JP4530988B2 - Membrane pump - Google Patents

Description

  The present invention relates generally to an improved membrane pump, and more particularly, under conditions such that the hydraulic fluid side of the membrane is primed and the membrane pump chamber side is at a relatively high vacuum, or the hydraulic fluid side of the membrane is not primed. Relates to an improved membrane pump for use in

  Known membrane pumps that are driven and rotated by hydraulic pressure are high-pressure pumps that are capable of pumping many difficult fluids by nature because there are no sliding pistons or seals to wear in the process fluid. The membrane completely isolates the pump from the surrounding environment (process fluid) and protects the pump against contamination.

  A typical membrane pump 20 is shown in FIG. The pump 20 includes a drive shaft 22 that is rigidly supported on the pump housing 24 by a small bearing (not shown) and a rear end by a large tapered roller bearing. A fixed angle cam or wobble plate 28 is sandwiched between another pair of large bearings (not shown). When the drive shaft rotates, the wobble plate swings back and forth, converting the motion around the shaft into linear motion. Three piston assemblies (only one piston assembly is shown) are displaced alternately by the wobble plate 28. As will be shown later, each piston is accommodated in a cover including a cylinder filled with hydraulic oil. The ball check valve 32 in the bottom of the piston / cylinder assembly 30 operates to fill the cover with hydraulic oil from the oil tank 27 (the wobble plate 28 is in the oil tank) during the intake stroke. In the discharge or pumping stroke, the hydraulic oil in the cover presses the rear side of the membrane 34, deflects the membrane forward as the wobble plate moves, and performs a pumping operation. The pump ideally hydraulically balances the pressure across the membrane over the entire design pressure range. This is not true under all circumstances in the known pumps as will be described later. Regardless, each membrane has its own pumping chamber with inlet and outlet check valve assemblies 36, 37 (see also FIG. 2). As the membrane retracts, process fluid enters the pump through one of the inlet check valves via a common inlet. In the discharge or pumping stroke, the membrane discharges process fluid through the common outlet of the manifold via an outlet check valve. Membranes spaced equidistant from each other at 120 ° operate in sequence to provide a constant, substantially pulse-free flow of process fluid.

  More specifically, FIG. 2 shows a part of the membrane pump 20. The membrane 34 is sandwiched between the two portions 38, 30 of the housing 24. The membrane 34 separates the drive side filled with pump hydraulic oil from the pump chamber side. On the drive side, a drive piston assembly 30 including a membrane plunger 42 is accommodated in a cover that is filled with hydraulic oil and functions as a transport chamber 44. A plurality of check valves 32 in the piston 46 separate the transport chamber 44 from an oil tank (not shown). The wobble plate 28 (not shown in FIG. 2) contacts the pad 48 and drives the piston 46. Arrow 49 generally indicates the direction of motion of the cam or wobble plate. When the piston and membrane finish the forward or pumping stroke, the end 50 of the piston 46 is located at top dead center (TDC). When the piston and membrane finish the return or suction stroke, the end 50 of the piston 46 is located at the bottom dead center (BDC).

  The piston 46 reciprocates in the cylinder 47. The piston 46 has a sleeve portion 52 that forms the outer wall of the piston. The sleeve portion 52 includes a sleeve 54 and an end portion 56 having a pad 48 that abuts against the wobble plate. The sleeve 54 accommodates the base portion 58. The base portion 58 includes a first base 60 that abuts against the end portion 56, and a sealing element 62 that seals between the first base 60 and the sleeve 54. The base portion 58 includes a second base 64 at an end opposite to the first base 60. The connecting wall 66 connects the first base 60 and the second base 63. The piston return spring 68 is a coil spring that extends between the first base 60 and the membrane stopper 70 that is a part of the pump housing 24. The valve housing 72 is accommodated in the base portion 58 and extends between the second base 64 and the end portion 56. The seal 74 seals between the valve housing 72 and the connection wall 66 near the second base 64.

  The end portion 56 and the opposite end portion 76 of the sleeve portion 52 are open. Similarly, the end 78 of the valve housing 72 is open. The second base 64 has an opening 80 for receiving the stem 82 of the plunger 42.

  The membrane plunger 42 has a valve spool 84 fitted to the valve housing 72, and a stem 82 extends from the valve spool 84 through the opening 80 to the head 86 on the transport chamber side of the membrane 34. The base plate 88 is on the pump chamber side of the membrane 34 and holds the membrane by screwing the membrane 90 to the head 86 and the hollow portion 92 of the plunger 42 with screws 90. The hollow portion 92 extends in the axial direction from one end of the plunger 42 to the other end. Screw 90 is threaded through the end of the membrane. The piston end of the hollow portion 92 is open. A plurality of openings 94 extending in the radial direction are provided in the stem 82. The bias spring 96 is a coil spring and extends between the second base 64 and the valve spool 84. The groove 100 extends in the connecting wall 66 from the farthest travel of the valve port 98 to the end 56. The check valve 102 is formed in the passage 104 of the end portion 56 communicating with an oil tank (not shown). Accordingly, the oil tank (not shown) passes through the passage 104 and the check valve 102 and communicates with the valve port 98 through the groove 100. When the valve is opened, further communication occurs through the space in which the coil spring 96 resides and one of the plurality of radial openings 94 and through the axial hollow 92 of the plunger 42. In addition, communication from the hollow portion 92 to various portions of the transport chamber 44 occurs through other radial openings 94. The hollow passage 92, along with the radial opening 94, provides communication from the portion of the transport chamber 44 near the membrane 34 to the portion of the transport chamber 44 in the valve housing 72 of the piston 30. The transport chamber includes a space occupied by the piston return spring 68.

  On the pump chamber side of the membrane 34 is an inlet check valve assembly 36 that opens when a vacuum is created in the pump chamber 106 during the suction stroke. There is also a check valve 37 that opens when pressure is generated in the pump chamber 106 during the pumping or discharge stroke.

3A-F illustrate the operation of the conventional pump 20 under normal standard operating conditions using a conventional bias spring. Representative vector directions of cams or wobble plates (not shown in FIGS. 3A-F) are shown. Inhalation is less than 101kPa (absolute pressure) . The discharge pressure is 101 kPa or more. The pressure difference before and after the membrane 34 is set to approximately 20.7 kPa .

Referring to FIG. 3A, the suction stroke begins at the end of the pumping stroke. As a condition, it is assumed that the pressure in the pump chamber decreases immediately from a high pressure, for example, 827 kPa, to 68.9 kPa . The pressure of the hydraulic oil in the transport chamber is 89.6 kPa, which is lower than 101 kPa in the oil tank. The piston 30 is at the top dead center and starts moving toward the bottom dead center. The bias spring 96 immediately moves the plunger 42, particularly the valve spool 84, to the right to open the port 98. Since the pressure in the transport chamber is smaller than the pressure in the oil tank, the check valve 32 opens, the hydraulic oil flows from the oil tank into the transport chamber, and the hydraulic oil lost in the previous pumping stroke is properly applied to the transport chamber. Meet. That is, the hydraulic oil flows out of the transport chamber into the oil tank through the somewhat loose piston dimensional tolerance due to the pressure of the pumping stroke. Therefore, the transport chamber is refilled with hydraulic fluid in the suction stroke so that there is sufficient hydraulic fluid to be able to supply pressure efficiently in the next pumping stroke.

FIG. 3B shows a state in the intermediate stroke. When process fluid is slightly drawn into the pump chamber ( indicated at 68.9 kPa ), the membrane 34 and spool 84 remain in the left position while the piston 30 moves to the right and the port 98 is closed. As the pressure is approximately the same and the membrane 34 moves to the right along with the piston 30, the pump chamber is filled with process fluid.

  As shown in FIG. 3C, the process fluid continues to fill the pump chamber as the membrane 34 moves to the right. The valve port 98 remains closed. Since the pressure is substantially the same, there is very little leakage of hydraulic oil from the oil tank (not shown) to the transport chamber 44. Thus, both sides of the membrane are properly filled.

When the piston 30 reaches bottom dead center, the suction stroke is completed, and the discharge or pumping stroke is started as shown in FIG. 3D. The pressure in the transport chamber immediately increases, for example from 89.6 kPa to 848 kPa . Similarly, the pressure in the pump chamber immediately increases, for example from 68.9 kPa to 827 kPa . The wobble plate begins to move the piston 30 to the left, creating pressure. The check valve 32 is closed. The membrane 34 moves greatly in cooperation with the hydraulic oil, and the process fluid remaining with the piston pushes out (pumps) the process fluid.

  In the intermediate stroke shown in FIG. 3E, the discharge continues. Hydraulic fluid leakage through dimensional tolerances between the piston and cylinder may cause the valve spool 84 of the membrane plunger 42 to move to the right and open the valve port 98. However, as long as the check valve 32 is closed and there is no leakage, the hydraulic oil is trapped in the transport chamber.

  The discharge stroke ends in the state shown in FIG. 3F. The filled transport chamber 44 pushes the membrane 34 to the left and the membrane moves to distribute the process fluid. The normal operation shown in FIGS. 3A-F causes little stress on the membrane 34.

  However, a problem with conventional membrane pumps is that the membrane breaks unexpectedly under certain operating conditions. The membrane breaks earlier or more often than usual and can break earlier than other pump members. The membrane breakage contaminates the process fluid line with hydraulic fluid. The operating condition that causes the most damage is high vacuum suction with a corresponding low discharge pressure. This is expected to occur in typical pumping systems when the suction filter begins to clog. In this case, clogging of the filter requires a high vacuum to draw process fluid through the filter. At the same time, the discharge pressure is reduced because the volume of the pumped process fluid is reduced. This means that the high vacuum on the pump chamber side reduces the pressure at the suction on the transport chamber side, and the transport chamber essentially “requires more hydraulic oil filling”, resulting in The inflowing hydraulic fluid overfills the transport chamber and creates a situation where the overfill does not have a corresponding high pressure to balance the pressure in the pumping or discharge stroke and push out the hydraulic fluid. The overfilling of the hydraulic fluid “swells” and breaks the membrane until it hits the process fluid valve port. In addition, in a high-speed, reversing vacuum / pressure pump such as this device, a high-speed valve closure results in a huge pressure spike called the Jaukowski shock. This spike can consist of fluid pressure waves or sonic waves and harmonics of both waves. These pressure spikes “require” the inflow of hydraulic fluid into the drive piston when it should not occur. This again causes overfilling and leads to breakage of the membrane. 4A-F show the overfill failure mode.

The inhalation stroke begins in FIG. 4A. Since it is assumed that the process fluid inlet is clogged, only a low pressure is generated in the discharge stroke. That is, the pressure in the pump chamber 106 decreases from 96.5 kPa to 68.9 kPa , for example, as shown in FIG. 3A. However, the suction rapidly increases the vacuum, and the pressure in the pump chamber 106 further decreases to, for example, 20.7 kPa , as shown in FIG. 4B. The membrane 34 and plunger 42 are far to the left and close the valve port 98 and the bias spring 96 is somewhat compressed. There is only a temporary inflow of hydraulic oil through the various passages of check valve 32, valve port 98 and stem 82.

In the inhalation intermediate stroke shown in FIG. 4B, if the membrane moves even a little to the right, the vacuum in the pump chamber 106 increases and tries to keep the membrane 34 and plunger 42 in the left position while the piston 46 moves to the right. To do. Although the valve port 98 is closed, a low pressure of 41.4 kPa , for example, still occurs in the transport chamber 44, and hydraulic fluid leaks from the oil tank (not shown) to the transport chamber 44 due to the dimensional tolerance of the system. The weak bias spring 96 of the conventional membrane pump keeps the plunger 42, especially the valve spool 84, far left, creating and sustaining a low pressure in the transport chamber 44.

  As shown in FIG. 4C, at the end of the inhalation stroke, the plunger 42 and membrane 34 remain far left and the low pressure in the transport chamber 44 continues to leak and after such a stroke is repeated many times, The transport chamber 44 is overfilled with hydraulic oil before starting the discharge stroke.

  The state at the start of the discharge stroke is shown in FIG. 4D. The piston 46 begins to move to the left. Since the pressure in the pump chamber 106 is low, the pressure in the transport chamber 44 does not rise until later in the discharge stroke.

As shown in the intermediate stroke of FIG. 4E, the overfilled transport chamber 44 moves the membrane 34 and valve spool 84 simultaneously to the left. As the base plate 88 and membrane 34 approach the pump chamber wall 108 of the pump, the pressure in the transport chamber 44 eventually rises. Since the time when the pressure is larger than 101 kPa, which is the pressure in the oil tank, is short, it is not sufficient to cause the hydraulic oil to leak from the transport chamber 44 to the oil tank and to balance the leakage flow in the suction stroke. Therefore, the membrane 34 bends due to overfilling of the hydraulic oil in the transport chamber 44. The weak bias spring 96 is compressed.

  The end of the discharge stroke is shown in FIG. 4F. The overfilled transport chamber 44 causes the base plate 88 to fully abut the wall 108 and the membrane 34 extends and abuts the port of the outlet check valve assembly 37. The rapid pressure rise in the transport chamber 44 at this point causes the membrane 34 to cut or rupture at the various surfaces that abut. The pump is destroyed at this time. As a result, contamination from the process fluid remains in the piston assembly 30, and contamination from the hydraulic oil remains in the process fluid line.

Thus, when a high vacuum (ie, filter clogging or inlet valve blockage) occurs on the membrane pump chamber side, the membrane does not move with the piston. This usually does not cause a problem because the valve spool 84 and the valve port 98 are closed. However, if this condition continues for a long time, the leakage between the piston and the housing combined with the leakage between the valve spool and the valve port results in overfilling in the transport chamber. In the discharge stroke, the pressure must be high enough to re-discharge the leak volume. However, since the ball check valve 32 prevents any outflow through the valve port, the discharge is limited to the piston and the housing. Since the pump inlet is closed and cannot suck in a large volume of process fluid, the pressure when discharging the process fluid is low or only part of the discharge stroke. It is empirically known that the discharge pressure must be 689 kPa or higher in order to “leak as much as inflow”. If the pump is not able to leak hydraulic oil as much as it leaks into the transport chamber, the increased volume is energized by the drive piston, causing the membrane to swell and break against the port or notch.

  The conventional pump 20 has the problem that the valve spool 84 sticks to the edge, particularly the edge of the opening of the valve port 98. In such a case, the membrane 34 tends to wrap around the base plate 88, thereby stressing or clamping the membrane material.

  The conventional pump 20 further has a volumetric efficiency problem. This occurs because there is no bypass passage that leaks hydraulic oil (and air) large enough to expel air from the transport chamber around the piston. In this case, the more air is stored in the transport chamber, the lower the volumetric efficiency. This decrease in volumetric efficiency occurs because the piston repeatedly compresses and depressurizes excess air trapped in the transport chamber. In that case, the compression of air changes the membrane stroke from a pure sine wave state to an almost rectangular wave state, causing increasingly severe pressure pulses. The immediate result is increased pressure fluctuations at the pump outlet and undesirable characteristics of the membrane pump.

  The present invention relates to a membrane pump that receives a driving force from an electric motor. This pump has a pump chamber for storing a fluid (process fluid) to be pumped, a transport chamber for storing hydraulic oil, and a casing for storing an oil tank. The pump has a membrane having a transport chamber side and a pump chamber side. The membrane is supported by the casing so as to be positioned between the pump chamber and the transport chamber, and reciprocates so as to contact and separate from the pump chamber. The pump has a piston in the cylinder of the casing that reciprocates the membrane between the discharge stroke and the suction stroke.

  The cylinder forms part of the transport chamber. When the cylinder is positioned to be generally horizontal and have an upper surface, the piston moves longitudinally with the cylinder within the cylinder. The wobble plate and the first spring cooperate to reciprocate the piston. The wobble plate is driven by a motor. The first spring can be compressed between the housing and the piston. The second spring connects its first end to the membrane and is supported by a piston that moves together with its second end to urge the membrane away from the pump chamber. A communication path for hydraulic oil is formed between the oil tank and the transport chamber. When the valve in the fluid communication path is opened, the hydraulic oil selectively moves back and forth between the oil tank and the transport chamber. A vent is formed on the upper surface of the cylinder. Thus, the air in the transport chamber is discharged to the outside through the vent of the cylinder, and as a result, the quality of the hydraulic oil remaining in the transport chamber is improved, and the pump self-primes.

  Thus, the present invention discloses a novel membrane pump that “blops” a small amount of trapped air and hydraulic fluid through the vents of each cylinder of the pump. This pump blows out only at the time when a large impact pressure does not occur in the stroke. The presence of only incompressible hydraulic fluid in the cylinder provides a “reliable” displacement and enhances pump hydraulic fluid metering, volumetric efficiency, and discharge pressure stability, respectively. Air removal prevents problems including the inability to self-prime due to trapped and accumulated air. This pump simplifies final assembly, final testing and user operation. The present invention maintains the biased hydraulic fluid drive described in US Pat. No. 3,775,030. However, the present invention discloses the use of a strong bias spring. Thus, in a high vacuum state, the bias spring maintains the hydraulic oil pressure above its vapor pressure, thereby preventing hydraulic oil cavitation, and the bias spring overcomes the suction force of the pump chamber and enters the transport chamber. Prevent overfilling of hydraulic fluid (thus, the membrane will not break).

  Thus, the improvements disclosed herein optimize the durability and efficiency of the membrane pump.

  The present invention relates to an improvement of the above-described conventional membrane pump. The same members are denoted by the same reference numerals as in the conventional example. The improved members will be described separately. The improved component is believed to provide a synergistic improvement in pump performance and durability.

  Referring to FIG. 5, the present invention is embodied in a pump 110. The housing 112 includes portions 38 and 114 similar to the portions 38 and 40 of the housing 24. The portion 114 has a vent consisting of a groove 116 formed in the surface of the upper portion 118 of the cylinder 120 similar to the cylinder 47. The groove 116 communicates with the transport chamber 44 and an oil tank (not shown). The groove 116 is shown to extend from beyond the right end of the piston 46 in the cylinder 120 when the piston 46 moves to the right end, ie, when the base plate 88 abuts the wall 122 of the housing portion 38. In a preferred embodiment, the piston extends beyond the point where it travels half a stroke. Thus, the piston “closes” the channel in the second half of the discharge stroke and the first half of the suction stroke. The groove opens just before the midpoint of the suction stroke, discharges air and hydraulic oil, and continues to open until just after the midpoint of the discharge stroke. Experience has proven that this provides the required easy priming while minimizing leakage. The groove 116 extends to the left towards the end 124 of the housing portion 114 and opens into the oil tank at this end.

  It should further be noted that the pump 110 has a significantly stronger bias spring 126. The extremely strong bias spring and groove 116 combination substantially eliminates membrane damage and reduces air in the hydraulic fluid in the transport chamber 44 when high vacuum conditions are created on the membrane's pump chamber side. Therefore, the pump 110 can be self-priming.

  A first embodiment of the present invention is shown in FIG. The pump 127 has a groove 128 similar to the groove 116 except that the groove 128 does not extend to the end 124 over its entire length. Rather, a radial passage 130 in the housing portion 114 extends from the groove 128 near the end 124 to the O-ring groove 132. The O-ring 134 is disposed in the groove 132.

  The O-ring 134 in the groove 132 functions as a check valve. When the inside of the transport chamber 44 is at a sufficient pressure, this pressure always lifts the O-ring 134 slightly from the passage 130 and releases air / working oil to an oil tank (not shown). In this embodiment, unlike the bi-directional flow through the groove 116 of the pump 110, the hydraulic oil only flows in one direction through the groove 128, the passage 130, the check valve of the O-ring 134, and the groove 132.

  A second embodiment of the present invention is shown in FIG. The pump 129 has a passage 131 extending from the upper part 118 of the cylinder 120. The passage 131 extends through the wall 133 of the portion 135 of the housing 137. The passage 131 communicates the transport chamber 44 and the oil tank. The passage 131 preferably extends vertically in the radial direction. The passage 131 is preferably located beyond the midpoint of the forward stroke of the piston 46. Thus, the piston 46 “closes” the passageway during the second half of the discharge stroke and the first half of the suction stroke. The passage starts to open just before the midpoint of the suction stroke and continues to open until just after the midpoint of the discharge stroke to release air and hydraulic oil. Thus, the passage 131 functions similarly to the groove 116.

Other features of the invention associated with all embodiments are shown in FIG. The valve housing 136 has a circumferential groove 138 at an axial position that intersects the valve port 140. Without this circumferential groove 138, a burr (edge) may be created when creating the radial valve port opening. If there is a flash, the valve spool 84 is caught by this flash and sticks. In that case, the membrane 34 is wound around the base plate 88 and receives stress or is tightened. By making the circumferential groove 138 , the possibility of such a flash is eliminated.

  The operation of the design configuration in which the pump of the present invention has a strong bias spring differentiated from the weak bias spring 96 will be described with reference to FIGS. 9A-9F. In FIG. 10, the weak bias spring 96 of the conventional pump is differentiated from the strong bias spring 126.

FIG. 10 is a graph plotting the spring length in cm on the X axis. The force exerted by the piston on the membrane on the left Y axis is calibrated and plotted as N, and the effective pressure at the membrane is plotted as kPa on the right Y axis. From U.S. Pat. No. 3,775,030 , it is known that in conventional pumps, a slight overpressure of, for example, 20.7 kPa must be applied to the transport chamber 44 in order for the pump to operate properly in normal conditions. Therefore, it was a conventional technical idea to use a weak spring so that the excess pressure maintained by the bias spring during normal compression operation does not greatly differ from 20.7 kPa at various spring lengths. The spring constant of a typical spring is shown by line 140 in FIG. However, as described with reference to FIGS. 4A to 4F, the conventional pump has a problem that the membrane 34 is damaged when the line supplying the process fluid to the pump is clogged due to contamination of the filter. Thus, the present invention considered two reference points. The first reference point occurs when the valve port 121 of FIG. 5 or the valve port 98 of FIG. When the valve port 98 is just closed, the bias spring resists fluid suction on the process fluid pumping side to prevent this fluid suction from retaining the membrane on the pumping side, and hydraulic fluid is inconvenient to the transport chamber. Must be prevented from being filled. Since the negative pressure in the pumping chamber is obviously undesirable because it always requires more hydraulic oil to flow into the transport chamber, the minimum value is of course zero. The experience already described with conventional pumps has shown that it works well at 20.7kPa . Even a little higher than 27.6kPa is acceptable. Therefore, the range of 0-27.6kPa is appropriate. The first reference point is indicated by numeral 142 in FIG.

The second reference point occurs when the transport chamber is maximally filled with hydraulic oil, that is, when the base plate 88 abuts the wall 108 as shown in FIG. 4F. The second reference point is indicated by the number 144. In the case of a weak spring, the pressure at the reference point 142 when the valve is closed is slightly larger than 20.7 kPa , and the pressure at the reference point 144 for maximum overfilling is approximately 27.6 kPa . In order to solve the problem of membrane breakage when the pump chamber of the pump is at high vacuum, the reference point 1 is substantially satisfied under normal operating conditions, and under high vacuum conditions, the spring is placed in the transport chamber 44 and the oil tank. It has become clear that it is necessary to apply a pressure of approximately 72.4 kPa indicated by reference numeral 146 in FIG. 10 so that a large pressure difference does not occur in the transport chamber. The oil tank is at atmospheric pressure or essentially 101 kPa . By connecting the first and second reference points with a straight line, an improved pump spring constant is determined.

  9A to 9F show the operation of the strong spring represented by the straight line 148 in FIG.

  9A-9F assumes a vacuum condition where the strong spring and process fluid lines are blocked. 9A-9F are similar to FIGS. 4A-4F except that a weak bias spring is replaced by a strong bias spring.

  The inhalation stroke begins in FIG. 9A. Since the inlet of the process fluid is blocked, no pressure is generated in the discharge stroke, so that the pump chamber 106 is rapidly brought into a vacuum state by suction in the suction stroke. The membrane 34 and plunger 42 remain far left, closing the port 121 and compressing the bias spring 126 somewhat.

  FIG. 9B shows the state of the intermediate stroke. The low pressure in the pump chamber 106 lowers the pressure in the transport chamber 44 and keeps the membrane 34 and plunger 42 on the left, but the stronger bias spring has a larger spring constant 146, so it is farther away as far as the prior art shown in FIG. Can't keep up. Accordingly, overfilling of the transport chamber 44 is limited to the stretch volume of the membrane 34 under such conditions.

In FIG. 9C, the suction stroke reaches the bottom dead center and ends. High suction in the pump chamber still exists, but a strong spring (see the second reference point in FIG. 10) balances the suction force to increase the pressure in the transport chamber 44 and transport before the discharge stroke begins. The chamber 44 is prevented from being overfilled. In a more preferred case, the pressure difference in the transport chamber relative to the pump chamber for balancing the bias spring is, for example, approximately 72.4 kPa .

  In FIG. 9D, the discharge stroke begins. Since the pump chamber is very low pressure, the piston 46 moves to the left. Since no pressure is generated in the transport chamber other than that generated by the strong bias spring 126, the membrane 34, the plunger 42, and the piston 46 move together.

  In the intermediate stroke shown in FIG. 9E, the check valve 102 remains closed and the strong spring 126 biases the leak out of the transport chamber rather than into the transport chamber. The discharge stroke ends in the state shown in FIG. 9F. Since the transport chamber 44 is not overfilled, the membrane 34 does not swell and normal operation continues even if the inlet line to the pump chamber is clogged. From this, the strong bias spring 126 prevents the failure mode as described in FIGS.

Thus, as the valve spool moves further after closing the port, the strong bias spring prevents the valve spool from moving further. As shown in FIG. 10, in the normal port closed position (first reference point), both weak and strong springs exert a force of 17.8 N , ie a pressure of 24.1-31.0 kPa , on the membrane. Therefore, the biased hydraulic fluid drive described in US Pat. No. 3,775,030 is maintained. However, as the valve spool continues to move toward maximum spring compression, a strong spring produces a force of 53.4N , whereas a weak spring is only about 22.2N . The added force limits the ability of the membrane to move farther under high vacuum. This is correct because the attractive force from the transport chamber side is the sum of the spring force and the pressure difference between the pump chamber and the transport chamber. Traditional weak springs can only effectively balance a vacuum of approximately 34.5 kPa , but the improved strong springs are optimized to balance a vacuum of approximately 72.4 kPa (theoretically yields 101 kPa) This 72.4kPa is actually achievable value. The design for the maximum force possible ensures that hydraulic fluid is never injected into a fully filled transport room, but only that there is no net increase in hydraulic fluid during the entire pump suction and discharge cycle. is required. In other words, there will be no average increase in hydraulic fluid in the transport chamber as long as there is more time for the transport chamber to be below atmospheric pressure during multiple intake and discharge strokes.

注：ばり発見；弁ハウジングの内部のばり除去

A film destruction test was performed under vacuum. The test results are shown in Table 1. The pump bias spring 126 described in FIG. 2 was used with a larger spring constant as shown in Table 1. A vacuum was maintained at the inlet (check valve 36). The vacuum was maintained at a mercury column of 381 mm or less for 1 to 2 hours and then maintained at a mercury column of 508 mm or more until breakage or the end of the test.

Table 1

Note: Flash detection; flash removal inside valve housing

The first three tests were performed using a strong spring with a spring constant of 7.54 N / mm . The membrane broke after 97 hours in test 1 and 55 hours in test 2. Examination of the pump after Test 2 revealed a flash in the valve housing. As a result, the valve spool 84 stuck and eventually the membrane expanded and was captured by the base plate 90. Test 3 was performed with the flash in the valve housing removed. The membrane broke in 106 hours. The burr was found to be insignificant in the results except for the time to destruction. With a spring constant of 7.54 N / mm , the membrane broke in about 100 hours.

Tests 4 to 6 were performed using a bias spring having a spring constant of 9.40 N / mm . In each test, the pump was run for 100 hours without membrane breakage, and in Test 6, it was run for 200 hours without membrane breakage.

From the above tests, it was found that a bias spring having a spring constant of 7.54 N / mm was barely acceptable. A pump with a bias spring with a spring constant of 9.40 N / mm was clearly acceptable because it did not break. The results of the test are shown in FIG. A straight line 150 represents a bias spring having a spring constant of 7.54 N / mm , and a straight line 148 represents a bias spring having a spring constant of 9.40 N / mm . Dashed line 152 shows the bias spring with the maximum spring constant required. That is, the maximum degree of vacuum achieved at the second reference point where the base plate 88 contacts the wall 108 (see FIG. 4E) is 101 kPa . Such a pump can never achieve such a vacuum. Accordingly, straight line 152 is shown as a dashed line and is somewhat approximate. In any case, this broken line gives a general concept of where the maximum spring constant is.

The spring constant can be calculated assuming the following design conditions for a specific pump as follows. First, the equivalent area in the middle stroke of the membrane is approximately equal to the piston cross-sectional area. Second, the required minimum pressure difference across the membrane must be equal to the pump design suction pressure. Third, the maximum pressure difference is 101 kPa . Based on the above, the following can be said. That is,
1. Overfill distance is the difference between the distance between the membrane and the piston in (i) the maximum overfill position and (ii) the neutral position (position where the valve is just closed).
2. The overfill spring force is a value obtained by multiplying the design suction pressure difference by the piston cross-sectional area.
3. The neutral spring force is the value obtained by multiplying the neutral operating pressure difference by the piston cross-sectional area.
4. The spring constant is the value obtained by subtracting the neutral spring force from the overfill spring force and dividing it by the overfill distance.

Based on the above assumptions and descriptions, the spring constant is calculated by the following equation.
k = A _p (P _s −P _n ) / d ₀

Here, k is a spring constant, A _p is a piston cross-sectional area, d ₀ is an overfilling distance, P _s is a design suction pressure difference, and P _n is a neutral operating pressure difference.

Based on the test described, a suitable maximum design suction pressure difference is 57.9 to 101 kPa , and a suitable neutral operating pressure difference is 0 to 27.6 kPa .

  10 and 11, it can be seen that the strong bias spring of the present invention is necessarily shorter than the conventional spring. This has the advantage when the pump is closed and the bias spring cannot always push hydraulic oil from the transport chamber through the piston assembly / housing to the oil pump. When a strong spring is used, once the transport chamber is properly filled and the pump is closed, the spring no longer develops a large force. This means that the hydraulic fluid filling of the transport chamber is in the proper pumping position and does not need to be refilled at the start of the next operation. On the other hand, short springs have drawbacks. The short spring cannot push air completely out of the transport chamber prior to the first start. The added air makes it very difficult to completely prime (prime) the transport chamber 44. In this case, the pump must be disassembled and each of the plurality of transport chambers must be manually called. Furthermore, the pump sometimes cannot self-suck in a state where air accumulates in the hydraulic oil and cannot be driven out. A groove 116 is provided to cope with such a drawback. FIGS. 12A-12F illustrate operation with the added benefit of allowing pumping air with a groove 116 and self-priming of the pump.

  The inhalation stroke begins in FIG. 12A. There is excess air in the transport chamber 44. The hydraulic fluid flows through the valve port 98 and pushes air up high in the cylinder 47. As the intake stroke begins, more hydraulic oil will try to flow through the check valve 32 and the valve port 121, but the strong bias spring 126 keeps the membrane 32 moving with the piston 46.

  In the intermediate stroke shown in FIG. 12B, since suction increases, the membrane 32 is pulled to the left to block the valve port 121. The strong bias spring 126 resists over compression so that the membrane 32 moves substantially with the piston 46.

  As shown in FIG. 12C, there is still significant suction in the pump chamber 106 even when the piston 46 approaches the bottom dead center (BDC). The strong bias spring restricts the movement of the membrane plunger 42 and the membrane 34 to the far left and raises the pressure in the transport chamber 44 to prevent overfilling of the hydraulic oil.

  As shown in FIG. 12D, when the discharge stroke starts, the piston 46 starts to move to the left, while the check valve 32 is closed and pressure is generated in the transport chamber. The pressure increase in the transport chamber 44 causes air to be released from the groove 116.

  In the intermediate stroke shown in FIG. 12E, the pressure in the transport chamber 44 exceeds the pressure in the oil tank, and air continues to be pushed out through the groove 116.

  When the piston 46 moves to the left at the end of the discharge stroke shown in FIG. 12F, the membrane 34 also moves to the left. Most of the air in the transport chamber 44 is now expelled. As the subsequent suction and discharge strokes proceed, all the air is expelled and the pump quickly self-primes.

  The grooves 116 can be rectangular, hemispherical, triangular, or any shape. Groove 116 must be large enough to allow air to escape rather quickly, but not so large that the efficiency of the pump is compromised. In general, a 1% loss in pump efficiency is acceptable. Therefore, for a particular pump, it is necessary to calculate the equivalent cross-sectional area of the groove 116 corresponding to 1% loss in efficiency. As already indicated, the groove 116 must be provided at the top of the cylinder 120 so that it is located where air collects. The groove 116 must be long enough to be exposed to the compressed hydraulic fluid at least in part of the piston stroke. The groove may extend to the end of the piston stroke so that it is exposed to the hydraulic fluid during the entire stroke of the piston. The best practice is to expose the groove to hydraulic fluid only during the first half of the stroke. The dimensions of the groove must be large enough to allow air to pass rapidly and small enough to resist the passage of hydraulic fluid so that pump efficiency is not significantly reduced.

For most pumps, the groove 116 has a cross-sectional area of approximately 0.129 mm ² and a groove height of 0.432 mm . To drive off the air efficiently, the cross-sectional area of the groove must be greater than 0.0323mm ^2. The maximum cross-sectional area of the groove is approximately 1.94 mm ² . The height and width of the groove cross section are both 0.127 mm or more.

  The improved pump of the present invention eliminates premature membrane failure due to unexpected overfilling of the transport chamber with hydraulic oil, resulting in improved reliability. The improved pump can continuously utilize the entire stroke of the intended membrane, leaving little air in the transport chamber during normal operation, resulting in improved efficiency and smooth discharge. The pump of the present invention improves the hydraulic / air metering capacity for the transport chamber and oil tank, thereby ensuring consistently high quality hydraulic fluid in the transport chamber and in the pump inlet and outlet situations. Nevertheless, it maintains the “strongest” hydraulic system. The pump of the present invention is self-priming and avoids any priming losses during operation. Thus, the pump of the present invention is a significant improvement over conventional membrane pumps.

  The specification, embodiments and data provide a complete description of the manufacture and use of the composition of the invention. Since many embodiments can be made without departing from the spirit and scope of the invention, the essence of the invention resides in the claims set forth below.

FIG. 1 is a perspective view of a conventional membrane pump. FIG. 2 is a partial cross-sectional view of a conventional membrane pump. FIG. 3A is a partial cross-sectional view showing a normal state of a conventional membrane pump. FIG. 3B is a partial cross-sectional view showing a normal state of a conventional membrane pump. FIG. 3C is a partial cross-sectional view showing a normal state of a conventional membrane pump. FIG. 3D is a partial cross-sectional view showing a normal state of a conventional membrane pump. FIG. 3E is a partial cross-sectional view showing a normal state of a conventional membrane pump. FIG. 3F is a partial cross-sectional view showing a normal state of a conventional membrane pump. FIG. 4A is a partial cross-sectional view showing a high vacuum state that causes membrane damage in a conventional membrane pump. FIG. 4B is a partial cross-sectional view showing a high vacuum state that causes membrane damage in a conventional membrane pump. FIG. 4C is a partial cross-sectional view showing a high vacuum state that causes membrane damage of a conventional membrane pump. FIG. 4D is a partial cross-sectional view showing a high vacuum state that causes membrane damage in a conventional membrane pump. FIG. 4E is a partial cross-sectional view showing a high vacuum state that causes membrane damage in a conventional membrane pump. FIG. 4F is a partial cross-sectional view showing a high vacuum state that causes membrane damage in a conventional membrane pump. FIG. 5 is a partial cross-sectional view of a membrane pump according to the present invention. FIG. 6 is a partial cross-sectional view of the first embodiment. FIG. 7 is a partial cross-sectional view of the second embodiment. FIG. 8 is an exploded cross-sectional view of the piston / cylinder assembly. FIG. 9A is a partial cross-sectional view showing the operation of the membrane pump using a bias spring having a high spring constant. FIG. 9B is a partial cross-sectional view showing the operation of the membrane pump using a bias spring having a high spring constant. FIG. 9C is a partial cross-sectional view showing the operation of the membrane pump using a bias spring having a high spring constant. FIG. 9D is a partial cross-sectional view showing the operation of the membrane pump using a bias spring having a high spring constant. FIG. 9E is a partial cross-sectional view showing the operation of the membrane pump using a bias spring having a high spring constant. FIG. 9F is a partial cross-sectional view showing the operation of the membrane pump using a bias spring having a high spring constant. FIG. 10 is a graph showing a conventional weak bias spring and a strong bias spring according to the present invention. FIG. 11 is a graph showing a spring constant range of the bias spring according to the present invention. FIG. 12A is a partial cross-sectional view showing a membrane pump having a discharge groove and its self-priming. FIG. 12B is a partial cross-sectional view showing a membrane pump having a discharge groove and its self-priming. FIG. 12C is a partial cross-sectional view showing a membrane pump having a discharge groove and its self-priming. FIG. 12D is a partial cross-sectional view showing a membrane pump having a discharge groove and its self-priming. FIG. 12E is a partial cross-sectional view showing a membrane pump having a discharge groove and its self-priming. FIG. 12F is a partial cross-sectional view showing a membrane pump having a discharge groove and its self-priming.

38 Housing part 46 Piston 88 Base plate
110 pump
112 housing
114 Housing part
116 groove
118 top of cylinder
120 cylinders
121 port
122 walls
124 Housing end
126 Bias spring

Claims (9)

In the membrane pump (110) that receives the driving force from the motor,
A pump chamber (106) for storing fluid to be pumped, a transport chamber (44) for storing hydraulic oil, a housing (112) having an oil tank,
A membrane (34) having a transport chamber side and a pump chamber side, disposed between the transport chamber (44) and the pump chamber (106), and reciprocatingly moving toward and away from the pump chamber (106);
A cylinder (120) that forms part of the transport chamber in the housing (112) and has a surface at the top when oriented to be generally horizontal by a membrane pump, and the cylinder (120) as a longitudinal A piston (46) reciprocating between the discharge stroke and the suction stroke in the direction;
A communication path (100, 104) for hydraulic oil provided between the oil tank and the transport chamber (44), and provided in the communication path, when the hydraulic oil is opened, the hydraulic oil is transferred from the oil tank to the transport chamber (44). A valve (136,84) to selectively flow to
The cylinder (120) comprises a longitudinal groove (116, 128) formed on the upper surface (118) of the cylinder (120), and includes a vent communicating the transport chamber (44) and the oil tank,
A membrane pump characterized in that air in the transport chamber (44) is discharged through a vent of the cylinder (120). 2. The membrane pump (110) according to claim 1, wherein a spring (126) having a first end connected to the membrane (34) and a second end supported by the piston (46) and moving with the piston (126). )
This spring (126) has a spring constant k given by the following equation, the designed suction pressure is in the range of 57.9 to 101.4 kPa (absolute pressure), and the neutral operating pressure is in the range of 0 to 27.6 kPa. A membrane pump characterized by being in range.
k = A _p (P _s −P _n ) / d ₀
Where A _p is the piston cross-sectional area, d ₀ is the overfill distance, P _s is the pump design suction pressure difference, and P _n is the pump neutral operating pressure difference.   The membrane pump (110) according to claim 1, wherein the groove (128) terminates just before the opening to the oil tank, and the housing (112) extends from the groove (128) to the oil tank. A membrane pump comprising a passage (130), and a check valve for preventing a flow of hydraulic oil from the oil tank to the groove is provided in the passage.   The membrane pump according to claim 3, wherein the check valve includes an O-ring groove (132) and an O-ring (134) in the groove, and the passage (130) is formed in the groove of the housing (112). A membrane pump characterized by ending with the O-ring groove (132) opposite to (128).   2. The membrane pump according to claim 1, wherein the piston (46) has an end, and the groove (116) is formed on the piston (46) when the piston (46) completes the discharge stroke. A membrane pump characterized by ending before reaching the end. The membrane pump (110) according to claim 1, wherein the groove (116) has a cross-sectional area of 0.000323 cm ² or more and 0.0194 cm ² or less in a cross section perpendicular to the longitudinal direction of the groove. Membrane pump. The membrane pump (110) according to claim 1, wherein the cylinder (120) has a wall (133) as part of the housing (112), and the vent penetrates the wall and A membrane pump comprising a passage (131) communicating with an oil tank from an upper surface (118) of a cylinder (120). The membrane pump (110) according to claim 7, wherein the passage (131) has a cross section perpendicular to the longitudinal direction of the passage of 0.000323 cm. ² More than that and 0.0194cm ² A membrane pump having the following cross-sectional area. 9. The membrane pump according to claim 8, wherein the passage has a diameter of 0.0127 cm or more.

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