi-directional fluid valve apparatus comprising the following:

a. a cover member having a flat manifold engaging surface;

b. a manifold member having a planar surface with which said manifold member is connected in abutting relation to said cover member, each of said members having an aperture generally perpendicular to said abutting planar surface, said apertures being axially aligned, and each of said members having a recessed portion surrounding the respective aperture, and each of said members being shaped as a shoulder having a preselected curved axial end surface spaced apart from said abutting surface by the same preselected distance, said annular shoulders having generally equal preselected transverse dimensions;

c. a valve member having two axial ends with a preselected curved surface on a first of said axial ends, the axial ends having a preselected transverse dimension greater than said preselected transverse dimension of said shoulders, said shoulders being positioned relative to said curved surfaces, said curved surfaces abutting said axial end surface of one of said shoulders; and at least two axially extending and circumferentially spaced ribs on a second axial end face, each of said ribs having the same preselected axial length and terminating in a distal end surface, said ribs being positioned such that said end faces are axially aligned with and spaced a preselected distance from said axial end face of the other of said shoulders; and

d. a hollow coil spring device disposed within said recess aligned with said aperture and having two ends: the first end being dimensioned to engage said other of said shoulders and the second end being dimensioned to engage said intermediate annular recess, said spring means being of such nature that it will (i) bias said valve member towards said axial end face of one of said shoulders to provide the function of closing the valve and (ii) compress under force to allow said valve member to travel axially a limited distance to provide the function of opening the valve.

11. A valve apparatus according to claim 10, further characterized in that said bore, recess, shoulder and valve member are of circular cross-section and said spring means is cylindrical with a circular cross-section.

12. The valve apparatus of claim 10, wherein said spring means maintains and stabilizes said valve member against lateral movement.