Compressing diaphragm pump with multiple effects

This application claims the benefit of provisional U.S. Patent Application number 62/000,597, filed May 20, 2014, and incorporated herein by reference. Field Of The Present Invention

The present invention relates to a compressing diaphragm pump with multiple effects used in a reverse osmosis (RO) purification system, and particularly to a compressing diaphragm pump having an innovative mating means for the pump head body and diaphragm membrane to reduce unwanted noise and shaking caused by resonant vibrations in the conventional compressing diaphragm pump, as well as a sloped top ring in the eccentric roundel mount that can eliminate the oblique pulling and squeezing phenomena of the pump so that the service lifespan of the compressing diaphragm pump and the durability of key components therein are prolonged.

Background Of The Invention Conventional compressing diaphragm pumps of the type commonly used with RO

(Reverse Osmosis) purifier or RO water purification systems are disclosed in U.S. Patent Nos. 4396357, 4610605, 5476367, 5571000, 5615597, 5649812, 5706715, 5791882 and 5816133. An example of a conventional compressing diaphragm pump is shown in FIGS. 1 through 10, and essentially comprises a brushed motor 10 with an output shaft 11, a motor upper chassis 30, a wobble plate with an integral protruding cam-lobed shaft 40, an eccentric roundel mount 50, a pump head body 60, a diaphragm membrane 70, three pumping pistons 80, a piston valvular assembly 90 and a pump head cover 20. The motor upper chassis 30 includes a bearing 31 through which an output shaft 11 of the motor 10 extends. The motor upper chassis 30 also includes an upper annular rib ring 32 with several fastening bores 33 evenly and circumferentially disposed in a rim of the upper annular rib ring 32 The wobble plate 40 includes a shaft coupling hole 41 through which the corresponding motor output shaft 11 of the motor 10 extends.

The eccentric roundel mount 50 includes a central bearing 51 at the bottom thereof for receiving the corresponding wobble plate 40. Three tubular eccentric roundels 52 are evenly and circumferentially disposed on the eccentric roundel mount 50. Each tubular eccentric roundel 52 has a horizontal top face 53, a female-threaded bore 54 and an annular positioning groove 55 formed in the top face thereof, as well as a rounded shoulder 57 created at the intersection of the horizontal top face 53 and a vertical flank 56.

The pump head body 60 covers the upper annular rib ring 32 of the motor upper chassis 30 to encompass the wobble plate 40 and eccentric roundel mount 50 therein, and includes three operating holes 61 evenly and circumferentially disposed therein. Each operating hole 61 has an inner diameter that is slightly bigger than the outer diameter of the corresponding tubular eccentric roundel 52 in the eccentric roundel mount 50 for receiving each corresponding tubular eccentric roundel 52 respectively, a lower annular flange 62 formed thereunder for mating with corresponding upper annular rib ring 32 of the motor upper chassis 30, and several fastening bores 63 evenly disposed around a circumference of the pump head body 60.

The diaphragm membrane 70, which is extrusion-molded from a semi-rigid elastic material and placed on the pump head body 60, includes a pair of parallel rims, including outer raised rim 71 and inner raised rim 72, as well as three evenly spaced radial raised partition ribs 73 such that each end of radial raised partition ribs 73 connects with the inner raised rim 72, thereby forming three equivalent piston acting zones 74 within and partitioned by the radial raised partition ribs 73, wherein each piston acting zone 74 has an acting zone hole 75 created therein in correspondence with a respective female-threaded bore 54 in the tubular eccentric roundel 52 of the eccentric roundel mount 50, and an annular positioning protrusion 76 for each acting zone hole 75 is formed at the bottom side of the diaphragm membrane 70 (as shown in FIGS. 9 and 10).

Each pumping piston 80, which is respectively disposed in each corresponding piston acting zones 74 of the diaphragm membrane 70, has a tiered hole 81 extending therethrough. After each of the annular positioning protrusions 76 in the diaphragm membrane 70 have been inserted into a corresponding annular positioning dent 55 in the tubular eccentric roundel 52 of the eccentric roundel mount 50, respective fastening screws 1 are inserted through the tiered hole 81 of each pumping piston 80 and the acting zone hole 75 of each corresponding piston acting zone 74 in the diaphragm membrane 70, so that the diaphragm membrane 70 and three pumping pistons 80 can be securely screwed into female-threaded bores 54 of the corresponding three tubular eccentric roundels 52 in the eccentric roundel mount 50 (as can be seen in the enlarged portion of FIG. 11).

Piston valvular assembly 90 covers the diaphragm membrane 70 and includes a downwardly extending raised rim 91 for insertion into the gap ring between the outer raised rim 71 and inner raised rim 72 in the diaphragm membrane 70, a central dish-shaped round outlet mount 92 having a central positioning bore 93 with three equivalent sectors, each of which contains multiple evenly circumferentially-located outlet ports 95, a T-shaped plastic anti-backflow valve 94 with a central positioning shank, and three circumferentially-adjacent inlet mounts 96. Each of the circumferentially-adjacent inlet mounts 96 includes multiple evenly circumferentially-located inlet ports 97 and an inverted central piston disk 98 respectively so that each piston disk 98 serves as a valve for each corresponding group of multiple inlet ports 97. The central positioning shank of the plastic anti-backflow valve 94 mates with the central positioning bore 93 of the central outlet mount 92 such that multiple outlet ports 95 in the central round outlet mount 92 are in communication with the three inlet mounts 96, and a hermetically sealed preliminary-compression chamber 26 is formed between each inlet mount 96 and a corresponding piston acting zone 74 in the diaphragm membrane 70 upon insertion of the downwardly extending raised rim 91 into the gap ring between the outer raised rim 71 and inner raised rim 72 of diaphragm membrane 70, such that one end of each preliminary-compressing chamber 26 is in communication with each of the corresponding inlet ports 97 (as shown in the enlarged portion of FIG. 11). The pump head cover 20, which covers the pump head body 60 to encompass the piston valvular assembly 90, pumping piston 80 and diaphragm membrane 70 therein, includes a water inlet orifice 21, a water outlet orifice 22, and several fastening bores 23. A tiered rim 24 and an annular rib ring 25 are disposed in the bottom inside of the pump head cover 20 such that the outer rim for the assembly of diaphragm membrane 70 and piston valvular assembly 90 can be hermetically attached to the tiered rim 24 (as shown in the enlarged portion of FIG. 11). A high-compression chamber 27 is formed between the cavity formed by the inside wall of the annular rib ring 25 and the central outlet mount 92 of the piston valvular assembly 90 when the bottom of the annular rib ring 25 closely covers the rim of the central outlet mount 92 (as shown in FIG. 11). By running each fastening bolt 2 through a corresponding fastening bore 23 of pump head cover 20 and a corresponding fastening bore 63 in the pump head body 60, and then putting a nut 3 onto each fastening bolt 2 to securely screw the pump head cover 20 to the pump head body 60 via the corresponding fastening bores 33 in the motor upper chassis 30, the whole assembly of the compressing diaphragm pump is finished (as shown in FIGS, l and 11).

Please refer to FIGS. 12 and 13, which are illustrative figures for the operation of the conventional compressing diaphragm pump of Figs. 1-11.

Firstly, when the motor 10 is powered on, the wobble plate 40 is driven to rotate by the motor output shaft 11 so that the three tubular eccentric roundels 52 on the eccentric roundel mount 50 constantly move in a sequential up-and-down reciprocal stroke.

Secondly, in the meantime, the three pumping pistons 80 and three piston acting zones 74 in the diaphragm membrane 70 are sequentially driven by the up-and-down reciprocal stroke of the three tubular eccentric roundels 52 to move in an up-and-down displacement.

Thirdly, when the tubular eccentric roundel 52 moves in a down stroke, causing pumping piston 80 and piston acting zone 74 to be displaced downwardly, the piston disk 98 in the piston valvular assembly 90 is pushed into an open status so that tap water W can flow into the preliminary-compression chamber 26 via water inlet orifice 21 in the pump head cover 20 and inlet ports 97 in the piston valvular assembly 90 (as indicated by the arrowhead extending from W in the enlarged view of FIG. 12);

Fourthly, when the tubular eccentric roundel 52 moves in an up stroke, causing pumping piston 80 and piston acting zone 74 to be displaced upwardly, the piston disk 96 in the piston valvular assembly 90 is pulled into a closed status to compress the tap water

W in the preliminary-compression chamber 26 and increase the water pressure therein up to a range of 80psi-100psi. The resulting pressurized water Wp causes the plastic anti-backflow valve 94 in the piston valvular assembly 90 to be pushed to an open status. Fifthly, when the plastic anti-backflow valve 94 in the piston valvular assembly 90 is pushed to an open status, the pressurized water Wp in the preliminary-compression chamber 26 is directed into high-compression chamber 27 via the group of outlet ports 95 for the corresponding sector in the central outlet mount 92, and then expelled out of the water outlet orifice 22 in the pump head cover 20 (as indicated by arrowhead W in the enlarged portion of FIG. 13).

Finally, the sequential iterative action for each group of outlet ports 95 for the three sectors in central outlet mount 92 causes the pressurized water Wp to be constantly discharged out of the conventional compressing diaphragm pump to be further RO-filtered by the RO-cartridge so that the final filtered pressurized water Wp can be used in the reverse osmosis water purification system.

Referring to FIGS. 14 through 16, a serious vibration-related drawback has long existed in the conventional compressing diaphragm pump. As described previously, when the motor 10 is powered on, the wobble plate 40 is driven to rotate by the motor output shaft 11 so that the three tubular eccentric roundels 52 on the eccentric roundel mount 50 constantly move in a sequential up-and-down reciprocal stroke, while in the meantime three pumping pistons 80 and three piston acting zones 74 in the diaphragm membrane 70 are sequentially driven by the up-and-down reciprocal stroke of the three tubular eccentric roundels 52 to undergo up-and-down displacement so that an equivalent force F constantly acts on the three piston acting zones 74 with a length of moment arm LI measured from the outer raised rim 71 to the periphery of the annular positioning protrusion 76 (as shown in FIG. 15). Thereby, a resultant torque is created by the acting force F multiplying the length of moment arm LI according to the formula "torque = acting force F x length of moment arm LI." The resultant torque causes the whole conventional compressing diaphragm pump to vibrate directly. With a high rotational speed of the motor output shaft 11 in the motor 10 up to a range of 700-1200 rpm, the vibrating strength caused by the alternately acting of three tubular eccentric roundels 52 can reach a persistently unacceptable condition. To address the drawbacks of the conventional compressing diaphragm pump, as shown in FIG. 16, a cushion base 100 with a pair of wing plates 101 is always provided as a supplemental support, with each wing plate 101 being further sleeved by a rubber shock absorber 102 for enhancing vibration suppression. Upon installation of the conventional compressing diaphragm pump, the cushion base 100 is firmly screwed onto the housing C of the reverse osmosis purification unit by means of suitable fastening screws 103 and corresponding nuts 104. However, the practical vibration suppressing efficiency of the cushion base 100 with wing plates 101 and rubber shock absorber 102 only reduces noise caused by the primary vibration without affect noise caused by secondary vibrations that occur as a result of resonant shaking of the housing C. The secondary vibration actually cause the overall vibration noise of the housing C for the reverse osmosis purification unit to increase.

In addition to drawback of increasing overall vibration noise of the housing C, a further drawback occurs in that the water pipe P connected to the water outlet orifice 22 of the pump head cover 20 will synchronously shake in resonance with the vibrations described above (as indicated by the broken line depictions of water pipe P in FIGS. 16 and 16a). This synchronous shaking of the water pipe P will result in still further drawbacks by causing other parts of the conventional compressing diaphragm pump to simultaneously shake. As a result, after a certain period, the water leakage of the conventional compressing diaphragm pump will occur due to gradual loosening of the connection between water pipe P and water outlet orifice 22, as well as gradual loosening of the fit between other parts affected by the shaking. The additional drawbacks of overall resonant shaking and water leakage in the conventional compressing diaphragm pump cannot be resolved by the above-described conventional way of addressing primary vibrations using a shock-absorbing cushion base 100. Therefore, how to substantially reduce all of the drawbacks associated with the operating vibration for the compressing diaphragm pump has become an urgent and critical issue.

FIGS. 17 and 18 illustrate yet another problem with the conventional compressing diaphragm pump. As described previously, when the motor 10 is powered on, the wobble plate 40 is driven to rotate by the motor output shaft 11 so that three tubular eccentric roundels 52 on the eccentric roundel mount 50 constantly move in a sequential up-and-down reciprocal stroke, and the three piston acting zones 74 in the diaphragm membrane 70 are sequentially driven by the up-and-down reciprocal stroke of the three tubular eccentric roundels 52 to move in up-and-down displacement so that a force F constantly acts on the bottom side of each piston acting zone 74.

Meanwhile a corresponding plurality of rebounding forces Fs are created in reaction to the acting force F exerted on the bottom side of diaphragm membrane 70, with different components distributed over the entire bottom area of each corresponding piston acting zone 74 in the diaphragm membrane 70, as shown in FIG. 18, so that a squeezing phenomenon caused by the rebounding forces Fs occurs on a section of the diaphragm membrane 70.

Among all of the distributed components of the rebounding force Fs, the maximum component force is exerted at the contacting bottom position P of the diaphragm membrane 70 with the rounded shoulder 57 of the horizontal top face 53 in the tubular eccentric roundel 52 so that the squeezing phenomenon at the bottom position P is also maximum, as shown in FIG. 18.

With the rotational speed for the motor output shaft 11 of the motor 10 reaching a range of 700-1200 rpm, each bottom position P of the piston acting zone 74 of the diaphragm membrane 70 suffers from the squeezing phenomenon at a frequency of four times per second. Under such circumstances, the bottom position P of the diaphragm membrane 70 is always the first broken place for the entire conventional compressing diaphragm pump, which is an essential cause of not only shortening the service lifespan but also terminating the normal function of the conventional compressing diaphragm pump.

Therefore, how to substantially reduce the drawbacks associated with the squeezing phenomenon caused by the constant application of force F to the bottom side of each piston acting zone 74 of the diaphragm membrane 70 as a result of the movement of the tubular eccentric roundel 52 has also become an urgent and critical issue.

Summary Of The Invention

An objective of the present invention is to provide a compressing diaphragm pump with multiple effects, including an innovative mating means for a pump head body and a diaphragm membrane, in which the pump head body includes three operating holes and a basic curved groove, slot, or perforated segment, or a curved protrusion or set of protrusions, at least partially circumferentially-disposed around the upper side of each operating hole while the diaphragm membrane includes three equivalent piston acting zones, each of which has an acting zone hole, an annular positioning protrusion for each acting zone hole, and a basic curved protrusion or set of protrusions, or a groove, slot, or perforated segment, at least partially circumferentially-disposed around each concentric annular positioning protrusion at a position corresponding to the position of a corresponding mating basic curved groove, slot, or perforated segment, or curved protrusion or set of protrusions, in the pump head body, so that the three basic curved protrusions, sets of protrusions, grooves, slots, or perforated segments are completely inserted into or received by the corresponding three basic curved grooves, slots, perforated segments, protrusions, or sets of protrusions in the pump heat body with a short length of moment arm to generate less torque, the torque being obtained by multiplying the length of the moment arm by a constant acting force. With less torque, the vibration strength of the compressing diaphragm pump is substantially reduced.

Another objective is to provide a compressing diaphragm pump with multiple effects, including an innovative mating means for a pump head body and a diaphragm membrane, in which the pump head body has three basic curved grooves, slots, or perforated segments, or curved protrusions or set of protrusions, and the diaphragm membrane has three basic curved protrusions or sets of protrusions, or grooves, slots, or perforated segments, such that three basic curved protrusions or sets of protrusions, or grooves, slots, or perforated segments are completely inserted into or received by the corresponding three basic curved grooves, slots, or perforated segments, or curved protrusions or set of protrusions, with a short length of moment arm that generates less torque, the torque being obtained by multiplying the length of the moment arm by a constant acting force. With less torque, the vibration strength of the compressing diaphragm pump is substantially reduced. When the present invention is installed on the housing of a reverse osmosis purification unit of a water supplying apparatus in either a house or mobile home and cushioned by a conventional cushion base with a rubber shock absorber, the annoying noise caused by resonant shaking that occurred in the conventional compressing diaphragm pump can be completely eliminated. A further object of the present invention is to provide a compressing diaphragm pump with multiple effects, which includes a cylindrical eccentric roundel disposed in an eccentric roundel mount. The cylindrical eccentric roundel includes an annular positioning groove, a vertical flank and an annular top surface portion that is inclined relative to horizontal to form a sloped top ring between the annular positioning groove and the vertical flank. By means of the sloped top ring, the high-frequency oblique pulling and squeezing phenomena that occurs in a conventional tubular eccentric roundel are completely eliminated because the sloped top ring flatly attaches the bottom area of corresponding piston acting zone for the diaphragm membrane. Thus, not only is the durability of the diaphragm membrane enhanced to better withstand the sustained high-frequency pumping action of the eccentric roundels, but the service lifespan of the diaphragm membrane is also greatly prolonged.

Yet another objective of the present invention is to provide a compressing diaphragm pump with multiple effects, which includes a cylindrical eccentric roundel disposed in an eccentric roundel mount. The cylindrical eccentric roundel includes an annular positioning groove, a vertical flank and a sloped top ring formed between the annular positioning groove and the vertical flank. By means of the sloped top ring, all distributed components of the rebounding force for the cylindrical eccentric roundels that are generated in reaction to the acting force caused by the pumping action are substantially reduced because the sloped top ring flatly attaches to the bottom area of the corresponding piston acting zone for the diaphragm membrane.

In achieving the above-described objectives, which are not intended to be limiting, at least the following benefits are obtained:

1. The durability of the diaphragm membrane for sustaining the high-frequency pumping action of the cylindrical eccentric roundels is substantially enhanced.

2. The power consumption of the compressing diaphragm pump is tremendously diminished due to less current being wasted as a result of the above-described high-frequency squeezing phenomena.

3. The working temperature of the compressing diaphragm pump is tremendously reduced due to less power consumption.

4. The annoying noise of the bearings that results from aged lubricant in the compressing diaphragm pump, which is expeditiously accelerated by the high working temperature, is mostly eliminated.

Brief Description Of The Drawings FIG. 1 is a perspective assembled view of a conventional compressing diaphragm pump.

FIG. 2 is a perspective exploded view of a conventional compressing diaphragm pump.

FIG. 3 is a perspective view of an eccentric roundel mount for the conventional compressing diaphragm pump.

FIG. 4 is a cross sectional view taken against the section line 4-4 from previous FIG. 3.

FIG. 5 is a perspective view of a pump head body for the conventional compressing diaphragm pump.

FIG. 6 is a cross sectional view taken against the section line 6-6 from previous

FIG. 5. FIG. 7 is a top view of a pump head body for the conventional compressing diaphragm pump.

FIG. 8 is a perspective view of a diaphragm membrane for the conventional compressing diaphragm pump.

FIG. 9 is a cross sectional view taken against the section line 9-9 from previous FIG. 8.

FIG. 10 is a bottom view of a diaphragm membrane for the conventional compressing diaphragm pump.

FIG. 11 is a cross sectional view taken against the section line 1 1-1 1 from previous FIG. 1. FIG. 12 is a first operation illustrative view of a conventional compressing diaphragm pump. FIG. 13 is a second operation illustrative view of a conventional compressing diaphragm pump.

FIG. 14 is a third operation illustrative view of a conventional compressing diaphragm pump. FIG. 15 is a partially enlarged view taken from circled-portion-a of previous FIG.

14.

FIG. 16 is a schematic view showing a conventional compressing diaphragm pump installed on a mounting base in a reverse osmosis (RO) purification system.

FIG. 17 is a fourth operation illustrative view of a conventional compressing diaphragm pump .

FIG. 18 is a partially enlarged view taken from circled-portion-b of previous FIG.

17.

FIG. 19 is a perspective exploded view of a the first exemplary embodiment of the present invention. FIG. 20 is a perspective view of a pump head body in the first exemplary embodiment of the present invention.

FIG. 21 is a cross sectional view taken against the section line 21-21 from previous FIG. 20.

FIG. 22 is a top view of a pump head body in the first exemplary embodiment of the present invention.

FIG. 23 is a perspective view of a diaphragm membrane in the first exemplary embodiment of the present invention.

FIG. 24 is a cross sectional view taken against the section line 24-24 from previous FIG. 23.

FIG. 25 is a bottom view of a diaphragm membrane in the first exemplary embodiment of the present invention.

FIG. 26 is a perspective view of a eccentric roundel mount in the first exemplary embodiment of the present invention.

FIG. 27 is a cross sectional view taken against the section line 27-27 from previous FIG. 26. FIG. 28 is an assembled cross sectional view of the first exemplary embodiment of the present invention.

FIG. 29 is the first operation illustrative view of the first exemplary embodiment of the present invention.

FIG. 30 is a partially enlarged view taken from circled-portion-a of previous FIG. 29.

FIG. 31 is a second operation illustrative view of the first exemplary embodiment of the present invention.

FIG. 32 is a partially enlarged view taken from circled-portion-b of previous FIG.

13. FIG. 33 is a cross sectional illustrative view showing a comparison between the cylindrical eccentric roundel acting on the diaphragm membrane of the conventional compressing diaphragm pump and that of the first exemplary embodiment of the present invention.

FIG. 34 is a perspective view for an adapted pump head body in the first exemplary embodiment of the present invention.

FIG. 35 is a cross sectional view taken against the section line 35-35 from previous FIG. 34.

FIG. 36 is an exploded cross sectional view showing an adapted pump head body and diaphragm membrane in the first exemplary embodiment of the present invention.

FIG. 37 is a cross sectional view showing assembly of an adapted pump head body and diaphragm membrane in the first exemplary embodiment of the present invention.

FIG. 38 is a perspective view of a pump head body in the second exemplary embodiment of the present invention.

FIG. 39 is a cross sectional view taken against the section line 39-39 from previous FIG. 38.

FIG. 40 is a top view of a pump head body in the second exemplary embodiment of the present invention.

FIG. 42 is a perspective view of a diaphragm membrane in the second exemplary embodiment of the present invention.

FIG. 42 is a cross sectional view taken against the section line 42-42 from previous FIG. 41.

FIG. 43 is a bottom view of a diaphragm membrane in the second exemplary embodiment of the present invention. FIG. 44 is a cross sectional view showing the assembly of a diaphragm membrane and a pump head body for the second exemplary embodiment of the present invention.

FIG. 45 is a perspective view of an adapted pump head body in the second exemplary embodiment of the present invention.

FIG. 46 is a cross sectional view taken against the section line 46-46 from previous FIG. 45.

FIG. 47 is an exploded cross sectional view showing an adapted pump head body and diaphragm membrane in the second exemplary embodiment of the present invention.

FIG. 48 is a cross sectional view showing assembly of an adapted pump head body and diaphragm membrane in the second exemplary embodiment of the present invention.

FIG. 49 is a perspective view of a pump head body in the third exemplary embodiment of the present invention.

FIG. 50 is a cross sectional view taken against the section line 50-50 from previous FIG. 49.

FIG. 51 is a top view of a pump head body in the third exemplary embodiment of the present invention.

FIG. 52 is a perspective view of a diaphragm membrane in the third exemplary embodiment of the present invention.

FIG. 53 is a cross sectional view taken against the section line 53-53 from previous FIG. 52.

FIG. 54 is a bottom view of a diaphragm membrane in the third exemplary embodiment of the present invention.

FIG. 55 is a cross sectional view showing the assembly of a diaphragm membrane and a pump head body for the third exemplary embodiment of the present invention.

FIG. 56 is a perspective view of an adapted pump head body in the third exemplary embodiment of the present invention.

FIG. 57 is a cross sectional view taken against the section line 57-57 from previous FIG. 56.

FIG. 58 is a cross sectional view showing explosion of an adapted pump head body and diaphragm membrane in the third exemplary embodiment of the present invention.

FIG. 59 is a cross sectional view showing assembly of an adapted pump head body and diaphragm membrane in the third exemplary embodiment of the present invention.

FIG. 60 is a perspective view of a pump head body in the fourth exemplary embodiment of the present invention. FIG. 61 is a cross sectional view taken against the section line 61-61 from previous FIG. 60.

FIG. 62 is a top view of a pump head body in the fourth exemplary embodiment of the present invention.

FIG. 63 is a perspective view of a diaphragm membrane in the fourth exemplary embodiment of the present invention.

FIG. 64 is a cross sectional view taken against the section line 64-64 from previous FIG. 63. FIG. 65 is a bottom view of a diaphragm membrane in the fourth exemplary embodiment of the present invention.

FIG. 66 is a cross sectional view showing the assembly of a diaphragm membrane and a pump head body for the fourth exemplary embodiment of the present invention. FIG. 67 is a perspective view of a an adapted pump head body in the fourth exemplary embodiment of the present invention.

FIG. 68 is a cross sectional view taken against the section line 68-68 from previous FIG. 67.

FIG. 69 is a cross sectional view showing explosion of an adapted pump head body and diaphragm membrane in the fourth exemplary embodiment of the present invention.

FIG. 70 is a cross sectional view showing assembly of an adapted pump head body and diaphragm membrane in the fourth exemplary embodiment of the present invention.

FIG. 71 is a perspective view of a pump head body in the fifth exemplary embodiment of the present invention.

FIG. 72 is a cross sectional view taken against the section line 72-72 from previous FIG. 71.

FIG. 73 is a top view of a pump head body in the fifth exemplary embodiment of the present invention. FIG. 74 is a perspective view of a diaphragm membrane in the fifth exemplary embodiment of the present invention.

FIG. 75 is a cross sectional view taken against the section line 75-75 from previous FIG. 74.

FIG. 76 is a bottom view of a diaphragm membrane in the fifth exemplary embodiment of the present invention.

FIG. 77 is a cross sectional view showing the assembly of a diaphragm membrane and a pump head body for the fifth exemplary embodiment of the present invention.

FIG. 78 is a perspective view of an adapted pump head body in the fifth exemplary embodiment of the present invention.

FIG. 79 is a cross sectional view taken against the section line 79-79 from previous FIG. 78.

FIG. 80 is an exploded cross sectional view showing an adapted pump head body and diaphragm membrane in the fifth exemplary embodiment of the present invention.

FIG. 81 is a cross sectional view showing assembly of an adapted pump head body and diaphragm membrane in the fifth exemplary embodiment of the present invention.

FIG. 82 is a perspective view of a pump head body in the sixth exemplary embodiment of the present invention.

FIG. 83 is a cross sectional view taken against the section line 83-83 from previous FIG. 82.

FIG. 84 is a top view of a pump head body in the sixth exemplary embodiment of the present invention.

FIG. 85 is a perspective view of a diaphragm membrane in the sixth exemplary embodiment of the present invention. FIG. 86 is a cross sectional view taken against the section line 86-86 from previous FIG. 85.

FIG. 87 is a bottom view of a diaphragm membrane in the sixth exemplary embodiment of the present invention.

FIG. 88 is a cross sectional view showing the assembly of a diaphragm membrane and a pump head body for the sixth exemplary embodiment of the present invention.

FIG. 89 is a perspective view of a an adapted pump head body in the sixth exemplary embodiment of the present invention.

FIG. 90 is a cross sectional view taken against the section line of 90-90 from previous FIG. 89.

FIG. 91 is an exploded cross sectional view showing an adapted pump head body and diaphragm membrane in the sixth exemplary embodiment of the present invention.

FIG. 92 is a cross sectional view showing assembly of an adapted pump head body and diaphragm membrane in the sixth exemplary embodiment of the present invention.

FIG. 93 is a top view of a pump head body in the seventh exemplary embodiment of the present invention.

FIG. 94 is a bottom view of a diaphragm membrane in the seventh exemplary embodiment of the present invention.

FIG. 95 is a cross sectional view showing the assembly of a diaphragm membrane and a pump head body for the seventh exemplary embodiment of the present invention.

FIG. 96 is a perspective view of an adapted pump head body in the seventh exemplary embodiment of the present invention. FIG. 97 is a cross sectional view taken against the section line 97-97 from previous FIG. 96.

FIG. 98 is an exploded cross sectional view showing an adapted pump head body and diaphragm membrane in the seventh exemplary embodiment of the present invention. FIG. 99 is a cross sectional view showing assembly of an adapted pump head body and diaphragm membrane in the seventh exemplary embodiment of the present invention.

FIG. 100 is a perspective view of a pump head body in the eighth exemplary embodiment of the present invention.

FIG. 101 is a cross sectional view taken against the section line 101-101 from previous FIG. 100.

FIG. 102 is a cross sectional view showing the assembly of a diaphragm membrane and a pump head body for the eighth exemplary embodiment of the present invention.

FIG. 103 is an operation illustrative view for the eighth exemplary embodiment of the present invention.

FIG. 104 is a partially enlarged view taken from circled-portion-a of previous FIG.

103.

FIG. 105 is a cross sectional illustrative view showing a comparison between the cylindrical eccentric roundel acting on the diaphragm membrane for the conventional compressing diaphragm pump and for the present invention in the eighth exemplary embodiment of the present invention.

FIG. 106 is a perspective exploded view showing the cylindrical eccentric roundel for the eighth exemplary embodiment of the present invention.

FIG. 107 is a cross sectional view taken against the section line 107-107 from previous FIG. 106.

FIG. 108 is a perspective assembled view showing an adapted cylindrical eccentric roundel for the eighth exemplary embodiment of the present invention.

FIG. 109 is a cross sectional view taken against the section line 109-109 from previous FIG. 108.

FIG. 110 is a cross sectional view showing the adapted cylindrical eccentric roundel for the eighth exemplary embodiment of the present invention. FIG. Ill is an operation illustrative view showing the adapted cylindrical eccentric roundel for the eighth exemplary embodiment of the present invention.

FIG. 112 is a partially enlarged view taken from circled-portion-a of previous FIG.

111.

FIG. 113 is a cross operation illustrative view showing a comparison between the adapted cylindrical eccentric roundel acting on the diaphragm membrane for the conventional compressing diaphragm pump and for the present invention in the eighth exemplary embodiment of the present invention.

Detailed Description Of The Preferred Embodiments

FIGS. 19 through 28 are illustrative figures of a compressing diaphragm pump with multiple effects according to a first exemplary embodiment of the present invention.

A basic curved groove 65 is circumferentially disposed around the upper side of each operating hole 61 in the pump head body 60 while a basic curved protrusion 77 is circumferentially disposed around each concentric annular positioning protrusion 76 at the bottom side of the diaphragm membrane 70 at a position corresponding to the position of each mating basic curved groove 65 in the pump head body 60. Thereby, each basic curved protrusions 77 at the bottom side of the diaphragm membrane 70 is completely inserted into each corresponding basic curved groove 65 at the upper side of the pump head body 60 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in FIG. 28). As a result, a short length of moment arm L2 from the basic curved protrusions 77 to the periphery of the annular positioning protrusion 76 in the diaphragm membrane 70 is obtained in the operation of the present invention (as shown in the enlarged portion of FIG. 28).

Moreover, the cylindrical eccentric roundel 52 in the eccentric roundel mount 50 includes an annular top surface portion that is inclined relative to horizontal to form a sloped top ring 58 between the annular positioning groove 55 and a vertical flank 56, the sloped top ring 58 replacing the conventional rounded shoulder 57 in each tubular eccentric roundel 52 of the eccentric roundel mount 50 (as shown in FIGS. 26 and 27).

FIGS. 29, 30, 15 and 16 are illustrative figures for the operation of the compressing diaphragm pump with multiple effects of the first exemplary embodiment in the present invention. During operation of a conventional compressing diaphragm pump, a length of moment arm LI from the outer raised rim 71 to the periphery of the annular positioning protruding block 76 in the diaphragm membrane 70 is obtained, as shown in FIG. 15). In contrast, a shorter length of moment arm L2 from the basic curved protrusions 77 to the periphery of the annular positioning protruding block 76 in the diaphragm membrane 70 is obtained in the operation of the present invention, as shown in FIG. 30.

Because the resultant torque is calculated by same acting force F multiplying the length of moment arm, the resultant torque of the present invention is smaller than that of the conventional compressing diaphragm pump since the length of moment arm L2 is shorter than the length of moment arm LI. With the smaller resultant torque of the present invention, the vibration strength related resulting therefrom is substantially reduced.

In a practical test of a prototype of the present invention, the vibration strength was reduce to only one tenth (10 %) of the vibration strength in the conventional compressing diaphragm pump .

If the present invention is installed on the housing C of a reverse osmosis purification unit cushioned by a conventional cushion base 100 with a rubber shock absorber 102, as shown in FIG. 16, the unwanted noise caused by resonant shaking that is present in the conventional compressing diaphragm pump can be completely eliminated. FIGS. 31 through 33 are illustrative figures for the operation of the compressing diaphragm pump with multiple effects in the first exemplary embodiment of the present invention.

Firstly, when the motor 10 is powered on, the wobble plate 40 is driven to rotate by the motor output shaft 11 so that the three cylindrical eccentric roundels 52 on the eccentric roundel mount 50 constantly move in a sequential up-and-down reciprocal stroke.

Secondly, three piston acting zones 74 in the diaphragm membrane 70 are sequentially driven by the up-and-down reciprocal stroke of three cylindrical eccentric roundels 52 to move in up-and-down displacement.

Thirdly, when the conventional tubular eccentric roundel or cylindrical eccentric roundel 52 of the present invention moves in an up stroke with the piston acting zone 74 in up displacement, an acting force F will obliquely pull on the partial portion between the corresponding annular positioning protrusion 76 and outer raised rim 71 of the diaphragm membrane 70.

By comparing the operation of the conventional tubular eccentric roundels 52 shown in FIG. 18 and the cylindrical eccentric roundels 52 of the present invention, as illustrated in FIG. 32, at least the following two differences are evident: In the case of conventional tubular eccentric roundel 52 shown in FIG. 18, the maximum among all of the distributed components Fs of the rebounding force is the component force exerted at the contacting bottom position P of the diaphragm membrane 70, which is located at an edge of the rounded shoulder 57 on a horizontal top face 53 of tubular eccentric roundel 52, so that the "squeezing phenomenon" at point P is also maximum. With such nonlinear distribution of the "squeezing phenomena," the obliquely pulling action becomes severe. In contrast, in the case of cylindrical eccentric roundels 52 as illustrated in FIG. 32, the distribution of components of the rebounding force Fs is more linear because the sloped top ring 58 therein flatly attaches to the bottom area of the piston acting zone 74 for the diaphragm membrane 70, so that the oblique pulling action is almost eliminated due to reduction in the squeezing phenomenon.

Moreover, under the same acting force F, the rebounding force Fs is inversely proportional to the contact area so that the magnitudes of the distributed components of the rebounding force Fs for the cylindrical eccentric roundels 52 of the present invention, as shown in FIG. 32, are substantially less than the magnitudes of the distributed components of the rebounding force Fs for the conventional tubular eccentric roundel 52 shown in FIG. 18.

The improved distribution linearity and decreased magnitudes of the rebounding force components Fs result of forming the sloped top ring 58 between the annular positioning groove 55 and the vertical flank 56 in the eccentric roundel mount 50, and results in at least two advantages. First, this arrangement eliminates susceptibility to breakage of the diaphragm membrane 70 caused by the high frequency squeezing phenomena, that occurs in the conventional arrangement as a result of the rounded shoulder 57 in the otherwise horizontal top face 53 of the tubular eccentric roundel52. Second, the rebounding force Fs of the diaphragm membrane 70 caused by the acting force F, resulting from the sequential up-and-down displacement of the three piston acting zones 74 in the diaphragm membrane 70 driven by the up-and-down reciprocal stroke of the three tubular eccentric roundels or cylindrical eccentric roundels 52, is tremendously reduced.

These advantages result in the following practical benefits:

1. The durability of the diaphragm membrane 70 for sustaining the high frequency pumping action of the cylindrical eccentric roundels 52 is substantially enhanced.

2. The power consumption of the compressing diaphragm pump is tremendously diminished due to less current being wasted as a result of the squeezing phenomena at high frequencies.

3. The working temperature of the compressing diaphragm pump is tremendously reduced due to the decrease in power consumption. 4. The undesirable bearing noise caused by aging of the lubricant in the compressing diaphragm pump, which is normally accelerated by the high working temperature, is mostly eliminated.

Test results carried out on a prototype of the present invention are as follows. A. The service lifespan of the tested diaphragm membrane 70 is was more than doubled.

B. The reduction in electric current consumption exceeded 1 ampere.

C. The working temperature was reduced by over 15 degrees Celsius.

D. The smoothness of the bearing was improved. As shown in FIGS. 34 and 35, in a variation of the first exemplary embodiment, each basic curved groove 65 of the pump head body 60 can be adapted into a basic curved bore 64.

As shown in FIGS. 36 and 37, in the first exemplary embodiment, each basic curved groove 65 in the pump head body 60 (as shown in FIGS. 20 and 22) and each corresponding basic curved protrusion 77 in the diaphragm membrane 70 (as shown in FIGS. 24 and 25) can be exchanged into a basic curved protrusion 651 in the pump head body 60 (as shown in FIG. 36) and a corresponding basic curved groove 771 in the diaphragm membrane 70 (as shown in FIG. 36) without affecting their mating condition.

Each basic curved protrusion 651 at the upper side of the pump head body 60 is completely inserted into each corresponding basic curved groove 771 at the bottom side of the diaphragm membrane 70 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in FIG. 37) with the result that a short length of moment arm L3 from the basic curved groove 771 to the periphery of the annular positioning protrusion 76 in the diaphragm membrane 70 is also obtained in the operation of the present invention

(as shown in the enlarged portion of FIG. 37) so that the newly devised contrivances of pump head body 60 and diaphragm membrane 70 have a significant effect in reducing vibration as well.

Referring to FIGS. 38 through 44, which are illustrative figures of a compressing diaphragm pump with multiple effects for the second exemplary embodiment of the present invention, a second outer curved groove 66 is further circumferentially disposed around each basic curved groove 65 in the pump head body 60 (as shown in FIGS. 38 through 40) while a second outer curved protrusion 78 is further circumferentially disposed around each basic curved protrusion 77 in the diaphragm membrane 70 at a position corresponding to a position of each mating second outer curved groove 66 in the pump head body 60 (as shown in FIGS. 42 and 43).

Each pair of basic curved protrusions 77 and second outer curved protrusion 78 at the bottom side of the diaphragm membrane 70 is completely inserted into each pair of corresponding basic curved grooves 65 and second outer curved grooves 66 at the upper side of the pump head body 60 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in the enlarged portion of FIG. 44) resulting in relatively a short length of moment arm L2 from the basic curved protrusion 77 to the periphery of the annular positioning protrusion 76 in the diaphragm membrane 70 during operation of the present invention (as shown in the enlarged portion of FIG. 44).

The shortened length of moment arm L2 not only has a significant effect in reducing vibration but also enhances stability by preventing displacement and maintaining the length of moment arm L2 to resist the acting force F on the eccentric roundel 52.

As shown in FIGS. 45 and 46, in the second exemplary embodiment, each pair of basic curved grooves 65 and second outer curved grooves 66 of the pump head body 60 can be replaced by a pair of basic curved bores 64 and second outer curved bores 67. As shown in FIGS. 47 and 48, in the second exemplary embodiment, each pair of basic curved grooves 65 and second outer curved grooves 66 in the pump head body 60 (as shown in FIGS. 38 to 40) and each corresponding pair of basic curved protrusions 77 and second outer curved protrusions 78 in the diaphragm membrane 70 (as shown in FIGS. 42 and 43) can be exchanged with a pair of basic curved protrusions 651 and second outer curved protrusions 661 in the pump head body 60 (as shown in FIG. 47) and a pair of corresponding basic curved grooves 771 and second outer curved grooves 781 in the diaphragm membrane 70 (as shown in FIG. 47) without affecting their mating condition.

Each pair of basic curved protrusions 651 and second outer curved protrusions 661 at the upper side of the pump head body 60 is completely inserted into each corresponding pair of basic curved grooves 771 and second outer curved grooves 781 at the bottom side of the diaphragm membrane 70 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in FIG. 48) with the result that a short length of moment arm L3 from the basic curved groove 771 to the periphery of the annular positioning protrusion 76 in the diaphragm membrane 70 is also obtained during operation of the present invention (as shown in the enlarged portion of FIG. 48), thereby achieving significantly reduced vibration enhanced stability in preventing displacement and maintaining the length of moment arm L2.

Referring to FIGS. 49 through 55, which are illustrative figures of the compressing diaphragm pump with multiple effects of a third exemplary embodiment of the present invention a basic annular groove 601 is further circumferentially disposed around each operating hole 61 in the pump head body 60 (as shown in FIGS. 49 through 51) while a basic protruded ring 701 is further circumferentially disposed around each annular positioning protrusion 76 in the diaphragm membrane 70 at a position corresponding to a position of each mating basic annular groove 601 in the pump head body 60 (as shown in FIGS. 53 and 54).

Each basic protruded ring 701 at the bottom side of the diaphragm membrane 70 is completely inserted into each corresponding basic annular groove 601 at the upper side of the pump head body 60 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in FIG. 55), with the result that a short length of moment arm L2 from the basic protruded ring 701 to the periphery of the annular positioning protrusion 76 in the diaphragm membrane 70 is obtained during operation of the present invention (as shown in FIG. 55), thereby achieving significantly reduced vibration and enhanced stability in preventing displacement and maintaining the length of moment arm L2 for resisting the acting force F on the eccentric roundel 52.

As shown in FIGS. 56 and 57, in the third exemplary embodiment, each basic annular groove 601 of the pump head body 60 can be replaced by a basic perforated hole 600. As shown in FIGS. 58 and 59, in the third exemplary embodiment, each basic annular groove 601 in the pump head body 60 (as shown in FIGS. 49 to 51) and each corresponding basic protruding ring 701 in the diaphragm membrane 70 (as shown in FIGS. 53 and 54) can be exchanged with a basic protruding ring 610 in the pump head body 60 (as shown in FIG. 58) and a corresponding basic annular groove 710 in the diaphragm membrane 70 (as shown in FIG. 58) without affecting their mating condition.

Each basic protruding ring 610 at the upper side of the pump head body 60 is completely inserted into each corresponding basic annular groove 710 at the bottom side of the diaphragm membrane 70 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in FIG. 59) with the result that a short length of moment arm L3 from the basic annular groove 710 to the periphery of the annular positioning protrusion 76 in the diaphragm membrane 70 is also obtained during operation of the present invention (as shown in FIG. 59) so that the newly devised contrivances of pump head body 60 and diaphragm membrane 70 have a significant effect in reducing vibration.

Referring to FIGS. 60 through 66, which are illustrative figures of the compressing diaphragm pump with multiple effects of a fourth exemplary embodiment of the present invention, a pair of curved indented segments 602 is further circumferentially disposed around each said operating hole 61 in the pump head body 60 (as shown in FIGS. 60 through 62) while a pair of curved protruding segments 702 is further circumferentially disposed around each annular positioning protrusion 76 in the diaphragm membrane 70at a position corresponding to a position of each mating curved indented segment 602 in the pump head body 60 (as shown in FIGS. 64 and 65). Each pair of curved protruding segments 702 at the bottom side of the diaphragm membrane 70 is completely inserted into each corresponding pair of curved indented segments 602 at the upper side of the pump head body 60 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in FIG. 66), with the result that a short length of moment arm L2 from the curved protruding segment 702 to the periphery of the annular positioning protrusion 76 in the diaphragm membrane 70 is obtained during operation of the present invention (as shown in FIG. 66), thereby achieving significantly reduced vibration and enhanced stability in preventing displacement and maintaining the length of moment arm L2.

As shown in FIGS. 67 and 68, in the fourth exemplary embodiment, each pair of curved indented segments 602 of the pump head body 60 can be replaced by a pair of curved perforated segments 611.

As shown in FIGS. 69 and 70, in the fourth exemplary embodiment, each pair of curved indented segments 602 in the pump head body 60 (as shown in FIGS. 60 to 62) and each corresponding pair of curved protruding segments 702 in the diaphragm membrane 70 (as shown in FIGS. 64 and 65) can be exchanged with a pair of curved protruding segments 620 in the pump head body 60 (as shown in FIG. 69) and a pair of corresponding curved indented segments 720 in the diaphragm membrane 70 (as shown in FIG. 69) without affecting their mating condition.

Each pair of curved protruding segments 620 at the upper side of the pump head body 60 is completely inserted into each pair of corresponding curved indented segments 720 at the bottom side of the diaphragm membrane 70 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in FIG. 70), with the result that a short length of moment arm L3 from the curved indented segment 720 to the periphery of the annular positioning protrusion 76 in the diaphragm membrane 70 is also obtained during operation of the present invention (as shown in FIG. 70) so that the newly devised contrivances of pump head body 60 and diaphragm membrane 70 have a significant effect in reducing vibration.

Referring to FIGS. 71 through 77, which are illustrative figures of the compressing diaphragm pump with multiple effects of a fifth exemplary embodiment in the present invention, a group of round openings or holes 603 are further circumferentially disposed around each operating hole 61 in the pump head body 60 (as shown in FIGS. 71 through 73) while a group of round protrusions 703 are further circumferentially disposed around each of the annular positioning protrusions 76 in the diaphragm membrane 70 at a position corresponding to a position of each group of mating round openings or holes 603 in the pump head body 60 (as shown in FIGS. 75 and 76). Each group of round protrusions 703 at the bottom side of the diaphragm membrane 70 is completely inserted into each corresponding group of round openings or holes 603 at the upper side of the pump head body 60 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in FIG. 77), with the result that a short length of moment arm L2 from the round protrusion 703 to the periphery of the annular positioning protrusion 76 in the diaphragm membrane 70 is obtained in the operation of the present invention (as shown in FIG. 77), thereby achieving significantly reduced vibration and enhanced stability in preventing displacement and maintaining the length of moment arm L2.

As shown in FIGS. 69 and 70, in the fifth exemplary embodiment, each group of round openings or holes 603 in the pump head body 60 can be replaced by a group of round perforated holes 612.

As shown in FIGS. 80 and 81, in the fifth exemplary embodiment, each group of round openings or holes 603 in the pump head body 60 (as shown in FIGS. 71 to 73) and each corresponding group of round protrusions 703 in the diaphragm membrane 70 (as shown in FIGS. 75 and 76) can be exchanged for a group of round protrusions 630 in the pump head body 60 (as shown in FIG. 80) and a group of corresponding round openings or holes 730 in the diaphragm membrane 70 (as shown in FIG. 80) without affecting their mating condition.

Each group of round protrusions 630 at the upper side of the pump head body 60 is completely inserted into each group of corresponding round openings or holes 730 at the bottom side of the diaphragm membrane 70 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in FIG. 81), with the result that a short length of moment arm L3 from the round dents 730 to the periphery of the annular positioning protrusion 76 in the diaphragm membrane 70 is also obtained during operation of the present invention (as shown in FIG. 81) so that the newly devised contrivances of pump head body 60 and diaphragm membrane 70 have a significant effect in reducing vibration.

Referring to FIGS. 82 through 88, which are illustrative figures of the compressing diaphragm pump with multiple effects of a the sixth exemplary embodiment in the present invention.

A group of square openings or holes 604 are further circumferentially disposed around each operating hole 61 in the pump head body 60 (as shown in FIGS. 82 through 84) while a group of square protrusions 704 are further circumferentially disposed around each annular positioning protrusion 76 in the diaphragm membrane 70 at a position corresponding to a position of each mating group of square openings or holes 604 in the pump head body 60 (as shown in FIGS. 86 and 87).

Each group of square protrusions 704 at the bottom side of the diaphragm membrane 70 is completely inserted into each corresponding group of square openings or holes 604 at the upper side of the pump head body 60 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in FIG. 88), with the result that a short length of moment arm L2 from the square protrusions 704 to the periphery of the annular positioning protrusion 76 in the diaphragm membrane 70 is obtained during operation of the present invention (as shown in FIG. 88), thereby achieving significantly reduced vibration and enhanced stability in preventing displacement and maintaining the length of moment arm L2.

As shown in FIGS. 89 and 90, in the sixth exemplary embodiment, each group of square openings or holes 604 in the pump head body 60 can be replaced by a group of square perforated holes 613.

As shown in FIGS. 91 and 92 in the sixth exemplary embodiment, each group of square openings or holes 604 in the pump head body 60 (as shown in FIGS. 82 to 84) and each corresponding group of square protrusions 704 in the diaphragm membrane 70 (as shown in FIGS. 86 and 87) can be exchanged for a group of square protrusions 640 in the pump head body 60 (as shown in FIG. 91) and a group of corresponding square openings or holes 740 in the diaphragm membrane 70 (as shown in FIG. 91) without affecting their mating condition.

Each group of square protrusions 640 at the upper side of the pump head body 60 is completely inserted into each group of corresponding square openings or holes 740 at the bottom side of the diaphragm membrane 70 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in FIG. 92), with the result that a short length of moment arm L3 from the square dents 740 to the periphery of the annular positioning protrusion 76 in the diaphragm membrane 70 is also obtained in the operation of the present invention (as shown in FIG. 92 and enlarged view of association) so that the newly devised contrivances of pump head body 60 and diaphragm membrane 70 have a significant effect in reducing vibration. Referring to FIGS. 93 through 95, which are illustrative figures of the compressing diaphragm pump with multiple effects of a seventh exemplary embodiment of the present invention, a pair of concentric first inner annular grooves 605 and second outer annular grooves 606 are further circumferentially disposed around each operating hole 61 in the pump head body 60 (as shown in FIG. 93) while a pair of concentric first inner protruding rings 705 and second outer protruding rings 706 are further circumferentially disposed around each annular positioning protrusion 76 in the diaphragm membrane 70 at a position corresponding to a position of each mating pair of first inner annular grooves 605 and second outer annular grooves 606 in the pump head body 60 (as shown in FIG. 94).

Each pair of first inner protruding rings 705 and second outer protruding rings 706 at the bottom side of the diaphragm membrane 70 is completely inserted into each pair of corresponding first inner annular grooves 605 and second outer annular grooves 606 at the upper side of the pump head body 60 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in FIG. 95), with the result that a short length of moment arm L2 from the first inner protruding ring 705 to the periphery of the annular positioning protrusion 76 in the diaphragm membrane 70 is obtained during operation of the present invention (as shown in FIG. 95 and enlarged view of association),thereby achieving reduced vibration and enhanced stability in the length of moment arm L2 in resisting the acting force F on the eccentric roundel 52. As shown in FIGS. 96 and 97, in the seventh exemplary embodiment, each pair of concentric first inner annular grooves 605 and second outer annular grooves 606 in the pump head body 60 can be replaced by a pair of concentric first inner perforated rings 614 and second outer perforated rings 615. As shown in FIGS. 98 and 99, in the seventh exemplary embodiment, each pair of concentric first inner annular grooves 605 and second outer annular grooves 606 in the pump head body 60 (as shown in FIG. 83) and each corresponding pair of concentric first inner protruding rings 705 and second outer protruding rings 706 in the diaphragm membrane 70 (as shown in FIGS. 94) can be exchanged for a pair of concentric first inner protruding rings 650 and second outer protruding rings 660 in the pump head body 60 (as shown in FIG. 98) and a corresponding pair of concentric first inner annular grooves 750 and second outer annular grooves 760 in the diaphragm membrane 70 (as shown in FIG. 98) without affecting their mating condition.

Each pair of first inner protruding rings 650 and second outer protruding rings 660 at the upper side of the pump head body 60 is completely inserted into each corresponding pair of first inner annular grooves 750 and second outer annular grooves 760 at the bottom side of the diaphragm membrane 70 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in FIG. 99), with the result that a short length of moment arm L3 from the first inner annular grooves 750 to the periphery of respective annular positioning protrusions 76 in the diaphragm membrane 70 is also obtained during operation of the present invention (as shown in FIG. 99), thereby achieving significantly reduced vibration and enhanced stability in preventing displacement and maintaining the length of moment arm L2. Please refer to FIGS. 100 through 102, which are illustrative figures of the compressing diaphragm pump with multiple effects of a variation of the eighth exemplary embodiment of the present invention.

In this variation, the cylindrical eccentric roundel 52 is modified into an inverted frustoconical eccentric roundel 502 in an eccentric roundel mount 500.

The frustoconical eccentric roundel 502 includes an integral inverted frustoconical flank 506 and a sloped top ring 508 such that the outer diameter of the frustoconical eccentric roundel 502 is enlarged but still smaller than the inner diameter of the operating hole 61 in the pump head body 60, as well as the sloped top ring 508 extending between an annular positioning groove 505 and the inverted frustoconical flank 506.

FIGS. 103 through 105 are illustrative figures showing the modified operation of the "compressing diaphragm pump with multiple effects" in the eighth exemplary embodiment of the present invention.

Firstly, when the motor 10 is powered on, the wobble plate 40 is driven to rotate by the motor output shaft 11 so that the three frustoconical eccentric roundels 502 on the eccentric roundel mount 500 constantly move in a sequential up-and-down reciprocal stroke.

Secondly, the three piston acting zones 74 in the diaphragm membrane 70 are sequentially driven by the up-and-down reciprocal stroke of the three frustoconical eccentric roundels 502 to move in up-and-down displacement.

Thirdly, when the frustoconical eccentric roundel 502 in the present invention moves in an up stroke so that piston acting zone 74 is displaced upwardly, the acting force F will obliquely pull the partial portion between the corresponding annular positioning protrusion 76 and outer raised rim 71 of the diaphragm membrane 70.

Consequently, the inclusion of the sloped top ring 508 in the eccentric roundel mount 500 eliminates breakage of the diaphragm membrane 70 caused by the high frequency squeezing phenomena that would otherwise result from the rounded shoulder 57 in the conventional tubular eccentric roundel 502 (as indicated in FIG. 105 by a dotted line, and also causes the rebounding force Fs of the diaphragm membrane 70 caused by the acting force F to be tremendously reduced. Meanwhile, by means of the inverted frustoconical flank 506, the possibility of collision between the frustoconical eccentric roundel 502 and the operating hole 61 in the pump head body 60 is eliminated even though the outer diameter of the frustoconical eccentric roundel 502 is enlarged.

Moreover, under the same acting force F, the rebounding force Fs is inversely proportional to the contact area. By means of the enlarged outer diameter of the inverted frustoconical eccentric roundel 502, the contact area of the sloped top ring 508 with the bottom side of the diaphragm membrane 70 is increased (as indicated by ring A shown in FIG. 105) so that all distributed components of the rebounding force Fs for the inverted frustoconical eccentric roundels 502 of the present invention are further reduced.

The inverted frustoconical eccentric roundel 502 of this embodiment of the present invention therefore provides at least some of the following benefits: 1. The durability of the diaphragm membrane 70 for sustaining the high frequency pumping action is substantially increased as a result of the inverted frustoconical eccentric roundel 502.

2. The power consumption of the compressing diaphragm pump is tremendously diminished due to less current being wasted as a result of the high frequency squeezing phenomena.

3. The working temperature of the compressing diaphragm pump is tremendously reduced due to less power consumption. 4. The undesirable bearing noise resulting from aged lubricant in the compressing diaphragm pump, which is exacerbated by accelerated aging due to a high working temperature, is mostly eliminated.

5. The service lifespan of the compressing diaphragm pump is further prolonged because all distributed components of the rebounding force Fs for the inverted frustoconical eccentric roundels 502 of the present invention are reduced.

FIGS. 106 through 109 are illustrative figures showing an adaptation of the compressing diaphragm pump with multiple effects in the eighth exemplary embodiment of the present invention, in which the cylindrical eccentric roundel 52 is replaced by a combinational eccentric roundel 502 in an eccentric roundel mount 500. The combinational eccentric roundel 502 includes a roundel mount 511 and an inverted frustoconical roundel yoke 521 in detachable separation such that the outer diameter of the frustoconical roundel yoke 521 is enlarged but still smaller than the inner diameter of the operating hole 61 in the pump head body 60, wherein the roundel mount 511, which has two layers and a includes bottom-layer base with a crescent surface 512 facing inwardly and a top-layer protruding cylinder 513 with a central female-threaded bore 514. The inverted frustoconical roundel yoke 521 is sleeved over the corresponding roundel mount 511 and includes an upper bore 523, a middle bore 524 and a lower bore 525 stacked as a three -layered integral hollow frustoconical structure, as well as an inverted frustoconical flank 522 and a sloped top ring 526 extending from the upper bore 523 to the inverted frustoconical flank 522 such that the bore diameter of the upper bore 523 is bigger than the outer diameter of the protruding cylinder 513, such that the bore diameter of the middle bore 524 is approximately equal to the outer diameter of the protruding cylinder 513, such that the bore diameter of the lower bore 525 is approximately equal to the outer diameter of the bottom-layer base in the roundel mount 511, and such that the crescent engages a corresponding surface of the lower bore to prevent relative rotation of the roundel yoke

521 and the corresponding roundel mount 511. A positioning annular groove 515 is formed between the protruding cylinder 513 and the inside wall of the upper bore 523 when the frustoconical roundel yoke 521 is sleeved over the roundel mount 511 (as shown in FIGS. 108 and 109).

FIGS. 110 and 113 illustrate the manner in which the compressing diaphragm pump with multiple effects of the above-described adaptation of the eighth exemplary embodiment of the present invention is assembled. Firstly, the frustoconical roundel yoke 521 is fitted over the roundel mounts 511.

Secondly, all three annular positioning protrusions 76 of the diaphragm membrane 70 are inserted into three corresponding positioning annular grooves 515 in the three combinational eccentric roundels 502 of the eccentric roundel mount 500.

Finally, each fastening screw 1 is inserted through a corresponding tiered hole 81 of the pumping piston 80 and each corresponding acting zone hole 75 in the piston acting zones 74 of the diaphragm membrane 70, and then the fastening screw 1 is securely screwed into the three corresponding female-threaded bores 514 in the three roundel mounts 511 of the eccentric roundel mount 500 to firmly assembly the diaphragm membrane 70 and three pumping pistons 80 (as shown in FIG. 110).

FIGS. Ill and 113 illustrate the operation of the above-described adaptation of the compressing diaphragm pump with multiple effects of the eighth exemplary embodiment of the present invention. Firstly, when the motor 10 is powered on, the wobble plate 40 is driven to rotate by the motor output shaft 11 so that three combinational eccentric roundels 502 on the eccentric roundel mount 50 constantly move in a sequential up-and-down reciprocal stroke.

Secondly, the three piston acting zones 74 in the diaphragm membrane 70 are sequentially driven by the up-and-down reciprocal stroke of the three combinational eccentric roundels 502 to move in up-and-down displacement.

Thirdly, when the combinational eccentric roundel 502 in the present invention moves in an up stroke to displace the piston acting zone 74 upwardly, the acting force F will obliquely pull the partial portion between corresponding annular positioning protrusion 76 and outer raised rim 71 of the diaphragm membrane 70.

Consequently, the inclusion of the sloped top ring 526 in the inverted frustoconical roundel yoke 521 of the eccentric roundel mount 500 eliminates susceptibility to breakage of the diaphragm membrane 70 caused by the high frequency squeezing phenomena that would otherwise result from the rounded shoulder 57 in the conventional tubular eccentric roundel indicated in FIG. 113 by a dotted line, and also causes the rebounding force Fs of the diaphragm membrane 70 caused by the acting force F to be tremendously reduced (as shown in FIG. 112). Moreover, under the same acting force F, the rebounding force Fs is inversely proportional to the contact area. By means of the enlarged outer diameter of the inverted frustoconical roundel yoke 521, the contact area of the sloped top ring 508 with the bottom side of the diaphragm membrane 70 is increased (as indicated by ring A shown in FIG. 113) so that all distributed components of the rebounding force Fs for the inverted frustoconical roundel yoke 521 of the present invention are further reduced.

The fabrication of this adaptation of the compressing diaphragm pump with multiple effects of the eighth exemplary embodiment of the present invention is as follows: Firstly, the roundel mount 511 and eccentric roundel mount 500 are fabricated together as an integral body.

Secondly, the frustoconical roundel yoke 521 is independently fabricated as a separate entity.

Finally, the frustoconical roundel yoke 521 and the integral body of the roundel mount 511 are assembled with eccentric roundel mount 500 to become a united entity and form the assembled eccentric roundel 502 best shown in FIGS. 108 and 109.

Thereby, the contrivance of the combinational eccentric roundel 502 not only meets the requirement of mass production but also reduces the overall manufacturing cost.

The eccentric roundel 502 with frustoconical roundel yoke 521 of the present invention provides at least some of the following benefits:

1. The durability of the diaphragm membrane 70 for sustaining the high frequency pumping action is substantially increased by including the inverted frustoconical roundel yoke 521.

2. The power consumption of the compressing diaphragm pump is tremendously reduced due to less current being wasted as a result of the high frequency squeezing phenomena. 3. The working temperature of the compressing diaphragm pump is tremendously reduced due to the reduction in power consumption.

4. The undesired bearing noise resulting from temperature-accelerated aging of the lubricant in the compressing diaphragm pump is mostly eliminated.

5. The service lifespan of the compressing diaphragm pump is further prolonged because all distributed components of the rebounding force Fs for the inverted frustoconical roundel yoke 521 of the present invention are further reduced.

6. The manufacturing cost of the compressing diaphragm pump is reduced because the present invention is suitable for mass production.

As described above, the present invention substantially achieves a vibration reducing effect in the compressing diaphragm pump by means of a simple newly devised mating means for the pump head body and diaphragm membrane without increasing overall cost, so that it solves all issues of vibration-induced noise and resonant shaking that occurs in the conventional compressing diaphragm pump. Additionally, by means of simple sloped top ring for various cylindrical eccentric roundels of the present invention, the service lifespan of the diaphragm membrane in the compressing diaphragm pump can be doubled, which has valuable industrial applicability.

What Is Claimed Is: