Diaphragm pump with dual spring overfill limiter

Abstract

A diaphragm pump includes a housing having a pumping chamber containing fluid. The pump has a transfer chamber containing hydraulic fluid, and a hydraulic fluid reservoir in fluid communication with the transfer chamber. The pump housing forms a cylinder with a piston defining a piston inner chamber and sliding in the cylinder. A valve leads to the piston inner chamber with a valve spool slidably mounted in the piston inner chamber to cover the valve and uncover the valve. A diaphragm connects to the valve spool by a plunger. An overfill limiter includes a spacer slidably mounted in the piston inner chamber. A first spring is intermediate the valve spool and the spacer and a second spring is intermediate the end of the piston inner chamber and the spacer, the second spring having a second spring constant greater than the spring constant of the first spring.

Claims

1. A diaphragm pump comprising: a housing having a pumping chamber containing fluid to be pumped; a transfer chamber adapted to contain hydraulic fluid, and a hydraulic fluid reservoir in fluid communication with the transfer chamber; a cylinder; a piston sliding in a reciprocating motion in the cylinder, the piston defining a piston inner chamber, the piston inner chamber having an end; a valve leading to the piston inner chamber; a valve spool slidably mounted in the piston inner chamber, the valve spool covering the valve in a first position and uncovering the valve in a second position; a moveable spacer slidably mounted in the piston inner chamber intermediate the valve spool and the end of the piston inner chamber; a diaphragm connected to the valve spool by a plunger and supported by the housing, the diaphragm defining a pumping chamber side and a transfer chamber side, the pumping chamber side at least partially defining the pumping chamber and the transfer chamber side at least partially defining the transfer chamber; a first spring in the piston inner chamber engaging the valve spool and a first side of the moveable spacer, the first spring having a first spring constant; a second spring in the piston chamber engaging the end of the piston inner chamber and a second side of the moveable spacer, the second spring having a second spring constant greater than the first spring constant.

2. A diaphragm pump according to claim 1, wherein the valve comprises a port in the piston.

3. A diaphragm pump according to claim 1, wherein the first spring is configured so that at dry startup the springs exert pressure of 1 to 4 psi.

4. A diaphragm pump according to claim 1, wherein the plunger comprises a hollow shaft forming a fluid communication path from the reservoir to the transfer chamber.

5. A diaphragm pump according to claim 1, wherein the second spring is configured to exert a pressure less than atmospheric pressure.

6. A diaphragm pump according to claim 1, wherein the diaphragm pump comprises a synchronous pump.

7. A diaphragm pump according to claim 1, further comprising a motor providing power to actuate the piston.

8. A diaphragm pump according to claim 1, wherein the first spring and the second spring are configured so that at dry startup the springs exert pressure of 1 to 4 psi; wherein in normal operation position the springs exert pressure of 2 to 5 psi; and wherein in an over-filled condition, the springs are configured to exert a pressure of 10 to 15 psi.

9. A diaphragm pump comprising: a housing having a pumping chamber containing fluid to be pumped; a transfer chamber adapted to contain hydraulic fluid, and a hydraulic fluid reservoir in fluid communication with the transfer chamber; a cylinder; a piston sliding in a reciprocating motion the cylinder, the piston defining a piston inner chamber, the piston inner chamber having an end; a valve leading to the piston inner chamber; a valve spool slidably mounted in the piston inner chamber, the valve spool covering the valve in a first position and uncovering the valve in a second position; a moveable spacer slidably mounted in the piston inner chamber intermediate the valve spool and the end of the piston inner chamber; a diaphragm connected to the valve spool by a plunger and supported by the housing, the diaphragm defining a pumping chamber side and a transfer chamber side, the pumping chamber side at least partially defining the pumping chamber and the transfer chamber side at least partially defining the transfer chamber; a first spring in the piston inner chamber engaging the valve spool and a first side of the moveable spacer, the first spring having a first spring constant; a second spring in the piston chamber engaging the end of the piston inner chamber and a second side of the moveable spacer, the second spring having a second spring constant greater than the first spring constant; wherein the first spring and the second spring are configured so that at dry startup the springs exert pressure of 1 to 4 psi; wherein in normal operation position the springs exert pressure of 2 to 5 psi; and wherein in an over-filled condition, when the piston is at top dead center, the springs are configured to exert a pressure of 10 to 15 psi.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) Referring now to the drawings, wherein like reference numerals and letters indicate corresponding structure throughout the several views:

(2) FIG. 1 is a side sectional view of a diaphragm pump according to the principles of the present invention in a first position;

(3) FIG. 2 is a side sectional view of a diaphragm pump shown in FIG. 1 in a second position;

(4) FIG. 3 is a side sectional view of a diaphragm pump shown in FIG. 1 in a third position;

(5) FIG. 4 is a side sectional view of a diaphragm pump shown in FIG. 1 in a fourth position; and

(6) FIG. 5 is a graph of pressure versus spring deflection for the overfill assembly of the diaphragm pump shown in FIG. 1.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

(7) Referring now to the drawings and in particular to FIGS. 1-4, there is shown a diaphragm pump, generally designated (10). The diaphragm pump (10) includes a pump housing (12). The housing (12) forms a cylinder (14) that receives a reciprocating piston (16). The diaphragm (18) forms a barrier between the transfer chamber in which oil acts on the diaphragm and a pumping chamber (20) receiving the fluid to be pumped. The diaphragm (18) deflects in a reciprocating manner to pump the fluid.

(8) A plunger (26) extends from a valve spool (30) in the piston (18) and connects to the diaphragm (18). The plunger (26) may be hollow and have holes (28) formed therein that provides for oil flow when replenishment of oil in the transfer chamber is needed. The valve spool (30) moves longitudinally along the direction of travel of the piston (16) within a cavity (34) formed in the interior of the piston (16). A valve port (32) is formed in the side of the piston (16) and is covered by the valve spool (30) to open and close the passage of hydraulic oil under normal operating conditions. The end of the piston (16) includes inlets (52) and ball type check valves (50) that control flow of hydraulic fluid from a hydraulic oil reservoir. The valve spool (30) also includes a first spring (40), a second spring (42) that is stiffer than the first spring (40), and a movable spacer (44) that are configured to function as an overfill limiter.

(9) Referring to FIG. 3, the pump (10) is shown configured at startup without having been primed with hydraulic oil. The piston (16) is at the top dead center position. However, with no hydraulic oil, the diaphragm (18) is forced to the bottom dead center position by the first spring (40). At this position, the valve spool (30) does not cover the valve port (32). The first spring (40) is compressed during installation with the deflection of approximately one inch so that at the startup position, the first spring (40) exerts a small pressure such as for example, 2 psi. The springs (40 and 42) have different spring constants, with the second spring (42) being stiffer and with a higher spring constant than the first spring (40). A typical spring constant for the first spring (40) will result in approximately 10 psi across the diaphragm (18) while the second spring (42) may have a spring constant that produces approximately 100 psi. It can be appreciated that when the first spring (40) is being acted on, deflection of 1.96 inches provides a pressure of 4 psi in the embodiment shown. From a dry startup as shown in FIG. 3, the springs (40 and 42) produce a pressure of between 1-4 psi to assist with priming the pump (10) with hydraulic oil. In the embodiment shown and in the startup configuration of FIG. 3, the first spring (40) is compressed during installation so that the startup pressure is approximately 2 psi.

(10) Referring to FIG. 1, the pump (10) is shown with the piston (16) at the bottom dead center position. In this position, the diaphragm (18) is pulled back into the transfer chamber rather than being deflected outward. At this position, the valve spool (30) covers most of the valve port (32) but does not seal the valve port (32). This is a normal operating position when the pump (10) is primed and working as designed.

(11) Referring to FIG. 2, the piston (16) is at the top dead center position. The diaphragm (18) is deflected outward to act on fluid to be pumped. The valve spool (30) is positioned so that the port (32) is slightly open. This is a normal operating position when the pump (10) is primed and working as designed.

(12) In FIG. 4, the pump (10) is an overfill condition with the piston (16) at top dead center. In such a condition, the valve spool (30) is moved to contact the spacer (44) and completely compresses the first spring (40), which has a lower spring constant. As the first spring (40) cannot be further compressed, the load also compresses the second spring (42). The valve spool (30) is moved at this condition so that the valve port (32) is fully covered by the valve spool (30). It can be appreciated that with the higher spring constant of the second spring (42), normally only a very slight deflection of the second spring (42) is required in order to prevent further overfill. It can be appreciated that the first and second springs (40 and 42) are configured to limit overfill in a very simple configuration without requiring special channels, conduits or other modifications to the piston (16) and/or cylinder (14) as in previous systems. Moreover, the system of the present invention is reliable and relatively inexpensive to manufacture while providing automatic overfill limiting to safeguard against damage to the pump (10).

(13) Referring now to FIG. 5, the pressure and its effect on the springs (40 and 42) can be appreciated. For the embodiment shown, the pump has a piston area of 4.9 square inches, which is an equivalent area of the diaphragm (18). Therefore, the force applied by the diaphragm divided by the equivalent area gives the pressure across the diaphragm (18) according to the formula P=F/A where P is the pressure, F is the force and A is the area. The first spring with a spring constant of 100 psi, when deflected one half inch over 4.9 square inches, would result in a pressure of approximately 10 psi. In normal operation, the springs (40 and 42) produce between 2-5 psi. It can be appreciated that additional pressure stresses the diaphragm (18) and could result in failure. Less pressure makes priming difficult and increases net positive suction head required (NPSH.sub.R). Moreover, it can be seen that in the configuration shown, when the piston (16) is at the overfill position at top dead center and the diaphragm (18) is close to touching the manifold, the pressure is between approximately 10-15 psi. It is preferred to keep the pressure driving hydraulic oil to the chamber at below atmospheric pressure (approximately 14.7 psi at sea level) so that in practice the pump (10) usually produces less than 10 psi vacuum and up to 15 psi is normally acceptable.

(14) It can be appreciated that the present invention provides a reliable diaphragm pump (10) with a simple and reliable overfill limiter. The overfill limiter is simple and reliable and functions automatically. Moreover, the pump (10) requires only simple modifications for the overfill limiting system.

(15) It is to be understood, however, that even though numerous characteristics and advantages of the present invention have been set forth in the foregoing description, together with details of the structure and function of the invention, the disclosure is illustrative only, and changes may be made in detail, especially in matters of shape, size and arrangement of parts within the principles of the invention to the full extent indicated by the broad general meaning of the terms in which the appended claims are expressed.